JP2007327531A - Power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission device capable of preventing power loss by avoiding generation of high pressure when providing a reaction force to a rotation member connected to variable displacement pump motors. <P>SOLUTION: In the power transmission device for transmitting power output from the power source 1 to an output member 16 via a driving mechanism, the driving mechanism has mechanisms 3, 4, 17, 18, 19, 20 for transmitting power which the power source 1 outputs to the output member 16 as the reaction force is provided, a variable displacement fluid pressure pump motors 12, 13 connected to the driving mechanism and brake mechanisms 22, 25, 26, 28 for selectively connecting rotors of the variable displacement fluid pressure pump motors 12, 13 with a predetermined fixing part 27 and fixing them. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an apparatus for transmitting power from a power source to an output member via a transmission mechanism.

  This type of power transmission device is mounted on a vehicle, and is configured as a transmission capable of appropriately changing a gear ratio. A vehicle transmission is required to have a large number of gear ratios that can be set, to be small and light, and to have high power transmission efficiency. Thus, for example, Patent Document 1 describes a transmission that can set seven or more shift stages and that can be downsized.

  The transmission described in Patent Document 1 is a so-called twin clutch type stepped transmission, which is connected to an engine via a first clutch and a first input shaft connected to the engine via a first clutch. The second input shaft, the output shaft, the auxiliary shaft connected to the first input shaft via a gear pair, and the first input shaft and the auxiliary shaft are provided and selectively engaged by the mesh clutch mechanism. And a plurality of gear pairs that are provided between the second input shaft and the output shaft and that are selectively connected by a meshing clutch mechanism. The transmission includes a gear stage that transmits torque from any one of the input shafts to the output shaft through a predetermined gear pair, and any output shaft from the input shaft to the output shaft through the predetermined gear pair and the sub shaft. It is configured to set a gear stage for transmitting torque, and as a result, it is configured to set seven or more gear stages including the reverse gear.

Japanese Patent Application Laid-Open No. 2003-120764

  In the transmission described in Patent Document 1 described above, since the number of shift speeds that can be set is large, the engine can be operated in a state with good fuel efficiency, and the auxiliary shaft is effectively used. The transmission is reduced in size and weight as a whole, and as a result, the fuel consumption of the vehicle can be improved.

  However, the first clutch and the second clutch used for setting and changing the power transmission path are constituted by a hydraulic friction clutch to absorb the inertial force at the time of shifting transition, Therefore, there is room for improvement in terms of energy efficiency and shift response. In other words, since the hydraulic friction clutch is engaged by pressing the friction plate with hydraulic pressure, the clutch is engaged even in a steady state where the vehicle is traveling with a predetermined gear set. It is necessary to generate the hydraulic pressure, and power for that is always consumed.

  In addition, the clutch that is not involved in the transmission of torque is controlled in a so-called released state, but drag torque is generated by relative rotation of the friction plate, and power loss is caused by the accompanying friction. Furthermore, since heat is generated by the friction, it is necessary to constantly supply lubricating oil for cooling, and power is consumed for the lubrication, which may increase power loss.

  The present invention has been made by paying attention to the above technical problem, and an object of the present invention is to provide a power transmission device that reduces power loss and has good overall energy efficiency.

  In order to achieve the above object, the invention according to claim 1 is directed to a power transmission device that transmits power output from a power source to an output member via a power transmission mechanism, wherein the power transmission mechanism is provided with a reaction force. A variable displacement fluid pressure pump motor that has a mechanism for transmitting the power output from the power source to the output member and applies a reaction force to the transmission mechanism, and a predetermined fixed amount of the rotor of the variable displacement fluid pressure pump motor And a brake mechanism that is selectively connected and fixed to the portion.

  According to a second aspect of the present invention, in the first aspect of the invention, the transmission mechanism includes a rotary shaft connected to a rotor of the variable displacement fluid pressure pump motor, and is rotatably fitted to the rotary shaft and the rotary shaft. A transmission rotator that transmits power to the output member by being connected to a rotation shaft; and a clutch mechanism that selectively connects the transmission rotator to the rotation shaft; A power having a fixed engaging portion for connecting the rotating shaft to the predetermined fixing portion by engaging the clutch mechanism with the clutch mechanism being separated from the transmission rotating body. It is a transmission device.

