WO2014073479A1 - 自動変速装置 - Google Patents
自動変速装置 Download PDFInfo
- Publication number
- WO2014073479A1 WO2014073479A1 PCT/JP2013/079708 JP2013079708W WO2014073479A1 WO 2014073479 A1 WO2014073479 A1 WO 2014073479A1 JP 2013079708 W JP2013079708 W JP 2013079708W WO 2014073479 A1 WO2014073479 A1 WO 2014073479A1
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- WIPO (PCT)
- Prior art keywords
- clutch
- power transmission
- transmission system
- coupling mechanism
- direct coupling
- Prior art date
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19019—Plural power paths from prime mover
Definitions
- the present invention relates to an automatic transmission, and more specifically to an automatic transmission including two types of power transmission systems including a continuously variable transmission (CVT) and a direct connection mechanism.
- CVT continuously variable transmission
- the continuously variable transmission is almost OD ratio on suburban roads and highways, and OD has the highest ratio frequency over the entire run. Therefore, by providing a direct connection mechanism and setting the OD to the direct connection mode via the direct connection mechanism, fuel efficiency can be improved in suburban roads and highway driving.
- the OD ratio has a small winding diameter on the driven pulley side and a high bending stress of the ring. Therefore, it is possible to improve the durability of the belt by traveling directly with the OD having the highest traveling frequency. it can. However, even if the torque is not transmitted, the belt / pulley only rotates and generates a loss torque, and the ring is bent and fatigued. Therefore, it is necessary to make the belt / pulley non-rotating during direct connection.
- a drive pulley connected to an input shaft connected to a drive source mounted on a vehicle via a first clutch, and a second output shaft connected to a drive wheel.
- a continuously variable transmission having a driven pulley connected via a clutch and an endless flexible member hung between them, and a continuously variable transmission arranged in parallel therewith, directly connecting the input shaft and the output shaft to fix the rotation of the input shaft
- a direct coupling mechanism (chain or gear type) that transmits to the output shaft at a (predetermined) gear ratio, and a first power transmission system by a continuously variable transmission or a second power transmission system by a direct coupling mechanism can be established.
- a configured automatic transmission has been proposed.
- a direct coupling mechanism that establishes a second power transmission system is connected to an output shaft via a third clutch, and when the first power transmission system is established, the first clutch and the second clutch are engaged.
- the third clutch is engaged, and the third clutch is engaged to release the first clutch and the second clutch.
- the continuously variable transmission is usually set based on the maximum rotational speed of the driving source and the output shaft based on the maximum vehicle speed that can be reached on a flat ground, and the pulley deceleration ratio (Top) of the maximum vehicle speed is Since it is set to a value larger than OD, in the technique described in Patent Document 1, since the direct coupling mechanism is connected to the output shaft by the third clutch, the rotational speed input to the third clutch is high. There was an inconvenience.
- an object of the present invention is to solve the above-mentioned inconvenience, and in an automatic transmission having two types of first and second power transmission systems comprising a continuously variable transmission and a direct coupling mechanism, the second power transmission system by the direct coupling mechanism. It is an object of the present invention to provide an automatic transmission that reduces the rotation input to a third clutch that establishes the above.
- an input shaft connected to a drive source mounted on a vehicle, an output shaft connected to drive wheels, and a first clutch on the input shaft.
- a continuously variable transmission having a drive pulley connected to the output shaft, a driven pulley connected to the output shaft via a second clutch, and an endless flexible member hung between them; and parallel to the continuously variable transmission
- a direct connection mechanism that directly connects the input shaft and the output shaft to transmit the rotation of the input shaft to the output shaft at a predetermined speed ratio, and the first power transmission system by the continuously variable transmission and the direct connection
- a control means for controlling establishment of a second power transmission system by the mechanism, wherein the predetermined gear ratio of the direct coupling mechanism is set to a minimum gear ratio of the continuously variable transmission, and the direct coupling mechanism is the input Connect to shaft via third clutch
- the control means engages the first clutch and the second clutch and releases the third clutch, while establishing the second power transmission system.
- the third clutch is
- the control means gradually engages the second clutch while the second power transmission system is established. Then, when it is determined that the rotational speed of the direct coupling mechanism and the rotational speed of the drive pulley of the continuously variable transmission are substantially synchronized, the third clutch is released and the first clutch is engaged. Configured.
- the continuously variable transmission is a transmission that operates by supplying hydraulic oil to the drive pulley and the driven pulley, and the control means includes the second power transmission. While the system was established, the pressure of the hydraulic oil to be supplied to the drive pulley and the driven pulley was reduced to a predetermined pressure.
- the automatic transmission according to claim 5 is configured such that the predetermined pressure is a pressure sufficient to maintain the transmission ratio.
- the direct transmission mechanism is arranged in parallel with the continuously variable transmission and directly connects the input shaft and the output shaft to transmit the rotation of the input shaft to the output shaft at a predetermined speed ratio.
- the predetermined gear ratio is set to the minimum gear ratio of the continuously variable transmission
- the direct coupling mechanism is connected to the input shaft via the third clutch, that is, the input in which the rotation of the direct coupling mechanism is decelerated with respect to the output shaft. Since the third clutch is arranged on the shaft side, when power is transmitted by the first power transmission system by the continuously variable transmission, the decelerated rotation is input to the third clutch, and the direct coupling mechanism
- the rotational speed input to the clutch (third clutch) that establishes the second power transmission system can be reduced.
