JP2011144869A - One-way clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To accurately detect the rotation angle of a reciprocatingly rotating outer member of a one-way clutch by an inexpensive linear position sensor. <P>SOLUTION: The one-way clutch 44 transmits driving force to an inner member 41 through rollers 42 when the outer member 43 is rotated in one direction, and slips on the inner member 41 when the outer member 43 is rotated in the other direction. The other end side of a cable 48 with one end bound to the outer member 43 of the one-way clutch 44 is guided in a linearly reciprocating manner by a guide member 49, and when the linear position sensor 50 detects the position of the cable 48, an outer member rotation angle computing means M1 computes the rotation angle of the outer member 43 based on the position of the cable 48. The rotation angle of the outer member 43 reciprocatingly rotated in short time intervals can thereby be accurately detected by the inexpensive linear position sensor 50 without needing an expensive rotation angle sensor capable of detecting rotation angles in two rotating directions. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention includes an outer member that reciprocally rotates, an inner member that is coaxially disposed radially inward of the outer member, and a plurality of rollers that are disposed between an inner peripheral surface of the outer member and an outer peripheral surface of the inner member. The outer member transmits a driving force to the inner member when rotating in one direction, and the outer member slips with respect to the inner member when rotating in the other direction.

  In a continuously variable transmission that continuously changes the rotation of the input shaft and transmits it to the output shaft, one end of the connecting rod is connected to a fulcrum that is eccentric with respect to the axis of the input shaft, and the other end of the connecting rod is connected to the one-way clutch. Connected to the output shaft via the shaft, the reciprocating motion of the connecting rod is converted into a one-way rotational motion with a one-way clutch and transmitted to the output shaft, and the gear ratio is changed by increasing or decreasing the eccentric amount of the fulcrum Is known from Patent Document 1 below.

JP-T-2005-502543

  By the way, the one-way clutch connected to the connecting rod of the continuously variable transmission uses a hall element or the like because the outer member reciprocates and rotates repeatedly at the same cycle as the rotational speed of the input shaft. If the rotation angle of the outer member is detected by the magnetic rotation angle sensor, there is a problem that an expensive rotation angle sensor having a function of identifying the rotation direction is required.

  The present invention has been made in view of the above-described circumstances, and an object of the present invention is to accurately detect the rotation angle of an outer member that reciprocally rotates a one-way clutch with an inexpensive linear position sensor.

  In order to achieve the above object, according to the invention described in claim 1, an outer member that reciprocates, an inner member that is coaxially disposed radially inward of the outer member, and an inner circumference of the outer member And a plurality of rollers arranged between the outer surface of the inner member and the outer member, and when the outer member rotates in one direction, a driving force is transmitted to the inner member, and the outer member rotates in the other direction. In a one-way clutch that sometimes slips with respect to the inner member, a cable having one end bound to the outer member, a guide member that guides the other end of the cable in a reciprocating linear motion, and a guide to the guide member And a linear position sensor for detecting the position of the cable, and an outer position for calculating the rotation angle of the outer member based on the position of the cable. The one-way clutch is proposed, characterized in that it comprises a chromatography member rotation angle calculation means.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the outer member calculated by the inner member angular velocity detecting means for detecting the angular velocity of the inner member and the outer member rotation angle calculating means. An outer member angular velocity calculating means for calculating an angular velocity of the outer member from an angle of rotation, an angular velocity of the inner member detected by the inner member angular velocity detecting means, and an angular velocity of the outer member calculated by the outer member angular velocity calculating means. A one-way clutch characterized by comprising engagement state determination means for comparing and determining the engagement state of the one-way clutch is proposed.

  According to a third aspect of the present invention, in addition to the configuration of the second aspect, the angular velocity of the outer member is integrated and calculated from the moment when the engagement state determination means determines the engagement of the one-way clutch. And the rotation angle calculated by integrating the angular velocity of the inner member from the moment when the engagement state determination means determines the engagement of the one-way clutch, and the one-way is calculated from the difference between the rotation angles. A one-way clutch characterized by comprising torque calculation means for calculating torque transmitted by the clutch is proposed.