  According to a third aspect of the present invention, in the second aspect of the invention, the clutch mechanism is engaged with the transmission rotating body by moving a sleeve in the axial direction of the rotating shaft, and the rotating shaft, the transmission rotating body, The fixed engagement portion is disposed on the opposite side of the transmission rotating body with the synchronous connection mechanism interposed therebetween, and selectively engages with the sleeve to rotate the rotation shaft. The power transmission device includes a fixing hub connected to the predetermined fixing portion.

  According to a fourth aspect of the present invention, in the second or third aspect of the invention, the transmission mechanism includes a planetary gear mechanism that performs a differential action using a sun gear, a carrier, and a ring gear as rotational elements. One rotating element is connected to the rotor of the variable displacement fluid pressure pump motor, the other rotating element is connected to the transmission rotating body directly or via the clutch mechanism, and the other rotating element is connected to the rotor. A power transmission device connected to a power source.

  According to the first aspect of the present invention, by applying a reaction force to a predetermined rotating member connected to the variable displacement fluid pressure pump motor by the variable displacement type fluid pressure pump motor, the power is transmitted from the power source to the output member, and the reaction force can be applied. The increased state is a state where the predetermined rotating member or the variable displacement fluid pressure pump motor is fixed. This fixed state is set when the brake mechanism is in a so-called engaged state, and therefore there is no need to confine and fix the fluid in the variable displacement fluid pressure pump motor, so that the fluid in the variable displacement fluid pressure pump motor is not required. Can be prevented or suppressed. As a result, since the fluid pressure can be relatively low, power loss due to fluid leakage or the like can be suppressed, and the durability of the apparatus can be improved.

  According to the invention of claim 2, in addition to the effect similar to the effect obtained by the invention of claim 1 described above, the clutch mechanism has a function of connecting the rotary shaft or the variable displacement hydraulic pump motor to the transmission rotor. And a function of connecting to the fixed portion and stopping its rotation, the number of components can be reduced to simplify the overall configuration and reduce the size. Moreover, since neither the state which connected the transmission rotating body to the rotating shaft nor the state which fixed the rotating shaft is materialized, fail safe can be established.

  According to the invention of claim 3, in addition to the same effects as those obtained by the invention of claim 1 and claim 2, the synchronous connecting mechanism also functions to fix the rotating shaft, and the synchronous connecting mechanism As a result, the entire configuration can be simplified and the size can be reduced by reducing the number of components.

  According to the invention of claim 4, the same effect as that of the invention of claims 1 to 3 can be obtained. In addition to this, when the brake mechanism is engaged, any one of the rotating elements in the planetary gear mechanism is fixed, and the planetary gear mechanism performs a speed change action accordingly, and power is transmitted from the power source to the transmission rotating body. introduce.

  Next, the present invention will be described based on specific examples. The example shown in FIG. 1 is an example configured as a transmission for a vehicle, and four forward speeds and one reverse speed are set as a so-called fixed speed ratio that can be set by transmitting torque without using fluid. This is a configured example. That is, the input member 2 is connected to the power source (E / G) 1, and the torque is transmitted from the input member 2 to the first planetary gear mechanism 3 and the second planetary gear mechanism 4.

  The power source 1 may be a general power source used in a vehicle such as an internal combustion engine, an electric motor, or a combination thereof. Further, an appropriate transmission means such as a damper, a clutch, or a torque converter may be interposed between the power source 1 and the input member 2.

  The first planetary gear mechanism 3 is disposed on the same axis as the input member 2, the second planetary gear mechanism 4 is separated outward in the radial direction of the first planetary gear mechanism 3, and the respective central axes are parallel to each other. They are arranged in parallel. As these planetary gear mechanisms 3 and 4, a planetary gear mechanism of an appropriate type such as a single pinion type or a double pinion type can be adopted. The example shown in FIG. 1 is an example constituted by a single-pinion type planetary gear mechanism, and sun gears 3S and 4S which are external gears, and a ring gear 3R which is an internal gear arranged concentrically with the sun gears 3S and 4S. , 4R, and carriers 3C, 4C holding pinion gears meshed with these sun gears 3S, 4S and ring gears 3R, 4R so as to be rotatable and revolved. The input member 2 is connected to a ring gear 3R in the first planetary gear mechanism 3, and the ring gear 3R serves as an input element.