- FIG. 12 is a schematic diagram partially showing the configuration of the technique described in Patent Document 1, and FIG. It is explanatory drawing which shows the relationship of engine speed NE. It is.
- Patent Document 1 is a drive pulley connected to an input shaft via a first clutch, a driven pulley connected to an output shaft via a second clutch, and a belt ( An endless flexible member) is arranged in parallel with the CVT, and the input shaft and the output shaft are directly connected to rotate the input shaft at a predetermined (fixed) speed ratio, for example, an OD ratio.
- a direct-coupled mechanism that shifts and transmits the output to the output shaft, and is configured to establish a first power transmission system by CVT or a second power transmission system by the direct-coupled mechanism, and the direct-coupled mechanism is connected to the output shaft via a third clutch.
- a third clutch are configured to connect.
- the belt type CVT sets a reduction ratio and a speed increase ratio of approximately the same value centering on a 1: 1 ratio, and as shown in FIG. 13, the ratio when reaching the maximum vehicle speed on a flat ground.
- Is defined as iTop, iTop is set to a value larger than iOD (i: pulley ratio).
- the automatic transmission according to claim 1 has a configuration similar to that of Patent Document 1 as shown in FIG. 1 and sets the predetermined transmission ratio of the direct connection mechanism to the minimum transmission ratio of the CVT. Is connected to the input shaft via the third clutch, and when establishing the first power transmission system, the first clutch and the second clutch are engaged, while when establishing the second power transmission system, the third clutch And the second clutch is released.
- FIG. 2 is an explanatory diagram showing the relationship between the output shaft rotational speed (vehicle speed) V and the input shaft rotational speed (engine rotational speed) NE of the automatic transmission according to claim 1.
- the direct coupling mechanism When the predetermined gear ratio of the direct coupling mechanism is set to the OD (minimum gear ratio) of the CVT, the direct coupling mechanism is connected to the input shaft via the third clutch, and when the first power transmission system is established, the first clutch and the first clutch As a result of engaging the two clutches, when establishing the first power transmission system, a lower rotational speed than the output shaft rotational speed is transmitted to the input shaft side direct coupling mechanism. The rotation of the direct connection mechanism is decelerated.
- the first clutch and the second clutch are engaged and the third clutch is released, while when the second power transmission system is established, the third clutch is engaged. Since the first clutch and the second clutch are configured to be released, when the second power transmission system is established, the continuously variable transmission can be disconnected from the drive source to be non-rotated to reduce the load on the drive source. it can.
- the third transmission is established when the speed ratio of the continuously variable transmission becomes the minimum speed ratio (OD) in the first power transmission system. Since the second clutch is gradually released when it is judged that the first clutch is released and then the second power transmission system is established while engaging the clutch, in addition to the above-described effects, the direct coupling mechanism Since the third clutch is engaged with the rotational speed of the continuously variable transmission and the rotational speed of the drive pulley of the continuously variable transmission synchronized, the second power transmission system is established in a short time without shocking the occupant. In other words, the first power transmission system can be switched to the second power transmission system in a short time.
- the second clutch when the first power transmission system is established, the second clutch is gradually engaged while the second power transmission system is established, and then the rotation of the direct coupling mechanism is performed.
- the third clutch is disengaged and the first clutch is engaged. Since the third clutch is released while the rotational speed of the direct coupling mechanism and the rotational speed of the drive pulley of the continuously variable transmission are synchronized, the first power transmission system is established in a short time without shocking the passenger. In other words, the second power transmission system can be switched to the first power transmission system in a short time.
- the second clutch is gradually engaged while the second power transmission system is established, the rising speed of the pulley rotation of the continuously variable transmission can be slowed, and the inertia shock can be reduced. The passengers will not be shocked.
- the continuously variable transmission maintains the OD ratio while the second power transmission system is established, the ratio adjustment at the time of transition becomes unnecessary, and the transition time can be shortened.
- the continuously variable transmission is a transmission that operates by supplying hydraulic oil to the drive pulley and the driven pulley, and while the second power transmission system is established, Since the pressure of the hydraulic oil to be supplied to the drive pulley and the driven pulley is reduced to a predetermined pressure, fuel efficiency can be improved in addition to the above effects.
- the pulley of the continuously variable transmission is shut off at the input and output, so that the loss associated with the rotation of the endless flexible member and the pulley can be almost eliminated, and the drive
- the pulley pressure to be supplied to the pulley and the driven pulley can be lowered to a predetermined pressure.
- the hydraulic pump pressure can be reduced, and the hydraulic pump loss can be reduced to improve fuel efficiency.
- the automatic transmission according to claim 5 is configured such that the predetermined pressure is sufficient to maintain the transmission ratio (ratio).
- the pressure can be further reduced to further improve fuel efficiency. Can be made.
- the pulley and the endless flexible member maintain the OD ratio state, interference, backlash, and hitting sound of each part do not occur.
- FIG. 1 is a schematic diagram showing an entire automatic transmission according to a first embodiment of the present invention.
- FIG. FIG. 2 is an explanatory diagram showing a relationship between an output shaft rotational speed (vehicle speed) V and an input shaft rotational speed (engine rotational speed) NE of the automatic transmission device shown in FIG. 1. It is explanatory drawing of the torque flow when establishing a 2nd power transmission system in the automatic transmission apparatus shown in FIG. It is explanatory drawing of the torque flow when establishing a 1st power transmission system in the automatic transmission apparatus shown in FIG. 3 is a time chart showing an operation when a second power transmission system is established in the automatic transmission shown in FIG. 1. 2 is a time chart showing an operation when a first power transmission system is established in the automatic transmission device shown in FIG. 1.
