JP5978491B2 - Hydraulic continuously variable transmission - Google Patents
Hydraulic continuously variable transmission Download PDFInfo
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- JP5978491B2 JP5978491B2 JP2012070622A JP2012070622A JP5978491B2 JP 5978491 B2 JP5978491 B2 JP 5978491B2 JP 2012070622 A JP2012070622 A JP 2012070622A JP 2012070622 A JP2012070622 A JP 2012070622A JP 5978491 B2 JP5978491 B2 JP 5978491B2
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Description
本発明は、油圧式無段変速機に関する。 The present invention relates to a hydraulic continuously variable transmission.
従来より、無段変速機の一種としてプランジャ式油圧ポンプとプランジャ式油圧モータを油圧閉回路を介して繋いで構成される油圧式無段変速機が知られている（例えば特許文献１を参照。）。 Conventionally, as a type of continuously variable transmission, a hydraulic continuously variable transmission configured by connecting a plunger hydraulic pump and a plunger hydraulic motor via a hydraulic closed circuit is known (see, for example, Patent Document 1). ).
特許文献１に開示されている油圧式無段変速機では、シリンダブロックとともにプランジャが回転し、プランジャの先端部に斜板部材が接しながら回転する。斜板部材は、所定の揺動中心を中心として揺動する斜板ホルダに内嵌されたラジアルベアリングおよびアンギュラベアリングの更に内径側に内嵌されている。 In the hydraulic continuously variable transmission disclosed in Patent Document 1, the plunger rotates together with the cylinder block, and the swash plate member rotates while contacting the tip of the plunger. The swash plate member is fitted further on the inner diameter side of a radial bearing and an angular bearing fitted in a swash plate holder that swings around a predetermined swing center.
ところが、特許文献１の油圧式無段変速機は、外径側から斜板ホルダ、ベアリング、斜板部材の順に配設されていることから、ベアリングが大型化し、油圧式無段変速機全体も大型化してしまう点で問題がある。特にベアリングが大型化すると、斜板部材と斜板ホルダとの差回転による伝達トルクロスが大きくなる点で問題がある。 However, since the hydraulic continuously variable transmission of Patent Document 1 is arranged in the order of the swash plate holder, the bearing, and the swash plate member from the outer diameter side, the size of the bearing is increased, and the entire hydraulic continuously variable transmission is also included. There is a problem in that the size is increased. In particular, when the bearing is enlarged, there is a problem in that the transmission torque cross due to the differential rotation between the swash plate member and the swash plate holder becomes large.
本発明は、かかる問題に鑑みて創案されたものであり、油圧式無段変速機において、斜板ホルダおよびベアリングの小径化、小型化を可能とした油圧式無段変速機を提供することを目的とする。 The present invention has been made in view of such problems, and provides a hydraulic continuously variable transmission capable of reducing the diameter and size of a swash plate holder and a bearing in a hydraulic continuously variable transmission. Objective.
本発明の油圧式無段変速機は、回転軸と、該回転軸の外周に回転一体に設けられたシリンダブロックと、該シリンダブロックの軸線方向一方において、同軸線周りの円周上に間隔をあけて往復摺動可能に挿入された複数の油圧ポンプ用プランジャと、前記油圧ポンプ用プランジャの先端に摺接する油圧ポンプ用斜板部材と、所定の揺動中心を中心に揺動することで、傾斜量変更可能に設けられ、前記油圧ポンプ用斜板部材より回転軸側のボール軸受を介して前記油圧ポンプ用斜板部材を支持する油圧ポンプ用斜板ホルダと、前記シリンダブロックの軸線方向他方において、同軸線周りの円周上に間隔をあけて往復摺動可能に挿入された油圧モータ用プランジャと、前記油圧モータ用プランジャの先端が摺接する油圧モータ用斜板部材と、前記油圧モータ用斜板部材より回転軸側のボール軸受を介して前記油圧モータ用斜板部材を支持する油圧モータ用斜板ホルダと、を備えるものを前提としており、前記油圧ポンプ用斜板ホルダに前記ボール軸受が外嵌され、該ボール軸受に前記油圧ポンプ用斜板部材が外嵌されている。また、前記油圧モータ用斜板ホルダに前記ボール軸受が外嵌され、該ボール軸受に前記油圧モータ用斜板部材が外嵌されている。そして、前記ボール軸受のボールのピッチ円径が、前記プランジャのピッチ円径より小さくなっている。 