JP2911743B2 - Swash plate angle changing structure of variable displacement hydraulic motor - Google Patents
Swash plate angle changing structure of variable displacement hydraulic motorInfo
- Publication number
- JP2911743B2 JP2911743B2 JP3173794A JP3173794A JP2911743B2 JP 2911743 B2 JP2911743 B2 JP 2911743B2 JP 3173794 A JP3173794 A JP 3173794A JP 3173794 A JP3173794 A JP 3173794A JP 2911743 B2 JP2911743 B2 JP 2911743B2
- Authority
- JP
- Japan
- Prior art keywords
- swash plate
- speed
- posture
- cylinder block
- low
- 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 - Lifetime
Links
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- Hydraulic Motors (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、クローラ型走行装置の
駆動用等に利用される可変容量型油圧モータにおいて、
斜板の角度を変更し高低２段に変速操作する構造に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement hydraulic motor used for driving a crawler type traveling device.
The present invention relates to a structure in which the angle of a swash plate is changed and a shift operation is performed in two steps of height.
【０００２】[0002]
【従来の技術】前述のような可変容量型油圧モータの一
例を、図８に示している。この可変容量型油圧モータで
は、本体ケース１に形成した駆動室Ｄの回転軸芯Ｘ周り
にシリンダブロック７を回転自在に支持し、複数個のプ
ランジャ６をシリンダブロック７の回転軸芯Ｘと平行に
シリンダブロック７に備えている。各プランジャ６の先
端部を受け止める斜板９を、シリンダブロック７の回転
軸芯Ｘと直交する方向で回転軸芯Ｘ上に位置する支持軸
芯Ｙ周りに揺動自在に支持し、斜板９を支持軸芯Ｙ周り
に低速姿勢と高速姿勢とに亘って揺動操作する油圧シリ
ンダ１８，１９を備えている。2. Description of the Related Art FIG. 8 shows an example of a variable displacement hydraulic motor as described above. In this variable displacement hydraulic motor, a cylinder block 7 is rotatably supported around a rotation axis X of a drive chamber D formed in a main body case 1, and a plurality of plungers 6 are parallel to the rotation axis X of the cylinder block 7. Is provided in the cylinder block 7. A swash plate 9 for receiving the tip end of each plunger 6 is swingably supported around a support axis Y located on the rotation axis X in a direction orthogonal to the rotation axis X of the cylinder block 7. The hydraulic cylinders 18 and 19 are configured to swing around the support shaft center Y between a low-speed posture and a high-speed posture.
【０００３】これによって、シリンダブロック７の各プ
ランジャ６に作動油が順番に供給され、各プランジャ６
が斜板９を押すことに対する反力の円周方向の分力によ
り、シリンダブロック７が回転軸芯Ｘ周りに回転駆動さ
れる。そして、油圧シリンダ１８，１９により、斜板９
の角度を支持軸芯Ｙ周りに低速姿勢（Ｌ１の姿勢参
照）、及び高速姿勢（Ｈ１の姿勢参照）に変更操作する
ことにより、前述の円周方向の分力を大小に変更操作し
て、シリンダブロック７の回転速度を高低２段に変速操
作する。この場合に図８に示す可変容量型油圧モータで
は、斜板９の支持軸芯Ｙをシリンダブロック７の回転軸
芯Ｘ上に設定している。[0003] As a result, hydraulic oil is supplied to each plunger 6 of the cylinder block 7 in order, and each plunger 6
The cylinder block 7 is driven to rotate about the rotation axis X by the circumferential component of the reaction force to the pressing of the swash plate 9. Then, the swash plate 9 is moved by the hydraulic cylinders 18 and 19.
Is changed around the support axis Y into a low-speed posture (see the posture of L1) and a high-speed posture (see the posture of H1), thereby changing the above-described component force in the circumferential direction to large and small, The rotational speed of the cylinder block 7 is shifted between high and low. In this case, in the variable displacement hydraulic motor shown in FIG. 8, the support axis Y of the swash plate 9 is set on the rotation axis X of the cylinder block 7.
