JP5422603B2 - Continuously variable transmission with locking mechanism and pulley lock confirmation method thereof - Google Patents

Description

  The present invention relates to a continuously variable transmission including a lock mechanism that mechanically locks a movable sheave in an axial direction.

  The continuously variable transmission includes a primary pulley, a secondary pulley, and a flexible transmission member (belt or chain) wound around these pulleys. Each pulley includes a fixed sheave and a movable sheave that is movable in the axial direction with respect to the fixed sheave. The transmission ratio of the continuously variable transmission is changed by moving the movable sheave of each pulley in the axial direction and changing the groove width of each pulley. The movable sheave is moved by changing the hydraulic pressure supplied from the oil pump to the oil chamber formed on the back surface of the movable sheave.

  In order to maintain the target gear ratio in such a continuously variable transmission, it is necessary to constantly supply hydraulic pressure to the movable sheave. This is because when the supply of hydraulic pressure is stopped, the hydraulic pressure is reduced due to leakage from the oil chamber or the control valve, the gear ratio cannot be maintained, and belt slippage occurs.

  However, if oil pressure is constantly supplied to the movable sheave, the oil pump must be constantly driven, and the oil pressure required to maintain the gear ratio is very high, so there is no friction loss due to the oil pump. This was a cause of deteriorating fuel consumption of a vehicle equipped with a step transmission.

JP 2002-327814 A

  By providing a lock mechanism that mechanically locks the movable sheave in the axial direction and locking the movable sheave as necessary, the hydraulic pressure supplied to the movable sheave can be reduced to zero or reduced, The above problem can be solved.

  When such a lock mechanism is provided, it is preferable that it can be confirmed whether or not the movable sheave is locked by the lock mechanism.

  This is because if the intention to lock the movable sheave is not locked, the gear ratio changes to an unintended value when the hydraulic pressure supplied to the movable sheave is reduced to zero or reduced. Further, if the intention to release the lock of the movable sheave remains locked, the gear ratio cannot be changed even if the hydraulic pressure supplied to the movable sheave is adjusted in order to change the gear ratio.

  However, if a sensor for confirming whether or not the movable sheave is locked by the lock mechanism is separately provided, the structure of the continuously variable transmission becomes complicated and the cost increases.

  The present invention has been made in view of such a technical problem, and makes it possible to check whether or not the movable sheave is locked in a continuously variable transmission having a lock mechanism without adding a sensor. For the purpose.

  According to an aspect of the present invention, the first and second pulleys having variable groove widths having a fixed sheave and a movable sheave that is axially displaceable with respect to the fixed sheave in accordance with a supplied hydraulic pressure, A flexible transmission member wound between the first and second pulleys, a lock mechanism for mechanically locking the movement of the movable sheave in the axial direction of the first pulley, and the first pulley Alternatively, the movable sheave of the first pulley is locked by the lock mechanism based on whether or not a change in the gear ratio of the continuously variable transmission occurs when the hydraulic pressure supplied to the second pulley is changed. There is provided a continuously variable transmission comprising: a lock confirming means for confirming whether or not

According to another aspect of the present invention, the first and second pulleys having variable groove widths, each having a fixed sheave and a movable sheave that is axially displaceable with respect to the fixed sheave according to a supplied hydraulic pressure, A flexible transmission member wound between the first and second pulleys, and a lock mechanism that mechanically locks the movement of the first sheave in the axial direction of the movable sheave. A pulley lock confirmation method for a step transmission, the procedure for changing the hydraulic pressure supplied to the first pulley or the second pulley, and the hydraulic pressure supplied to the first pulley or the second pulley. A procedure for confirming whether the movable sheave of the first pulley is locked by the locking mechanism, based on whether or not a gear ratio change of the continuously variable transmission occurs when
A pulley lock confirmation method is provided.

  According to these aspects, whether or not the movable sheave is locked based on whether or not the transmission ratio change of the continuously variable transmission occurs when the hydraulic pressure supplied to the first pulley or the second pulley is changed. Is confirmed. There is no need to provide a separate sensor for the confirmation, and the structure of the continuously variable transmission can be prevented from becoming complicated and costly.