The hydraulic continuously variable transmission according to the present invention includes a rotating shaft, a cylinder block provided integrally with the outer periphery of the rotating shaft, and one axial direction of the cylinder block at an interval on a circumference around the coaxial line. A plurality of hydraulic pump plungers inserted so as to be slidable in a reciprocating manner, a hydraulic pump swash plate member slidably contacting the tip of the hydraulic pump plunger, and swinging about a predetermined swing center, A swash plate holder for a hydraulic pump that is provided so as to be capable of changing the amount of inclination and supports the swash plate member for the hydraulic pump via a ball bearing on the rotating shaft side of the swash plate member for the hydraulic pump; and the other axial direction of the cylinder block in the plunger hydraulic motor inserted for reciprocal sliding spaced circumferentially around the coaxial line, a hydraulic motor swash plate member whose tip sliding contact of the plunger hydraulic motor, wherein A swash plate holder hydraulic motor for supporting the swash plate member for the hydraulic motor via the ball bearing of the rotary shaft side of the swash plate member for pressure motor, has assumed that comprises, in the swash plate holder for the hydraulic pump The ball bearing is externally fitted, and the hydraulic pump swash plate member is externally fitted to the ball bearing. The ball bearing is externally fitted to the hydraulic motor swash plate holder, and the hydraulic motor swash plate member is externally fitted to the ball bearing. And the pitch circle diameter of the ball of the ball bearing is smaller than the pitch circle diameter of the plunger.
かかる構成を備える油圧式無段変速機によれば、斜板ホルダにボール軸受が外嵌され、該ボール軸受に斜板部材が外嵌され、ボール軸受のボールのピッチ円径が、プランジャのピッチ円径より小さくなっている。これらにより、本発明の油圧式無段変速機では、従来例に係る油圧式無段変速機と比較して、斜板ホルダおよびボールベアリングの小径化が図られ、ひいては油圧式無段変速機全体の小型化および軽量化が図られる。 According to the hydraulic continuously variable transmission having such a configuration, a ball bearing is externally fitted to the swash plate holder, a swash plate member is externally fitted to the ball bearing, and the pitch circle diameter of the ball bearing ball is equal to the pitch of the plunger. It is smaller than the circle diameter. Thus, in the hydraulic continuously variable transmission according to the present invention, the diameter of the swash plate holder and the ball bearing can be reduced as compared with the hydraulic continuously variable transmission according to the conventional example. Can be reduced in size and weight.
本発明の油圧式無段変速機によれば、従来例に係る油圧式無段変速機と比較して、斜板ホルダおよびボールベアリングの小径化が図られ、ひいては油圧式無段変速機全体の小型化および軽量化が図られる。また、ボールベアリングが小径化されることにより、斜板部材と斜板ホルダとの差回転による伝達トルクロスが低減され、差回転数の高速回転化などが可能となる。 According to the hydraulic continuously variable transmission of the present invention, the diameter of the swash plate holder and the ball bearing can be reduced as compared with the hydraulic continuously variable transmission according to the conventional example. Reduction in size and weight is achieved. Further, by reducing the diameter of the ball bearing, the transmission torque cross due to the differential rotation between the swash plate member and the swash plate holder is reduced, and the differential rotation speed can be increased.
以下、本発明の実施の形態に係る油圧式無段変速機について図面を参照しながら説明する。図１に示すように、油圧式無段変速機１の入力軸（回転軸）２には、ダンパー３を介してエンジンのクランクシャフト４から回転動力が伝達される。入力軸２に伝達された回転動力は、油圧式無段変速機１において変速された後、油圧モータ用斜板ホルダ５等を介して図示しない差動歯車機構、駆動輪等へ伝達される。 Hereinafter, a hydraulic continuously variable transmission according to an embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, rotational power is transmitted from an engine crankshaft 4 to an input shaft (rotary shaft) 2 of a hydraulic continuously variable transmission 1 via a damper 3. The rotational power transmitted to the input shaft 2 is shifted in the hydraulic continuously variable transmission 1 and then transmitted to a differential gear mechanism (not shown), drive wheels and the like via the hydraulic motor swash plate holder 5 and the like.