【０００４】[0004]
【発明が解決しようとする課題】図８に示すような可変
容量型油圧モータでは各プランジャ６が斜板９を押すこ
とに対する反力により、前述のようなシリンダブロック
７の回転駆動用の円周方向の分力が発生すると同時に、
各プランジャ６が接当する斜板９の面を直角に押す分力
も発生する。この場合、斜板９の低速姿勢における前述
の斜板９の面を直角に押す分力の合力は、斜板９の低速
姿勢における各プランジャ６の先端部を通る仮想平面Ｌ
１と直交するもので、シリンダブロック７の回転軸芯Ｘ
を通る低速仮想線Ｌ２上に位置していると考えられる。
そして、斜板９の高速姿勢における前述の斜板９の面を
直角に押す分力の合力は、斜板９の高速姿勢における各
プランジャ６の先端部を通る仮想平面Ｈ１と直交するも
ので、シリンダブロック７の回転軸芯Ｘを通る高速仮想
線Ｈ２上に位置していると考えられる。In the variable displacement type hydraulic motor as shown in FIG. 8, a reaction force against each plunger 6 pressing the swash plate 9 causes the rotation of the cylinder block 7 as described above. At the same time as the component force in
A component force is also generated that presses the surface of the swash plate 9 with which each plunger 6 contacts at right angles. In this case, when the swash plate 9 is in the low-speed posture, the resultant force of the component force for pressing the surface of the swash plate 9 at a right angle is the virtual plane L passing through the tip of each plunger 6 in the low-speed posture of the swash plate 9.
1 and perpendicular to the axis of rotation X of the cylinder block 7
Is located on the low-speed imaginary line L2 passing through.
Then, the resultant force of the component force for pressing the surface of the swash plate 9 at a right angle in the high-speed posture of the swash plate 9 is orthogonal to the virtual plane H1 passing through the distal end of each plunger 6 in the high-speed posture of the swash plate 9, It is considered that it is located on the high-speed virtual line H2 passing through the rotation axis X of the cylinder block 7.
【０００５】従って、図８に示す可変容量型油圧モータ
において、油圧シリンダ１８，１９により斜板９の角度
を、低速姿勢（Ｌ１の姿勢参照）から高速姿勢（Ｈ１の
姿勢参照）に変更操作する場合には、前述の斜板９の面
を直角に押す分力の合力が、斜板９の角度の変更操作方
向と同じ向きのモーメントになるので、斜板９の角度の
変更操作が楽に行える。しかしながら、油圧シリンダ１
８，１９により斜板９の角度を逆に高速姿勢（Ｈ１の姿
勢参照）から低速姿勢（Ｌ１の姿勢参照）に変更操作す
る場合には、前述の斜板９の面を直角に押す分力の合力
のモーメントに抗して、斜板９の角度を変更操作しなけ
ればならないので、斜板９の角度の変更操作に大きな力
が必要になる。本発明は可変容量型油圧モータの斜板角
変更構造において、斜板の角度の変更操作による高低２
段の変速操作が、前述のような力の不釣り合いなく行え
るように構成することを目的としている。Accordingly, in the variable displacement hydraulic motor shown in FIG. 8, the angle of the swash plate 9 is changed from the low-speed posture (see the posture of L1) to the high-speed posture (see the posture of H1) by the hydraulic cylinders 18 and 19. In this case, the resultant force of the component force for pressing the surface of the swash plate 9 at a right angle becomes a moment in the same direction as the direction of the operation for changing the angle of the swash plate 9, so that the operation of changing the angle of the swash plate 9 can be performed easily. . However, the hydraulic cylinder 1
When changing the angle of the swash plate 9 from the high-speed posture (see the posture of H1) to the low-speed posture (see the posture of L1) in reverse by the steps 8 and 19, the component force for pressing the surface of the swash plate 9 at a right angle is used. Since the angle of the swash plate 9 must be changed to oppose the moment of the resultant force, a large force is required to change the angle of the swash plate 9. The present invention relates to a swash plate angle changing structure for a variable displacement hydraulic motor.
It is an object of the present invention to provide a configuration in which a gear change operation of a gear can be performed without disproportionate force as described above.