- FIG. 8 is a time chart showing an operation when a second power transmission system is established in the automatic transmission device shown in FIG. 7.
- FIG. 8 is a time chart showing an operation when the first power transmission system is established in the automatic transmission device shown in FIG. 7.
- FIG. 7 is the schematic which shows partially the automatic transmission which concerns on 3rd Example of this invention.
- It is explanatory drawing which shows the relationship between the output shaft rotational speed (vehicle speed) V and the input shaft rotational speed (engine rotational speed) NE of the automatic transmission apparatus shown in FIG.
- It is the schematic which shows partially the automatic transmission which concerns on patent document 1 description technique.
- It is explanatory drawing which shows the relationship between the output-shaft rotational speed (vehicle speed) V and the input-shaft rotational speed (engine rotational speed) NE of the automatic transmission apparatus shown in FIG.
- FIG. 1 is a schematic diagram showing the overall automatic transmission according to the first embodiment of the present invention.
- FIG. 2 shows an output shaft rotational speed (vehicle speed) V and an input shaft rotational speed (engine rotational speed) of the configuration shown in FIG. It is explanatory drawing which shows the relationship of NE.
- reference numeral 10 denotes an automatic transmission.
- An input shaft 12 of the automatic transmission 10 is connected to an engine (internal combustion engine, drive source) 14.
- the engine 14 is mounted on a vehicle 20 (partially indicated by the drive wheels 16 or the like) 20 having drive wheels 16.
- the input shaft 12 is connected to the engine 10 via a starting mechanism 22 and a forward / reverse switching mechanism 24 on the one hand, and a continuously variable transmission (Continuously Variable Transmission, hereinafter referred to as “CVT”) 26 on the other hand.
- CVT Continuous Variable Transmission
- the start mechanism 22 includes a torque converter or a start clutch
- the forward / reverse switching mechanism 24 includes a forward clutch that allows the vehicle 20 to travel in the forward direction, a reverse brake clutch that enables the vehicle 20 to travel in the reverse direction, It consists of the planetary gear mechanism arrange
- the input shaft 12 is connected to the pulley input shaft 12a via the first clutch 30, and the output shaft 32 arranged in parallel to the input shaft 12 is connected to the pulley output shaft 32a via the second clutch 34.
- the CVT 26 includes a drive pulley 26a connected to the pulley input shaft 12a, a driven pulley 26b connected to the pulley output shaft 32a, and an endless flexible member, for example, a metal V-belt 26c.
- the first clutch 30 and the second clutch 34 are both wet hydraulic clutches (friction clutches) that are supplied with hydraulic oil (hydraulic pressure) and operate between engagement (fastening) and release (non-fastening).
- the drive pulley 26a has a fixed pulley half that is not rotatable relative to the outer peripheral shaft of the pulley input shaft 12a and is not movable in the axial direction, and a fixed pulley half that is not rotatable relative to the outer peripheral shaft. It consists of a movable pulley half that can move in the axial direction.
- the driven pulley 26b is also fixed to the outer peripheral shaft of the pulley output shaft 32a so as not to rotate relative to the outer periphery of the pulley, and to the axial movement of the stationary pulley 26b. It consists of possible movable pulley halves.
- the rotation of the output shaft 32 is transmitted to the intermediate shaft 40 through the gear 36 (the driving gear 36a and the driven gear 36b), and the rotation is transmitted from the differential 44 to the left and right driving wheels (only the left side is shown) 16 through the gear 42. It is done.
- the automatic transmission 10 includes a direct coupling mechanism 46 arranged in parallel with the CVT 26.
- the direct coupling mechanism 46 includes a chain type transmission device, and directly couples the input shaft 12 and the output shaft 32 to shift the rotation of the input shaft 12 at a fixed (predetermined) gear ratio and transmit the rotation to the output shaft 32.
- the fixed gear ratio of the direct coupling mechanism 46 is set to the minimum gear ratio (OD ratio) of the CVT 26.
- the direct connection mechanism 46 is connected to the input shaft 12 via the third clutch 50.
- the third clutch 50 is a hydraulic clutch (friction clutch).
- the automatic transmission 10 transmits the power of the engine 14.
- paths for transmitting to the drive wheels 16 there are provided two types of paths including a first power transmission system by CVT 26 (via) and a second power transmission system by direct connection mechanism 46 (via).
- the input shaft 12 is provided with an input shaft rotational speed sensor 54, which outputs a pulse signal indicating the rotational speed of the input shaft 12 input to the CVT 26, and an NDR sensor (rotational speed sensor) in the vicinity of the drive pulley 26a of the CVT 26. ) 56 is provided to output a pulse signal corresponding to the rotational speed of the drive pulley 26a (rotational speed of the pulley input shaft 12a) NDR.
- An NDN sensor (rotational speed sensor) 60 is provided in the vicinity of the driven pulley 26b to output a pulse signal indicating the rotational speed NDN of the driven pulley 26b, and an output shaft rotational speed sensor 62 is provided on the output shaft 32. Then, a pulse signal indicating the rotational speed (and the vehicle speed V, more precisely the vehicle speed before being corrected with the final ratio) on the output side of the direct coupling mechanism 46 is output.