  According to the configuration of the first aspect, the one-way clutch transmits the driving force to the inner member via the roller when the outer member rotates in one direction, and the one-way clutch acts on the inner member when the outer member rotates in the other direction. Slip. The other end of the cable having one end coupled to the outer member of the one-way clutch is guided by the guide member so as to be able to reciprocate linearly. When the linear position sensor detects the position of the cable, the outer member rotation angle calculating means Since the rotation angle of the outer member is calculated based on the position, the rotation angle of the outer member that reciprocates at short time intervals can be detected without the need for an expensive rotation angle sensor that can detect the rotation angles in the two rotation directions. It can be detected with high accuracy by an inexpensive linear position sensor.

  According to the second aspect of the present invention, when the inner member angular velocity detecting unit detects the angular velocity of the inner member and the outer member angular velocity calculating unit calculates the angular velocity of the outer member from the rotation angle of the outer member, the engagement state determining unit is Since the engagement state of the one-way clutch is determined by comparing the angular velocity of the inner member and the angular velocity of the outer member, the engagement state of the one-way clutch can be determined with extremely high accuracy.

  According to the third aspect of the present invention, the torque calculation means integrates the rotation angle calculated by integrating the angular velocity of the outer member from the moment when the one-way clutch is engaged, and the inner member from the moment when the one-way clutch is engaged. By comparing the rotation angle calculated by integrating the angular velocity, the torque transmitted by the one-way clutch can be accurately calculated in real time from the difference between both rotation angles.

The longitudinal cross-sectional view of a continuously variable transmission. FIG. 2 is a view taken in the direction of arrows 2-2 in FIG. FIG. 3 is a sectional view taken along line 3-3 in FIG. FIG. 4-4 is an arrow view (neutral position) in FIG. 3. 5A-5A line, 5B-5B line and 5C-5C line view of FIG. 3 (neutral position). The figure (UD position) corresponding to the said FIG. FIG. 7 is a view on arrow 7-7 in FIG. 6 (UD position). The figure which shows the eccentric state of the four eccentric discs in a UD position. The figure (OD position) corresponding to the said FIG. FIG. 10 is a view taken along line 10-10 in FIG. 9 (OD position). The figure which shows the eccentric state of four eccentric discs in OD position. The disassembled perspective view of a transmission unit. Explanatory drawing of the drive reaction force which a control shaft receives. Explanatory drawing of the shift control of a continuously variable transmission by a control valve. Explanatory drawing of the shift control from the start of an engine to a stop. The figure which shows the structure of the determination apparatus of the operating state of a one-way clutch. Explanatory drawing of the calculation method of the rotation angle of the outer member of a one-way clutch.

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

  As shown in FIGS. 1 to 5 and 12, the continuously variable transmission T that transmits the driving force of the engine E to the left and right drive wheels W and W is connected in series and coaxially to the crankshaft 11 of the engine E. An input shaft 12 and an output shaft 13 arranged in parallel with the input shaft 12 are provided. The output shaft 13 is connected to the left and right axles 14 and 14 via a differential gear D, and one axle 14 penetrates the inside of the output shaft 13 in a relatively rotatable manner.

  The input shaft 12 and the output shaft 13 are connected by four sets of transmission units 15 that have the same structure and are overlapped in the direction of the axis L of the input shaft 12. The input shaft 12 formed in a crank shape has two journals 17 and 17 that are positioned at both ends and supported by ball bearings 16 and 16, and four journals that are arranged 90 ° out of phase with each other. The crank pins 18 are constituted by five crank webs 19 that integrally connect the journals 17, 17 and the crank pins 18.

  The control shaft 20 slides in the direction of the axis L through the centers of the two journals 17 and 17 of the input shaft 12 and the through holes 19a formed in the five crank webs 19 (see FIGS. 2 and 12). A hydraulic cylinder 22 is connected to one end of the control shaft 20 via a coupling 21 that transmits a thrust force in the direction of the axis L and does not transmit torque.