1 is an overall configuration diagram of a continuously variable transmission according to an embodiment of the present invention. It is sectional drawing of a primary pulley. It is a figure for demonstrating the locking operation of the movable sheave by a locking mechanism. It is a figure for demonstrating the locking operation of the movable sheave by a locking mechanism. It is a figure for demonstrating the locking operation of the movable sheave by a locking mechanism. It is a figure for demonstrating the locking operation of the movable sheave by a locking mechanism. It is the flowchart which showed the processing content of the controller when locking a movable sheave. It is a figure for demonstrating the unlocking operation | movement of the movable sheave by a locking mechanism. It is a figure for demonstrating the unlocking operation | movement of the movable sheave by a locking mechanism. It is a figure for demonstrating the unlocking operation | movement of the movable sheave by a locking mechanism. It is a figure for demonstrating the unlocking operation | movement of the movable sheave by a locking mechanism. It is the flowchart which showed the processing content of the controller when releasing the lock | rock of a movable sheave. 6 is a time chart showing changes in primary pressure and secondary pressure when a movable sheave is locked by a locking mechanism and then unlocked.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 shows the overall configuration of a continuously variable transmission 100 according to an embodiment of the present invention. The continuously variable transmission 100 includes a primary pulley 1, a secondary pulley 11, a flexible transmission member 2, a hydraulic circuit 51, a controller 52, and an oil pump 53.

  The primary pulley 1 includes a fixed sheave 3, a movable sheave 4 that is axially displaceable with respect to the fixed sheave 3, an oil chamber 8 that is supplied with hydraulic pressure for displacing the movable sheave 4 in the axial direction, and a movable sheave. 4 and a lock mechanism 6 that mechanically locks the movement in the axial direction. A V-shaped groove is formed between the fixed sheave 3 and the movable sheave 4, and the groove width can be changed by displacing the movable sheave 4 in the axial direction. An input shaft 10 is connected to the primary pulley 1, and rotation from a power source (not shown) such as an engine or a motor is input via the input shaft 10.

  The secondary pulley 11 includes a fixed sheave 12, a movable sheave 13 that is axially displaceable with respect to the fixed sheave 12, and an oil chamber 14 that is supplied with hydraulic pressure for displacing the movable sheave 13 in the axial direction. A V-shaped groove is formed between the fixed sheave 12 and the movable sheave 13, and the groove width can be changed by displacing the movable sheave 13 in the axial direction. An output shaft 20 is connected to the secondary pulley 11, and the rotation of the secondary pulley 11 is transmitted to driving wheels (not shown) via the output shaft 20.

  The flexible transmission member 2 is wound between the primary pulley 1 and the secondary pulley 11 and transmits rotation from the primary pulley 1 to the secondary pulley 11. In the present embodiment, the flexible transmission member 2 is a chain in which a plurality of links are connected by pins, but may be a belt as will be described later.

  The hydraulic circuit 51 includes a plurality of oil passages, a flow path switching valve, a pressure adjustment valve, and the like. The hydraulic circuit 51 receives a signal from the controller 52, generates a desired hydraulic pressure using the hydraulic pressure supplied from the oil pump 53 as a source pressure, and supplies it to the oil chambers 8 and 14. In the following description, the hydraulic pressure supplied to the oil chamber 8 is expressed as “primary pressure”, and the hydraulic pressure supplied to the oil chamber 14 is expressed as “secondary pressure”.

  In a state where the movable sheave 4 of the primary pulley 1 is not locked by the lock mechanism 6, the primary pulley 1 and the secondary pulley 11 are adjusted by adjusting the primary pressure and the secondary pressure supplied from the hydraulic circuit 51 to the oil chambers 8 and 14. And changing the contact radii between the flexible transmission member 2 and the primary pulley 1 and the secondary pulley 11 to change the gear ratio of the continuously variable transmission 100 (the input shaft 10 and the output shaft 20). The reduction ratio between the two is changed.