  Further, a counter drive gear 5 is attached to the input member 2, and an idle gear 6 is engaged with the counter drive gear 5, and a counter driven gear 7 is engaged with the idle gear 6. The counter driven gear 7 is disposed on the same axis as the second planetary gear mechanism 4 and is connected to the ring gear 4R of the second planetary gear mechanism 4 so as to rotate together. Therefore, in the second planetary gear mechanism 4, the ring gear 4R serves as an input element. The ring gears 3R and 4R, which are input elements of the planetary gear mechanisms 3 and 4, are configured so that the counter gear pair includes the idle gear 6, and thus rotate in the same direction.

  The carrier 3C in the first planetary gear mechanism 3 serves as an output element, and the first intermediate shaft 8 is connected to the carrier 3C so as to rotate together. The first intermediate shaft 8 is a hollow shaft into which a motor shaft 9 is rotatably inserted. One end of the motor shaft 9 is a sun gear that is a reaction force element in the first planetary gear mechanism 3. It is connected to 3S so as to rotate together.

  The second planetary gear mechanism 4 has the same configuration, and the carrier 4C serves as an output element, and the second intermediate shaft 10 is connected to the carrier 4C so as to rotate together. The second intermediate shaft 10 is a hollow shaft into which a motor shaft 11 is rotatably inserted. One end of the motor shaft 11 is a sun gear that is a reaction force element in the second planetary gear mechanism 4. 4S is connected to rotate integrally.

  The other end of the motor shaft 9 is connected to the output shaft of the variable displacement pump motor 12. The variable displacement pump motor 12 is a fluid pressure (hydraulic) pump capable of changing the discharge capacity, such as a slant shaft pump, a swash plate pump, or a radial piston pump, and is rotated by applying torque to its output shaft. It functions as a motor by discharging pressure fluid (pressure oil) by functioning as a pump and supplying pressure fluid from a discharge port or suction port. In the following description, the variable displacement pump motor 12 is referred to as a first pump motor 12 and is represented as PM1 in the drawing.

  The other end of the motor shaft 11 is connected to the output shaft of the variable displacement pump motor 13. The variable displacement pump motor 13 is a fluid pressure (hydraulic) pump capable of changing the discharge capacity, such as an oblique shaft pump, a swash plate pump, or a radial piston pump, and is rotated by applying torque to its output shaft. It functions as a motor by discharging pressure fluid (pressure oil) by functioning as a pump and supplying pressure fluid from a discharge port or suction port. In the following description, the variable displacement pump motor 13 is referred to as a second pump motor 13 and is indicated as PM2 in the figure.

  The pump motors 12 and 13 are communicated with each other by oil passages 14 and 15 so that the pressure oil, which is a pressure fluid, can be transferred to each other. That is, the suction ports 12 </ b> S and 13 </ b> S are communicated with each other through the oil passage 14, and the discharge ports 12 </ b> D and 13 </ b> D are communicated with each other through the oil passage 15. Accordingly, a closed circuit is formed by the oil passages 14 and 15. The suction ports 12S and 13S in the pump motors 12 and 13 are ports for sucking fluid such as oil when the pump motors 12 and 13 rotate in the same direction as the power source 1, and discharge ports. 12D and 13D are ports for discharging fluid such as oil during forward rotation. A mechanism for controlling the hydraulic pressure in the closed circuit will be described later.

  An output shaft 16 corresponding to the output member of the present invention is arranged in parallel with each of the intermediate shafts 8 and 10 described above. A transmission mechanism for setting a predetermined gear ratio is provided between the output shaft 16 and each of the intermediate shafts 8 and 10. The transmission mechanism in the present invention is not limited to a mechanism that transmits power at a fixed gear ratio, and a mechanism with a variable gear ratio can be adopted. In the example shown in FIG. 1, power is transmitted at a fixed gear ratio. A plurality of gear pairs 17, 18, 19, and 20 for transmitting the above are employed.

  More specifically, a fourth speed drive gear 17A and a second speed drive gear 18A are arranged on the first intermediate shaft 8 in order from the first planetary gear mechanism 3 side. 17A and the second speed drive gear 18A are rotatably fitted to the first intermediate shaft 8. A fourth speed driven gear 17B meshed with the fourth speed drive gear 17A and a second speed driven gear 18B meshed with the second speed drive gear 18A are attached to the output shaft 16 so as to rotate integrally. Yes. Accordingly, the drive gears 17A and 18A and the driven gears 17B and 18B correspond to the transmission rotor of the present invention.