The hydraulic cylinder 22 is partitioned on both sides of the piston rod 23 disposed on the axis L, the piston 24 fixed to the piston rod 23, the cylinder 25 in which the piston 24 is slidably fitted, and the piston 24. First and second oil chambers 26 and 27 and a return spring 28 that urges the piston 24 in one direction are provided. The oil passage 29 that connects the first and second oil chambers 26 and 27 to each other has a position that allows only the flow of hydraulic oil from the first oil chamber 26 to the second oil chamber 27, and the first and second oil chambers 27 and 27. It consists of a solenoid valve that can select a position that prevents the flow of hydraulic oil between the oil chambers 26 and 27 and a position that only allows the flow of hydraulic oil from the second oil chamber 27 to the first oil chamber 26. Next, the structure of the transmission units 15 will be described with reference to FIGS. 1 to 5 and FIG. 12. Since the four sets of the transmission units 15 have the same structure except that their phases are shifted from each other by 90 ° (see FIGS. 2 and 5), one structure will be described as a representative.

  The transmission unit 15 includes a shallow cup-shaped eccentric disc 31 having a pin hole 31a rotatably supported on the outer periphery of the crank pin 18 of the input shaft 12. The eccentric amount ε of the pin hole 31a with respect to the center O of the eccentric disk 31 is equal to the eccentric amount ε of the crank pin 18 with respect to the axis L of the input shaft (see FIGS. 4 and 8). Therefore, when the eccentric disk 31 is in a predetermined positional relationship with the crank pin 18 of the input shaft 12, the center O of the eccentric disk 31 coincides with the axis L of the input shaft 12. When the eccentric disk 31 swings around the crank pin 18, an arc-shaped long hole 31b centered on the pin hole 31a is formed on the bottom surface of the eccentric disk 31 in order to avoid interference with the control shaft 20.

  A support shaft 33 extending in a direction orthogonal to the crank pin 18 is rotatably supported by a pair of brackets 32, 32 provided on one side surface of the crank web 19 facing the bottom surface of the shallow cup-shaped eccentric disc 31. A pinion 34 and a bevel gear 35 which are coaxially coupled to the support shaft 33 are provided. The pinion 34 meshes with a rack 36 (see FIGS. 4 and 12) formed on the surface of the control shaft 20 in the direction of the axis L, and the bevel gear 35 is formed in an arc shape around the pin hole 31a on the bottom surface of the eccentric disk 31. Meshed with the sector gear 37.

  On the outer peripheral surface of the eccentric disc 31, the inner peripheral surface of one end of the pull side connecting rod 39 and the push side connecting rod 40 is supported via ball bearings 38, 38, respectively. One-way clutches 44, 44 each having an inner member 41, a plurality of rollers 42, and an outer member 43 are supported on the outer periphery of the output shaft 13, and are pulled by a convex portion 43 a provided on the upper portion of one outer member 43. The other end of the side connecting rod 39 is connected via a pin 45, and the other end of the push side connecting rod 40 is connected via a pin 45 to a convex portion 43 b provided at the lower portion of the other outer member 43.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  When the input shaft 12 connected to the crankshaft 11 of the engine E rotates, the four eccentric disks 31 supported by the four crankpins 18 of the input shaft 12 with the pin holes 31a are integrated with the input shaft 12. Rotate to. 2 to 4, the eccentricity of the eccentric discs 31 is zero, and the center O of the eccentric discs 31 coincides with the axis L of the input shaft 12 at the neutral position shown in FIGS. Yes. Accordingly, the four pull-side connecting rods 39 and the four push-side connecting rods 40 supported on the outer peripheral surface of the eccentric disc 31 through the ball bearings 38 do not reciprocate, and the pull-side connecting rods are not reciprocated. Also, the output shaft 13 connected to the 39... And the push side connecting rod 40 through the one-way clutch 44 does not rotate.