【０００６】[0006]
【課題を解決するための手段】本発明の特徴は、以上の
ような可変容量型油圧モータの斜板角変更構造におい
て、次のように構成することにある。つまり、本体ケー
スに形成した駆動室にシリンダブロックを回転自在に支
持し、複数個のプランジャをシリンダブロックの回転軸
芯と平行にシリンダブロックに備えて、各プランジャの
先端部を受け止める斜板を、シリンダブロックの回転軸
芯と直交する方向の支持軸芯周りに揺動自在に駆動室の
内奥部に配置し、斜板を支持軸芯周りに低速姿勢と高速
姿勢とに亘って揺動操作する油圧シリンダを備えると共
に、斜板の低速姿勢における各プランジャの先端部を通
る仮想平面と直交するものでシリンダブロックの回転軸
芯を通る低速仮想線、並びに、斜板の高速姿勢における
各プランジャの先端部を通る仮想平面と直交するもので
シリンダブロックの回転軸芯を通る高速仮想線を想定し
て、低速仮想線と高速仮想線との間に斜板の支持軸芯を
位置させてある。A feature of the present invention is that the swash plate angle changing structure of the above-described variable displacement hydraulic motor is configured as follows. That is, a swash plate that rotatably supports a cylinder block in a drive chamber formed in a main body case, includes a plurality of plungers in the cylinder block in parallel with the rotation axis of the cylinder block, and receives a tip of each plunger, The swash plate is swingably arranged around the support shaft center in the low-speed posture and high-speed posture around the support shaft center in the direction perpendicular to the rotation axis of the cylinder block. A low-speed imaginary line passing through the axis of rotation of the cylinder block at right angles to a virtual plane passing through the tip of each plunger in the low-speed posture of the swash plate, and Assuming a high-speed imaginary line that is perpendicular to the imaginary plane passing through the tip and passes through the rotation axis of the cylinder block, the support axis of the swash plate is placed between the low-speed imaginary line and the high-speed imaginary line. It is allowed to location.
【０００７】[0007]
〔Ｉ〕図８に示す構成の場合と同様に本発明の構成でも
例えば図７に示すように、斜板９の低速姿勢における各
プランジャ６が接当する斜板９の面を直角に押す分力の
合力は、斜板９の低速姿勢における各プランジャ６の先
端部を通る仮想平面Ｌ１と直交するもので、シリンダブ
ロック７の回転軸芯Ｘを通る低速仮想線Ｌ２上に位置し
ていると考えられる。そして、斜板９の高速姿勢におけ
る各プランジャ６が接当する斜板９の面を直角に押す分
力の合力は、斜板９の高速姿勢における各プランジャ６
の先端部を通る仮想平面Ｈ１と直交するもので、シリン
ダブロック７の回転軸芯Ｘを通る高速仮想線Ｈ２上に位
置していると考えられる。[I] In the configuration of the present invention, as in the configuration shown in FIG. 8, for example, as shown in FIG. 7, the plunger 6 in the low-speed posture of the swash plate 9 presses the surface of the swash plate 9 at a right angle. The resultant force is orthogonal to the virtual plane L1 passing through the tip of each plunger 6 in the low-speed posture of the swash plate 9, and is located on the low-speed virtual line L2 passing through the rotation axis X of the cylinder block 7. Conceivable. Then, the resultant force of the component force of pressing the surface of the swash plate 9 with which the plungers 6 come into contact with the swash plate 9 in the high-speed posture at right angles is the force of each plunger 6 in the high-speed posture of the swash plate 9.
Is orthogonal to the virtual plane H1 passing through the tip of the cylinder block 7, and is considered to be located on the high-speed virtual line H2 passing through the rotation axis X of the cylinder block 7.
【０００８】これにより例えば図７のような本発明のよ
うに、斜板９の支持軸芯Ｙを前述の低速仮想線Ｌ２と高
速仮想線Ｈ２の間に配置すると、斜板９を低速姿勢及び
高速姿勢のどちらに操作していても、各プランジャ６が
接当する斜板９の面を直角に押す分力の合力は、斜板９
の支持軸芯Ｙの近傍を通ることになる。従って、油圧シ
リンダ１８，１９により斜板９の角度を低速姿勢（Ｌ１
の姿勢参照）から高速姿勢（Ｈ１の姿勢参照）に変更操
作する場合（又は高速姿勢から低速姿勢に変更操作する
場合）、前述の斜板９の面を直角に押す分力の合力のモ
ーメントが斜板９の角度の変更操作に対して逆向きに作
用することになっても、そのモーメントは小さなものと
なる。これにより、斜板９の角度の低速姿勢から高速姿
勢への変更操作、及び高速姿勢から低速姿勢への変更操
作の両変更操作において、前述の斜板９の面を直角に押
す分力の合力のモーメントが小さなものとなり、前述の
両変更操作に力の不釣合いは生じない。When the support axis Y of the swash plate 9 is arranged between the low-speed imaginary line L2 and the high-speed imaginary line H2, for example, as in the present invention as shown in FIG. Regardless of which of the high-speed postures is operated, the resultant force of the component force that pushes the surface of the swash plate 9 with which each plunger 6 contacts at right angles is the swash plate 9
In the vicinity of the support shaft center Y. Accordingly, the angle of the swash plate 9 is reduced by the hydraulic cylinders 18 and 19 to the low-speed posture (L1).