- the hydraulic pressure switch 64 is provided in the first clutch 30 to generate an output indicating engagement / release of the first clutch 30, and the hydraulic switch 66 is also provided in the third clutch 50 to engage the third clutch 50. Generates output indicating merge / release.
- the automatic transmission 10 is provided with a hydraulic circuit 70 and a shift controller 72.
- the hydraulic circuit 70 includes a hydraulic pump (oil feed pump, not shown).
- the hydraulic pump is driven by the engine 14 to pump up the hydraulic oil stored in the reservoir and discharge it to the oil passage.
- Various electromagnetic control valves are arranged in the oil passage.
- the output of the NT sensor 54 and the like described above is sent to the shift controller 72.
- the shift controller 72 includes a microcomputer including a CPU, ROM, RAM, I / O, and the like.
- the engine 14 includes a microcomputer, and includes an engine controller 74 that controls the operation of the engine 14 based on outputs from various sensors such as a crank angle sensor.
- the shift controller 72 is communicably connected to the engine controller 74, and excites and demagnetizes the electromagnetic control valve of the hydraulic circuit 70 based on the input output of the NT sensor 54 and the sensor output obtained by communicating with the engine controller 74.
- the hydraulic pressure supply to the starting mechanism 22, the forward / reverse switching mechanism 24, the CVT 26, the CVT 26 for controlling the operations of the first and second clutches 30 and 34, and the like are controlled to control the operation.
- the shift controller 72 supplies a high pressure hydraulic oil to the piston chamber of the movable pulley half through the hydraulic circuit 70, for example, for the CVT 26, and generates a pulley pressure (clamping force) that moves the movable pulley half in the axial direction. generate. Accordingly, the pulley widths of the drive pulley 26a and the driven pulley 26b change, the winding radius of the belt 26c changes, and the ratio (transmission ratio) for transmitting the output of the engine 14 to the drive wheels 16 can be changed steplessly. .
- the ratio is changed steplessly between the maximum gear ratio Low ratio (iLow) and the minimum gear ratio OD ratio (direct coupling ratio (iOD)) according to the pulley pressure.
- the shift controller 72 functions as a switching control unit that controls switching between the first and second power transmission systems.
- FIG. 3 establishes the second power transmission system, in other words, when switching from the first power transmission system to the second power transmission system
- FIG. 4 establishes the first power transmission system, in other words, from the second power transmission system to the second power transmission system.
- FIG. 5 is an explanatory diagram of torque flow when switching to one power transmission system
- FIG. 5 is an operation of FIG. 3
- FIG. 6 is a time chart showing the operation of FIG.
- the power transmission of the CVT 26 by the first power transmission system is “CVT mode”
- the power transmission of the direct coupling mechanism 46 by the second power transmission system is “direct mode”
- the operations in between are performed.
- the first clutch 30 and the third clutch 50 are referred to as a CVT-direct connection mode switching mechanism
- the second clutch 34 is referred to as a wheel (drive wheel) -CVT connecting / disconnecting mechanism.
- the shift controller 72 controls mode switching (switching of the first and second power transmission systems) from the CVT mode through the transition mode 1 and the transition mode 2 to the direct connection mode.
- the pulleys 26a and 26b are supplied with pulley pressure necessary for gear shifting and torque transmission, and the pulleys 26a and 26b rotate from the outputs of the NDR sensor 56 and the NDN sensor 60. Measure the speed and calculate the ratio.
- the shift controller 72 detects the rotational speed of the input shaft 12 (input rotational speed to the CVT 26) detected from the input shaft rotational speed sensor 54 and the rotational speed detected from the output shaft rotational speed sensor 62 at time t1 in the time chart of FIG.
- the rotational speed of the direct coupling mechanism 46 obtained by correcting the speed with the gear ratio (ratio) of the direct coupling mechanism 46 is compared, and the rotational speed of the input shaft 12 and the rotational speed of the direct coupling mechanism 46 are substantially (or completely) synchronized ( Judgment is made as to whether or not they roughly match.
- the shift controller 72 When it is determined that the shift controller 72 is substantially synchronized at time t2, the shift controller 72 outputs a mode switching signal and quickly switches the switching mechanism (from time t2 to time with the connection / disconnection mechanism (second clutch 34) engaged).
- the CVT 26 side is switched to the direct coupling mechanism 46 side. More specifically, the first clutch 30 is released and the third clutch 50 is engaged to switch from the CVT 26 side to the direct coupling mechanism 46 side.
- the rotational speeds of the CVT 26 side and the direct coupling mechanism 46 side of the input shaft 12 are substantially synchronized, they can be switched in a short time without shocking the occupant.
- the shift controller 72 determines from the output of the hydraulic switch 64 that the first clutch 30 has been released (switched from the CVT 26 side to the direct coupling mechanism 46 side) (time t4), the connecting / disconnecting mechanism (second The hydraulic pressure is gradually discharged from the clutch 34) and gradually released during a time ⁇ T2 from time t4 to time t5. As a result, the pulleys 26a and 26b of the CVT 26 slowly stop rotating without applying inertial shock to the occupant.
- the shift controller 72 determines whether or not the rotation of the pulleys 26a and 26b has stopped from the output of the NDR sensor 56 and / or the NDN sensor 60. Reduce to maintenance pressure (predetermined pressure) and switch to direct connection mode completely.
- the first clutch 30 of the switching mechanism is released (on the direct connection mechanism 46 side), and the connection / disconnection mechanism including the second clutch 34 is also released.