  When the movable sheave 4 of the primary pulley 1 is locked by the lock mechanism 6, the primary pressure supplied from the hydraulic circuit 51 to the oil chamber 8 is made zero. In the present embodiment, the movable sheave 4 of the primary pulley 1 is fixed at a position corresponding to the overdrive speed ratio (the highest speed speed ratio, hereinafter referred to as “OD speed ratio”), as will be described later. In this state, the secondary pressure supplied from the hydraulic circuit 51 to the oil chamber 14 can also be made zero.

  The controller 52 includes a sensor 55 for detecting the rotational speed of the input shaft 10, a sensor 56 for detecting the rotational speed of the output shaft 20, a sensor (not shown) for detecting the accelerator operation amount, and a sensor for detecting the position of the selector (not shown). A detection signal such as that shown in FIG.

  As described above, the controller 52 adjusts the primary pressure and the secondary pressure to change the gear ratio of the continuously variable transmission 100. Further, the controller 52 switches the lock state of the lock mechanism 6, confirms whether the movable sheave 4 is locked, and monitors a change in the gear ratio of the continuously variable transmission 100 for the confirmation.

  FIG. 2 shows a cross section of the primary pulley 1.

  The primary pulley 1 includes a fixed sheave 3, a movable sheave 4, a cylinder portion 5, a lock mechanism 6, and a back cover 7.

  The fixed sheave 3 has a shaft portion 31 extending in the axial direction. A hydraulic pressure supply passage 32 and a drain passage 33 are formed in the shaft portion 31. A primary pressure is supplied to the hydraulic pressure supply passage 32.

  A concave lock key accommodating portion 61 is formed on the outer peripheral surface of the shaft portion 31. A lock key 62 and a lock key spring 63 are accommodated in the lock key accommodating portion 61. The lock key 62 is a button-like movable member that is hollowed out inside, and is urged toward the movable sheave 4 by a lock key spring 63. The lock key accommodating portion 61 communicates with the drain passage 33, so that no hydraulic pressure acts on the inside of the lock key 62.

  A key groove 34 extending in the axial direction is formed on the outer peripheral surface of the shaft portion 31. When the rotation preventing pin 41 extending from the movable sheave 4 is engaged with the key groove 34, relative rotation of the stationary sheave 3 and the movable sheave 4 is prevented while allowing relative displacement in the axial direction.

  The movable sheave 4 has a cylindrical sleeve portion 42 extending in the rotation axis direction, and is externally fitted to the shaft portion 31 via the sleeve portion 42. A drum-shaped cylinder portion 5 is fixed to the outermost peripheral portion of the back surface of the movable sheave 4. The cylinder unit 5 rotates and moves in the axial direction integrally with the movable sheave 4.

  A lock key receiving portion 64 is formed on the inner peripheral surface of the sleeve portion 42. The lock key receiving portion 64 has a concave shape that is large enough to fit the tip of the lock key 62, and a communication hole 65 that connects the lock key receiving portion 64 and the outside of the sleeve portion 42 is formed at the bottom. . A cylindrical release piston 66 is slidably accommodated in the communication hole 65. A cap 67 is fixed to the outer peripheral side opening of the communication hole 65. The cap 67 has an opening that communicates the inside and the outside, and functions exclusively as a stopper that prevents the release piston 66 from falling out of the communication hole 65.

  The back cover 7 has a deformed cylindrical shape whose diameter gradually increases as it approaches the movable sheave 4. The back cover 7 has an end on the side opposite to the movable sheave 4 fixed to the shaft portion 31, and an outermost peripheral end on the movable sheave 4 side is in sliding contact with the cylinder portion 5. A seal member 71 is interposed between the outermost peripheral end of the back cover 7 and the cylinder portion 5. Between the back cover 7, the back surface of the movable sheave 4, and the cylinder portion 5, a variable capacity oil chamber 8 is defined in which the capacity changes as the movable sheave 4 is displaced in the axial direction.

  The sleeve portion 42 is formed with a hydraulic pressure introduction hole 43 that communicates the inside and the outside. A gap 9 extending in the axial direction is formed between the shaft portion 31 and the sleeve portion 42 due to a difference in diameter between the shaft portion 31 and the sleeve portion 42. The hydraulic pressure supply passage 32 and the oil chamber 8 always communicate with each other through the gap 9 and the hydraulic pressure introduction hole 43.