When changing from the high-speed posture (see the posture of H1) to the high-speed posture (or when changing from the high-speed posture to the low-speed posture), the resultant moment of the component force that pushes the surface of the swash plate 9 at a right angle is obtained. Even when the swash plate 9 changes its angle in the opposite direction, the moment becomes small. As a result, in both of the operation of changing the angle of the swash plate 9 from the low-speed posture to the high-speed posture and the operation of changing the angle of the swash plate 9 from the high-speed posture to the low-speed posture, the resultant force of the component force for pressing the surface of the swash plate 9 at a right angle. Is small, and no force imbalance occurs between the two changing operations.
【０００９】〔ＩＩ〕又、仮に斜板９の低速姿勢におけ
る各プランジャ６が接当する斜板９の面を直角に押す分
力の合力が、前述の低速仮想線Ｌ２上に正確に位置し、
斜板９の高速姿勢における各プランジャ６が接当する斜
板９の面を直角に押す分力の合力が、前述の高速仮想線
Ｈ２上に正確に位置していたとする。[II] Also, if the swash plate 9 is in the low-speed posture, the resultant force of the component force of pressing the surface of the swash plate 9 with which the plungers 6 contact at right angles is accurately located on the low-speed virtual line L2. ,
It is assumed that the resultant force of the component force of pressing the surface of the swash plate 9 at which the plungers 6 come into contact with the swash plate 9 in the high-speed posture at right angles is accurately positioned on the high-speed virtual line H2.
【００１０】このような場合には例えば図７に示すよう
に、油圧シリンダ１８，１９により斜板９の角度を低速
姿勢（Ｌ１の姿勢参照）から、高速姿勢（Ｈ１の姿勢参
照）に変更操作する場合（又は高速姿勢から低速姿勢に
変更操作する場合）、前述の斜板９の面を直角に押す分
力の合力のモーメントが、斜板９の角度の変更操作と同
じ向きに作用することになるので、斜板９の角度の変更
操作が小さな力で行える。In such a case, for example, as shown in FIG. 7, the angle of the swash plate 9 is changed from the low-speed posture (see the posture of L1) to the high-speed posture (see the posture of H1) by the hydraulic cylinders 18 and 19. (Or when the operation is changed from the high-speed posture to the low-speed posture), the moment of the resultant force of the component force for pushing the surface of the swash plate 9 at a right angle acts in the same direction as the operation for changing the angle of the swash plate 9. Therefore, the operation of changing the angle of the swash plate 9 can be performed with a small force.
【００１１】[0011]
【発明の効果】以上のように可変容量型油圧モータの斜
板角変更構造において、斜板の角度の低速姿勢から高速
姿勢への変更操作、及び高速姿勢から低速姿勢への変更
操作の両変更操作が力の不釣り合いなく行えるようにな
り、斜板の角度の変更操作による高低２段の変速操作の
操作性を向上させることができた。又、斜板の面を直角
に押す分力の合力のモーメントが斜板の角度の変更操作
と同じ向きに作用することになれば、斜板の角度の変更
操作が小さな力で行えるようになり、斜板の角度の変更
操作による高低２段の変速操作の操作性をさらに向上さ
せることができる。As described above, in the swash plate angle changing structure of the variable displacement hydraulic motor, both the operation of changing the angle of the swash plate from the low speed posture to the high speed posture and the operation of changing the angle of the swash plate from the high speed posture to the low speed posture are performed. The operation can be performed without disproportionate force, and the operability of the high-low two-step shift operation by changing the angle of the swash plate can be improved. Also, if the resultant moment of the component force that presses the swash plate surface at a right angle acts in the same direction as the swash plate angle changing operation, the swash plate angle changing operation can be performed with a small force. In addition, the operability of a two-step high-low gear change operation by changing the angle of the swash plate can be further improved.