  From this state, as shown in FIG. 6, when the piston rod 23 of the hydraulic cylinder 22 moves slightly in the right direction in the drawing (UD position), the control shaft 20 connected to the piston rod 23 via the coupling 21 is moved. The rack 36 formed on the surface moves in the direction of the axis L and rotates the pinion 34 of each transmission unit 15 around the support shaft 33. As a result, the eccentric disc 31 in which the sector gear 37 is meshed with the bevel gear 35 rotating integrally with the pinion 34 swings around the crank pin 18 of the input shaft 12, and as shown in FIG. Is eccentric from the axis L of the input shaft 12 by the amount of eccentricity ε1.

  As a result, the pull-side connecting rod 39 and the push-side connecting rod 40 supported on the outer peripheral surface of the eccentric disc 31 via ball bearings 38 and 38 reciprocate with a stroke twice the eccentric amount ε1. In FIG. 7, when the pull-side connecting rod 39 is pulled to the right side in the drawing, the rollers 42 are engaged between the inner member 41 and the outer member 43 and the one-way clutch 44 is engaged, and the pull-side connecting rod 39 is shown in FIG. When pushed to the middle left, the rollers 42 slip and the one-way clutch 44 is disengaged.

  When the push side connecting rod 40 is pushed to the left in the figure, the rollers 42 are engaged between the inner member 41 and the outer member 43 and the one-way clutch 44 is engaged, so that the push side connecting rod 40 is on the right side in the figure. When pulled, the rollers 42 slip and the one-way clutch 44 is disengaged. Thus, when the pull-side connecting rod 39 and the push-side connecting rod 40 are reciprocated by the eccentric disc 31 as the input shaft 12 rotates, the pull-side connecting rod 39 is pulled and the push-side connecting rod 40 is pushed. Accordingly, the output shaft 13 rotates intermittently.

  As is apparent from FIG. 8, the four eccentric disks 31 of the four sets of transmission units 15 are out of phase with each other by 90 °, so that the four sets of transmission units 15 are rotated during the rotation of the input shaft 12. Any one of the sets always transmits the driving force, so that the output shaft 13 rotates continuously. The rotation of the output shaft 13 is transmitted to the left and right drive wheels W and W via the differential gear D and the left and right axles 14 and 14. At this time, since the eccentric amount ε1 of the eccentric discs 31 is small, the pull side connecting rods 39 and the push side connecting rods 40 reciprocate with a small stroke, and the output shaft 13 does not rotate with a large torque and a small rotational speed. The step transmission T is in the UD position (maximum gear ratio state).

  As shown in FIG. 9, when the piston rod 23 of the hydraulic cylinder 22 further moves to the right in the drawing beyond the UD position, the OD position (minimum speed ratio state) is reached, and the eccentric disc 31 is moved to the crank pin 18 of the input shaft 12. As shown in FIG. 10, the center O of the eccentric disk 31 is eccentric from the axis L of the input shaft 12 by an eccentric amount ε2 that is larger than the eccentric amount ε1 at the UD position.

  As a result, the pull-side connecting rod 39 and the push-side connecting rod 40 supported on the outer peripheral surface of the eccentric disc 31 via ball bearings 38 and 38 reciprocate with a stroke twice the eccentric amount ε2, The pull-side connecting rod 39 and the push-side connecting rod 40 reciprocate with a larger stroke than in the UD position, and the output shaft 13 rotates at a small torque and a large rotational speed so that the transmission gear ratio of the continuously variable transmission T becomes OD. Become.

  As described above, the position of the control shaft 20 is continuously controlled by the hydraulic cylinder 22 so that the transmission ratio of the continuously variable transmission T can be set to the neutral position and the OD position without requiring a special actuator such as an electric motor. Stepless control can be performed between them, and the number of parts and cost can be reduced. In addition, the eccentric discs 31 are swingably supported by the crank pins 18 of the input shaft 12, so that the eccentric discs 31 can be firmly supported to ensure stable transmission performance and durability performance.

  By the way, the hydraulic cylinder 22 of the present embodiment does not require a special drive source such as a hydraulic pump or an electric motor, and operates by a reaction force that the control shaft 20 receives from the eccentric discs 31. Hereinafter, the operation of the hydraulic cylinder 22 will be described.