- the CVT 26 is blocked by the input / output, and the rotation is stopped.
- the CVT 26 can maintain the ratio even when the pulley pressure is low, and therefore the CVT 26 is supplied with a pulley pressure that is as low as possible (the ratio maintaining pressure during stoppage) so that the OD ratio can be maintained. Is done. Thereby, a hydraulic pump pressure can be lowered
- the shift controller 72 controls mode switching (switching of the first and second power transmission systems) so that the direct connection mode becomes the CVT mode through the transition mode 3 and the transition mode 4.
- the shift controller 72 switches the mode to shift to the CVT mode. While outputting a signal, the pulley pressure is increased to the pulley pressure required for gear shifting and torque transmission.
- the shift controller 72 starts supplying hydraulic pressure to the connecting / disconnecting mechanism (second clutch 34) of the output shaft 32 at time t1, and gradually engages until time t2 (during time ⁇ T3).
- the pulleys 26a and 26b of the CVT 26 slowly start to rotate without giving an inertia shock to the occupant.
- the shift controller 72 has substantially (or completely) the rotational speed of the input shaft 12 detected from the NT sensor 54 and the rotational speed of the direct coupling mechanism 46 detected from the output shaft rotational speed sensor 62 at time t3 as described above. It is determined whether or not synchronization (substantially coincides) (time t3), and when it is determined that the synchronization is almost complete, the switching mechanism is quickly moved (from time t3 to time t4) from the direct coupling mechanism 46 side to the CVT 26 side. Switch. That is, the first clutch 30 is engaged and the third clutch 50 is released to switch from the direct coupling mechanism 46 side to the CVT 26 side.
- the technique described in Patent Document 1 is based on the drive pulley 26a connected to the input shaft 12 (the pulley input shaft 12a connected to the first clutch 30 via the first clutch 30) and the output shaft 32 ( CVT having a driven pulley 26b connected to a pulley output shaft 32a connected via a second clutch 34 and a belt 26c hung between them, and arranged in parallel with the CVT, the input shaft 12 and the output
- a direct coupling mechanism 46 that directly couples the shaft 32 to change the rotation of the input shaft 12 at a predetermined (fixed) transmission ratio and transmits the rotation to the output shaft 32; and CVT mode (first power transmission system) by the CVT 26 as power transmission
- a direct connection mode second power transmission system
- the direct connection mechanism 46 is connected to the output shaft 32 via the third clutch.
- the predetermined gear ratio of the direct coupling mechanism 46 is set to the OD ratio (minimum gear ratio) of the CVT 26, and the third clutch 50 is attached to the direct coupling mechanism 46 on the input shaft 12.
- the first clutch 30 and the second clutch 34 are engaged.
- the third clutch 50 is engaged, and the first clutch 30 and the second clutch 34 are engaged. Since the two-clutch 34 is configured to be released, as shown in FIG. 1, when the CVT mode is established, the rotational speed of the input shaft 12 which is lower than the rotational speed of the output shaft 32 is applied to the direct coupling mechanism 46 on the input shaft side. Therefore, the rotation of the direct coupling mechanism 46 on the input shaft 12 side is decelerated.
- the third clutch 50 when establishing the direct connection mode, the third clutch 50 is engaged when the transmission ratio of the CVT 26 becomes the minimum transmission ratio (OD) in the CVT mode.
- the first clutch 30 is released (from time t1 to t3), and then, when it is determined that the direct connection mode has been established, the second clutch 34 is gradually released (from time t4 to t5).
- the third clutch is engaged in a state where the rotational speed of the direct coupling mechanism 46 and the rotational speed (NDR) of the drive pulley 26a of the CVT 26 are synchronized (from time t1 to time t4), so that the passenger is shocked. Therefore, the direct connection mode can be established in a short time, in other words, the CVT mode can be switched to the direct connection mode in a short time.
- the second clutch 34 is gradually released (from time t4 to time t5), so that the speed of decrease in pulley rotation of the CVT 26 can be reduced, and inertial shock can be reduced. It can be reduced and the passengers will not be shocked further.
- the pulleys 26a and 26b of the CVT 26 are shut off by input / output, so that the loss due to the rotation of the belt 26c and the pulleys 26a and 26b can be almost eliminated, and until time t5.
- the pulley pressure can be lowered to the stopping ratio maintaining pressure at time t6
- the hydraulic pump pressure can be lowered, the hydraulic pump loss can be reduced, and the fuel consumption can be improved.
- the pulleys 26a, 26b and the belt 26c maintain the OD ratio state, interference, backlash, and hitting sound of each part do not occur.
- the second clutch 34 is gradually engaged (time t1 to t2) while the direct connection mode is established, and then the direct connection is established.
- the third clutch 50 is released and the first clutch is engaged (from time t3 to t4).
- the third clutch 50 is released in a state where the rotational speed of the direct coupling mechanism 46 and the rotational speed of the drive pulley 26a of the CVT 26 are synchronized.
- the CVT mode is established in time, in other words, the direct connection mode can be switched to the CVT mode in a short time.
- the second clutch 34 is gradually engaged (from time t1 to t2) while the direct connection mode is established, the rising speed of the pulley rotation of the CVT 26 can be slowed and inertia shock is reduced.
- the CVT 26 maintains the OD ratio while the direct connection mode is established, and it is not necessary to adjust the ratio at the time of transition, and the transition time can be shortened. .