油圧式無段変速機１は、前記入力軸２、シリンダブロック８、油圧ポンプ用プランジャ９、油圧モータ用プランジャ１０、油圧ポンプ用斜板部材１１、油圧モータ用斜板部材１２などで構成される。 The hydraulic continuously variable transmission 1 includes the input shaft 2, a cylinder block 8, a hydraulic pump plunger 9, a hydraulic motor plunger 10, a hydraulic pump swash plate member 11, a hydraulic motor swash plate member 12, and the like. .
シリンダブロック８は、略円柱体形状をしており、入力軸２の途中位置において入力軸２の外周に回転一体に設けられている。このシリンダブロック８には、油圧ポンプ用プランジャ９、油圧モータ用プランジャ１０、油圧ポンプ用スプール弁１３、油圧モータ用スプール弁１４などが設けられている。 The cylinder block 8 has a substantially cylindrical shape, and is provided integrally with the outer periphery of the input shaft 2 at an intermediate position of the input shaft 2. The cylinder block 8 is provided with a hydraulic pump plunger 9, a hydraulic motor plunger 10, a hydraulic pump spool valve 13, a hydraulic motor spool valve 14, and the like.
油圧ポンプ用プランジャ９は、シリンダブロック８の軸線方向一方（エンジン側）に設けられており、軸線Ｎ周りの円周上に等間隔をあけて軸線Ｎ方向に往復摺動可能に複数挿入されている。この油圧ポンプ用プランジャ９は、シリンダブロック８に形成されたシリンダボア１５内で往復摺動することで、作動油を吸入又は排出する。なお、油圧ポンプ用プランジャ９はコイルスプリング１６によって油圧ポンプ用斜板部材１１側に付勢されている。 Plungers 9 for the hydraulic pump are provided on one side (engine side) of the cylinder block 8 in the axial direction, and a plurality of hydraulic pump plungers 9 are inserted on the circumference around the axis N so as to be reciprocally slidable in the direction of the axis N. Yes. The hydraulic pump plunger 9 reciprocates in a cylinder bore 15 formed in the cylinder block 8 to suck or discharge hydraulic oil. The hydraulic pump plunger 9 is biased toward the hydraulic pump swash plate member 11 by a coil spring 16.
油圧モータ用プランジャ１０は、シリンダブロック８の軸線方向他方（反エンジン側）に設けられている。油圧モータ用プランジャ１０は、軸線Ｎ周りの円周上に等間隔をあけて軸線Ｎ方向に往復摺動可能に複数挿入されている。この油圧モータ用プランジャ１０も、シリンダブロック８に形成されたシリンダボア１７内で往復摺動することで、作動油を吸入又は排出する。この油圧モータ用プランジャ１０はコイルスプリング１６によって油圧モータ用斜板部材１２側に付勢されている。なお、シリンダブロック８において、油圧ポンプ用プランジャ９が挿入されるシリンダボア１５と、油圧モータ用プランジャ１０が挿入されるシリンダボア１７とは、周方向位置を違えている。 The plunger 10 for the hydraulic motor is provided on the other side in the axial direction of the cylinder block 8 (on the side opposite to the engine). Plural hydraulic motor plungers 10 are inserted on the circumference around the axis N so as to be slidable back and forth in the direction of the axis N at equal intervals. The hydraulic motor plunger 10 also reciprocates and slides in the cylinder bore 17 formed in the cylinder block 8 to suck or discharge the hydraulic oil. The plunger 10 for the hydraulic motor is biased toward the swash plate member 12 for the hydraulic motor by a coil spring 16. In the cylinder block 8, the cylinder bore 15 into which the hydraulic pump plunger 9 is inserted and the cylinder bore 17 into which the hydraulic motor plunger 10 is inserted have different circumferential positions.
油圧ポンプ用スプール弁１３および油圧モータ用スプール弁１４は、シリンダブロック８の内径側に周方向に交互に設けられ、各プランジャ９，１０毎に設けられている。各スプール弁１３，１４は、それぞれ対応するプランジャ９，１０の回転位置に応じて開閉弁動作をして、プランジャ９，１０によって吸入又は排出される作動油の油路を切り換える。 The hydraulic pump spool valve 13 and the hydraulic motor spool valve 14 are alternately provided in the circumferential direction on the inner diameter side of the cylinder block 8, and are provided for each of the plungers 9 and 10. Each spool valve 13, 14 performs an on-off valve operation according to the rotation position of the corresponding plunger 9, 10, and switches the oil path of the hydraulic oil sucked or discharged by the plunger 9, 10.