  As shown in FIG. 13, when the one-way clutch 44 is engaged and the pull-side connecting rod 39 transmits a driving force, the pull-side connecting rod 39 receives a reaction torque from the one-way clutch 44 to the eccentric disc 31. Act. Similarly, when the one-way clutch 44 is engaged and the push-side connecting rod 40 transmits driving force, reaction torque is applied to the eccentric disc 31 by the driving reaction force received by the push-side connecting rod 40 from the one-way clutch 44. . These two reaction torques are both sinusoidal and out of phase with each other by approximately 180 °. The control shaft 20 is moved from the eccentric disk 31 via the sector gear 37, bevel gear 35, pinion 34 and rack 36 in the direction of the axis L. It acts to push and pull in both directions.

  When the thrust forces of the control shaft 20 due to the two reaction torques received by the four eccentric disks 31 are all superimposed, a waveform with 90 ° as one cycle is obtained, and in each cycle of 90 °, the control shaft 20 is pushed and pulled in the direction in which the gear ratio is changed to the OD side and the direction in which the gear ratio is changed to the UD side.

  FIG. 14 shows a control method of the gear ratio of the continuously variable transmission T by the control valve 30. In the figure, the hold area is the area where the transmission ratio is held, the UD side shift area is the area where the transmission ratio is downshifted from the OD side to the UD side, and the OD side shift area is upshifted from the UD side to the OD side. It is an area.

  In the hold region, the communication between the first and second oil chambers 26 and 27 is blocked by turning off both the pair of solenoids 46 and 47 that operate the control valve 30. As a result, the hydraulic cylinder 22 is locked, the control shaft 20 is locked so as not to move, and the gear ratio is held.

  In the UD side shift region, by turning on one solenoid 46, the first and second oil chambers 26 and 27 are communicated with each other via one check valve. As a result, during the period in which the control shaft 20 is biased to the UD side, the hydraulic oil pushed out from the first oil chamber 26 passes through the control valve 30 and flows into the second oil chamber 27 on the opposite side, and the control is performed. Since the hydraulic cylinder 22 is locked during the period in which the shaft 20 is biased toward the OD side, the control shaft 20 moves intermittently toward the UD side.

  In the OD side shift region, the first and second oil chambers 26 and 27 are communicated with each other via the other check valve by turning on the other solenoid 47. As a result, during a period in which the control shaft 20 is urged to the OD side, the hydraulic oil pushed out from the second oil chamber 27 passes through the control valve 30 and flows into the first oil chamber 26 on the opposite side, and is controlled. Since the hydraulic cylinder 22 is locked during the period in which the shaft 20 is biased toward the UD side, the control shaft 20 moves intermittently toward the OD side.

  As described above, according to the present embodiment, the speed change ratio can be changed by operating the control shaft 20 by the driving reaction force received from the eccentric discs 31. It becomes unnecessary and the number of parts and cost can be reduced.

  By the way, when the gear ratio of the continuously variable transmission T is infinite and the eccentric amount of the eccentric discs 31 is zero, the pull side connecting rod 39 and the push side connecting rod 40 stop without reciprocating. ing. Therefore, the control shaft 20 is not pushed or pulled in the direction of the axis L, and the vehicle cannot be started because the gear ratio cannot be shifted from an infinite state to a finite state. .

  Further, when the continuously variable transmission T reduces the engine speed when the vehicle is traveling at a finite speed ratio, the one-way clutch 44 is disengaged and the pull side connecting rod 39 and the push side connecting rod 40. There is a problem that the driving force is not transmitted, and the speed change by the reaction force becomes impossible and the speed ratio cannot be returned to infinity via UD.

  Therefore, in the present embodiment, the above problem is solved by the following method. As shown in FIG. 15, since the weight distribution is set so that the gravity center position G of each eccentric disk 31 is eccentric from the center O by a distance ε3, the eccentric disk 31 is eccentric in a state where the gear ratio is infinite. Even when the center O of the disk 31 rotates in line with the axis L, a moment is generated that causes the eccentric disk 31 to swing by the centrifugal force acting on the gravity center position G.

