JPH07286653A - Hydraulic type drive device - Google Patents
Hydraulic type drive deviceInfo
- Publication number
- JPH07286653A JPH07286653A JP7889094A JP7889094A JPH07286653A JP H07286653 A JPH07286653 A JP H07286653A JP 7889094 A JP7889094 A JP 7889094A JP 7889094 A JP7889094 A JP 7889094A JP H07286653 A JPH07286653 A JP H07286653A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- speed
- planetary
- input shaft
- hydraulic
- 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
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は微速運転・高速運転共に
円滑な運転が可能な油圧駆動装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic drive system capable of smooth operation in both slow speed operation and high speed operation.
【０００２】[0002]
【従来の技術】油圧ポンプの吐出量を可変にすること、
又はバルブスプ−ルをストロ−クさせモ−タへの流入量
を変化させる方法はしられている。しかし微速でスム−
ズに回転でき、且つ高速でも回転可能なモ−タが無いの
で、微速と高速を兼ねそなえる駆動装置はなかった。又
モ−タを２ケ使用して停止機能をそなえるものもしられ
ているが、２ケのモ−タそれぞれへの流量に微少な差を
つける微速運転をすることはこれ又困難であった。2. Description of the Related Art The discharge amount of a hydraulic pump is variable,
Alternatively, a method of changing the amount of inflow into the motor by stroking a valve spool is known. But at a slow speed
Since there is no motor that can rotate at a high speed and can rotate at a high speed as well, there has been no driving device capable of achieving both a slow speed and a high speed. It is also known that two motors are used to provide a stopping function, but it has been difficult to operate at a very low speed with a slight difference in the flow rate to each of the two motors.
【０００３】[0003]
【発明が解決しようとする課題】微速運転，高速運転共
にスム−ズに運転可能な油圧駆動装置を提供することを
目的とする。SUMMARY OF THE INVENTION It is an object of the present invention to provide a hydraulic drive system capable of operating smoothly in both slow speed operation and high speed operation.
【０００４】[0004]
【課題を解決するための手段】遊星減速機における内歯
歯車３の外側に設けた外歯歯車４にピニオン歯車５を噛
み合わせ、外歯歯車４を遊星入出力軸の中心回りに駆動
する油圧駆動手段を設けた。又このような油圧駆動装置
における遊星減速機部の減速比，平歯車減速機部の減速
比，モ−タ吸収量の差，ポンプ入力軸回転の差を調整
し、入力軸回転数／出力軸回転数の比率をより大きく取
りうるようにした。A hydraulic pressure that drives a pinion gear 5 to mesh with an external gear 4 provided outside an internal gear 3 in a planetary speed reducer to drive the external gear 4 around the center of a planet input / output shaft. Drive means were provided. Further, in such a hydraulic drive system, the speed reduction ratio of the planetary speed reducer unit, the speed reduction ratio of the spur gear speed reducer unit, the difference in motor absorption amount, and the difference in pump input shaft rotation are adjusted to adjust the input shaft speed / output shaft The ratio of the number of rotations can be made larger.
【０００５】[0005]
【実施例】図１，図２に本発明のギアトレインを示す。
１は太陽歯車、２は遊星歯車、３は内歯歯車でこれらに
より遊星減速機を形成している。内歯歯車３の外側には
外歯歯車４も形成されており、その外歯歯車４にはピニ
オン歯車５が噛み合っている。又遊星歯車２はキャリア
兼出力軸ｃに回動可能に固定されている。内歯歯車３は
ピニオン歯車５を回転させることで、入力軸ａ（又は出
力軸ｃ）の周りを自由に回転可能に支持されている。又
入力軸ａと入力軸ｂはそれぞれ油圧モ−タ１０Ａと１０
Ｂ（図３）にそれぞれ接続されている。1 and 2 show the gear train of the present invention.
1 is a sun gear, 2 is a planetary gear, 3 is an internal gear, and these form a planetary speed reducer. An external gear 4 is also formed outside the internal gear 3, and a pinion gear 5 meshes with the external gear 4. The planet gear 2 is rotatably fixed to the carrier / output shaft c. The internal gear 3 is rotatably supported around the input shaft a (or the output shaft c) by rotating the pinion gear 5. Further, the input shaft a and the input shaft b are respectively connected to the hydraulic motors 10A and 10A.
B (FIG. 3).
