WO2012131965A1 - Continuously variable transmission - Google Patents
Continuously variable transmission Download PDFInfo
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- WO2012131965A1 WO2012131965A1 PCT/JP2011/058183 JP2011058183W WO2012131965A1 WO 2012131965 A1 WO2012131965 A1 WO 2012131965A1 JP 2011058183 W JP2011058183 W JP 2011058183W WO 2012131965 A1 WO2012131965 A1 WO 2012131965A1
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- WIPO (PCT)
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- peripheral surface
- clearance
- movable sheave
- outer peripheral
- inner peripheral
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/52—Pulleys or friction discs of adjustable construction
- F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
- F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
- F16H63/065—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions hydraulic actuating means
Definitions
- the present invention relates to a continuously variable transmission that is wound around a plurality of pulleys and transmits power between the plurality of pulleys, and in particular, an outer peripheral surface of a shaft that rotates integrally with a fixed sheave, and a movable sheave fitted to the shaft.
- the present invention relates to a continuously variable transmission in which a sealing is interposed between the inner peripheral surface of the continuously variable transmission.
- a belt type continuously variable transmission using a belt as a transmission member is known as a continuously variable transmission capable of continuously changing a gear ratio, that is, continuously.
- shifting is performed by changing the groove width of a pulley around which the belt is wound by hydraulic pressure, and the clamping pressure by which the pulley pinches the belt is applied by hydraulic pressure, thereby transmitting a predetermined torque. It is configured to set the capacity.
- the invention described in International Publication No. 2010/021218 includes a low hydraulic pressure supply unit that supplies a hydraulic pressure adjusted to a relatively low pressure using a hydraulic pressure generated by a hydraulic pump as a source pressure, A high hydraulic pressure supply unit that supplies a hydraulic pressure adjusted to a relatively higher pressure than the hydraulic pressure supplied to the low hydraulic pressure supply unit, and a high pressure hydraulic source that holds a higher hydraulic pressure than the hydraulic pressure to be supplied to the high hydraulic pressure supply unit A supply-side control valve that opens and closes the supply oil path by driving a valve body that is interposed in a supply oil path that supplies hydraulic pressure from the high-pressure hydraulic source to the high hydraulic pressure supply unit and that is pressed against a valve seat;
- the hydraulic control device for a continuously variable transmission is provided with a discharge-side control valve that causes the high hydraulic pressure supply unit to communicate with a drain location by driving a valve body that is pressed against the valve seat.
- a continuously variable transmission described in JP 2009-275825A includes a fixed sheave integrated with a shaft, a movable sheave attached to a cylindrical portion of the fixed sheave so as to be movable in the axial direction thereof, By pressing the movable sheave so as to approach or separate from the fixed sheave side, a hydraulic chamber that applies a clamping pressure to sandwich the belt between the fixed sheave and the movable sheave, an inner peripheral surface of the movable sheave, and a fixed sheave And a seal ring interposed between the outer peripheral surface of the integrally rotating shaft.
- a continuously variable transmission as described in Japanese Patent Application Laid-Open No. 2009-275825 has an inner peripheral surface of a movable sheave and a fixed sheave in order to improve at least one of responsiveness of shift and controllability of shift.
- a seal ring is interposed between the outer peripheral surface and the pressure difference between both sides of the seal ring is large. The seal ring is pressed against the low-pressure side of the annular groove or mounting part where it is attached. It becomes a state. Such pressing to the inner surface is caused by, for example, the control oil pressure of the pulley.
- control oil is filled in the clearance between the inner peripheral surface of the movable sheave on the high-pressure side and the outer peripheral surface of the shaft portion integrated with the fixed sheave with the seal ring interposed therebetween.
- sealing is in close contact with the low-pressure side of the annular groove or mounting part so as not to cause leakage of the control hydraulic pressure, the inner peripheral surface of the movable sheave on the low-pressure side and the outer periphery of the fixed sheave across the seal ring There is almost no control oil in the clearance between the surfaces.
- the present invention has been made paying attention to the technical problem described above, and has a large pressure difference between both sides sandwiching the seal ring, and the outer peripheral surface of the shaft rotating integrally with the inner peripheral surface of the movable sheave and the fixed sheave. It is an object of the present invention to provide a continuously variable transmission that suppresses a decrease in durability due to wear or heat generation when the surfaces contact with each other due to eccentric rotation or sliding.
- the present invention is provided with a fixed sheave integrated with the shaft portion, and attached to the shaft portion so as to be movable toward and away from the fixed sheave.
- a seal ring is interposed between the seal ring and the belt side sandwiching the seal ring is a low-pressure part, and the other side is a high-pressure part, and fluid leakage from these high-pressure parts to the low-pressure part is caused by the seal ring.
- the continuously variable transmission configured to prevent at the high pressure portion side, the clearance between the outer peripheral surface of the shaft portion and the inner peripheral surface of the movable sheave on the high pressure portion side, and on the low pressure portion side Kicking a clearance between the inner peripheral surface of the movable sheave and the outer peripheral surface of the shank, and is characterized in different.
- the clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, and the outer periphery of the shaft portion on the low pressure portion side is different based on the axial length of the movable sheave.
- a clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, and the shaft portion on the low pressure portion side is different.
- the clearance between the outer peripheral surface of the movable sheave and the inner peripheral surface of the movable sheave has a clearance on the low-pressure portion side larger than a clearance on the high-pressure portion side.
- a clearance between the outer peripheral surface of the shaft portion and the inner peripheral surface of the movable sheave on the low-pressure portion side is the axial direction of the shaft portion.
- a continuously variable transmission characterized in that it is small on the seal ring side and large on one side.
- the clearance between the outer peripheral surface of the shaft portion on the high-pressure portion side and the inner peripheral surface of the movable sheave, and the outer peripheral surface of the shaft portion on the low-pressure portion side and the movable sheave is different. Therefore, when each pulley rotates or slides, the pulley rotates eccentrically or tilts with respect to the rotation axis of the fixed sheave integrated with the shaft portion.
- FIG. 1 is a schematic diagram of a continuously variable transmission according to the present invention. It is sectional drawing of the pulley which concerns on this invention. It is sectional drawing which shows the other example of the clearance of the pulley which concerns on this invention. It is sectional drawing which shows the further another example of the clearance of the pulley which concerns on this invention.