- FIG. 7 is a schematic diagram partially showing an automatic transmission (indicated by reference numeral 10a) according to a second embodiment of the present invention
- FIG. 8 shows establishment of a direct connection mode in the second embodiment, in other words, a CVT mode
- first FIG. 9 shows the establishment of the CVT mode, in other words, from the direct connection mode (second power transmission system) to the CVT mode (first power transmission system).
- It is a time chart which shows switching.
- the first clutch 30 and the third clutch 50 are hydraulic clutches (friction clutches).
- the first clutch and the third clutch (indicated by reference numerals 30a and 50a) were constituted by mechanical dog clutches having uneven engagement surfaces.
- the shift mechanism 80 is provided on the outer periphery of the first clutch 30a and the third clutch 50a.
- the shift mechanism 80 includes a sleeve 80a (and a shift fork and an actuator, which are not shown), and either the first clutch 30a or the third clutch 50a is connected to the input shaft according to a command from the shift controller 72. 12 (or pulley input shaft 12a).
- a stroke sensor 80b for detecting the displacement is provided in the vicinity of the sleeve 80a.
- the shift mechanism 80 preferably includes a synchronization mechanism that synchronizes rotation, but is not essential.
- the shift controller 72 operates after the time t1 in FIG. 8 or after the time t1 in FIG. 12 and the rotation speed of the direct coupling mechanism 46 are substantially synchronized.
- the switching mechanism first clutch 30a, third clutch 50a, shift mechanism 80
- Is released or engaged more specifically, the first and third clutches 30a and 50a are released or engaged via the shift mechanism 80) and quickly (time) from the CVT 26 side to the direct coupling mechanism 46 side or vice versa. Switch between ⁇ T4).
- the third clutch 50a is a dog clutch
- the engine 14 may be blown up for a moment. Therefore, it is necessary to reduce the output of the engine 14 to prevent the blow-up, but the output reduction time is extremely small. Because it is short and short, it does not give the occupant a feeling of free running.
- the first clutch 30a and the third clutch 50a can be reduced in size and weight.
- the remaining configuration and effects are the same as in the first embodiment.
- FIG. 10 is a schematic view partially showing an automatic transmission (indicated by reference numeral 10b) according to a third embodiment of the present invention
- FIG. 11 is an output shaft rotational speed (vehicle speed) V and an input shaft of the configuration shown in FIG. It is explanatory drawing which shows the relationship of rotational speed (engine rotational speed) NE.
- the automatic transmission according to the third embodiment also has a drive pulley 26a connected to the input shaft 12 (a pulley input shaft 12a connected to the input shaft 12 via the first clutch 30) and an output shaft 32 ( A CVT (continuously variable transmission) 26 having a driven pulley 26b connected to a pulley output shaft 32a) connected to the second clutch 34 through an endless flexible member (for example, belt) 26c.
- a direct coupling mechanism 46 that is arranged in parallel with the CVT 26, directly connects the input shaft 12 and the output shaft 32, changes the rotation of the input shaft 12 at a predetermined (fixed) gear ratio, and transmits the transmission to the output shaft 32.
- Control means for establishing a CVT mode (first power transmission system) by the CVT 26 and a direct connection mode (second power transmission system) by the direct coupling mechanism 46,
- VT mode first power transmission system
- second power transmission system second power transmission system
- the first clutch 30 and the second clutch 34 are engaged, while when establishing the direct connection mode (second power transmission system), the third clutch (reference numeral 50b). And the first clutch 30 and the second clutch 34 are disengaged.
- the predetermined transmission ratio of the direct coupling mechanism 46 is set to the maximum transmission ratio Low ratio (not the minimum transmission ratio OD ratio) of the CVT 26.
- the direct coupling mechanism 46 is configured to be connected to the output shaft 32 via the third clutch 50b.
- the direct coupling mechanism 46 on the output shaft 32 side is decelerated and can be kept at Vmax ⁇ iTop / iLow even at the maximum engine speed NEmax.
- the rotation of the output shaft 32 that has been decelerated is input to the third clutch 50b, and thus the durability of the third clutch 50b is increased. It is possible to reduce the necessity of taking countermeasures for turning around. Furthermore, since the rotation of the direct coupling mechanism 46 is decelerated, noise can be reduced accordingly.
- the rotational speed of the direct coupling mechanism 46 is set to the low ratio, and the direct coupling mechanism 46 is connected to the output shaft 32 via the third clutch 50b, so that the maximum gear ratio Low ratio is obtained. Except for the point of switching at this time, the remaining configuration and effects are the same as in the first embodiment.
- the input shaft 12 connected to the drive source (engine) 14 mounted on the vehicle 20 the output shaft 32 connected to the drive wheels 16, A drive pulley 26a connected to the input shaft 12 via the first clutch 30 (connected via the pulley input shaft 12a) and the output shaft 32 are connected via the second clutch 34 (pulley output shaft 32a).
- a continuously variable transmission (CVT) 26 having a driven pulley 26b and an endless flexible member (belt) 26c wound between the driven pulley 26b and the continuously variable transmission 26;
- a direct connection mechanism 46 for directly connecting the input shaft 12 and the output shaft 32 to transmit the rotation of the input shaft 12 to the output shaft 32 at a predetermined speed ratio; and a first power transmission system by the continuously variable transmission 26;
- Direct coupling mechanism 46 In the automatic transmissions 10 and 10a including control means (shift controller 72) for controlling the establishment of the second power transmission system, the predetermined gear ratio of the direct coupling mechanism 46 is set to the minimum gear ratio of the continuously variable transmission 26 ( OD ratio), and the direct coupling mechanism 46 is connected to the input shaft 12 via the third clutches 50 and 50a, and the control means establishes the first power transmission system when the first clutch is established.
