JPH0134772Y2 - - Google Patents
Info
- Publication number
- JPH0134772Y2 JPH0134772Y2 JP3565684U JP3565684U JPH0134772Y2 JP H0134772 Y2 JPH0134772 Y2 JP H0134772Y2 JP 3565684 U JP3565684 U JP 3565684U JP 3565684 U JP3565684 U JP 3565684U JP H0134772 Y2 JPH0134772 Y2 JP H0134772Y2
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- gear
- carrier
- cylindrical internal
- clutch
- 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
Links
- 230000005540 biological transmission Effects 0.000 claims description 19
- 230000007246 mechanism Effects 0.000 claims description 18
- 230000033001 locomotion Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000470 constituent Substances 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
Description
【考案の詳細な説明】
［考案の技術分野］
この考案は遊星歯車式変速機の改良に係り、特
に、二重に遊星歯車機構を利用し、前・後進切換
クラツチのトルクを小とし、小形軽量化を図つた
遊星歯車式変速機に関する。[Detailed description of the invention] [Technical field of the invention] This invention relates to the improvement of a planetary gear type transmission.In particular, it utilizes a double planetary gear mechanism, reduces the torque of the forward/reverse switching clutch, and is compact. This invention relates to a planetary gear type transmission that is lightweight.
［従来技術］
原動機からの回転動力を、逆転を含めて変速す
る機構として、やや高価ではあるが、使用容易性
等の特徴を有する遊星歯車機構が採用される場合
がある。[Prior Art] A planetary gear mechanism, which is somewhat expensive but has features such as ease of use, is sometimes employed as a mechanism for changing the speed of rotational power from a prime mover, including reverse rotation.
第１図は、遊星歯車機構を二重にタンデム一体
的に利用した公知の変速機を示す。入力軸１は第
１太陽歯車２及び第２太陽歯車３と一体的に固着
され、第１太陽歯車２と第１遊星歯車機構の複数
の第１遊星歯車４と、第２太陽歯車３は第２遊星
歯車機構の複数の第２遊星歯車５とそれぞれかみ
合つている。第１キヤリヤ１１は第１遊星歯車４
を軸支しており、その第１キヤリヤ１１は非回転
部との間に後進クラツチ６が設けられており、図
示しない操縦機構によつて接離自在に構成されて
いる。第１遊星歯車４にかみ合う第１円筒内歯車
７は第２遊星歯車５を軸支する第２キヤリヤ１２
と一体的に構成されている。出力軸８はこの第２
キヤリヤ１２に連結固着されている。第２遊星歯
車にかみ合つている第２円筒内歯車９には非回転
部との間に前進クラツチ１０が設けられており、
図示しない操縦装置によつて接離自在に構成され
ている。 FIG. 1 shows a known transmission that utilizes a double planetary gear mechanism in tandem. The input shaft 1 is integrally fixed with a first sun gear 2 and a second sun gear 3, and the first sun gear 2 and a plurality of first planetary gears 4 of the first planetary gear mechanism, and the second sun gear 3 are connected to the first sun gear 2 and the second sun gear 3. The second planetary gears 5 of the second planetary gear mechanism mesh with each other. The first carrier 11 is the first planetary gear 4
A reverse clutch 6 is provided between the first carrier 11 and the non-rotating part, and the first carrier 11 is configured to be able to move toward and away from the vehicle by a control mechanism (not shown). The first cylindrical internal gear 7 that meshes with the first planetary gear 4 is connected to the second carrier 12 that pivotally supports the second planetary gear 5.
It is integrally constructed with. The output shaft 8 is this second
It is connected and fixed to the carrier 12. A forward clutch 10 is provided between the second cylindrical internal gear 9 meshing with the second planetary gear and the non-rotating part,
It is configured to be able to approach and separate freely using a control device (not shown).
次に作用を説明する。後進クラツチ６を自由と
し、前進クラツチ１０を拘束とすれば、入力軸１
から入つた動力は、太陽歯車３から第２遊星歯車
５に伝達され、第２円筒内歯車９は前進クラツチ
１０によつて固定されているので、第２遊星歯車
の公転が第２キヤリヤ１２に伝達され、この第２
キヤリヤ１２の回転が出力軸８に伝達され、正方
向回転で出力される。 Next, the effect will be explained. If the reverse clutch 6 is free and the forward clutch 10 is constrained, the input shaft 1
The power input from the sun gear 3 is transmitted to the second planetary gear 5, and since the second cylindrical internal gear 9 is fixed by the forward clutch 10, the revolution of the second planetary gear is transmitted to the second carrier 12. This second
The rotation of the carrier 12 is transmitted to the output shaft 8, and the rotation in the forward direction is output.