  Further, a third speed drive gear 19A meshed with the fourth speed driven gear 17B and a first speed drive gear 20A meshed with the second speed driven gear 18B are rotatable on the second intermediate shaft 10. It is made to fit. Accordingly, the fourth speed driven gear 17B also serves as the third speed driven gear, and the second speed driven gear 18B also serves as the first speed driven gear. Accordingly, the drive gears 19A and 20A for the third speed and the first speed and the driven gears 17B and 18B meshing with the third and first speed drive gears 19A and 20B correspond to the transmission rotor of the present invention. Here, the gear ratio of each gear pair 17, 18, 19, and 20 (ratio of the number of teeth of the driven gear to the number of teeth of each drive gear) will be described. The second speed gear pair 18, the third speed gear pair 19, and the fourth speed gear pair 17 are configured to decrease in order.

  Furthermore, a starting gear pair 21 is provided. The starting gear pair 21 is used to transmit the power to the output shaft 16 together with the first speed gear pair 20 so that the driving force at the time of starting is sufficiently large. A starting drive gear 21A rotatably attached to the motor shaft 9 on the pump motor 12 side and a starting driven gear 21B attached to the output shaft 16 are provided.

  A clutch mechanism is provided for allowing each of the gear pairs 17, 18, 19, 20, and 21 described above to transmit torque between any of the intermediate shafts 8 and 10 and the output shaft 16. The clutch mechanism is a mechanism for selectively transmitting torque, and a conventionally known mechanism such as a dog clutch mechanism or a synchronous coupling mechanism (synchronizer) can be employed. FIG. An example of adopting a Nizer is shown.

  The synchronizer basically moves the sleeve that rotates together with the rotating shaft in the axial direction, and engages with the spline of the rotating member that is mounted so as to rotate relative to the rotating shaft. The rotating shaft and the rotating member are connected by synchronizing the rotating shaft and the rotating member by the frictional contact of the knit ring with the rotating member. On the motor shaft 9, a first synchronizer (hereinafter referred to as a first synchronizer) 22 is provided at a position adjacent to the start drive gear 21A. The first sync 22 moves its sleeve to the right side in FIG. 1 to connect the start drive gear 21A to the motor shaft 9, and the start gear pair 21 is torqued between the motor shaft 9 and the output shaft 18. Is configured to communicate.

  On the second intermediate shaft 10, a second synchronizer (hereinafter referred to as a second synchronizer) 23 is provided between the third speed drive gear 19A and the first speed drive gear 20A. The second synchronizer 23 connects the first speed drive gear 20A to the second intermediate shaft 10 by moving the sleeve to the left side in FIG. 1, and the first speed gear pair 20 is connected to the second intermediate shaft 10. Torque is transmitted to and from the output shaft 16. On the other hand, the third speed drive gear 19A is connected to the second intermediate shaft 10 by moving the sleeve to the right in FIG. 1, and the third speed gear pair 19 is connected to the second intermediate shaft 10 and the output shaft 16. Torque is transmitted between the two.

  Further, on the first intermediate shaft 8, a third synchronizer (hereinafter referred to as a third synchronizer) 24 is provided between the second speed drive gear 18A and the fourth speed drive gear 17A. The third synchronizer 24 moves the sleeve to the left side in FIG. 1 to connect the second speed drive gear 18A to the first intermediate shaft 8, and the second speed gear pair 18 is connected to the first intermediate shaft 8. Torque is transmitted to and from the output shaft 16. On the other hand, the fourth speed drive gear 17A is connected to the first intermediate shaft 8 by moving the sleeve to the right in FIG. 1, and the fourth speed gear pair 17 is connected to the first intermediate shaft 8 and the output shaft 16. Torque is transmitted between the two.

  Furthermore, a reverse synchronizer (hereinafter referred to as “R synchro”) 25 is provided on the motor shaft 11 on the second pump motor 13 side at a position adjacent to the shaft end of the second intermediate shaft 10. The R synchro 25 connects the motor shaft 11 and the second intermediate shaft 10, that is, the sun gear 4S and the carrier 4C in the second planetary gear mechanism 4 by moving the sleeve to the right in FIG. The entire planetary gear mechanism 4 is configured to rotate integrally.