トランスミッションケース１８内には、円筒面支持部１９が形成され、該円筒面支持部１９に、軸線Ｎ上の揺動中心Ｏを中心に揺動自在に油圧ポンプ用斜板ホルダ２０が支持されている。また、油圧ポンプ用斜板ホルダ２０には、ラジアルボール軸受６およびアンギュラボール軸受７が並んで外嵌されており、これらのボール軸受７，８のさらに外周に油圧ポンプ用斜板部材１１が外嵌されている。この油圧ポンプ用斜板部材１１において油圧ポンプ用プランジャ９の先端部が摺接する部分には、油圧ポンプ用プランジャ９の先端部の半球状に対応した球面状窪み１１ａが形成されている。油圧ポンプ用斜板部材１１は、油圧ポンプ用プランジャ９とともに入力軸２の周囲を回転する。 A cylindrical surface support portion 19 is formed in the transmission case 18, and a hydraulic pump swash plate holder 20 is supported on the cylindrical surface support portion 19 so as to be swingable about a swing center O on the axis N. Yes. Further, a radial ball bearing 6 and an angular ball bearing 7 are externally fitted side by side on the hydraulic pump swash plate holder 20, and the hydraulic pump swash plate member 11 is disposed on the outer periphery of these ball bearings 7 and 8. It is fitted. In this hydraulic pump swash plate member 11, a spherical recess 11 a corresponding to the hemispherical shape of the distal end portion of the hydraulic pump plunger 9 is formed at a portion where the distal end portion of the hydraulic pump plunger 9 is in sliding contact. The hydraulic pump swash plate member 11 rotates around the input shaft 2 together with the hydraulic pump plunger 9.
油圧ポンプ用斜板ホルダ２０は、アクチュエータ２１の伸縮動作に連動して揺動中心Ｏを中心として揺動し、油圧ポンプ用斜板部材１１の軸線Ｎに対する傾斜量が任意の角度に設定される。 The hydraulic pump swash plate holder 20 swings about the swing center O in conjunction with the expansion / contraction operation of the actuator 21, and the amount of inclination of the hydraulic pump swash plate member 11 with respect to the axis N is set to an arbitrary angle. .
油圧ポンプ用斜板部材１１の軸線Ｎに対する傾斜量が所定角度に設定された状態で、シリンダブロック８が回転すると、シリンダブロック８とともに回転する油圧ポンプ用プランジャ９が油圧ポンプ用斜板部材１１の傾斜量に応じて往復動し、スプール弁１３とともに、ポンプ作用を発動し、油圧ポンプ用斜板部材１１の傾斜量に応じた圧油を油圧モータ用プランジャ１０の油圧室１０ａへ供給する。 When the cylinder block 8 rotates in a state in which the inclination amount of the swash plate member 11 for the hydraulic pump is set to a predetermined angle, the plunger 9 for the hydraulic pump that rotates together with the cylinder block 8 moves to the swash plate member 11 for the hydraulic pump. It reciprocates in accordance with the amount of inclination, activates a pump action together with the spool valve 13, and supplies pressure oil corresponding to the amount of inclination of the hydraulic pump swash plate member 11 to the hydraulic chamber 10 a of the hydraulic motor plunger 10.