前進クラツチ１０を自由とし、後進クラツチ６
を拘束とすれば、第１キヤリヤ１１は固定される
ので、入力軸１からの動力は、第１太陽歯車２か
ら第１遊星歯車４の自転を介して第１円筒内歯車
７に伝達され、一体構成である第２キヤリヤ１２
を経て出力軸８に入力軸１逆方向回転で出力され
る。 The forward clutch 10 is free and the reverse clutch 6 is released.
If , the first carrier 11 is fixed, so the power from the input shaft 1 is transmitted from the first sun gear 2 to the first cylindrical internal gear 7 through the rotation of the first planetary gear 4, The second carrier 12 is an integrated structure.
The signal is output to the output shaft 8 by rotating the input shaft 1 in the opposite direction.
［従来技術の問題点］
以上述べた第１図に示す公知の遊星歯車式変速
機について減速比を調べると、
ρF＝第２太陽歯車３の歯数（28枚）／第２円筒内歯
車９の歯数（80枚）
ρR＝第１太陽歯車２の歯数（24枚）／第１円筒内歯
車７の歯数（78枚）
とすると、
前進時減速比iF＝１＋ρF／ρF＝3.857、
後進時減速比iR＝−１／ρR＝−3.25
となる。[Problems with the prior art] When examining the reduction ratio of the known planetary gear type transmission shown in FIG . 9 teeth (80 teeth) ρ R = Number of teeth of the first sun gear 2 (24 teeth) / Number of teeth of the first internal cylindrical gear 7 (78 teeth), Forward reduction ratio i F = 1 + ρ F / ρ F = 3.857, and the reduction ratio during reverse movement i R = -1/ρ R = -3.25.
また、クラツチを拘束するときに必要なトルク
は、入力軸１のトルクをTiとすれば、
前進クラツチ１０のトルクは、
TF＝１／ρF・Ti＝2.857・Ti、
後進クラツチ６のトルクは、
TR＝（１＋１／ρR）・Ti＝4.25・Ti、
となり、いずれも比較的大きな拘束トルクを必要
とする。したがつて、クラツチの摩擦板の数を増
したり、大きな寸法としなければならず、この変
速機の全体構成が大形となる。 Also, the torque required to lock the clutch is: If the torque of input shaft 1 is Ti, the torque of forward clutch 10 is T F = 1/ρ F・Ti=2.857・Ti, and the torque of reverse clutch 6 is: T R = (1+1/ρ R )・Ti=4.25・Ti, Both of which require a relatively large restraint torque. Therefore, the number of friction plates in the clutch must be increased and the size of the clutch must be increased, resulting in an increase in the overall size of the transmission.
［考案の目的］
そこで、この考案の目的は、この遊星歯車式変
速機の減速比を１に近づけ、クラツチを拘束する
ための摩擦板の受け持つトルクを小さくすること
により、全体として小形軽量化を図つた遊星歯車
式変速機を実現しようとするものである。[Purpose of the invention] Therefore, the purpose of this invention is to reduce the overall size and weight of the planetary gear transmission by bringing the reduction ratio close to 1 and reducing the torque handled by the friction plate for restraining the clutch. This is an attempt to realize a planetary gear type transmission.
［考案の構成］
この目的を達成するために、この考案は、遊星
歯車式変速機において、入力軸は第１遊星歯車と
歯合する第１円筒内歯車に連結され、前記第１遊
星歯車を軸支する第１キヤリヤは第２遊星歯車と
歯合する第２円筒内歯車と一体に形成され、前記
第２遊星歯車を軸支する第２キヤリヤには非回転
部との間に後進クラツチ機構が設けられ、前記第
１遊星歯車に歯合する第１太陽歯車及び前記第２
遊星歯車に歯合する第２太陽歯車は前記第１円筒
内歯車との間に前進クラツチ機構を有する共通軸
に固着され、該共通軸を出力軸と一体に構成した
ことを特徴とする。[Structure of the invention] In order to achieve this object, the invention provides a planetary gear type transmission in which the input shaft is connected to a first cylindrical internal gear that meshes with the first planetary gear, and the first planetary gear The first carrier that pivotally supports the second planetary gear is integrally formed with a second cylindrical internal gear that meshes with the second planetary gear, and the second carrier that pivotally supports the second planetary gear has a reverse clutch mechanism between it and a non-rotating part. are provided, a first sun gear meshing with the first planetary gear, and a second sun gear.