  When the primary pressure is supplied to the hydraulic pressure supply passage 32, the primary pressure is introduced into the oil chamber 8 through the hydraulic pressure introduction hole 43. The movable sheave 4 is moved in the axial direction by the primary pressure introduced into the oil chamber 8, whereby the contact radius between the flexible transmission member 2 and the primary pulley 1 is changed, and the gear ratio of the continuously variable transmission 100 is changed. Change.

  The lock mechanism 6 is a mechanism that mechanically locks the movement of the movable sheave 4 in the axial direction. In the present embodiment, the lock mechanism 6 includes a lock key accommodating portion 61, a lock key 62, a lock key spring 63, a lock key receiving portion 64, a communication hole 65, and a release piston 66.

  The state shown in FIG. 2 is a state where the movable sheave 4 is not locked. That is, since the lock key 62 is in contact with the inner peripheral surface of the sleeve portion 42 and is not fitted into the lock key receiving portion 64, the movable sheave 4 can freely move in the axial direction.

  When the movable sheave 4 moves toward the fixed sheave 3 from this state, the distance between the lock key 62 and the lock key receiving portion 64 is reduced. When the speed ratio of the continuously variable transmission 100 reaches the OD speed ratio, the axial positions of the lock key 62 and the lock key receiving portion 64 coincide with each other, and the lock key 62 protrudes by the urging force of the lock key spring 63. The movable sheave 4 is locked in the axial direction by fitting into the lock key receiving portion 64.

  In a state where the movable sheave 4 is locked, a force for clamping the flexible transmission member 2 necessary for torque transmission is secured by a reaction force when the movable sheave 4 presses the lock key 62. In this state, even if the primary pressure is zero, a thrust load acts on the lock key 62 from the movable sheave 4 in addition to the urging force of the lock key spring 63, so that the lock key 62 comes out of the lock key receiving portion 64. Nevertheless, the locked state is maintained.

  In order to unlock the movable sheave 4, first, the supply of the primary pressure to the oil chamber 8 is resumed, and the thrust load acting on the lock key 62 is reduced. Next, the primary pressure is increased, and the lock key 62 is pushed by the release piston 66 against the urging force of the lock key spring 63, and the lock key receiving portion 64 is retreated. Thereby, the lock of the movable sheave 4 is released.

  Next, the operation when the movable sheave 4 is locked by the lock mechanism 6 and the confirmation process that the movable sheave 4 is locked will be described with reference to FIGS. FIG. 7 is a time chart showing how the primary pressure and the secondary pressure change.

  FIG. 3A shows a state in which the movable sheave 4 is located farthest from the fixed sheave 3 and the continuously variable transmission 100 has the lowest gear ratio. In this state, the movable sheave 4 is not locked.

  When the primary pressure supplied from the hydraulic pressure supply passage 32 to the oil chamber 8 is increased from the state shown in FIG. 3A, the movable sheave 4 moves toward the fixed sheave 3 as shown in FIG. 3B. As a result, the gear ratio of the continuously variable transmission 100 continuously changes from the lowest to the OD gear ratio. In the time chart of FIG. 7, time t1 corresponds.

  When the movable sheave 4 moves to a position corresponding to the OD gear ratio, the lock key 62 protrudes by pushing away the release piston 66 by the urging force of the lock key spring 63 as shown in FIG. Mating. Thereby, the movable sheave 4 is locked at a position corresponding to the OD gear ratio. In the time chart of FIG. 7, time t2 corresponds.

  To confirm that the movable sheave 4 is locked, the primary pressure is lowered to a pressure (hereinafter referred to as “OD balance pressure”) at which the OD transmission ratio is maintained, and the primary pressure is temporarily reduced from the OD balance pressure. This is performed by slightly lowering and monitoring the change in the gear ratio of the continuously variable transmission 100 at this time. In the time chart of FIG. 7, time t3 corresponds.