- the continuously variable transmission mechanism that is the subject of this invention is a conventionally known belt type, and the belt is sandwiched in a winding groove having a V-shaped cross section formed on the outer peripheral portion of the pulley.
- the torque is transmitted by a frictional force generated between the pulley and the pulley.
- An example thereof is schematically shown in FIG. 2, and the belt 1 is wound around a driving pulley 3 and a driven pulley 4 constituting a continuously variable transmission 2.
- These pulleys 3 and 4 are arranged so that the fixed sheaves 5 and 6 and the movable sheaves 7 and 8 face each other, whereby a winding groove having a V-shaped cross section is formed between these sheaves.
- the driven pulley 4 is taken up here.
- the driven pulley 4 is integrated with a fixed sheave 6 integrated with the driven shaft 11 (shaft portion), and a cylindrical portion 12 fitted to the driven shaft 11 so as to approach and separate from the fixed sheave 6.
- the movable sheave 8 is provided.
- a spline 13 is formed on the inner peripheral surface of the cylindrical portion 12
- a spline 14 is formed on the outer peripheral surface of the driven shaft 11 corresponding to the spline 13, and the spline 14 of the driven shaft 11 and the cylindrical portion 12 The spline 13 is fitted.
- the surfaces 6a and 8a of the sheaves 6 and 8 facing each other are formed in a tapered shape, and a winding groove 15 having a V-shaped cross section around which the belt 1 is wound is formed between the tapered surfaces 6a and 8a.
- the driven shaft 11 is fitted to the outer periphery of the bearing portion 17 fixed by the casing 16 and is rotatably supported by the bearing portion 17.
- a hydraulic chamber 10 is formed on the back side of the movable sheave 8 (opposite to the tapered surface). By supplying hydraulic pressure to the hydraulic chamber 10, the movable sheave 8 is pushed toward the fixed sheave 6 side.
- the belt 1 is configured to be sandwiched between the fixed sheave 6.
- the hydraulic pressure supplied to the hydraulic chamber 10 is controlled so that the width of the winding groove 15 becomes a width that sets the target speed ratio in a pulley that is controlled to set the speed ratio, and the transmission torque capacity. Is controlled so as to generate a belt clamping pressure corresponding to the input torque.
- An oil passage 18 for supplying control oil to the hydraulic chamber 10 is formed along the central axis of the bearing portion 17 and the driven shaft 11, and the oil passage 18 and the hydraulic chamber 10 have a radius of the driven shaft 11. It communicates with another oil passage 19 provided in the direction. Further, the control oil supplied to the hydraulic chamber 10 is formed between the outer peripheral surface of the driven shaft 11 integrated with the movable sheave 8 connected to the hydraulic chamber 10 and the inner peripheral surface of the movable sheave 8 integrated with the cylindrical portion 12. Into the clearance between.
- the control oil that has flowed into the clearance between the outer peripheral surface of the driven shaft 11 that is integral with the fixed sheave 6 and the inner peripheral surface of the movable sheave 8 that is integrated with the cylindrical portion 12 is the winding groove 15 that continues to this clearance.
- 3 is enlarged between the outer peripheral surface of the driven shaft 11 integrated with the movable sheave 8 and the inner peripheral surface of the movable sheave 8 as shown in FIG.
- a seal ring 20 (seal member) is interposed.
- An annular groove 21 into which the seal ring 20 is fitted is formed in the inner peripheral portion of the movable sheave 8.
- one side (hydraulic chamber side) sandwiching the seal ring 20 is a hydraulic circuit in which control oil exists, corresponds to the high pressure portion 22, and the other side (belt 1 side sandwiched between tapered surfaces) ) Is a low pressure portion 23 communicating with the winding groove 15 around which the belt 1 is wound. Therefore, control oil exists in the clearance on the high-pressure part side 22 across the seal ring 20, but almost no leakage of control oil occurs in the clearance on the low-pressure part side 23 across the seal ring 20.
- the clearance in the high pressure portion and the clearance in the low pressure portion are provided differently.
- the radial clearance between the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 in the high-pressure portion 22 (that is, the hydraulic circuit in which the control oil exists) is
- the inner peripheral surface of the movable sheave 8 is formed so that the radial clearance b between the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 in the low-pressure portion 23 is larger than the smallest portion a. Yes.
- the radius of the outer peripheral surface of the driven shaft 11 in the low pressure portion and the movable sheave 8 are different from the difference a between the radius of the outer peripheral surface of the driven shaft 11 in the high pressure portion and the radius of the inner peripheral surface of the movable sheave 8. It can be said that the inner peripheral surface of the movable sheave 8 is formed so that the difference b from the radius of the inner peripheral surface becomes larger.
- the inner peripheral surface of the movable sheave 8 and the outer peripheral surface of the driven shaft 11 on the low-pressure portion side 23 where leakage of control oil is suppressed can be prevented from being worn or seized, and thus durable. Can be improved.
- FIG. 4 shows another embodiment of the invention, and the clearance on the high-pressure part side and the clearance on the low-pressure part side are different based on the axial length of the movable sheave integrated with the cylindrical part. It may be formed.
- the fixed sheave integrated with the driven shaft 11 has the maximum inclination angle ⁇ of the movable sheave 8 integrated with the cylindrical portion 12 with respect to the rotation axis of the fixed sheave 6 integrated with the driven shaft 11.
- the location a see FIG. In the embodiment shown in FIG. 4, a location d (in the embodiment shown in FIG.
- the high pressure portion 22 side Although the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 are in contact with each other at a location a where the radial clearance is small, there is no problem because the lubricant is lubricated with control oil. Moreover, since the inner peripheral surface of the movable sheave 8 on the low pressure part side and the outer peripheral surface of the driven shaft 11 are provided so as not to contact each other even at the maximum angle ⁇ , the contact can be suppressed. As a result, the inner peripheral surface of the movable sheave 8 on the low-pressure part side where leakage of control oil is suppressed and the outer peripheral surface of the driven shaft 11 can be suppressed from causing wear and seizure. Can be improved.
- FIG. 5 shows still another embodiment of the present invention, and the clearance on the low pressure part side is small on the seal ring side in the axial direction of the driven shaft 11 and large on one side thereof (opening end side of the movable sheave). It may be formed as follows.
- the radial clearance between the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 in the low-pressure portion 23 is the clearance e on the annular groove side in the radial direction in the axial direction of the driven shaft 11.