【００１２】[0012]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。本発明の可変容量型油圧モータＭを、バックホウ
等の建設機械におけるクローラ走行装置の駆動等として
使用した場合を図６及び図１に示している。可変容量型
油圧モータＭの本体ケース１が、フランジ１ａを介して
機体側のトラックフレーム２に連結されており、トラッ
クフレーム２側に向けて駆動室Ｄを本体ケース１に開口
して、駆動室Ｄの開口部が直列に連結される２個の油圧
ブロック３，４によって閉じられている。Embodiments of the present invention will be described below with reference to the drawings. FIGS. 6 and 1 show a case where the variable displacement hydraulic motor M of the present invention is used for driving a crawler traveling device in a construction machine such as a backhoe. A main body case 1 of the variable displacement hydraulic motor M is connected to a track frame 2 on the machine body via a flange 1a, and a drive chamber D is opened in the main body case 1 toward the track frame 2 side. The opening of D is closed by two hydraulic blocks 3, 4 connected in series.
【００１３】図１に示すように駆動室Ｄの中心に回転軸
５が水平に支持されて、シリンダブロック７が回転軸５
に固定されており、回転軸５の回転軸芯Ｘと平行にスラ
イド自在な複数個のアキシャル型のプランジャ６が、シ
リンダブロック７の円周方向に沿って備えられている。
各プランジャ６の先端部の回動ヘッド６ａをスラストプ
レート８を介して受け止める斜板９が、駆動室Ｄ内に配
置されている。As shown in FIG. 1, the rotary shaft 5 is horizontally supported at the center of the drive chamber D, and the cylinder block 7 is
And a plurality of axial plungers 6 slidable in parallel with the rotation axis X of the rotation shaft 5 along the circumferential direction of the cylinder block 7.
A swash plate 9 for receiving the rotating head 6a at the tip of each plunger 6 via a thrust plate 8 is arranged in the drive chamber D.
【００１４】図１及び図６に示すように、回転ケース１
０がベアリング１１を介して回転自在に本体ケース１に
外嵌され、クローラベルト１２に係合する駆動スプロケ
ット１３が回転ケース１０に連結されている。回転軸５
に同芯状に連結された出力軸１４が回転ケース１０内に
配置されており、出力軸１４と回転ケース１０とが遊星
ギヤ式の減速機構１５を介して連動連結されている。As shown in FIG. 1 and FIG.
Numeral 0 is rotatably fitted to the main body case 1 via the bearing 11, and a driving sprocket 13 that engages with the crawler belt 12 is connected to the rotating case 10. Rotary axis 5
An output shaft 14 concentrically connected to the output shaft 14 is disposed in the rotating case 10, and the output shaft 14 and the rotating case 10 are interlocked and connected via a planetary gear type reduction mechanism 15.
【００１５】図３，４，１に示すように、斜板９の外周
部に一対のトラニオン軸１６が固定され、トラニオン軸
１６を回転自在に支持する一対の支持ブロック１７が、
駆動室Ｄの内奥底面に着脱自在にボルト固定されてお
り、斜板９がトラニオン軸１６の支持軸芯Ｙ周りに、図
１に示す低速姿勢及び図２に示す高速姿勢に揺動操作自
在に支持されている。この場合に図７に示すように、図
１に示す斜板９の低速姿勢における各プランジャ６の先
端部を通る仮想平面Ｌ１と直交するもので、シリンダブ
ロック７の回転軸芯Ｘを通る低速仮想線Ｌ２、並びに、
図２に示す斜板９の高速姿勢における各プランジャ６の
先端部を通る仮想平面Ｈ１と直交するもので、シリンダ
ブロック７の回転軸芯Ｘを通る高速仮想線Ｈ２を想定し
ている。そして、図７に示すように低速仮想線Ｌ２と高
速仮想線Ｈ２との間に、斜板９のトラニオン軸１６の支
持軸芯Ｙを位置させている。As shown in FIGS. 3, 4, and 1, a pair of trunnion shafts 16 are fixed to the outer peripheral portion of the swash plate 9, and a pair of support blocks 17 for rotatably supporting the trunnion shaft 16 are provided.