【０００６】図３は本発明の油圧回路で、１０は油圧モ
−タ、１１は方向切換弁、１２は圧力設定弁、１３は油
圧ポンプである。１４は油圧ポンプの吐出量可変機構、
１５は作動油タンク、１６は油圧ポンプを駆動する動力
源、１７は動力源の速度可変機構である。尚油圧モ−タ
１０、方向切換弁１１、圧力設定弁１２、油圧ポンプ１
３は入力軸ａ用と入力軸ｂ用で独立しており、それぞれ
ＡとＢ２ケ宛ある。ポンプ１３Ａと１３Ｂは機械的に結
合されており、常に同じ速度で回転する。FIG. 3 shows a hydraulic circuit of the present invention, in which 10 is a hydraulic motor, 11 is a direction switching valve, 12 is a pressure setting valve, and 13 is a hydraulic pump. 14 is a hydraulic pump discharge amount variable mechanism,
Reference numeral 15 is a hydraulic oil tank, 16 is a power source for driving a hydraulic pump, and 17 is a speed varying mechanism of the power source. Incidentally, the hydraulic motor 10, the direction switching valve 11, the pressure setting valve 12, the hydraulic pump 1
3 are independent for the input shaft a and the input shaft b, and are addressed to A and B, respectively. Pumps 13A and 13B are mechanically coupled and always rotate at the same speed.
【０００７】[0007]
【作動】入力軸ａと入力軸ｂ及び出力軸ｃの回転速度比
は表１の如くなる。ただしｉ1は太陽歯車の歯数、ｉ2は
内歯歯車の歯数、ｉ3は外歯歯車の歯数、ｉ4はピニオン
歯車の歯数である。[Operation] The rotation speed ratio of the input shaft a to the input shaft b and the output shaft c is as shown in Table 1. However, i 1 is the number of teeth of the sun gear, i 2 is the number of teeth of the internal gear, i 3 is the number of teeth of the external gear, and i 4 is the number of teeth of the pinion gear.
【表１】 [Table 1]
【０００８】従って、ｉ4・ｉ2＝ｉ3・ｉ1となる様に
すれば出力軸ｃは静止する。又、 ｉ4・ｉ2＝０.９ｉ3・ｉ1となる様にすれば出力軸回
転速度は数式１となり微速運転が可能となる。Therefore, if i 4 · i 2 = i 3 · i 1 , the output shaft c is stationary. Further, if i 4 · i 2 = 0.9i 3 · i 1 , the output shaft rotation speed is given by the formula 1 and fine speed operation becomes possible.
【数１】 この状態で入力軸ｂを静止させると、出力軸ｃの回転は
数式２、ｉ2／ｉ1は通常３〜５程度であるから、今ｉ2
／ｉ1を４とすると数式１は０.０２、数式２は０.２、
又入力軸を逆転させると出力軸は数式３となる。[Equation 1] When the stationary input shaft b in this state, since the rotation of the output shaft c Equation 2, i 2 / i 1 is usually about 3 to 5, now i 2
If / i 1 is 4, Formula 1 is 0.02, Formula 2 is 0.2,
Further, when the input shaft is reversed, the output shaft becomes the formula 3.
【数２】 [Equation 2]
【数３】 [Equation 3]
【０００９】これにより本減速機構により、０.３８／
０.０２＝１９.０倍の速度変化を出すことができる。こ
のことと動力減の速度制御とポンプの吐出量制御により
２０倍程度の速度変化が得られるので、合わせて１９.
０×２０＝３８０倍程度の速度領域が制御可能となる。
又ｉ4・ｉ2／ｉ3・ｉ1を変化させることにより微速域を
自由に設定することができる。又ｉ4・ｉ2＝ｉ3・ｉ1の
状態で入力軸ａと入力軸ｂの回転速度比を１：０.９９
としても同じ効果が得られる。As a result, the speed reduction mechanism provides 0.38 /
A speed change of 0.02 = 19.0 times can be produced. By this, speed control of power reduction and discharge amount control of pump, speed change of about 20 times can be obtained, so total 19.
It is possible to control a speed range of 0 × 20 = 380 times.
Also, by changing i 4 · i 2 / i 3 · i 1 , the fine speed range can be freely set. Further, in the state of i 4 · i 2 = i 3 · i 1 , the rotation speed ratio between the input shaft a and the input shaft b is 1: 0.99.
The same effect can be obtained as.
【００１０】入力軸ａと入力軸ｂの回転速度に微小な差
をつける手段としては油圧モ−タ１０Ａの吸収量ＱA cc
／rev と油圧モ−タ１０Ｂの吸収量ＱB cc／rev に微小
差をつける方法、或いは図４の如く動力源とポンプの間
にパワ−デバイダ−１８を配置してポンプ１３Ａとポン
プ１３Ｂの入力軸回転数に微小差をつける方法が考えら
れる。入力軸ａとｂの回転数をｎ1，ｎ2とした時、出力
軸回転数は数式４となり、これが目的の速度となる様、
ポンプ入力軸回転差，モ−タ吸収量差・歯数ｉ1〜ｉ4を
調整すればよい。As a means for making a minute difference in the rotational speeds of the input shaft a and the input shaft b, the absorption amount QAcc of the hydraulic motor 10A.
/ Rev and the absorption amount QBcc / rev of the hydraulic motor 10B are made to have a slight difference, or as shown in FIG. 4, a power divider 18 is arranged between the power source and the pump to input the pump 13A and the pump 13B. A method of making a minute difference in the number of shaft revolutions can be considered. When the number of rotations of the input shafts a and b is n 1 and n 2 , the number of rotations of the output shaft is given by Equation 4, so that the target speed is obtained.