  Since the OD balance pressure is a pressure at which the OD gear ratio is maintained at the limit, if the primary pressure becomes lower than the OD balance pressure when the movable sheave 4 is not locked, the movable sheave 4 is displaced in the axial direction. Thus, the groove width of the primary pulley 1 increases, and the transmission ratio of the continuously variable transmission 100 changes from the OD transmission ratio to the low side. On the contrary, if the movable sheave 4 is in a locked state, the gear ratio of the continuously variable transmission 100 does not change even if the primary pressure becomes lower than the OD balance pressure. Therefore, it is possible to confirm whether or not the movable sheave 4 is locked by monitoring whether or not a gear ratio change of the continuously variable transmission 100 occurs.

  When it is confirmed that the movable sheave 4 is locked, both the primary pressure and the secondary pressure are reduced to zero. In the time chart of FIG. 7, time t4 corresponds.

  In the state where the primary pressure is zero, the thrust load acting on the movable sheave 4 from the flexible transmission member 2 acts on the lock key 62 as shown by the broken line arrow in FIG. 3D, and the movable sheave 4 becomes stronger. Locked. In the time chart of FIG. 7, time t4 corresponds. Since the primary pressure and the secondary pressure are zero, the oil pump can be stopped, the friction loss due to the oil pump can be eliminated, and the fuel efficiency of the vehicle equipped with the continuously variable transmission 100 can be improved.

  FIG. 4 is a flowchart showing the processing contents of the controller 52 when the movable sheave 4 is locked.

  In S11, the controller 52 increases the primary pressure and changes the gear ratio of the continuously variable transmission 100 to the OD gear ratio. If the lock mechanism 6 is operating normally, the movable sheave 4 is locked by the lock mechanism 6 when the gear ratio of the continuously variable transmission 100 reaches the OD gear ratio.

  In S12, the controller 52 reduces the primary pressure to the OD balance pressure.

  In S13, the controller 52 slightly lowers the primary pressure from the OD balance pressure. The amount of pressure drop at this time is an amount that can detect a change in gear ratio that occurs when the movable sheave 4 is not locked. The controller 52 calculates the gear ratio of the continuously variable transmission 100 by dividing the rotational speed of the input shaft 10 by the rotational speed of the output shaft 20, and stores the change in the gear ratio of the continuously variable transmission 100 when the primary pressure decreases. To do. Then, the controller 52 returns the primary pressure to the OD balance pressure balance pressure.

  In S14, the controller 52 determines whether or not the gear ratio of the continuously variable transmission 100 has changed from the OD gear ratio to the low side when the primary pressure has decreased S13 in S13. If it is determined that the gear ratio of the continuously variable transmission 100 has changed to the low side, the process proceeds to S15.

  In S15, the controller 52 reduces both the primary pressure and the secondary pressure to zero.

  If it is determined in S14 that the gear ratio has changed from the OD balance gear ratio to the low side, the process returns to S11, and the movable sheave 4 is re-locked.

  Next, an operation when the lock of the movable sheave 4 is released by the lock mechanism 6 will be described with reference to FIGS. 5A to 5D and FIG.

  In order to release the lock of the movable sheave 4, first, the supply of the primary pressure from the hydraulic pressure supply passage 32 to the oil chamber 8 is resumed (FIG. 5A). As a result, the thrust load acting on the lock key 62 from the movable sheave 4 is reduced. In the time chart of FIG. 7, time t5 corresponds.

  Next, the primary pressure and the secondary pressure are increased to a release pressure higher than the pressure that realizes the OD gear ratio, and the lock key 62 is pushed down by the release piston 66 (FIG. 5B). Thereby, the lock key 62 is accommodated in the lock key accommodating part 61, and the lock | rock of the movable sheave 4 is cancelled | released. In the time chart of FIG. 7, time t6 corresponds.

  The confirmation that the movable sheave 4 is unlocked is made by temporarily raising the secondary pressure from the release pressure and monitoring whether or not the gear ratio of the continuously variable transmission 100 occurs at this time. Done. In the time chart of FIG. 7, time t7 corresponds.