  The first sync 22 and the R sync 25 constitute part of the brake mechanism in the present invention. That is, a fixed hub 26 having splines formed on the outer peripheral surface is disposed on the opposite side of the first drive gear 21A with the first synchro 22 interposed therebetween. The fixed hub 26 is attached to a fixed portion 27 such as a casing. Therefore, by moving the sleeve of the first synchro 22 to the left side in FIG. 1 to be separated from the starting drive gear 21A and engaging with the fixed hub 26, the motor shaft 9 is connected to the fixed portion 27, and the motor shaft 9 And the rotor (not shown) of the 1st pump motor 12 connected with this is fixed.

  Similarly, a fixed hub 28 having a spline formed on the outer peripheral surface is disposed on the opposite side to the first speed drive gear 20A across the R synchro 25. The fixed hub 28 is attached to a fixed portion 27 such as a casing. Accordingly, by moving the sleeve of the R synchro 25 to the left side in FIG. 1 and separating it from the first speed drive gear 20A and engaging with the fixed hub 28, the motor shaft 11 is connected to the fixed portion 27, and the motor shaft 11 and a rotor (not shown) of the second pump motor 13 connected thereto are fixed. Therefore, each synchro 22 and 25 and each fixed hub 26 and 28 constitute a brake mechanism in the present invention.

  Each of the synchros 22, 23, 24, and 25 can be configured to be switched by manual operation, but can be configured to perform so-called automatic control instead. In that case, for example, an appropriate actuator (not shown) for moving the above-described sleeve in the axial direction may be provided, and the actuator may be electrically controlled.

  As described above, the transmission shown in FIG. 1 is configured such that the torque output from the power source 1 is transmitted to the output shaft 16 via any one of the intermediate shafts 8 and 10 or the motor shafts 9 and 11. Has been. A differential 30 is connected to the output shaft 16 through a transmission means 29 such as a gear mechanism or a winding transmission mechanism such as a chain, and the power is output from this to the left and right axles 31.

  Next, a fluid pressure circuit (hydraulic circuit) for controlling the pump motors 12 and 13 will be described. A charge pump (sometimes referred to as a boost pump) 32 for replenishing fluid (specifically oil) is provided in the closed circuit in which the pump motors 12 and 13 are communicated with each other. The charge pump 32 is for compensating for the shortage of oil due to leakage from the closed circuit, and is driven by the power source 1 or a motor (not shown) to pump oil from the oil pan 33. It is designed to supply a closed circuit.

  Accordingly, the discharge port of the charge pump 32 communicates with the oil passage 14 and the oil passage 15 in the closed circuit via the check valves 34 and 35, respectively. The check valves 34 and 35 are configured to open in the discharge direction from the charge pump 32 and close in the opposite direction. Further, a relief valve 36 for adjusting the discharge pressure of the charge pump 32 is communicated with the discharge port of the charge pump 32. The relief valve 36 is configured to open and discharge oil to the oil pan 33 when a pressure higher than the sum of the elastic force of the spring and the pilot pressure or the pressing force of the solenoid is applied. The discharge pressure is set to a pressure corresponding to the pilot pressure.

  Further, a relief valve 37 is provided between the suction port 12 </ b> S of the first pump motor 12 and the oil passage 15. In other words, the relief valve 37 is provided in parallel with the first pump motor 12 so as to communicate the oil passages 14 and 15. The relief valve 37 is configured to maintain the discharge pressure at a preset pressure when pressure oil is discharged from the suction port 12S of the first pump motor 12 or the suction port 13S of the second pump motor 13. ing. A relief valve 38 is provided between the discharge port 13 </ b> D of the second pump motor 13 and the oil passage 14. In other words, the relief valve 38 is provided in parallel with the second pump motor 13 so as to communicate the oil passages 14 and 15. The relief valve 38 is configured to maintain the discharge pressure at a preset pressure when pressure oil is discharged from the discharge port 12D of the first pump motor 12 or the discharge port 13D of the second pump motor 13. ing.