- first power transmission system or the second power transmission system direct connection mechanism can be established smoothly without giving a shock to the occupant, and when establishing the second power transmission system, the continuously variable transmission ( The CVT) 26 can be separated from the drive source (engine) 14 to be non-rotated to reduce the load on the drive source.
- the control means establishes the second power transmission system, it is determined that the speed ratio of the continuously variable transmission (CVT) 26 in the first power transmission system substantially matches the minimum speed ratio.
- the third clutch 50, 50a is engaged, the first clutch 30 is released, and then the second clutch 34 is gradually released when it is determined that the second power transmission system is established.
- the third clutch 50, 50a is engaged in a state in which the rotational speed of the direct coupling mechanism 46 and the rotational speed of the drive pulley 26a of the continuously variable transmission 46 are synchronized.
- the second power transmission system can be established in a short time without giving a shock, in other words, the first power transmission system can be switched to the second power transmission system in a short time.
- the second clutch 34 is gradually released, so that the speed of reduction of the pulley rotation of the continuously variable transmission 26 can be reduced, and the inertia shock Can be reduced and the passengers will not be shocked further.
- the control means gradually engages the second clutch 34 while the second power transmission system is established, and then rotates the direct coupling mechanism 46.
- the third clutch 50, 50a is released and the first clutch 30 is engaged.
- the third clutch 50, 50a is released in a state where the rotational speed of the direct coupling mechanism 46 and the rotational speed of the drive pulley 26a of the continuously variable transmission 26 are synchronized.
- the first power transmission system can be established in a short time without giving the power, in other words, the second power transmission system can be switched to the first power transmission system in a short time.
- the second clutch 34 is gradually engaged while the second power transmission system is established, the rising speed of the pulley rotation of the continuously variable transmission 26 can be reduced, and inertial shock can be reduced. It can be reduced and the passengers will not be shocked further.
- the continuously variable transmission 26 maintains the OD ratio while the second power transmission system is established, the ratio adjustment at the time of transition becomes unnecessary, and the transition time can be shortened.
- the continuously variable transmission (CVT) 26 is a transmission that operates by supplying hydraulic oil to the drive pulley 26a and the driven pulley 26b, and the control means has the second power transmission system established. Since the pressure of the hydraulic oil to be supplied to the drive pulley 26a and the driven pulley 26b is reduced to a predetermined pressure (ratio maintaining pressure during stop) during the operation, fuel efficiency can be improved in addition to the above-described effects. .
- the pulleys 26a and 26b of the continuously variable transmission (CVT) 26 are shut off at the input and output, and therefore the endless flexible member (belt) 26c and the pulleys 26a and 26b.
- the pulley pressure to be supplied to the drive pulley 26a and the driven pulley 26b can be reduced to a predetermined pressure.
- the hydraulic pump pressure can be reduced, and the hydraulic pump loss can be reduced to improve fuel efficiency.
- the pulleys 26a and 26b and the endless flexible member (belt) 26c maintain the OD ratio state, interference, backlash, and hitting sound of each part do not occur.
- the predetermined pressure is configured to be a pressure sufficient to maintain the gear ratio, in addition to the above-described effects, the pressure can be further reduced and fuel consumption can be further improved.
- the direct coupling mechanism 46 is constituted by a chain, but may be constituted by a gear.
- the direct coupling mechanism 46 may have any structure as long as the input shaft 12 and the output shaft 32 are directly coupled to transmit the rotation of the input shaft 12 to the output shaft 32 at a predetermined speed ratio.
- a structure having a metal V-belt as the CVT (continuously variable transmission) 26 has been disclosed, a metal chain, a resin belt, or a rubber belt may be used.
- the “pulley pressure” used above is synonymous with the clamping force.
- first, second, and third clutches 30, 34, and 50 are hydraulic clutches, they may be dry clutches or electromagnetic clutches.
- predetermined (fixed) gear ratio of the direct coupling mechanism 46 is equal to the minimum gear ratio of the CVT 26, it may not be strictly equal as long as it is within the allowable error range.
- the engine internal combustion engine
- a motor / generator or a hybrid of the engine and the engine
- a hybrid vehicle having a motor / generator on the input shaft does not pass through the continuously variable transmission mechanism when decelerating at high speed, so that in addition to the effects described above, an improvement in regeneration efficiency can be expected.