  Further, since the eccentric disk 31 has a predetermined moment of inertia, when the rotational speed of the input shaft 12 increases, that is, when the angular acceleration of the input shaft 12 increases, the moment that urges the eccentric disk 31 toward the rotational direction delay side is increased. When the rotational speed of the input shaft 12 decreases, that is, when the angular acceleration of the input shaft 12 decreases, a moment is generated that biases the eccentric disk 31 toward the forward side in the rotational direction.

  Now, when the engine E is started at time t1 in FIG. 15, the speed ratio of the continuously variable transmission T is infinite and no driving force is transmitted, and the eccentricity of the eccentric discs 31 is zero. The pull side connecting rods 39 and the push side connecting rods 40 are not subjected to a driving reaction force for shifting. At this time, the load for urging the control shaft 20 includes the elastic force (UD side) of the return spring 28 of the hydraulic cylinder 22, the centrifugal force (OD side) acting on the eccentric center of gravity G of the eccentric disc 31, and the eccentric. The inertial force (according to acceleration / deceleration of the rotation of the disk 31) (OD side during acceleration, UD side during deceleration).

  The return spring 28 is arranged so as to bias the control shaft 20 toward the UD side, and in the event that an oil passage 29 connecting the first and second oil chambers 26 and 27 is lost, By urging the control shaft 20 to the UD side by the return spring 28, the vehicle speed can be reduced to ensure safety.

  Even if the solenoid 47 is turned on at time t1 to change the gear ratio from infinity to the OD side, the load acting on the eccentric disc 31 at that time is only the elastic force of the return spring 28 toward the UD side. The gear ratio is held in an infinite state without changing. When the sum of the centrifugal force and the inertial force exceeds the elastic force of the return spring 28 at time t2 due to the subsequent acceleration of the engine E, the transmission ratio starts to change from infinity to the OD side and starts to change from the input shaft 12 to the output shaft. Transmission of the driving force to 13 is started, and the OD position is reached at time t3.

  When the solenoid 46 is turned on at time t4 to change the gear ratio to the UD side, the pull-side connecting rod 39 and the push-side connecting rod 40 have already received a periodic driving reaction force due to transmission of the driving force. The gear ratio changes from the OD toward the UD side by the driving reaction force. During a cruise from time t5 to time t6, both solenoids 46 and 47 are turned off and the transmission ratio is held.

  When the solenoid 46 is turned on to reduce the engine speed at time t7 and decelerate the vehicle and further change the gear ratio to the UD side, the load that biases the eccentric disc 31 to the UD side is The elastic force and the inertial force accompanying the deceleration of the rotation of the eccentric disk 31, and the load that urges the eccentric disk 31 to the OD side is a centrifugal force that acts on the gravity center position G of the eccentric disk 31. At time t7, the shift to the UD side starts when the sum of the elastic force of the return spring 28, which is the urging force to the UD side, and the centrifugal force, which is the urging force to the OD side, exceeds the centrifugal force. Even after the engine E is stopped at time t8, the shift toward the UD side is continued by the resilient force of the return spring 28, and the neutral position is reached at time t9 to complete the shift.

  Note that when the engine E is started at time t1, the speed of the foot shaft (vehicle speed) has already exceeded zero because the vehicle of the present embodiment is a hybrid vehicle and the drive wheels W connected to the engine E , W is traveling by driving a drive wheel different from W.

  As shown in FIG. 16, the cable 48 having one end bonded to the outer member 43 of the one-way clutch 44 of each transmission unit 15 extends in a direction away from the output shaft 13, passes through the guide member 49, and then reaches the other end. Is connected to a linear position sensor 50 for detecting the position of the cable 48 in the longitudinal direction. In the present embodiment, the cable 48 and the linear position sensor 50 on the other end side from the guide member 49 are arranged on a straight line passing through the center of the output shaft 13. As the linear position sensor 50, for example, an inexpensive stroke sensor is suitable.