  If the movable sheave 4 is locked, the gear ratio of the continuously variable transmission 100 does not change even if the secondary pressure is increased from the release pressure. However, if the movable sheave 4 is not locked, when the clamping force of the flexible transmission member 2 by the fixed sheave 12 and the movable sheave 13 of the secondary pulley 11 increases, the flexible transmission member 2 and the secondary pulley 11 are In response to the increase in the contact radius, the flexible transmission member 2 is pulled toward the secondary pulley 11 and the groove width of the primary pulley 1 is expanded by the flexible transmission member 2, so that the gear ratio of the continuously variable transmission 100 is increased. Changes to the low side. Therefore, it is possible to confirm whether or not the movable sheave 4 is unlocked by monitoring whether or not the gear ratio change of the continuously variable transmission 100 occurs.

  When it is confirmed that the movable sheave 4 is unlocked, the secondary pressure is increased more than the release pressure. As a result, the groove width of the secondary pulley 11 is reduced, and accordingly, the groove width of the primary pulley 1 is increased, the movable sheave 4 is moved away from the fixed sheave 3, and the movable sheave 4 is prevented from being locked again. (FIG. 5C). In the time chart of FIG. 7, time t8 corresponds.

  After that, the hydraulic pressure is reduced to a hydraulic pressure that achieves a gear ratio targeting the primary pressure and the secondary pressure (FIG. 5D). Since the lock key 62 is in contact with the inner peripheral surface of the sleeve portion 42, the lock key 62 remains housed in the lock key housing portion 61 even when the primary pressure is lowered, and the unlocked state is maintained. In the time chart of FIG. 7, time t9 corresponds.

  FIG. 6 is a flowchart showing the processing content of the controller 52 when the movable sheave 4 is unlocked.

  In S21, the controller 52 increases the primary pressure and the secondary pressure to the balance pressure, respectively.

  In S22, the controller 52 increases the primary pressure and the secondary pressure to a release pressure that is set to a pressure higher than the balance pressure.

  In S23, the controller 52 slightly increases the secondary pressure from the release pressure. The amount of pressure increase at this time is an amount by which a change in the gear ratio that occurs when the movable sheave 4 is not locked can be detected. The controller 52 stores the speed ratio change of the continuously variable transmission 100 at this time, and then returns the secondary pressure to the release pressure.

  In S24, the controller 52 determines whether the gear ratio of the continuously variable transmission 100 has changed from the OD gear ratio to the low side when the secondary pressure is increased in S23. If it is determined that the gear ratio of the continuously variable transmission 100 has changed to the low side, the process proceeds to S25.

  In S25, the controller 52 increases the secondary pressure to change the gear ratio of the continuously variable transmission 100 to the low side and shifts the axial position of the lock key 62 and the lock key receiving portion 64 to move the movable sheave 4. Then, the primary pressure and the secondary pressure are respectively adjusted to pressures that achieve the target gear ratio.

  If it is determined in S24 that the gear ratio has not changed to the low side, the process returns to S22, and the unlocking of the movable sheave 4 is retried.

  Then, the effect of embodiment of this invention is demonstrated.

  According to the present embodiment, the axial movement of the movable sheave 4 of the primary pulley 1 is mechanically locked by the lock mechanism 6, that is, the movable sheave 4 is fixed at a predetermined axial position. When the movable sheave 4 is locked, the primary pressure can be reduced, so that the oil pump is stopped to eliminate friction loss due to the oil pump, and the fuel efficiency of the vehicle equipped with the continuously variable transmission 100 can be improved. .

  When lowering the primary pressure, it is preferable to confirm whether the movable sheave 4 is locked before lowering the primary pressure. According to this embodiment, the gear ratio of the continuously variable transmission 100 is reduced when the primary pressure is reduced. Whether or not the movable sheave 4 is locked is confirmed based on whether or not it has changed to the low side.

  Since the rotational speeds of the input shaft 10 and the output shaft 20 necessary for calculating the gear ratio of the continuously variable transmission 100 can be detected by a sensor originally provided in the continuously variable transmission 100, the above confirmation is performed. There is no need to provide a separate sensor, and according to the present embodiment, it is possible to prevent the structure of the continuously variable transmission 100 from becoming complicated and costly to be increased (effects corresponding to claims 1, 2, and 4). .

  Further, when the movable sheave 4 is unlocked and the gear ratio of the continuously variable transmission 100 is controlled to the target gear ratio, the primary pressure and the secondary pressure are adjusted to pressures that realize the target gear ratio. It is preferable to confirm that the lock of the movable sheave 4 is released before the operation.