The pump input shaft rotation difference, the motor absorption amount difference, and the number of teeth i 1 to i 4 may be adjusted.
【数４】 [Equation 4]
【００１１】[0011]
【効果】例えばウインチでは従来２ｍ／min 程度の最低
速度しか得られず連続壁掘削機等で求められる０.１ｍ
／min 程度の用途には対応できなかったものが、本発明
により対応可能となった。[Effect] For example, a winch can only obtain a minimum speed of about 2 m / min, which is 0.1 m required for continuous wall excavators.
The present invention has made it possible to cope with applications that could not be dealt with in the order of / min.
【図面の簡単な説明】[Brief description of drawings]
【図１】本発明に適用するギヤトレ−ンの平面図。FIG. 1 is a plan view of a gear train applied to the present invention.
【図２】本発明に適用するギヤトレ−ンの断面図。FIG. 2 is a sectional view of a gear train applied to the present invention.
【図３】油圧回路図。FIG. 3 is a hydraulic circuit diagram.
【図４】動力源とポンプ間にパワ−デバイダを配置して
２つのポンプ入力軸回転数に微小差をつける構成を示
す。FIG. 4 shows a configuration in which a power divider is arranged between a power source and a pump to make a minute difference between the two pump input shaft rotational speeds.
ａ 入力軸 ｂ 入力軸 ｃ 出力軸 １ 太陽歯車 ２ 遊星歯車 ３ 内歯歯車 ４ 外歯歯車 ５ ピニオン歯車 10,10A,10B 油圧モ−タ 11 方向切換弁 12 圧力設定弁 13,13A,13B 油圧ポ
ンプ 14 吐出量可変機構 15 作動油タンク 16 動力源 17 速度可変機構 18 パワ−デバイダ−a Input shaft b Input shaft c Output shaft 1 Sun gear 2 Planetary gear 3 Internal gear 4 External gear 5 Pinion gear 10,10A, 10B Hydraulic motor 11 Directional switching valve 12 Pressure setting valve 13,13A, 13B Hydraulic pump 14 Discharge amount variable mechanism 15 Hydraulic oil tank 16 Power source 17 Speed variable mechanism 18 Power divider
Claims (2)
車(１)と内歯歯車(３)との間に設けた遊星歯車(２)とか
らなる遊星減速機における内歯歯車(３)の外側に外歯歯
車(４)を設け、該外歯歯車(４)にピニオン歯車(５)を噛
み合わせ、前記ピニオン歯車(５)により前記外歯歯車
(４)を遊星入出力軸(ａとｃ)の中心回りに駆動する油圧
駆動手段を設けたことを特徴とする油圧式駆動装置。1. A planetary speed reducer comprising a sun gear (1), an internal gear (3), and a planetary gear (2) provided between the sun gear (1) and the internal gear (3). An external gear (4) is provided outside the tooth gear (3), a pinion gear (5) is meshed with the external gear (4), and the external gear is rotated by the pinion gear (5).
A hydraulic drive device comprising a hydraulic drive means for driving (4) around the center of the planet input / output shafts (a and c).
の減速比，油圧モ−タ吸収量の差，油圧ポンプ入力軸回
転の差を調整し、入力軸回転数／出力軸回転数の比率を
大きく取りうるようにした請求項１の油圧式駆動装置。2. The input shaft speed / output shaft speed is adjusted by adjusting the speed reduction ratio of the planetary speed reducer unit, the speed ratio of the spur gear speed reducer unit, the difference in the amount of absorbed hydraulic motor, and the difference in the input shaft rotation of the hydraulic pump. The hydraulic drive system according to claim 1, wherein a large number ratio can be set.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7889094A JPH07286653A (en) | 1994-04-18 | 1994-04-18 | Hydraulic type drive device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7889094A JPH07286653A (en) | 1994-04-18 | 1994-04-18 | Hydraulic type drive device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07286653A true JPH07286653A (en) | 1995-10-31 |
Family
ID=13674415
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7889094A Pending JPH07286653A (en) | 1994-04-18 | 1994-04-18 | Hydraulic type drive device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07286653A (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60157559A (en) * | 1983-10-07 | 1985-08-17 | ヴイリ−・シヨイエルレ・フア−ルツオイクフアブリ−ク・ゲ−・エム・ベ−・ハ−・ウント・コンパニ− | Device for driving large mass in adjustable manner |
-
1994
- 1994-04-18 JP JP7889094A patent/JPH07286653A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60157559A (en) * | 1983-10-07 | 1985-08-17 | ヴイリ−・シヨイエルレ・フア−ルツオイクフアブリ−ク・ゲ−・エム・ベ−・ハ−・ウント・コンパニ− | Device for driving large mass in adjustable manner |
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