- the clearance f on the opening end side of the movable sheave 8 is formed so as to increase in the radial direction in the axial direction of the driven shaft 11, and the inner peripheral surface of the movable sheave 8 may be so-called chamfered. Good.
- the clearance e on the annular groove side in the low pressure part 23 is set larger than the minimum clearance a on the high pressure part side.
- the clearance on the high-pressure part side and the clearance on the low-pressure part side are basically different from each other on the outer peripheral surface of the shaft part and the inner peripheral surface of the movable sheave of the continuously variable transmission according to the present invention. Just do it.
- the driven pulley was mentioned as an example in the structure example mentioned above, it is not limited to this, A drive pulley may be sufficient.
Abstract
Provided is a continuously variable transmission wherein there is a large pressure differential between opposing sides of a seal ring and degrading of durability due to abrasion or heat generation is controlled in a case where the inner periphery of a mobile sieve and the outer periphery of a fixed sieve come into contact on the contact surfaces thereof due to eccentric rotation, sliding, or the like. In a continuously variable transmission (2), a seal ring (20) is interposed between the outer periphery of a shaft member (11) and the inner periphery of a mobile sieve (8), the belt side on one side of this seal ring (20) is a low pressure section (23), the other side thereof is a high pressure section (22), and the leakage of fluids from the high pressure section (22) to the low pressure section (23) is prevented with the seal ring (20). A clearance (a) on the high pressure section (22) side between the outer periphery of the shaft member (11) and the inner periphery of the mobile sieve (8) and a clearance (b) on the low pressure section (23) side between the outer periphery of the shaft member (11) and the inner periphery of the mobile sieve (8) differ.
Description
この発明は、複数のプーリに巻き掛けられてそれら複数のプーリ間で動力伝達を行う無段変速機に関し、特に固定シーブと一体回転する軸の外周面と、その軸に嵌合させた可動シーブの内周面との間にシーリングを介在させた無段変速機に関するものである。
The present invention relates to a continuously variable transmission that is wound around a plurality of pulleys and transmits power between the plurality of pulleys, and in particular, an outer peripheral surface of a shaft that rotates integrally with a fixed sheave, and a movable sheave fitted to the shaft. The present invention relates to a continuously variable transmission in which a sealing is interposed between the inner peripheral surface of the continuously variable transmission.
変速比を無段階すなわち連続的に変化させることのできる無段変速機として、ベルトを伝動部材としたベルト式無段変速機が知られている。ベルト式無段変速機では、ベルトが巻き掛けられたプーリの溝幅を油圧によって変化させることにより変速を行い、またプーリがベルトを挟み付ける挟圧力を油圧によって付与し、これにより所定のトルク伝達容量を設定するように構成されている。
2. Description of the Related Art A belt type continuously variable transmission using a belt as a transmission member is known as a continuously variable transmission capable of continuously changing a gear ratio, that is, continuously. In a belt-type continuously variable transmission, shifting is performed by changing the groove width of a pulley around which the belt is wound by hydraulic pressure, and the clamping pressure by which the pulley pinches the belt is applied by hydraulic pressure, thereby transmitting a predetermined torque. It is configured to set the capacity.
このような無段変速機の一例が国際公開第２０１０／０２１２１８号に記載されている。この国際公開第２０１０／０２１２１８号に記載されている発明は、油圧ポンプで発生させられた油圧を元圧として相対的に低い圧力に調圧された油圧が供給される低油圧供給部と、その低油圧供給部に供給される油圧より相対的に高い圧力に調圧された油圧が供給される高油圧供給部と、前記高油圧供給部に供給すべき油圧より高い油圧を保持する高圧油圧源と、その高圧油圧源から前記高油圧供給部に油圧を供給する供給油路に介装され、かつ弁座に押し付けられる弁体を駆動することにより前記供給油路を開閉する供給側制御弁と、弁座に押し付けられる弁体を駆動することにより前記高油圧供給部をドレン箇所に連通させる排出側制御弁とを備えた無段変速機の油圧制御装置を構成している。
An example of such a continuously variable transmission is described in International Publication No. 2010/021218. The invention described in International Publication No. 2010/021218 includes a low hydraulic pressure supply unit that supplies a hydraulic pressure adjusted to a relatively low pressure using a hydraulic pressure generated by a hydraulic pump as a source pressure, A high hydraulic pressure supply unit that supplies a hydraulic pressure adjusted to a relatively higher pressure than the hydraulic pressure supplied to the low hydraulic pressure supply unit, and a high pressure hydraulic source that holds a higher hydraulic pressure than the hydraulic pressure to be supplied to the high hydraulic pressure supply unit A supply-side control valve that opens and closes the supply oil path by driving a valve body that is interposed in a supply oil path that supplies hydraulic pressure from the high-pressure hydraulic source to the high hydraulic pressure supply unit and that is pressed against a valve seat; The hydraulic control device for a continuously variable transmission is provided with a discharge-side control valve that causes the high hydraulic pressure supply unit to communicate with a drain location by driving a valve body that is pressed against the valve seat.
また、特開２００９－２７５８２５号公報に記載されている無段変速機は、軸と一体化された固定シーブと、固定シーブの円筒部にその軸線方向に移動可能に取り付けられた可動シーブと、その固定シーブ側に接近・離隔するように可動シーブを押圧することで、ベルトを固定シーブと可動シーブとで挟み付ける挟圧力を付与する油圧室と、その可動シーブの内周面と固定シーブと一体回転する軸の外周面との間に介在させたシールリングとを有している。
A continuously variable transmission described in JP 2009-275825A includes a fixed sheave integrated with a shaft, a movable sheave attached to a cylindrical portion of the fixed sheave so as to be movable in the axial direction thereof, By pressing the movable sheave so as to approach or separate from the fixed sheave side, a hydraulic chamber that applies a clamping pressure to sandwich the belt between the fixed sheave and the movable sheave, an inner peripheral surface of the movable sheave, and a fixed sheave And a seal ring interposed between the outer peripheral surface of the integrally rotating shaft.