The second sun gear meshing with the planetary gear is fixed to a common shaft having a forward clutch mechanism between it and the first cylindrical internal gear, and the common shaft is integrally formed with the output shaft.
［考案の実施例］
以下この考案を図示の実施例について詳述す
る。第２図はこの考案の一実施例を示す。この遊
星歯車式変速機は２組の遊星歯車機構を串形に組
合せた構成となつている。[Embodiments of the invention] This invention will be described in detail below with reference to illustrated embodiments. FIG. 2 shows an embodiment of this invention. This planetary gear type transmission has a configuration in which two sets of planetary gear mechanisms are combined in a skewer shape.
入力軸２１には図示しない原動機からの駆動力
が伝達され入力される。出力軸２８には、車両等
の場合、図示しない２速以上の複数の変速機構が
接続されるのが通常である。 Driving force from a prime mover (not shown) is transmitted and input to the input shaft 21 . In the case of a vehicle or the like, the output shaft 28 is normally connected to a plurality of transmission mechanisms (not shown) having two or more speeds.
入力軸２１は第１円筒内歯車２７の形成体に回
転力を伝達するよう同心に固着やスプライン等の
手段によつて連結されている。第１円筒内歯車２
７は第１遊星歯車２４とかみ合つている。また、
第１円筒内歯車２７と太陽歯車の共通軸３３との
間には前進クラツチ３０が設けられている。共通
軸３３には第１太陽歯車２２と第２太陽歯車２３
が同心串形に固着されている。第１遊星歯車２４
は第１太陽歯車２２と第１円筒内歯車２７とにか
み合い、第１キヤリヤ３１に軸支されている。第
１キヤリヤ３１は第２円筒内歯車２９と一体的に
形成されている。第２遊星歯車２５は第２太陽歯
車２３と第２円筒内歯車２９とにかみ合い、第２
キヤリヤ３２に軸支されている。第２キヤリヤ３
２は非回転部との間に後進クラツチ機構２６が設
けられている。出力軸２８は共通軸３３の回転力
を伝達するように連結されている。 The input shaft 21 is concentrically connected to the forming body of the first cylindrical internal gear 27 by means such as fixation or spline so as to transmit rotational force. First cylindrical internal gear 2
7 meshes with the first planetary gear 24. Also,
A forward clutch 30 is provided between the first cylindrical internal gear 27 and the common shaft 33 of the sun gear. The common shaft 33 has a first sun gear 22 and a second sun gear 23.
are fixed in a concentric skewer shape. First planetary gear 24
meshes with the first sun gear 22 and the first cylindrical internal gear 27, and is pivotally supported by the first carrier 31. The first carrier 31 is integrally formed with the second cylindrical internal gear 29. The second planetary gear 25 meshes with the second sun gear 23 and the second cylindrical internal gear 29.
It is pivotally supported by a carrier 32. 2nd carrier 3
2 is provided with a reverse clutch mechanism 26 between it and the non-rotating part. The output shaft 28 is connected to transmit the rotational force of the common shaft 33.
なお、クラツチ３０及び２６は図示しない操縦
装置によつて接又は離とされる。 Note that the clutches 30 and 26 are brought into contact or released by a control device (not shown).
次に、第２図に示すこの実施例による遊星歯車
式変速機の作用について説明する。 Next, the operation of the planetary gear type transmission according to this embodiment shown in FIG. 2 will be explained.
前進時は前進クラツチ３０を接とし、後進クラ
ツチ２６を断とする。すると、入力軸２１からの
動力は、第１円筒内歯車２７から前進クラツチ３
０を介して、共通軸３３に伝達され、出力軸２８
から同一回転で出力される。その他の構成部材は
相対回転はなく一体的に回転する。 When moving forward, the forward clutch 30 is engaged and the reverse clutch 26 is disengaged. Then, the power from the input shaft 21 is transferred from the first cylindrical internal gear 27 to the forward clutch 3.
0 to the common shaft 33 and the output shaft 28
output at the same rotation. The other constituent members do not rotate relative to each other but rotate integrally.
したがつて、減速比は１となる。 Therefore, the reduction ratio is 1.
入力軸２１からのトルクをそのまま前進クラツ
チ３０が負担するので、前進クラツチ３０の負担
トルクTFは入力軸トルクTiと同一であり、従来
例の2.857・Tiよりかなり小さくなる。 Since the forward clutch 30 directly bears the torque from the input shaft 21, the burden torque T F of the forward clutch 30 is the same as the input shaft torque Ti, which is considerably smaller than 2.857·Ti of the conventional example.