The swash plate 9 is swingably movable around the support axis Y of the trunnion shaft 16 into a low-speed posture shown in FIG. 1 and a high-speed posture shown in FIG. It is supported by. In this case, as shown in FIG. 7, the swash plate 9 is orthogonal to the virtual plane L1 passing through the tip of each plunger 6 in the low-speed posture shown in FIG. Line L2, and
A high-speed virtual line H2 passing through the rotation axis X of the cylinder block 7 is assumed to be orthogonal to the virtual plane H1 passing through the tip of each plunger 6 in the high-speed posture of the swash plate 9 shown in FIG. Then, as shown in FIG. 7, the support axis Y of the trunnion shaft 16 of the swash plate 9 is located between the low-speed virtual line L2 and the high-speed virtual line H2.
【００１６】図１及び図３に示すように、トラニオン軸
１６の支持軸心Ｙに対して紙面上下の本体ケース１の部
分に、一対の油圧シリンダ１８，１９及び油圧シリンダ
１８，１９への油路ｍ，ｈが設けられている。油圧シリ
ンダ１８にのみ圧油が供給されてプランジャ１８ａが進
出すると、図１のように斜板９の角度が大に設定されて
低速状態が設定され、逆に、油圧シリンダ１９にのみ圧
油が供給されてプランジャ１９ａが進出すると、図２に
ように斜板９の角度が小に設定されて高速状態が設定さ
れるように構成している。斜板９の背面には、駆動室Ｄ
の内奥底面との接当によって斜板５の角度を設定する比
較的小面積の座面ｓが***形成されている。As shown in FIGS. 1 and 3, a pair of hydraulic cylinders 18, 19 and oil to the hydraulic cylinders 18, 19 are provided on a portion of the main body case 1 above and below the paper with respect to the support axis Y of the trunnion shaft 16. Roads m and h are provided. When the pressure oil is supplied only to the hydraulic cylinder 18 and the plunger 18a advances, the angle of the swash plate 9 is set to a large value and the low-speed state is set as shown in FIG. When the plunger 19a is supplied and advances, the angle of the swash plate 9 is set to a small angle as shown in FIG. 2 to set a high-speed state. On the back of the swash plate 9, a driving room D
A relatively small area of the bearing surface s for setting the angle of the swash plate 5 by contact with the inner bottom surface is raised.
【００１７】次に、可変容量型油圧モータＭの駆動用の
油圧回路について説明する。図５に示すように、切換レ
バー（図示せず）によって切換操作される走行用制御弁
２０が備えられており、走行用制御弁２０を切換操作し
ポートＰ１又はポートＰ２に作動油を供給して、可変容
量型油圧モータＭを正転駆動又は逆転駆動する。正転用
油路ｆ及び逆転用油路ｒに接続される高圧選択用のシャ
トル弁２１が備えられており、正転用又は逆転用の作動
油を油圧シリンダ１８，１９に供給する。Next, a hydraulic circuit for driving the variable displacement hydraulic motor M will be described. As shown in FIG. 5, a traveling control valve 20 that is switched by a switching lever (not shown) is provided, and the traveling control valve 20 is switched to supply hydraulic oil to the port P1 or the port P2. Then, the variable displacement hydraulic motor M is driven forward or reverse. A shuttle valve 21 for selecting high pressure is connected to the oil passage f for forward rotation and the oil passage r for reverse rotation, and supplies hydraulic oil for forward rotation or reverse rotation to the hydraulic cylinders 18 and 19.
【００１８】シャトル弁２１と油圧シリンダ１８，１９
の間にパイロット操作式の流路切換弁２２を設けてお
り、パイロット圧が供給されない状態では、シャトル弁
２１からの作動油を油圧シリンダ１８への油路ｍに供給
して、油圧シリンダ１９への油路ｈをドレン油路ｄに連
通させる。逆にパイロット圧が供給されると、シャトル
弁２１からの作動油を油圧シリンダ１９への油路ｈに供
給し、油圧シリンダ１８への油路ｍをドレン油路ｄに連
通させるように構成している。油圧ブロック３にシャト
ル弁２１、流路切換弁２２及びカウンターバランス弁２
３が組み込まれており、油圧ブロック４にショックレス
機構２４が組み込まれている。Shuttle valve 21 and hydraulic cylinders 18, 19
, A pilot-operated flow path switching valve 22 is provided, and in a state where the pilot pressure is not supplied, the hydraulic oil from the shuttle valve 21 is supplied to an oil path m to the hydraulic cylinder 18 and is supplied to the hydraulic cylinder 19. Is connected to the drain oil passage d. Conversely, when the pilot pressure is supplied, the hydraulic oil from the shuttle valve 21 is supplied to the oil passage h to the hydraulic cylinder 19, and the oil passage m to the hydraulic cylinder 18 is connected to the drain oil passage d. ing. Shuttle valve 21, flow path switching valve 22, and counterbalance valve 2 in hydraulic block 3
3 is incorporated, and a shockless mechanism 24 is incorporated in the hydraulic block 4.