特開２００９－２７５８２５号公報に記載されているような無段変速機は、変速の応答性あるいは変速の制御性の少なくともいずれか一方を向上させるために、可動シーブの内周面と固定シーブの外周面との間にシールリングが介在させられており、そのシールリングを挟んだ両側での圧力差が大きく、シールリングはこれが取り付けられている環状溝あるいは取付部のうち低圧側に押し付けられた状態となる。このような内側面への押し付けは、例えば、プーリの制御油圧によって生じる。したがって、シールリングを挟んで高圧側の可動シーブの内周面と固定シーブと一体である軸部の外周面とのクリアランスには制御油が満たされている。また、制御油圧の漏洩を生じさせないように環状溝あるいは取付部のうち低圧側の側面にシーリングが密着しているため、シールリングを挟んで低圧側の可動シーブの内周面と固定シーブの外周面との間のクリアランスには、制御油がほとんど存在しない。
A continuously variable transmission as described in Japanese Patent Application Laid-Open No. 2009-275825 has an inner peripheral surface of a movable sheave and a fixed sheave in order to improve at least one of responsiveness of shift and controllability of shift. A seal ring is interposed between the outer peripheral surface and the pressure difference between both sides of the seal ring is large. The seal ring is pressed against the low-pressure side of the annular groove or mounting part where it is attached. It becomes a state. Such pressing to the inner surface is caused by, for example, the control oil pressure of the pulley. Accordingly, the control oil is filled in the clearance between the inner peripheral surface of the movable sheave on the high-pressure side and the outer peripheral surface of the shaft portion integrated with the fixed sheave with the seal ring interposed therebetween. In addition, since the sealing is in close contact with the low-pressure side of the annular groove or mounting part so as not to cause leakage of the control hydraulic pressure, the inner peripheral surface of the movable sheave on the low-pressure side and the outer periphery of the fixed sheave across the seal ring There is almost no control oil in the clearance between the surfaces.
そのため、各プーリが回転や摺動している際に、可動シーブの内周面と固定シーブと一体回転する軸の外周面とが接触した場合、シールリングを挟んで低圧側の可動シーブの内周面と固定シーブと一体回転する軸の外周面との接触面は、制御油による潤滑や冷却がほとんどできないため、摩耗が進行し、また発熱量が多くなって焼き付きが生じ、耐久性が低下する可能性がある。
Therefore, when each pulley rotates or slides, if the inner peripheral surface of the movable sheave contacts the outer peripheral surface of the shaft that rotates integrally with the fixed sheave, the inner side of the movable sheave on the low-pressure side with the seal ring in between. The contact surface between the peripheral surface and the outer peripheral surface of the shaft that rotates integrally with the fixed sheave is hardly lubricated or cooled by the control oil, so wear progresses, and the amount of generated heat increases, resulting in seizure and lower durability. there's a possibility that.
この発明は上記の技術的課題に着目してなされたものであって、シールリングを挟んだ両側での圧力差が大きく、かつ可動シーブの内周面と固定シーブと一体回転する軸の外周面との間のクリアランスにおいて、偏心回転や摺動などによりそれらの面が接触した場合に、摩耗あるいは発熱による耐久性の低下を抑制する無段変速機を提供することを目的とするものである。
The present invention has been made paying attention to the technical problem described above, and has a large pressure difference between both sides sandwiching the seal ring, and the outer peripheral surface of the shaft rotating integrally with the inner peripheral surface of the movable sheave and the fixed sheave. It is an object of the present invention to provide a continuously variable transmission that suppresses a decrease in durability due to wear or heat generation when the surfaces contact with each other due to eccentric rotation or sliding.
上記の目的を達成するために、この発明は、軸部に一体化された固定シーブと、その固定シーブに対して接近および離隔されるように前記軸部にその軸線方向に移動可能に取り付けられた円筒部に一体化された可動シーブとによって形成されたプーリを備え、前記固定シーブと前記可動シーブとの間に巻き掛けられたベルトと、前記軸部の外周面と前記可動シーブの内周面との間にシールリングが介在させられるとともに、そのシールリングを挟んだ前記ベルト側が低圧部とされ、かつ他方側が高圧部とされ、これら高圧部から低圧部への流体の漏洩を前記シールリングで防止するように構成された無段変速機において、前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとが、異なることを特徴とするものである。
In order to achieve the above object, the present invention is provided with a fixed sheave integrated with the shaft portion, and attached to the shaft portion so as to be movable toward and away from the fixed sheave. A pulley formed by a movable sheave integrated with the cylindrical portion, a belt wound between the fixed sheave and the movable sheave, an outer peripheral surface of the shaft portion, and an inner periphery of the movable sheave A seal ring is interposed between the seal ring and the belt side sandwiching the seal ring is a low-pressure part, and the other side is a high-pressure part, and fluid leakage from these high-pressure parts to the low-pressure part is caused by the seal ring. In the continuously variable transmission configured to prevent at the high pressure portion side, the clearance between the outer peripheral surface of the shaft portion and the inner peripheral surface of the movable sheave on the high pressure portion side, and on the low pressure portion side Kicking a clearance between the inner peripheral surface of the movable sheave and the outer peripheral surface of the shank, and is characterized in different.
また、この発明は、上記の構成において、前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとは、前記可動シーブの軸線方向の長さに基づいて、異なることを特徴とする無段変速機である。
また、この発明は、上記のいずれかの構成において、前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとでは、前記高圧部側のクリアランスよりも前記低圧部側のクリアランスが大きいことを特徴とする無段変速機である。 Further, according to the present invention, in the above configuration, the clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, and the outer periphery of the shaft portion on the low pressure portion side. In the continuously variable transmission, the clearance between the surface and the inner peripheral surface of the movable sheave is different based on the axial length of the movable sheave.
Further, according to the present invention, in any one of the configurations described above, a clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, and the shaft portion on the low pressure portion side. In the continuously variable transmission, the clearance between the outer peripheral surface of the movable sheave and the inner peripheral surface of the movable sheave has a clearance on the low-pressure portion side larger than a clearance on the high-pressure portion side.
また、この発明は、上記のいずれかの構成において、前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとでは、前記高圧部側のクリアランスよりも前記低圧部側のクリアランスが大きいことを特徴とする無段変速機である。 Further, according to the present invention, in the above configuration, the clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, and the outer periphery of the shaft portion on the low pressure portion side. In the continuously variable transmission, the clearance between the surface and the inner peripheral surface of the movable sheave is different based on the axial length of the movable sheave.