  According to the present embodiment, it is confirmed whether the movable sheave 4 is unlocked based on whether or not the gear ratio of the continuously variable transmission 100 has changed to the low side when the secondary pressure is increased. It is not necessary to separately provide a sensor for performing the confirmation, and it is possible to prevent the structure of the continuously variable transmission 100 from becoming complicated and increasing costs (operational effects corresponding to claims 1, 3, and 4).

  The embodiment of the present invention has been described above, but the above embodiment is merely an example of application of the present invention, and the technical scope of the present invention is not intended to be limited to the specific configuration of the above embodiment.

  For example, the above embodiment is configured to lock the movable sheave 4 at a position corresponding to the OD gear ratio, but may be configured to lock at a position corresponding to another gear ratio. Further, the movable sheave 13 of the secondary pulley 11 may be locked instead of the primary pulley 1.

  In the present embodiment, the primary pressure and the secondary pressure are set to zero in the locked state. However, it is not essential to set the primary pressure and the secondary pressure to zero, and the hydraulic pressure (> 0) is lower than the hydraulic pressure before locking. You can just lower it. Even with such a configuration, there are effects such as reduction of friction loss by the oil pump and improvement of fuel consumption of the vehicle. In addition, when releasing the locked state, the supply delay of the primary pressure is reduced, and the release responsiveness is improved. The effect that it can raise is show | played.

  Moreover, the flexible transmission member 2 should just be able to transmit rotation between the primary pulley 1 and the secondary pulley 11, and may be members other than a chain, for example, the belt which connected several elements with the ring. Good.

1 Primary pulley (first pulley)
2 Flexible transmission member 6 Lock mechanism 11 Secondary pulley (second pulley)
100 continuously variable transmission

Claims (4)

First and second pulleys having variable groove widths, each having a fixed sheave and a movable sheave that is axially displaceable with respect to the fixed sheave according to a supplied hydraulic pressure;
A flexible transmission member wound between the first and second pulleys;
A lock mechanism for mechanically locking the movement of the movable sheave of the first pulley in the axial direction;
Based on whether or not a change in the gear ratio of the continuously variable transmission occurs when the hydraulic pressure supplied to the first pulley or the second pulley is changed, the lock mechanism causes the first pulley to Lock confirmation means for confirming whether the movable sheave is locked,
A continuously variable transmission comprising: The continuously variable transmission according to claim 1,
The lock confirmation means locks the movable sheave of the first pulley by the lock mechanism when the transmission ratio of the continuously variable transmission does not change even if the hydraulic pressure supplied to the first pulley is reduced. Make sure that
Oil pressure reducing means for reducing the oil pressure supplied to the first pulley when the lock confirmation means confirms that the movable sheave of the first pulley is locked by the lock mechanism. A continuously variable transmission characterized by that. The continuously variable transmission according to claim 1 or 2,
The lock confirmation means unlocks the movable sheave of the first pulley by the lock mechanism when the transmission ratio of the continuously variable transmission changes when the hydraulic pressure supplied to the second pulley is increased. Make sure that
When the lock confirmation means confirms that the movable sheave of the first pulley is unlocked by the lock mechanism, the hydraulic pressure supplied to the first and second pulleys is adjusted. A continuously variable transmission, further comprising shift control means for changing a gear ratio of the continuously variable transmission. First and second pulleys having variable groove widths, each having a fixed sheave and a movable sheave that is axially displaceable with respect to the fixed sheave in accordance with a supplied hydraulic pressure; and the first and second pulleys A pulley lock confirmation method for a continuously variable transmission, comprising: a flexible transmission member wound between; and a lock mechanism that mechanically locks the movement of the movable sheave of the first pulley in the axial direction. And
Changing the hydraulic pressure supplied to the first pulley or the second pulley;
Based on whether or not a change in the gear ratio of the continuously variable transmission occurs when the hydraulic pressure supplied to the first pulley or the second pulley is changed, the lock mechanism causes the first pulley to A procedure to check if the movable sheave is locked,
A pulley lock confirmation method comprising:

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