油圧モータ用斜板部材１２は、トランスミッションケース１８内に回転自在に支持され入力軸２の軸線Ｎ回りに回転する油圧モータ用斜板ホルダ５の周囲に、ベアリングを介して回転自在に設けられている。すなわち、油圧モータ用斜板ホルダ５の周囲には、ラジアルボール軸受６およびアンギュラボール軸受７が並んで外嵌されており、これらのボール軸受７，８のさらに外周に油圧モータ用斜板部材１２が外嵌されている。但し、油圧モータ用斜板部材１２は、軸線Ｎに対して一定の傾斜量を維持したまま回転するように構成されている。この油圧モータ用斜板部材１２に、入力軸２の軸線Ｎ回りに回転する油圧モータ用プランジャ１０の先端部が摺接しており、入力軸２が回転すると油圧モータ用プランジャ１０も同軸回りに回転しながら、油圧ポンプ側から供給される圧油によって、往復動摺動しつつ、油圧モータ用斜板部材１２にスラスト荷重を与えながら、油圧モータ用斜板ホルダ５を回転させる。 The swash plate member 12 for the hydraulic motor is rotatably supported through a bearing around the swash plate holder 5 for the hydraulic motor that is rotatably supported in the transmission case 18 and rotates about the axis N of the input shaft 2. Yes. That is, a radial ball bearing 6 and an angular ball bearing 7 are externally fitted side by side around the hydraulic motor swash plate holder 5, and the hydraulic motor swash plate member 12 is further provided on the outer periphery of these ball bearings 7, 8. Is externally fitted. However, the hydraulic motor swash plate member 12 is configured to rotate while maintaining a certain amount of inclination with respect to the axis N. The tip of a hydraulic motor plunger 10 that rotates about the axis N of the input shaft 2 is in sliding contact with the swash plate member 12 for the hydraulic motor, and when the input shaft 2 rotates, the hydraulic motor plunger 10 also rotates about the same axis. The hydraulic motor swash plate holder 5 is rotated while applying a thrust load to the hydraulic motor swash plate member 12 while reciprocating and sliding with the pressure oil supplied from the hydraulic pump side.
以上に説明した油圧式無段変速機１では、油圧ポンプ用斜板ホルダ２０にボール軸受６，７が外嵌され、これらのボール軸受６，７に油圧ポンプ用斜板部材１１が外嵌されており、また、油圧モータ用斜板ホルダ５にボール軸受６，７が外嵌され、これらのボール軸受６，７に油圧モータ用斜板部材１２が外嵌されている。さらに、回転軸２側から順に斜板ホルダ５，２０、ボール軸受６，７、斜板部材１１、１２も配設されており、何れのボール軸受６，７のボールのピッチ円径も、プランジャ９，１０のピッチ円径より小さくなっている。これらの特徴的な構成により、本実施形態に係る油圧式無段変速機１によれば、従来例に係る油圧式無段変速機と比較して、斜板ホルダ５，２０およびボールベアリング６，７の小径化が図られ、ひいては油圧式無段変速機１全体の小型化が図られる。
In the hydraulic continuously variable transmission 1 described above, the ball bearings 6 and 7 are externally fitted to the hydraulic pump swash plate holder 20, and the hydraulic pump swash plate member 11 is externally fitted to these ball bearings 6 and 7. Further, ball bearings 6 and 7 are fitted on the hydraulic motor swash plate holder 5, and a hydraulic motor swash plate member 12 is fitted on these ball bearings 6 and 7. Further, swash plate holders 5, 20, ball bearings 6, 7, and swash plate members 11, 12 are also arranged in this order from the rotary shaft 2 side. It is smaller than the pitch circle diameter of 9,10. With these characteristic configurations, according to the hydraulic continuously variable transmission 1 according to the present embodiment, the swash plate holders 5 and 20 and the ball bearings 6 and 6 are compared with the hydraulic continuously variable transmission according to the conventional example. The diameter of the hydraulic continuously variable transmission 1 can be reduced.
また、ボールベアリング６，７の小径化により、斜板部材１１，１２と斜板ホルダ５，２０との差回転による伝達トルクロスの低減や、差回転数の高速回転化なども可能となる。 Further, by reducing the diameter of the ball bearings 6 and 7, it is possible to reduce the transmission torque cross due to the differential rotation between the swash plate members 11 and 12 and the swash plate holders 5 and 20 and to increase the differential rotation speed at a high speed.
本発明は、例えば、自動車等の車両に搭載される油圧式無段変速機に適用することが可能である。 The present invention can be applied to, for example, a hydraulic continuously variable transmission mounted on a vehicle such as an automobile.