Further, according to the present invention, in any one of the configurations described above, a clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, and the shaft portion on the low pressure portion side. In the continuously variable transmission, the clearance between the outer peripheral surface of the movable sheave and the inner peripheral surface of the movable sheave has a clearance on the low-pressure portion side larger than a clearance on the high-pressure portion side.
さらに、この発明は、上記のいずれかの構成において、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスが、前記軸部の軸線方向において前記シールリング側で小さく、その一方側で大きいことを特徴とする無段変速機である。
Further, according to the present invention, in any one of the above-described configurations, a clearance between the outer peripheral surface of the shaft portion and the inner peripheral surface of the movable sheave on the low-pressure portion side is the axial direction of the shaft portion. A continuously variable transmission characterized in that it is small on the seal ring side and large on one side.
この発明によれば、高圧部側における軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとが異なるように構成されている。そのため、各プーリが回転や摺動している際に、軸部と一体化している固定シーブの回転軸線に対して偏心回転したり傾倒すること等により、可動シーブの内周面と軸部に一体化された固定シーブの外周面との接触が生じる場合において、高圧部の半径方向のクリアランスが小さい箇所における軸部の外周面と可動シーブの内周面とが接触したとしても、その接触面は制御油で潤滑されており、そのクリアランスよりもクリアランスが大きい低圧部の可動シーブの内周面と軸部の外周面とは、接触を抑制することができる。その結果、制御油の漏洩が抑制されている低圧部側の可動シーブの内周面と軸部の外周面とは、摩耗や発熱による焼き付きが生じるのを抑制することができるため、耐久性を向上させることができる。
According to this invention, the clearance between the outer peripheral surface of the shaft portion on the high-pressure portion side and the inner peripheral surface of the movable sheave, and the outer peripheral surface of the shaft portion on the low-pressure portion side and the movable sheave The clearance between the inner peripheral surface and the inner peripheral surface is different. Therefore, when each pulley rotates or slides, the pulley rotates eccentrically or tilts with respect to the rotation axis of the fixed sheave integrated with the shaft portion. When contact with the outer peripheral surface of the integrated fixed sheave occurs, even if the outer peripheral surface of the shaft portion and the inner peripheral surface of the movable sheave are in contact with each other at a location where the radial clearance of the high pressure portion is small, the contact surface Is lubricated with control oil, and contact between the inner peripheral surface of the movable sheave in the low-pressure portion and the outer peripheral surface of the shaft portion, which has a clearance larger than the clearance, can be suppressed. As a result, the inner peripheral surface of the movable sheave on the low pressure part side where the leakage of control oil is suppressed and the outer peripheral surface of the shaft part can be prevented from being seized due to wear or heat generation, so durability is improved. Can be improved.
つぎに、この発明を具体例を参照して説明する。この発明で対象とする無段変速機構は、従来知られているベルト式のものであり、ベルトがプーリの外周部に形成された断面Ｖ字状の巻き掛け溝の内部に挟み込まれ、その結果、プーリとの間で生じる摩擦力でトルクを伝達するように構成されている。その一例を図２に模式的に示してあり、ベルト１は無段変速機２を構成している駆動プーリ３と従動プーリ４とに巻き掛けられている。これらの各プーリ３，４は、固定シーブ５，６と可動シーブ７，８とを対向させて配置することにより、これらのシーブの間に断面Ｖ字状の巻き掛け溝が形成され、その可動シーブ７，８を油圧シリンダなどのアクチュエータ９，１０（油圧室）によって固定シーブ５，６に対して前後動させることにより、巻き掛け溝の幅を変化させるように構成されている。
Next, the present invention will be described with reference to specific examples. The continuously variable transmission mechanism that is the subject of this invention is a conventionally known belt type, and the belt is sandwiched in a winding groove having a V-shaped cross section formed on the outer peripheral portion of the pulley. The torque is transmitted by a frictional force generated between the pulley and the pulley. An example thereof is schematically shown in FIG. 2, and the belt 1 is wound around a driving pulley 3 and a driven pulley 4 constituting a continuously variable transmission 2. These pulleys 3 and 4 are arranged so that the fixed sheaves 5 and 6 and the movable sheaves 7 and 8 face each other, whereby a winding groove having a V-shaped cross section is formed between these sheaves. By moving the sheaves 7 and 8 back and forth with respect to the fixed sheaves 5 and 6 by actuators 9 and 10 (hydraulic chambers) such as hydraulic cylinders, the width of the winding groove is changed.
図３を用いてより具体的に説明する。駆動プーリ３と従動プーリ４とは同様の構成であるため、ここでは従動プーリ４を取り上げる。従動プーリ４は、従動軸１１（軸部）と一体化されている固定シーブ６と、その固定シーブ６に対して接近し、また離れるように従動軸１１に嵌合された円筒部１２に一体化された可動シーブ８とを備えている。この円筒部１２の内周面にはスプライン１３が形成されており、このスプライン１３に対応する従動軸１１の外周面にスプライン１４が形成されるとともに、従動軸１１のスプライン１４と円筒部１２のスプライン１３とが嵌合している。また、これらのシーブ６，８の互いに対向する面６ａ、８ａがテーパ状に形成され、これらのテーパ面６ａ、８ａの間がベルト１を巻き掛ける断面Ｖ字状の巻き掛け溝１５となっている。従動軸１１は、ケーシング１６で固定されている軸受部１７の外周に嵌合されており、軸受部１７によって回転自在に支持されている。
This will be described more specifically with reference to FIG. Since the drive pulley 3 and the driven pulley 4 have the same configuration, the driven pulley 4 is taken up here. The driven pulley 4 is integrated with a fixed sheave 6 integrated with the driven shaft 11 (shaft portion), and a cylindrical portion 12 fitted to the driven shaft 11 so as to approach and separate from the fixed sheave 6. The movable sheave 8 is provided. A spline 13 is formed on the inner peripheral surface of the cylindrical portion 12, a spline 14 is formed on the outer peripheral surface of the driven shaft 11 corresponding to the spline 13, and the spline 14 of the driven shaft 11 and the cylindrical portion 12 The spline 13 is fitted. Further, the surfaces 6a and 8a of the sheaves 6 and 8 facing each other are formed in a tapered shape, and a winding groove 15 having a V-shaped cross section around which the belt 1 is wound is formed between the tapered surfaces 6a and 8a. Yes. The driven shaft 11 is fitted to the outer periphery of the bearing portion 17 fixed by the casing 16 and is rotatably supported by the bearing portion 17.