  A rotor 51 having a large number of protrusions on the outer periphery is fixed to the output shaft 13, and a detection head 52 made of a Hall element is provided so as to face the rotor 51. The rotor 51 and the detection head 52 constitute an inner member angular velocity detecting means 53 for detecting the angular velocity of the output shaft 13, that is, the angular velocity of the inner member 41 of the one-way clutch 44. The inner member angular velocity detecting means 53 is a well-known one, and a magnetic change caused by the rotation of the magnetic rotor 51 is detected by the detection head 52, and the angular velocity of the inner member 41 is determined based on the time interval of the pulse signal output from the detection head 52. Is detected.

  Note that the vehicle of the present embodiment is a hybrid vehicle, and the reverse travel is performed by driving the drive wheels other than the drive wheels W, W connected to the engine E in reverse rotation with a motor. During operation, the output shaft 13 does not reverse in the reverse direction. Therefore, the inner member angular velocity detection means 53 only needs to detect the angular velocity in one direction (forward direction) of the output shaft 13, and it is not necessary to employ an expensive angular velocity sensor that detects the angular velocity in both directions (forward direction and backward direction). .

  The linear position sensor 50 is connected to outer member rotation angle calculation means M1 that calculates the rotation angle of the outer member 43 of the one-way clutch 44, and the outer member rotation angle calculation means M1 calculates outer member angular velocity calculation means that calculates the angular velocity of the outer member 43. Connected to M2. Inner member angular velocity detection means 53 that detects the angular velocity of the inner member 41 of the one-way clutch 44 and outer member angular velocity calculation means M2 are connected to an engagement state determination means M3 that determines the engagement state of the one-way clutch 44. Outer member angular velocity calculation means M2, engagement state determination means M3, and inner member angular velocity detection means 53 are connected to torque calculation means M4 for calculating the torque transmitted by one-way clutch 44.

  FIG. 17 illustrates the function of the outer member rotation angle calculation means M1 that calculates the rotation angle of the outer member 43 of the one-way clutch 44.

  In the drawing, R is the radius of the outer member 43 of the one-way clutch 44, and X is the cable 48 between the guide member 49 and the outer member 43 when the cable 48 is positioned on a straight line passing through the center of the output shaft 13 (reference position). Length, α is a rotation angle of the outer member 43 from the reference position, β is a rotation angle of the cable 48 from the reference position, and X ′ is a length when the cable 48 is rotated by an angle β.

The radius R and the length X are known numbers, the length X ′ can be detected by the linear position sensor 50, and the angles α and β are unknown. Between these R, X, X ', α and β,
X′sinβ = Rsinα (1)
X ′ cos β + R cos α = X + R (2)
Is established,
When the equation (2) is transformed, the following equation is obtained,
X ′ cos β = X + R−R cos α (3)
The following equation is obtained by squaring sides of equation (1),
X ′ ² sin ² β = R ² sin ² α (4)
When the equation (3) is squared on each side, the following equation is obtained.

X ′ ² cos ² β = X ² + R ² + R ² cos ² α + 2XR
-2R ² cosα-2XRcosα (5)
When the formulas (4) and (5) are added together and rearranged using the relationship of sin ² α + cos ² α = 1 and the relationship of sin ² β + cos ² β = 1, the following formula is obtained.

cos α = (X ² −X ′ ² + 2R ² + 2XR) / (2R ² + 2XR) (6)
Since the radius R and length X of the right side of equation (6) are known numbers and the length X ′ can be detected, α on the left side, that is, the rotation angle α of the outer member 43 is calculated by the following equation.

α = cos ⁻¹ (X ² −X ′ ² + 2R ² + 2XR) / (2R ² + 2XR) (7)
As described above, by detecting the length X ′ by the linear position sensor 50, the rotation angle α of the outer member 43 of the one-way clutch 44 that reciprocates at short time intervals can be calculated in real time by the outer member rotation angle calculation means M1. Can be calculated. In addition, since an inexpensive linear position sensor 50 that requires an expensive rotational speed sensor having a function of identifying the rotational direction at that time can be used, the cost is low.