【００１９】以上の構造により、通常の状態では流路切
換弁２２にパイロット圧は供給されない状態となって、
低速用の油圧シリンダ１８にのみ作動油が供給されて、
図１に示すように油圧シリンダ１８により斜板９が低速
姿勢に保持される。そして、操作ペダル２６を踏み操作
しパイロット弁２５を切換操作して、パイロット圧を流
路切換弁２２に供給すると、流路切換弁２２が切換操作
され高速用の油圧シリンダ１９にのみ作動油が供給され
て、図１から図２に示すように油圧シリンダ１９により
斜板９が支持軸芯Ｙ周りに高速姿勢に揺動操作される。
逆に操作ペダル２６から足を離すと、前述のようにして
低速用の油圧シリンダ１８にのみ作動油が供給されて、
図２から図１に示すように油圧シリンダ１８により斜板
９が支持軸芯Ｙ周りに低速姿勢に揺動操作される。With the above structure, the pilot pressure is not supplied to the flow path switching valve 22 in a normal state.
Hydraulic oil is supplied only to the hydraulic cylinder 18 for low speed,
As shown in FIG. 1, the swash plate 9 is held in a low-speed posture by the hydraulic cylinder 18. When the pilot pressure is supplied to the flow path switching valve 22 by depressing the operation pedal 26 and switching the pilot valve 25, the flow path switching valve 22 is switched and hydraulic oil is supplied only to the high-speed hydraulic cylinder 19. The swash plate 9 is supplied with the hydraulic cylinder 19 to swing around the support axis Y in a high-speed attitude as shown in FIGS.
Conversely, when the foot is released from the operation pedal 26, the hydraulic oil is supplied only to the low-speed hydraulic cylinder 18 as described above,
As shown in FIGS. 2 to 1, the swash plate 9 is swung by the hydraulic cylinder 18 around the support axis Y in a low-speed posture.
【００２０】尚、特許請求の範囲の項に図面との対照を
便利にするために符号を記すが、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。In the claims, reference numerals are provided for convenience of comparison with the drawings, but the present invention is not limited to the configuration shown in the attached drawings.
【図１】低速状態での可変容量型油圧モータの縦断側面
図FIG. 1 is a longitudinal sectional side view of a variable displacement hydraulic motor in a low-speed state.
【図２】高速状態での可変容量型油圧モータの縦断側面
図FIG. 2 is a longitudinal sectional side view of a variable displacement hydraulic motor in a high-speed state.
【図３】図１の駆動室内を紙面左側から見た縦断正面図FIG. 3 is a longitudinal sectional front view of the driving room in FIG. 1 as viewed from the left side of the drawing.
【図４】斜板のトラニオン軸の支持部分を示す縦断側面
図FIG. 4 is a longitudinal sectional side view showing a support portion of a swash plate for supporting a trunnion shaft.
【図５】可変容量型油圧モータの油圧回路図FIG. 5 is a hydraulic circuit diagram of a variable displacement hydraulic motor.
【図６】可変容量型油圧モータをクローラ走行装置に取
り付けた状態での側面図FIG. 6 is a side view showing a state in which a variable displacement hydraulic motor is attached to a crawler traveling device.
【図７】斜板の支持軸芯の位置を示す概略側面図FIG. 7 is a schematic side view showing a position of a support shaft center of a swash plate.
【図８】従来の構造における斜板の支持軸芯の位置を示
す概略側面図FIG. 8 is a schematic side view showing a position of a support shaft center of a swash plate in a conventional structure.