また、可動シーブ８の背面側（テーパ面とは反対側）には油圧室１０が形成されており、その油圧室１０に油圧を供給することにより可動シーブ８が固定シーブ６側に押されてベルト１を固定シーブ６との間に挟み付けるように構成されている。この油圧室１０に供給される油圧は、変速比を設定するように制御されるプーリにおいては、巻き掛け溝１５の幅が目標変速比を設定する幅となるように制御され、また伝達トルク容量を設定するプーリにおいては、入力トルクに応じたベルト挟圧力を発生するように制御される。
A hydraulic chamber 10 is formed on the back side of the movable sheave 8 (opposite to the tapered surface). By supplying hydraulic pressure to the hydraulic chamber 10, the movable sheave 8 is pushed toward the fixed sheave 6 side. The belt 1 is configured to be sandwiched between the fixed sheave 6. The hydraulic pressure supplied to the hydraulic chamber 10 is controlled so that the width of the winding groove 15 becomes a width that sets the target speed ratio in a pulley that is controlled to set the speed ratio, and the transmission torque capacity. Is controlled so as to generate a belt clamping pressure corresponding to the input torque.
この油圧室１０に制御油を供給する油路１８は、軸受部１７と従動軸１１との中心軸線に沿って形成されており、この油路１８と油圧室１０とは、従動軸１１の半径方向に設けられた他の油路１９によって連通されている。また、油圧室１０に供給された制御油は、油圧室１０と連なる可動シーブ８に一体化された従動軸１１の外周面と円筒部１２に一体化された可動シーブ８の内周面との間のクリアランスに流入する。
An oil passage 18 for supplying control oil to the hydraulic chamber 10 is formed along the central axis of the bearing portion 17 and the driven shaft 11, and the oil passage 18 and the hydraulic chamber 10 have a radius of the driven shaft 11. It communicates with another oil passage 19 provided in the direction. Further, the control oil supplied to the hydraulic chamber 10 is formed between the outer peripheral surface of the driven shaft 11 integrated with the movable sheave 8 connected to the hydraulic chamber 10 and the inner peripheral surface of the movable sheave 8 integrated with the cylindrical portion 12. Into the clearance between.
固定シーブ６と一体である従動軸１１の外周面と円筒部１２に一体化された可動シーブ８の内周面との間のクリアランスに流入したこの制御油が、このクリアランスと連なる巻き掛け溝１５に流入するのを妨げるために、可動シーブ８に一体化された従動軸１１の外周面と可動シーブ８の内周面との間には、図３のI部分を拡大した図１に示すように、シールリング２０（シール部材）が介在させられている。そのシールリング２０を嵌合させた環状溝２１が、可動シーブ８の内周部に形成されている。上記のクリアランスにおいて、そのシールリング２０を挟んだ一方側（油圧室側）が制御油の存在する油圧回路であり高圧部２２に相当し、かつ他方側（テーパ面に挟まれているベルト１側）がベルト１が巻き掛かっている巻き掛け溝１５に連通する低圧部２３となっている。したがって、シールリング２０を挟んで高圧部側２２のクリアランスには制御油が存在しているが、シールリング２０を挟んで低圧部側２３のクリアランスには、制御油の漏洩がほとんど生じない。
The control oil that has flowed into the clearance between the outer peripheral surface of the driven shaft 11 that is integral with the fixed sheave 6 and the inner peripheral surface of the movable sheave 8 that is integrated with the cylindrical portion 12 is the winding groove 15 that continues to this clearance. 3 is enlarged between the outer peripheral surface of the driven shaft 11 integrated with the movable sheave 8 and the inner peripheral surface of the movable sheave 8 as shown in FIG. In addition, a seal ring 20 (seal member) is interposed. An annular groove 21 into which the seal ring 20 is fitted is formed in the inner peripheral portion of the movable sheave 8. In the clearance described above, one side (hydraulic chamber side) sandwiching the seal ring 20 is a hydraulic circuit in which control oil exists, corresponds to the high pressure portion 22, and the other side (belt 1 side sandwiched between tapered surfaces) ) Is a low pressure portion 23 communicating with the winding groove 15 around which the belt 1 is wound. Therefore, control oil exists in the clearance on the high-pressure part side 22 across the seal ring 20, but almost no leakage of control oil occurs in the clearance on the low-pressure part side 23 across the seal ring 20.
また、この発明に係る高圧部におけるクリアランスと低圧部におけるクリアランスとは、異なるように設けられている。例えば具体的に説明すると、図１に示すように、高圧部２２（つまり、制御油の存在する油圧回路）における従動軸１１の外周面と可動シーブ８の内周面との半径方向のクリアランスが最小である箇所ａよりも、低圧部２３における従動軸１１の外周面と可動シーブ８の内周面との半径方向のクリアランスｂが大きくなるように、可動シーブ８の内周面は形成されている。また、これを言い換えると、高圧部における従動軸１１の外周面の半径と可動シーブ８の内周面の半径との差分ａよりも、低圧部における従動軸１１の外周面の半径と可動シーブ８の内周面の半径との差分ｂが大きくなるように、可動シーブ８の内周面は形成されている、ともいえる。
Further, the clearance in the high pressure portion and the clearance in the low pressure portion according to the present invention are provided differently. For example, specifically, as shown in FIG. 1, the radial clearance between the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 in the high-pressure portion 22 (that is, the hydraulic circuit in which the control oil exists) is The inner peripheral surface of the movable sheave 8 is formed so that the radial clearance b between the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 in the low-pressure portion 23 is larger than the smallest portion a. Yes. In other words, the radius of the outer peripheral surface of the driven shaft 11 in the low pressure portion and the movable sheave 8 are different from the difference a between the radius of the outer peripheral surface of the driven shaft 11 in the high pressure portion and the radius of the inner peripheral surface of the movable sheave 8. It can be said that the inner peripheral surface of the movable sheave 8 is formed so that the difference b from the radius of the inner peripheral surface becomes larger.