  The pump volume of each of the pump motors 12 and 13 and the synchros 22, 23, 24, and 25 can be electrically controlled, and an electronic control unit (ECU) 39 is provided for that purpose. The electronic control unit 39 is configured mainly with a microcomputer, and receives the number of rotations of a predetermined rotating member and other detection signals, and the input signals and previously stored information. In addition, the calculation is performed based on the program, and the command signal is output according to the calculation result.

  Next, the operation of the power transmission device described above will be described. FIG. 2 is a chart collectively showing the operation states of the pump motors (PM1, PM2) 12, 13 and the synchros 22, 23, 24, 25 when setting the respective gear positions. “OFF” for each of the pump motors 12 and 13 makes the pump capacity substantially zero, does not generate pressure oil even if the output shaft is rotated, and the output shaft is not supplied even if hydraulic pressure is supplied. A state where the rotor does not rotate (free) is indicated, and “LOCK” indicates a state where the rotation of the rotor is stopped. In this case, the extrusion volume may be larger than substantially zero, and may be set to any of the maximum, minimum, and intermediate volume. Furthermore, “hydraulic pressure generation” indicates a state in which the pump capacity is made larger than substantially zero and pressure oil is discharged, and thus the corresponding pump motors 12 and 13 function as pumps. “Hydraulic pressure recovery” indicates a state in which pressure oil discharged from one pump motor 13 (or 12) is supplied and functions as a motor, and therefore the corresponding pump motor 13 (or 12) has a shaft torque. And driving torque is transmitted to the corresponding intermediate shafts 8 and 10.

  In addition, “right” and “left” for each of the synchros 22, 23, 24, and 25 indicate the positions of the sleeves in the respective synchros 22, 23, 24, and 25 in FIG. 1, and the parentheses are downshifted. The stand-by state, the brackets indicate the stand-by state for upshifting, and “◯” reduces drag by setting the corresponding synchro 22, 23, 24, 25 to the OFF state (neutral position). “●” indicates that the corresponding synchro 22, 23, 24, 25 is set to the OFF state (neutral position) and is in the neutral state.

  When the neutral (N) state is set by selecting a neutral position with a shift device (not shown), the pump motors 12 and 13 are set to the “OFF” state, and the synchros 22, 23, 24, 25 sleeves are set in the center position. Therefore, none of the gear pairs 17, 18, 19, 20, 21 is in a neutral state that is not connected to the output shaft 16. That is, the pump motors 12 and 13 are controlled so that the pump displacement is substantially zero, and as a result, a so-called idling state is established. Therefore, the power source 1 is connected to the ring gears 3R and 4R of the planetary gear mechanisms 3 and 4, respectively. No torque is transmitted to the intermediate shafts 8 and 10 connected to the carriers 3C and 4C as output elements because no reaction force acts on the sun gears 3S and 4S even if torque is transmitted from the motor.

  When the shift position is switched to a travel position such as a drive position, the sleeve of the first sync 22 is moved to the first right side and the sleeve of the second sync 23 is moved to the left side of FIG. Therefore, the starting drive gear 21A is connected to the motor shaft 9, the first pump motor 12 and the output shaft 16 are connected, and the first speed drive gear 20A is connected to the second intermediate shaft 10 to be the second planetary gear mechanism. 4 is the output element 4 and the output shaft 16 is connected. That is, the first speed that is the fixed gear ratio is set. At the same time, the extrusion volume of each pump motor 12, 13 is controlled to be larger than zero.

  Therefore, the second pump motor 13 is driven by the power of the power source 1 distributed by the second planetary gear mechanism 4 to function as a pump, and the reaction torque resulting from the generation of hydraulic pressure is applied to the motor shaft 11 and the sun gear 4S. To give. Therefore, torque is transmitted to the carrier 4 </ b> C by the differential action of the second planetary gear mechanism 4, and the torque is transmitted to the output shaft 16 via the first speed gear pair 20. On the other hand, since the hydraulic pressure generated by the second pump motor 13 is discharged from the suction port 13S and supplied to the suction port 12S of the first pump motor 12, the first pump motor 12 functions as a motor and rotates forward. In this way, the power transmitted to the first pump motor 12 is transmitted to the output shaft 16 via the starting gear pair 21. Such an operating state of the first pump motor 12 is indicated as “hydraulic pressure recovery” in FIG. Therefore, in the driving state from the start to the first speed, both so-called mechanical power transmission via the second planetary gear mechanism 4 and power transmission via the hydraulic pressure are generated, and the combined power of these powers is generated. Appears on the output shaft 16.