次に、後進時は後進クラツチ２６を接とし、前
進クラツチ３０は離とする。すると、入力軸２１
からの動力は第１円筒内歯車２７から第１遊星歯
車２４、第１キヤリヤ３１、第２円筒内歯車２９
に伝達され、後進クラツチ２６、第２キヤリヤ３
２によつて公転を拘束された第２遊星歯車２５を
自転させ、第２太陽歯車２３にその回転を伝達
し、出力軸２８が逆回転で出力される。 Next, when moving backward, the reverse clutch 26 is engaged and the forward clutch 30 is released. Then, the input shaft 21
The power is transmitted from the first cylindrical internal gear 27 to the first planetary gear 24, the first carrier 31, and the second cylindrical internal gear 29.
is transmitted to the reverse clutch 26 and the second carrier 3.
The second planetary gear 25 whose revolution is restrained by the second sun gear 23 is rotated, and the rotation is transmitted to the second sun gear 23, and the output shaft 28 is outputted in reverse rotation.
なお、第１遊星歯車２４は第１太陽歯車２２と
かみ合つており、１段目の遊星歯車機構と２段目
の遊星歯車機構との間でトルク循環をして、バラ
ンスしている。 Note that the first planetary gear 24 meshes with the first sun gear 22, and torque is circulated between the first-stage planetary gear mechanism and the second-stage planetary gear mechanism for balance.
このときの減速比iRは、
ρ1＝第１太陽歯車２２の歯数（34枚）／第１円筒内
歯車２７の歯数（80枚）
ρ2＝第２太陽歯車２３の歯数（34枚）／第２円筒内
歯車２９の歯数（80枚）
とすれば、
iR＝−｛ρ1＋ρ2・（１＋ρ1）｝
＝−１・03
となる。 The reduction ratio i R at this time is: ρ 1 = Number of teeth of the first sun gear 22 (34 teeth) / Number of teeth of the first internal cylindrical gear 27 (80 teeth) ρ 2 = Number of teeth of the second sun gear 23 ( 34 teeth)/number of teeth of the second cylindrical internal gear 29 (80 teeth), then i R =-{ρ 1 +ρ 2 ·(1+ρ 1 )} = −1·03.
後進クラツチ２６が負担するトルクは
TR＝｛（１＋ρ1）・（１＋ρ2）｝・Ti
＝2.03・Ti
となり、従来例の4.25・Tiよりかなり小さくな
る。 The torque borne by the reverse clutch 26 is T R ={(1+ρ 1 )·(1+ρ 2 )}·Ti = 2.03·Ti, which is considerably smaller than 4.25·Ti in the conventional example.
さらに、従来例の太陽歯車２，３は入力軸１と
同一のトルクTiを伝達していたが、この実施例
による第２太陽歯車２３の負担するトルクTsは、
Ts＝ρ1・Ti＝0.43・Ti
となり、従来例よりかなり小さくなる。 Furthermore, although the sun gears 2 and 3 in the conventional example transmit the same torque Ti as the input shaft 1, the torque Ts borne by the second sun gear 23 in this example is Ts=ρ 1・Ti=0.43・Ti, which is much smaller than the conventional example.
以上の説明において、便宜上、入力回転と出力
回転が同一方向となる場合を前進とし、逆回転と
なる場合を後進としたが、これは呼称だけの問題
であり、実物に対する適用においては、何れを前
進としても何れを後進としてもよい。 In the above explanation, for convenience, the case where the input rotation and the output rotation are in the same direction is referred to as forward movement, and the case where they rotate in the opposite direction is referred to as backward movement.However, this is only a matter of name, and when applied to the actual object, it is referred to as forward movement. Either may be used for forward movement or for backward movement.
また、出力軸と入力軸を逆にして適用しても、
この実施例では、大差なく利用できる。 Also, even if the output shaft and input shaft are reversed,
This embodiment can be used without much difference.
なお、操縦装置からクラツチ３０への操縦系統
は機械式の他、船舶の可変ピツチプロペラに用い
られているような油圧式、スリツプリングを用い
る電気式等を利用することができる。 The control system from the control device to the clutch 30 can be of a mechanical type, a hydraulic type as used in variable pitch propellers of ships, an electric type using a slip ring, or the like.