そのため、各プーリが回転や摺動している際に、従動軸１１と一体化している固定シーブ６の回転軸線に対して偏心回転したり傾倒すること等により、可動シーブ８の内周面と従動軸１１に一体化された固定シーブ６の外周面との接触が生じる場合において、高圧部２２の半径方向のクリアランスが小さい箇所ａにおける従動軸１１の外周面と可動シーブ８の内周面とが接触したとしても、その接触面は制御油で潤滑されているとともに、そのクリアランスａよりもクリアランスが大きい低圧部２３の可動シーブ８の内周面と従動軸１１の外周面とは、接触を抑制することができる。その結果、制御油の漏洩が抑制されている低圧部側２３の可動シーブ８の内周面と従動軸１１の外周面とは、摩耗や焼き付きが生じるのを抑制することができるため、耐久性を向上させることができる。
Therefore, when each pulley rotates or slides, the pulley rotates eccentrically or tilts with respect to the rotation axis of the fixed sheave 6 integrated with the driven shaft 11. When contact with the outer peripheral surface of the fixed sheave 6 integrated with the driven shaft 11 occurs, the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 at the location a where the radial clearance of the high-pressure portion 22 is small. Contact surface is lubricated with control oil, and the inner peripheral surface of the movable sheave 8 of the low-pressure portion 23 having a clearance larger than the clearance a and the outer peripheral surface of the driven shaft 11 are in contact with each other. Can be suppressed. As a result, the inner peripheral surface of the movable sheave 8 and the outer peripheral surface of the driven shaft 11 on the low-pressure portion side 23 where leakage of control oil is suppressed can be prevented from being worn or seized, and thus durable. Can be improved.
なお、図４は発明における他の実施例を示しており、高圧部側のクリアランスと低圧部側のクリアランスとは、円筒部と一体化した可動シーブの軸線方向の長さに基づいて、異なるように形成されていてもよい。例えば具体的に説明すると、従動軸１１と一体化している固定シーブ６の回転軸線に対する円筒部１２と一体化している可動シーブ８の最大傾き角αが、従動軸１１と一体化している固定シーブ６の回転軸線に対して円筒部１２と一体化している可動シーブ８が傾いた際に、高圧部２２における従動軸１１の外周面と可動シーブ８の内周面とが接触する箇所ａ（図４に示す実施例では、半径方向においてクリアランスが最小である箇所）から高圧部２２における従動軸１１の外周面と円筒部１２の内周面とが接触する箇所ｄ（図４に示す実施例では、円筒部１２の内周面に形成されたスプラインのと従動軸１１の外周面との間のクリアランスがその半径方向において最小である箇所）までのその軸線方向における距離Ｌと、円筒部１２の内周面に設けられたスプラインと従動軸１１の外周面に設けられたスプラインとの半径方向におけるクリアランスＣとにより、
α≒ｔａｎ－１（Ｃ／Ｌ）・・・（１）
として表される。従動軸１１と一体化している固定シーブ６の回転軸線に対して円筒部１２と一体化している可動シーブ８がこの最大傾き角αで傾いた際に、低圧部側における従動軸１１の外周面と可動シーブ８の内周面とが互いに接触しないように、その半径方向におけるクリアランスを設けてもよい。 FIG. 4 shows another embodiment of the invention, and the clearance on the high-pressure part side and the clearance on the low-pressure part side are different based on the axial length of the movable sheave integrated with the cylindrical part. It may be formed. For example, specifically, the fixed sheave integrated with the drivenshaft 11 has the maximum inclination angle α of the movable sheave 8 integrated with the cylindrical portion 12 with respect to the rotation axis of the fixed sheave 6 integrated with the driven shaft 11. When the movable sheave 8 integrated with the cylindrical portion 12 is tilted with respect to the rotational axis 6, the location a (see FIG. In the embodiment shown in FIG. 4, a location d (in the embodiment shown in FIG. 4) where the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the cylindrical portion 12 in the high-pressure portion 22 are in contact with the radial clearance) , The distance L in the axial direction to the point where the clearance between the spline formed on the inner peripheral surface of the cylindrical portion 12 and the outer peripheral surface of the driven shaft 11 is the smallest in the radial direction), Inner circumference By the clearance C in the radial direction of the spline provided on the spline and the outer peripheral surface of the driven shaft 11 provided in,
α≈tan −1 (C / L) (1)
Represented as: When themovable sheave 8 integrated with the cylindrical portion 12 is inclined at the maximum inclination angle α with respect to the rotational axis of the fixed sheave 6 integrated with the driven shaft 11, the outer peripheral surface of the driven shaft 11 on the low pressure portion side. A clearance in the radial direction may be provided so that the inner surface of the movable sheave 8 does not contact each other.
α≒ｔａｎ－１（Ｃ／Ｌ）・・・（１）
として表される。従動軸１１と一体化している固定シーブ６の回転軸線に対して円筒部１２と一体化している可動シーブ８がこの最大傾き角αで傾いた際に、低圧部側における従動軸１１の外周面と可動シーブ８の内周面とが互いに接触しないように、その半径方向におけるクリアランスを設けてもよい。 FIG. 4 shows another embodiment of the invention, and the clearance on the high-pressure part side and the clearance on the low-pressure part side are different based on the axial length of the movable sheave integrated with the cylindrical part. It may be formed. For example, specifically, the fixed sheave integrated with the driven
α≈tan −1 (C / L) (1)
Represented as: When the
各プーリが回転や摺動している際に、可動シーブ８が従動軸１１と一体化している固定シーブ６の回転軸線に対して傾倒する角度が最大角αである場合において、高圧部２２側の半径方向のクリアランスが小さい箇所ａにおける従動軸１１の外周面と可動シーブ８の内周面とは接触するが、制御油で潤滑されているため問題はない。また、低圧部側の可動シーブ８の内周面と従動軸１１の外周面とは、最大角αでも互いに接触しないように設けられているため、接触を抑制することができる。その結果、制御油の漏洩が抑制されている低圧部側の可動シーブ８の内周面と従動軸１１の外周面とは、摩耗や焼き付きが生じるのを抑制することができるため、耐久性を向上させることができる。
When the angle at which the movable sheave 8 tilts with respect to the rotation axis of the fixed sheave 6 integrated with the driven shaft 11 is the maximum angle α when each pulley rotates or slides, the high pressure portion 22 side Although the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 are in contact with each other at a location a where the radial clearance is small, there is no problem because the lubricant is lubricated with control oil. Moreover, since the inner peripheral surface of the movable sheave 8 on the low pressure part side and the outer peripheral surface of the driven shaft 11 are provided so as not to contact each other even at the maximum angle α, the contact can be suppressed. As a result, the inner peripheral surface of the movable sheave 8 on the low-pressure part side where leakage of control oil is suppressed and the outer peripheral surface of the driven shaft 11 can be suppressed from causing wear and seizure. Can be improved.