  When the rotational speed of the power source 1 and the vehicle speed are changed to the first speed gear ratio, the sleeve of the R synchro 25 is moved to the left side in FIG. That is, the motor shaft 11 and the second pump motor 13 connected thereto are fixed. At the same time, the first sync 22 is set to the OFF state. As a result, the sun gear 4S of the second planetary gear mechanism 4 is fixed, and the first planetary gear mechanism 3 is not involved in the transmission of power to the output shaft 16, so that the power output from the power source 1 is the second planetary gear. It is transmitted to the output shaft 16 via the mechanism 4 and the first speed gear pair 20. That is, a fixed gear ratio determined by the gear ratio of the first speed gear pair 20 is set.

  In this case, since the motor shaft 11 or the rotor of the first pump motor 12 is fixed by the R synchro 25, no torque acts on the first pump motor 12, and no hydraulic pressure is supplied. The first pump motor 12 does not generate hydraulic pressure. Therefore, hydraulic leakage and power loss due to this are avoided or suppressed.

  When upshifting to the second speed, which is a fixed gear ratio, the sleeve of the third sync 24 is moved to the left in FIG. 1 and the second speed drive gear 18 is connected to the first intermediate shaft 8. When engaging the second speed drive gear 18 of the sleeve of the third synchro 24, the hydraulic pressure of the charge pump 32 is supplied to the first pump motor 12 to rotate it, thereby rotating the sleeve of the third synchro 24. The synchronous control may be performed so that the rotational speed of the second speed driving gear 18 matches the rotational speed of the second speed drive gear 18.

  In this state, the R synchro 25 is set to the neutral state, and the extrusion volume of the first pump motor 12 is gradually increased toward the maximum. In the state of waiting for upshifting to the second speed, the first pump motor 12 rotates in the reverse direction. When the extrusion volume is gradually increased, the first pump motor 12 functions as a pump and generates hydraulic pressure. Appears at 9. As a result, transmission of power through the first planetary gear mechanism 3 and the second speed gear pair 18 is gradually performed. Further, the hydraulic pressure generated by the first pump motor 12 is supplied to the second pump motor 13 and functions as a motor, so that the second pump motor 13, the second planetary gear mechanism 4, and the first speed gear pair 20 are interposed. Power transmission occurs. Therefore, the speed ratio in the process of shifting from the first speed to the second speed is a value between the speed ratio of the first speed and the speed ratio of the second speed and is a continuously changing speed ratio. . That is, a continuously variable transmission state in which the gear ratio continuously changes is obtained. This is the same during the period from the start to the speed ratio of the first speed and between the fixed speed ratios. Therefore, the power transmission device described above can function as a continuously variable transmission. .

  When the extrusion volume of the first pump motor 12 is substantially maximized and its rotation is stopped or is almost stopped, the sleeve of the first synchro 22 is moved to the left side in FIG. As a result, the motor shaft 9 is fixed. In addition, the second pump motor 13 is set to the OFF state. Accordingly, since the sun gear 3S is fixed in the first planetary gear mechanism 3, the power input to the ring gear 3R is output from the carrier 3C to the second speed drive gear 18A via the intermediate shaft 8. On the other hand, the second pump motor 13 is in the OFF state, and the R synchro 25 and the second synchro 23 arranged coaxially with the second pump motor 13 are in the OFF state and the sleeve is in the neutral position. The motor 13 and the second planetary gear mechanism 4 are not involved in power transmission. Accordingly, the second speed, which is a fixed gear ratio determined by the gear ratio of the second speed gear pair 18, is set. Also in this case, since no hydraulic pressure is generated in each of the pump motors 12 and 13, a power loss is avoided or suppressed as in the case where the first speed is set.