１ 油圧式無段変速機
２ 入力軸（回転軸）
５ 油圧モータ用斜板ホルダ
６ ラジアルボール軸受（ボール軸受）
７ アンギュラボール軸受（ボール軸受）
８ シリンダブロック
９ 油圧ポンプ用プランジャ
１０ 油圧モータ用プランジャ
１１ 油圧ポンプ用斜板部材
１２ 油圧モータ用斜板部材
２０ 油圧ポンプ用斜板ホルダ
1 Hydraulic continuously variable transmission 2 Input shaft (rotating shaft)
5 Swash plate holder for hydraulic motor 6 Radial ball bearing (ball bearing)
7 Angular ball bearings (ball bearings)
8 Cylinder block 9 Plunger for hydraulic pump 10 Plunger for hydraulic motor 11 Swash plate member for hydraulic pump 12 Swash plate member for hydraulic motor 20 Swash plate holder for hydraulic pump
Claims (1)
該回転軸の外周に回転一体に設けられたシリンダブロックと、
該シリンダブロックの軸線方向一方において、同軸線周りの円周上に間隔をあけて往復摺動可能に挿入された複数の油圧ポンプ用プランジャと、
前記油圧ポンプ用プランジャの先端に摺接する油圧ポンプ用斜板部材と、
所定の揺動中心を中心に揺動することで、傾斜量変更可能に設けられ、前記油圧ポンプ用斜板部材より回転軸側のボール軸受を介して前記油圧ポンプ用斜板部材を支持する油圧ポンプ用斜板ホルダと、
前記シリンダブロックの軸線方向他方において、同軸線周りの円周上に間隔をあけて往復摺動可能に挿入された油圧モータ用プランジャと、
前記油圧モータ用プランジャの先端が摺接する油圧モータ用斜板部材と、
前記油圧モータ用斜板部材より回転軸側のボール軸受を介して前記油圧モータ用斜板部材を支持する油圧モータ用斜板ホルダと、
を備える油圧式無段変速機において、
前記油圧ポンプ用斜板ホルダに前記ボール軸受が外嵌され、該ボール軸受に前記油圧ポンプ用斜板部材が外嵌され、
前記油圧モータ用斜板ホルダに前記ボール軸受が外嵌され、該ボール軸受に前記油圧モータ用斜板部材が外嵌され、
前記ボール軸受のボールのピッチ円径が、前記プランジャのピッチ円径より小さいことを特徴とする油圧式無段変速機。 A rotation axis;
A cylinder block provided integrally with the outer periphery of the rotary shaft;
A plurality of plungers for a hydraulic pump inserted in a reciprocating manner at intervals on a circumference around a coaxial line on one axial direction of the cylinder block;
A hydraulic pump swash plate member that is in sliding contact with a tip of the hydraulic pump plunger;
The hydraulic pressure is provided so that the amount of inclination can be changed by swinging around a predetermined swing center, and supports the swash plate member for the hydraulic pump via a ball bearing closer to the rotating shaft than the swash plate member for the hydraulic pump. A swash plate holder for the pump;
On the other side in the axial direction of the cylinder block, a plunger for a hydraulic motor inserted so as to be reciprocally slidable on the circumference around the coaxial line, and
A swash plate member for a hydraulic motor with which a tip of the plunger for the hydraulic motor is in sliding contact;
A swash plate holder for a hydraulic motor that supports the swash plate member for the hydraulic motor via a ball bearing on the rotating shaft side of the swash plate member for the hydraulic motor;
In a hydraulic continuously variable transmission comprising:
The ball bearing is externally fitted to the hydraulic pump swash plate holder, and the hydraulic pump swash plate member is externally fitted to the ball bearing,
The ball bearing is externally fitted to the hydraulic motor swash plate holder, and the hydraulic motor swash plate member is externally fitted to the ball bearing,
The hydraulic continuously variable transmission, wherein a pitch circle diameter of balls of the ball bearing is smaller than a pitch circle diameter of the plunger.
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| JP2012070622A JP5978491B2 (en) | 2012-03-27 | 2012-03-27 | Hydraulic continuously variable transmission |
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Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02180376A (en) * | 1988-12-29 | 1990-07-13 | Minoru Atake | Hydraulic continuously variable transmission controller |
| JP3696382B2 (en) * | 1997-09-11 | 2005-09-14 | 本田技研工業株式会社 | Swash plate type continuously variable transmission |
| JP4510998B2 (en) * | 2000-07-17 | 2010-07-28 | ヤンマー株式会社 | Hydraulic device |
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