また、図５は発明におけるさらに他の実施例を示しており、低圧部側におけるクリアランスは、従動軸１１の軸線方向においてシールリング側で小さく、その一方側（可動シーブの開口端側）で大きいように形成されていてもよい。例えば具体的に説明すると、低圧部２３における従動軸１１の外周面と可動シーブ８の内周面との半径方向のクリアランスは、従動軸１１の軸線方向において環状溝側のクリアランスｅがその半径方向において小さく、従動軸１１の軸線方向において可動シーブ８の開口端側のクリアランスｆがその半径方向において大きくなるように形成されており、可動シーブ８の内周面がいわゆる面取りを行った形状としてもよい。なお、低圧部２３における環状溝側のクリアランスｅは、高圧部側の最小クリアランスａよりも、大きく設定されている。
FIG. 5 shows still another embodiment of the present invention, and the clearance on the low pressure part side is small on the seal ring side in the axial direction of the driven shaft 11 and large on one side thereof (opening end side of the movable sheave). It may be formed as follows. For example, specifically, the radial clearance between the outer peripheral surface of the driven shaft 11 and the inner peripheral surface of the movable sheave 8 in the low-pressure portion 23 is the clearance e on the annular groove side in the radial direction in the axial direction of the driven shaft 11. The clearance f on the opening end side of the movable sheave 8 is formed so as to increase in the radial direction in the axial direction of the driven shaft 11, and the inner peripheral surface of the movable sheave 8 may be so-called chamfered. Good. In addition, the clearance e on the annular groove side in the low pressure part 23 is set larger than the minimum clearance a on the high pressure part side.
なお、この発明に係る無段変速機の軸部の外周面と可動シーブの内周面とにおいて高圧部側のクリアランスと、低圧部側のクリアランスとは、要は、互いに異なるように構成されていればよい。また、上述した構成例では従動プーリを例に挙げたが、これに限定されず、駆動プーリでもよい。
The clearance on the high-pressure part side and the clearance on the low-pressure part side are basically different from each other on the outer peripheral surface of the shaft part and the inner peripheral surface of the movable sheave of the continuously variable transmission according to the present invention. Just do it. Moreover, although the driven pulley was mentioned as an example in the structure example mentioned above, it is not limited to this, A drive pulley may be sufficient.
Claims (4)
- 軸部と一体に設けられた固定シーブと、その固定シーブに対して接近および離隔されるように前記軸部にその軸線方向に移動可能に取り付けられた円筒部と一体化された可動シーブとによって形成されたプーリを備え、前記固定シーブと前記可動シーブとの間に巻き掛けられたベルトと、前記軸部の外周面と前記可動シーブの内周面との間にシールリングが介在させられるとともに、そのシールリングを挟んだ前記ベルト側が低圧部とされ、かつ他方側が高圧部とされ、これら高圧部から低圧部への流体の漏洩を前記シールリングで防止するように構成された無段変速機において、
前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとが、異なることを特徴とする無段変速機。 A fixed sheave provided integrally with the shaft portion, and a movable sheave integrated with a cylindrical portion attached to the shaft portion so as to be movable toward and away from the fixed sheave. A belt formed between the fixed sheave and the movable sheave and a seal ring interposed between an outer peripheral surface of the shaft portion and an inner peripheral surface of the movable sheave. The belt side sandwiching the seal ring is a low pressure part, and the other side is a high pressure part, and the continuously variable transmission configured to prevent fluid leakage from the high pressure part to the low pressure part by the seal ring In
The clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, the outer peripheral surface of the shaft portion on the low pressure portion side, and the inner peripheral surface of the movable sheave A continuously variable transmission characterized in that the clearance between them is different. - 前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとは、前記可動シーブの軸線方向の長さに基づいて、異なることを特徴とする請求項１に記載の無段変速機。 The clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, the outer peripheral surface of the shaft portion on the low pressure portion side, and the inner peripheral surface of the movable sheave 2. The continuously variable transmission according to claim 1, wherein the clearance is different based on a length of the movable sheave in an axial direction.
- 前記高圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスと、前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスとでは、前記高圧部側のクリアランスよりも前記低圧部側のクリアランスが大きいことを特徴とする請求項１または２に記載の無段変速機。 The clearance between the outer peripheral surface of the shaft portion on the high pressure portion side and the inner peripheral surface of the movable sheave, the outer peripheral surface of the shaft portion on the low pressure portion side, and the inner peripheral surface of the movable sheave The continuously variable transmission according to claim 1 or 2, wherein the clearance on the low pressure part side is larger than the clearance on the high pressure part side.
- 前記低圧部側における前記軸部の前記外周面と前記可動シーブの前記内周面との間のクリアランスが、前記軸部の軸線方向において前記シールリング側で小さく、その一方側で大きいことを特徴とする請求項１ないし３のいずれかに記載の無段変速機。 A clearance between the outer peripheral surface of the shaft portion and the inner peripheral surface of the movable sheave on the low-pressure portion side is small on the seal ring side in the axial direction of the shaft portion and large on one side thereof. The continuously variable transmission according to any one of claims 1 to 3.
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| PCT/JP2011/058183 WO2012131965A1 (en) | 2011-03-31 | 2011-03-31 | Continuously variable transmission |
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| Application Number | Priority Date | Filing Date | Title |
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| PCT/JP2011/058183 WO2012131965A1 (en) | 2011-03-31 | 2011-03-31 | Continuously variable transmission |
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Cited By (1)
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| WO2017080676A1 (en) * | 2015-11-09 | 2017-05-18 | Robert Bosch Gmbh | Hydraulically adjustable pulley device for a continuously variable transmission and the method for operating a hydraulically adjustable pulley device |
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| WO2017080676A1 (en) * | 2015-11-09 | 2017-05-18 | Robert Bosch Gmbh | Hydraulically adjustable pulley device for a continuously variable transmission and the method for operating a hydraulically adjustable pulley device |
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| CN108474471B (en) * | 2015-11-09 | 2021-02-26 | 罗伯特·博世有限公司 | Hydraulically adjustable pulley arrangement for a continuously variable transmission and method of operating the same |
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