  The eight one-way clutches 44 of the continuously variable transmission T are engaged when the pull-side connecting rod 39 performs a pull operation and are engaged when the push-side connecting rod 40 performs a push operation. Then, the outer member 43 and the inner member 41 are engaged and disengaged depending on the angular velocity in the forward direction. Specifically, the one-way clutch 44 is engaged when the angular velocity in the forward direction of the outer member 43 is larger than the angular velocity in the forward direction of the inner member 41, and the angular velocity in the forward direction of the outer member 43 is the forward direction of the inner member 41. The one-way clutch 44 is disengaged when the angular velocity is smaller than the angular velocity.

  Therefore, the outer member angular velocity calculation means M2 calculates the angular velocity of the outer member 43 by time-differentiating the rotation angle α of the outer member 43 calculated by the outer member rotation angle calculation means M1, and the angular velocity of the outer member 43 is calculated as the inner member. By comparing with the angular velocity of the inner member 41 detected by the angular velocity detecting means 53, the engagement state determining means M3 can determine in real time whether the one-way clutch 44 is in the engaged state or in the disengaged state. .

  The torque transmitted by the one-way clutch 44 is proportional to the twist angle between the outer member 43 and the inner member 41 due to the torque. Based on this principle, the torque calculation means M4 calculates the twist angle as a difference between the rotation angle of the outer member 43 and the rotation angle of the inner member 41 from the moment when the one-way clutch 44 is engaged, and based on the twist angle. The torque transmitted by the one-way clutch 44 is calculated in real time.

  Therefore, even when the eight one-way clutches 44 are in a state where the driving force is transmitted to the common output shaft 13 with different phases, the individual one-way clutches 44 are in the engaged state or in the disengaged state. Or how much torque each individual one-way clutch 44 is transmitting can be accurately known in real time.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, in the embodiment, the one-way clutch 44 is applied to the continuously variable transmission T, but the use of the one-way clutch of the present invention is arbitrary.

41 Inner member 42 Roller 43 Outer member 44 One-way clutch 48 Cable 49 Guide member 50 Linear position sensor 53 Inner member angular velocity detection means M1 Outer member rotation angle calculation means M2 Outer member angular velocity calculation means M3 Engagement state determination means M4 Torque calculation means

Claims (3)

An outer member (43) that reciprocates, an inner member (41) that is coaxially disposed radially inward of the outer member (43), an inner peripheral surface of the outer member (43), and the inner member (41) A plurality of rollers (42) disposed between the outer peripheral surfaces of the outer member (43), the outer member (43) transmits a driving force to the inner member (41) when rotating in one direction, and the outer member (43) ) Is a one-way clutch that slips against the inner member (41) when rotating in the other direction,
A cable (48) having one end bonded to the outer member (43), a guide member (49) for guiding the other end of the cable (48) so as to be capable of reciprocating linear movement, and the guide member (49) A linear position sensor (50) for detecting the position of the cable (48) to be guided, and an outer member rotation angle calculation means (for calculating the rotation angle of the outer member (43) based on the position of the cable (48)) M1) and a one-way clutch.   The inner member angular velocity calculating means (53) for calculating the angular velocity of the inner member (41) and the outer member (43) from the rotation angle of the outer member (43) calculated by the outer member rotation angle calculating means (M1). The outer member angular velocity calculating means (M2) for calculating the angular velocity of the inner member (41) detected by the inner member angular velocity detecting means (53) and the outer member angular velocity calculating means (M2). The one-way clutch according to claim 1, further comprising engagement state determination means (M3) for comparing the angular velocity of the member (43) and determining the engagement state of the one-way clutch (44).   The rotation angle calculated by integrating the angular velocity of the outer member (43) from the moment when the engagement state determination means (M3) determines the engagement of the one-way clutch (44), and the engagement state determination means (M3) ) Is compared with the rotation angle calculated by integrating the angular velocity of the inner member (41) from the moment when the engagement of the one-way clutch (44) is determined, and the one-way clutch (44) is calculated from the difference between the two rotation angles. The one-way clutch according to claim 2, further comprising torque calculating means (M4) for calculating torque transmitted by the motor.

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