［考案の効果］
以上詳細に説明したように、この考案によれ
ば、
(イ) 減速比を前後進共ほぼ１とすることができ
る。[Effects of the invention] As explained above in detail, according to this invention, (a) the reduction ratio can be set to approximately 1 in both forward and forward motion.
(ロ) 各クラツチ部の摩擦板が受け持つトルクを遊
星歯車機構内でトルク分割することにより小さ
くすることができる。(b) The torque handled by the friction plates of each clutch can be reduced by dividing the torque within the planetary gear mechanism.
(ハ) 太陽歯車の伝達トルクが遊星歯車機構により
トルク分割するため小さくなる。(c) The transmission torque of the sun gear becomes smaller because the torque is divided by the planetary gear mechanism.
このように、各種の伝達力を小とすることがで
きるので、構成部材を小とすることができ、全体
として小形軽量化された遊星歯車式変速機を実現
することができる。 In this way, since various transmission forces can be reduced, the number of structural members can be reduced, and a planetary gear type transmission that is smaller and lighter as a whole can be realized.
原動機の改善と高性能化が進み、これを搭載す
る車両等に対する要求性能の高度化にともない、
高速低トルク、軽量小形化されたこの考案による
変速機はきわめて有用であろう。 As prime movers continue to improve and become more sophisticated, and as the performance requirements for vehicles equipped with them become more sophisticated,
The transmission of this invention, which is high-speed, low-torque, lightweight, and compact, will be extremely useful.
第１図は遊星歯車式変速機の従来例の機構図、
第２図はこの考案による遊星歯車式変速機の実施
例の機構図である。
図において、２１は入力軸、２２は第１太陽歯
車、２３は第２太陽歯車、２４は第１遊星歯車、
２５は第２遊星歯車、２６は後進クラツチ、２７
は第１円筒内歯車、２８は出力軸、２９は第２円
筒内歯車、３０は前進クラツチ、３１は第１キヤ
リヤ、３２は第２キヤリヤ、３３は共通軸であ
る。
Figure 1 is a mechanical diagram of a conventional planetary gear transmission.
FIG. 2 is a mechanical diagram of an embodiment of the planetary gear type transmission according to this invention. In the figure, 21 is an input shaft, 22 is a first sun gear, 23 is a second sun gear, 24 is a first planetary gear,
25 is the second planetary gear, 26 is the reverse clutch, 27
28 is a first cylindrical internal gear, 28 is an output shaft, 29 is a second cylindrical internal gear, 30 is a forward clutch, 31 is a first carrier, 32 is a second carrier, and 33 is a common shaft.
Claims (1)
歯車と歯合する第１円筒内歯車に連結され、前記
第１遊星歯車を軸支する第１キヤリヤは第２遊星
歯車と歯合する第２円筒内歯車と一体に形成さ
れ、前記第２遊星歯車を軸支する第２キヤリヤに
は非回転部との間に後進クラツチ機構が設けら
れ、前記第１遊星歯車に歯合する第１太陽歯車及
び前記第２遊星歯車に歯合する第２太陽歯車は前
記第１円筒内歯車との間に前進クラツチ機構を有
する共通軸に固着され、該共通軸を出力軸と一体
に構成したことを特徴とする遊星歯車式変速機。 In a planetary gear type transmission, an input shaft is connected to a first cylindrical internal gear that meshes with a first planetary gear, and a first carrier that pivotally supports the first planetary gear is connected to a second cylindrical gear that meshes with a second planetary gear. A second carrier that is formed integrally with the cylindrical internal gear and pivotally supports the second planetary gear is provided with a reverse clutch mechanism between it and a non-rotating part, and a first sun gear that meshes with the first planetary gear. and a second sun gear that meshes with the second planetary gear is fixed to a common shaft having a forward clutch mechanism between it and the first cylindrical internal gear, and the common shaft is configured integrally with the output shaft. Planetary gear type transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3565684U JPS60147843U (en) | 1984-03-13 | 1984-03-13 | planetary gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3565684U JPS60147843U (en) | 1984-03-13 | 1984-03-13 | planetary gear transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60147843U JPS60147843U (en) | 1985-10-01 |
| JPH0134772Y2 true JPH0134772Y2 (en) | 1989-10-23 |
Family
ID=30540135
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3565684U Granted JPS60147843U (en) | 1984-03-13 | 1984-03-13 | planetary gear transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60147843U (en) |
-
1984
- 1984-03-13 JP JP3565684U patent/JPS60147843U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60147843U (en) | 1985-10-01 |
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