１ 本体ケース ６ プランジャ ７ シリンダブロック ９ 斜板 １８，１９ 油圧シリンダ Ｄ 駆動室 Ｘ 回転軸芯 Ｙ 支持軸芯 Ｌ１ 低速姿勢での仮想平面 Ｌ２ 低速仮想線 Ｈ１ 高速姿勢での仮想平面 Ｈ２ 高速仮想線 DESCRIPTION OF SYMBOLS 1 Main body case 6 Plunger 7 Cylinder block 9 Swash plate 18, 19 Hydraulic cylinder D Drive room X Rotation axis Y Support axis L1 Virtual plane at low speed posture L2 Low speed virtual line H1 Virtual plane at high speed posture H2 High speed virtual line
Claims (1)
（Ｄ）にシリンダブロック（７）を回転自在に支持し、
複数個のプランジャ（６）を前記シリンダブロック
（７）の回転軸芯（Ｘ）と平行に前記シリンダブロック
（７）に備えて、 前記各プランジャ（６）の先端部を受け止める斜板
（９）を、前記シリンダブロック（７）の回転軸芯
（Ｘ）と直交する方向の支持軸芯（Ｙ）周りに揺動自在
に前記駆動室（Ｄ）の内奥部に配置し、前記斜板（９）
を前記支持軸芯（Ｙ）周りに低速姿勢と高速姿勢とに亘
って揺動操作する油圧シリンダ（１８），（１９）を備
えると共に、 前記斜板（９）の低速姿勢における前記各プランジャ
（６）の先端部を通る仮想平面（Ｌ１）と直交するもの
で前記シリンダブロック（７）の回転軸芯（Ｘ）を通る
低速仮想線（Ｌ２）、並びに、前記斜板（９）の高速姿
勢における前記各プランジャ（６）の先端部を通る仮想
平面（Ｈ１）と直交するもので前記シリンダブロック
（７）の回転軸芯（Ｘ）を通る高速仮想線（Ｈ２）を想
定して、 前記低速仮想線（Ｌ２）と高速仮想線（Ｈ２）との間
に、前記斜板（９）の支持軸芯（Ｙ）を位置させてある
可変容量型油圧モータの斜板角変更構造。1. A cylinder block (7) is rotatably supported in a drive chamber (D) formed in a main body case (1),
A plurality of plungers (6) are provided on the cylinder block (7) in parallel with the rotation axis (X) of the cylinder block (7), and a swash plate (9) for receiving a tip end of each plunger (6). Is disposed in the inner part of the drive chamber (D) so as to be swingable around a support axis (Y) orthogonal to the rotation axis (X) of the cylinder block (7), and the swash plate ( 9)
Hydraulic cylinders (18) and (19) for swinging around the support axis (Y) between a low-speed posture and a high-speed posture, and the plungers (19) in the low-speed posture of the swash plate (9). 6) A low-speed imaginary line (L2) orthogonal to the imaginary plane (L1) passing through the tip and passing through the rotation axis (X) of the cylinder block (7), and the high-speed attitude of the swash plate (9). Assuming a high-speed virtual line (H2) orthogonal to the virtual plane (H1) passing through the tip of each plunger (6) and passing through the rotation axis (X) of the cylinder block (7), A swash plate angle changing structure of a variable displacement hydraulic motor in which a support axis (Y) of the swash plate (9) is positioned between a virtual line (L2) and a high-speed virtual line (H2).
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3173794A JP2911743B2 (en) | 1994-03-02 | 1994-03-02 | Swash plate angle changing structure of variable displacement hydraulic motor |
| GB9421357A GB2287069B (en) | 1994-03-02 | 1994-10-24 | Swash plate type hydraulic motor switchable between high speed and low speed |
| US08/329,121 US5649468A (en) | 1994-03-02 | 1994-10-25 | Swash plate type hydraulic motor having offset swash plate pivot axis |
| KR1019940027642A KR0150662B1 (en) | 1994-03-02 | 1994-10-27 | Swash plate type hydraulic motor switchable between high speed and low speed |
| DE4440452A DE4440452C2 (en) | 1994-03-02 | 1994-11-03 | Swashplate hydraulic motor switchable between high and low speed |
| FR9413448A FR2716939A1 (en) | 1994-03-02 | 1994-11-09 | Swing plate hydraulic motor. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3173794A JP2911743B2 (en) | 1994-03-02 | 1994-03-02 | Swash plate angle changing structure of variable displacement hydraulic motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07243375A JPH07243375A (en) | 1995-09-19 |
| JP2911743B2 true JP2911743B2 (en) | 1999-06-23 |
Family
ID=12339357
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3173794A Expired - Lifetime JP2911743B2 (en) | 1994-03-02 | 1994-03-02 | Swash plate angle changing structure of variable displacement hydraulic motor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2911743B2 (en) |
-
1994
- 1994-03-02 JP JP3173794A patent/JP2911743B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07243375A (en) | 1995-09-19 |
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