- the predetermined gear ratio of the direct coupling mechanism that is arranged in parallel with the continuously variable transmission and directly connects the input shaft and the output shaft to transmit the rotation of the input shaft to the output shaft at the predetermined gear ratio is continuously variable. Since the minimum gear ratio of the machine is set and the direct coupling mechanism is connected to the input shaft via the third clutch, when the power is transmitted by the first power transmission system by the continuously variable transmission, the speed is reduced. Is input to the third clutch, and the rotational speed input to the third clutch that establishes the second power transmission system by the direct coupling mechanism 46 can be reduced. As a result, measures for improving the rotational strength and durability of the third clutch and measures for accompanying rotation can be made unnecessary, and since the rotation of the direct coupling mechanism is decelerated, noise can be reduced accordingly.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- Transmission Devices (AREA)
Abstract
Description
である。
Claims (5)
- 車両に搭載される駆動源に接続される入力軸と、駆動輪に接続される出力軸と、前記入力軸に第1クラッチを介して接続されるドライブプーリと前記出力軸に第2クラッチを介して接続されるドリブンプーリとその間に掛け回される無端可撓部材とを有する無段変速機と、前記無段変速機と並列に配置され、前記入力軸と前記出力軸を直結して前記入力軸の回転を所定の変速比で前記出力軸に伝達する直結機構と、前記無段変速機による第1動力伝達系と前記直結機構による第2動力伝達系の確立を制御する制御手段とを備える自動変速装置において、前記直結機構の前記所定変速比を前記無段変速機の最小変速比に設定し、前記直結機構を前記入力軸に第3クラッチを介して接続すると共に、前記制御手段は、前記第1動力伝達系を確立するときは前記第1クラッチと前記第2クラッチを係合し、前記第3クラッチを解放する一方、前記第2動力伝達系を確立するときは前記第3クラッチを係合し、前記第1クラッチと前記第2クラッチを解放するように構成したことを特徴とする自動変速装置。
- 前記制御手段は、前記第2動力伝達系を確立するとき、前記第1動力伝達系において前記無段変速機の変速比が最小変速比にほぼ一致したと判断されるときに前記第3クラッチを係合すると共に、前記第1クラッチを解放し、次いで前記第2動力伝達系が確立されたと判断されるとき、前記第2クラッチを徐々に解放するように構成したことを特徴とする請求項1記載の自動変速装置。
- 前記制御手段は、前記第1動力伝達系を確立するとき、前記第2動力伝達系が確立されている間に前記第2クラッチを徐々に係合し、次いで前記直結機構の回転速度と前記無段変速機のドライブプーリの回転速度がほぼ同期したと判断されるとき、前記第3クラッチを解放すると共に、前記第1クラッチを係合するように構成したことを特徴とする請求項1または2記載の自動変速装置。
- 前記無段変速機は前記ドライブプーリとドリブンプーリに作動油を供給されて動作する変速機であると共に、前記制御手段は、前記第2動力伝達系が確立されている間、前記ドライブプーリとドリブンプーリに供給すべき作動油の圧力を所定圧力に低下させるように構成したことを特徴とする請求項1から3のいずれかに記載の自動変速装置。
- 前記所定圧力が前記変速比を維持するに足る圧力であることを特徴とする請求項4記載の自動変速装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014545685A JP6038949B2 (ja) | 2012-11-06 | 2013-11-01 | 自動変速装置 |
CN201380056657.3A CN104769333B (zh) | 2012-11-06 | 2013-11-01 | 自动变速装置和自动变速方法 |
DE112013005301.2T DE112013005301T5 (de) | 2012-11-06 | 2013-11-01 | Automatikgetriebevorrichtung |
US14/440,133 US9625018B2 (en) | 2012-11-06 | 2013-11-01 | Automatic transmission apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2012-244630 | 2012-11-06 | ||
JP2012244630 | 2012-11-06 |
Publications (1)
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WO2014073479A1 true WO2014073479A1 (ja) | 2014-05-15 |
Family
ID=50684585
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2013/079708 WO2014073479A1 (ja) | 2012-11-06 | 2013-11-01 | 自動変速装置 |
Country Status (5)
Country | Link |
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US (1) | US9625018B2 (ja) |
JP (1) | JP6038949B2 (ja) |
CN (1) | CN104769333B (ja) |
DE (1) | DE112013005301T5 (ja) |
WO (1) | WO2014073479A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016024494A1 (ja) * | 2014-08-12 | 2016-02-18 | アイシン・エィ・ダブリュ株式会社 | 自動変速機 |
KR20180037023A (ko) * | 2015-09-09 | 2018-04-10 | 쟈트코 가부시키가이샤 | 차량용 무단 변속기의 유압 제어 장치 및 유압 제어 방법 |
CN113544409A (zh) * | 2019-02-20 | 2021-10-22 | 蒂姆工业公司 | 带有无级变速器的动力传动系统布局 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6439756B2 (ja) * | 2016-07-07 | 2018-12-19 | トヨタ自動車株式会社 | 車両用変速機の制御装置 |
JP2018105495A (ja) * | 2016-12-28 | 2018-07-05 | トヨタ自動車株式会社 | 車両用動力伝達装置の制御装置 |
US20180320768A1 (en) * | 2017-05-05 | 2018-11-08 | GM Global Technology Operations LLC | Multi-mode continuously-variable transmission |
CN107366727A (zh) * | 2017-09-05 | 2017-11-21 | 中铁工程装备集团机电工程有限公司 | 一种隧道机车的轮轴测速传动机构 |
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- 2013-11-01 WO PCT/JP2013/079708 patent/WO2014073479A1/ja active Application Filing
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CN113544409A (zh) * | 2019-02-20 | 2021-10-22 | 蒂姆工业公司 | 带有无级变速器的动力传动系统布局 |
Also Published As
Publication number | Publication date |
---|---|
US20150316147A1 (en) | 2015-11-05 |
JPWO2014073479A1 (ja) | 2016-09-08 |
CN104769333B (zh) | 2016-10-12 |
DE112013005301T5 (de) | 2015-07-23 |
JP6038949B2 (ja) | 2016-12-07 |
US9625018B2 (en) | 2017-04-18 |
CN104769333A (zh) | 2015-07-08 |
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