  Similarly, in the third speed, the sleeve of the second synchro 23 is moved to the right in FIG. 1 to connect the third speed drive gear 19A to the second intermediate shaft 10, and the sleeve of the R synchro 25 is also shown in FIG. As in the case of the first speed, the motor shaft 11 and the second pump motor 13 are fixed, and the other synchros 22 and 24 are turned off. Accordingly, the power is transmitted to the output shaft 16 via the third speed gear pair 19, and the third speed, which is a fixed gear ratio, is set. For the fourth speed, the sleeve of the third sync 24 is moved to the right in FIG. 1 to connect the fourth speed drive gear 17A to the first intermediate shaft 8, and the sleeve of the first sync 22 is moved to the left in FIG. As in the case of the second speed, the motor shaft 9 and the first pump motor 12 are fixed, and the other synchros 23 and 25 are turned off. Therefore, power is transmitted to the output shaft 16 via the fourth speed gear pair 17 and the fourth speed, which is a fixed gear ratio, is set. At any of these gear ratios, the pump motors 12 and 13 are fixed by the first synchronizer 22 or R synchronizer 25 and the fixed hubs 26 and 28, which are mechanical brake mechanisms, thereby preventing or suppressing power loss. be able to.

  Further, the reverse gear will be described. When the reverse range is selected by a shift device (not shown), the sleeve of the first sync 22 is moved to the right side of FIG. 1, and the sleeve of the R sync 25 is moved as shown in FIG. The other syncs 23 and 24 are set to the OFF state. Therefore, when the second intermediate shaft 10 and the motor shaft 11 are connected by the R sync 25, the sun gear 4S of the second planetary gear mechanism 4 and the carrier 4C are connected, and the entire second planetary gear mechanism 4 is substantially the same. Integrated. The start drive gear 21 </ b> A is connected to the motor shaft 9, that is, the rotor of the first pump motor 12.

  Therefore, the power transmitted from the power source 1 to the second planetary gear mechanism 4 is transmitted to the second pump motor 13 as it is, and this is driven, and the second pump motor 13 generates hydraulic pressure. Since the second synchro 23 is in the OFF state, power is not transmitted from the second planetary gear mechanism 4 or the second intermediate shaft 10 to the output shaft 16. On the other hand, the extrusion volume of the first pump motor 12 is controlled to a volume larger than zero, for example, the maximum volume. As a result, the first pump motor 12 functions as a motor by the hydraulic pressure supplied from the second pump motor 13, and the motor shaft Torque is output to 9. In this case, since the hydraulic pressure is supplied to the first pump motor 12 from the discharge port 12D, the first pump motor 12 rotates in the reverse direction. Then, the torque is transmitted to the output shaft 16 via the starting gear pair 19, so that a reverse state is established. That is, in the reverse speed, power is transmitted via hydraulic pressure, and in FIG. 2, this is indicated as “hydraulic pressure recovery” for the first pump motor 12 and “hydraulic pressure generation” for the second pump motor 13.

  The specific example described above is an example in which the synchros 22 and 25 are used as a brake mechanism for fixing the rotors of the pump motors 12 and 13, that is, the motor shafts 9 and 11, but the present invention is not limited to the synchros 22 and 25 described above. An engagement mechanism such as a plate structure brake, a band brake, or a meshing brake may be used. Further, the so-called fixed transmission ratio for transmitting power without passing through the fluid does not have to be the above-described fourth speed, and may be less than the fourth speed, or conversely, may be more than the fourth speed. FIG. 3 shows an example in which first and second brakes B1 and B2 composed of multi-plate brakes or band brakes for directly fixing the motor shafts 9 and 11 are provided and the fixed gear ratio is set to the third speed.

  In the power transmission device shown in FIG. 3, the second speed drive gear 18 </ b> A is attached to the first intermediate shaft 8 so as to rotate integrally, and the second speed driven gear 18 </ b> B meshed with the second speed drive gear 18 </ b> B is connected to the output shaft 16. It is attached to be freely rotatable. A start driven gear 21B is rotatably attached to the output shaft 16 adjacent to the second speed driven gear 18B, and a start drive gear 21A meshed with the output driven gear 21B rotates integrally with the motor shaft 9. It is attached. Between the second speed driven gear 18B and the start driven gear 21B, a fourth sync 40 for selectively connecting the second speed driven gear 18B and the start driven gear 21B to the output shaft 16 is disposed. Yes.

  On the other hand, a first speed drive gear 20A is attached to the second intermediate shaft 10 so as to rotate integrally therewith, and a third speed drive gear 19A is disposed adjacent to the second intermediate shaft 10 and attached to the second intermediate shaft 10. It is attached to rotate together. A first speed driven gear 20B meshed with the first speed drive gear 20A is rotatably attached to the output shaft 16, and a third speed driven gear 19B meshed with the third speed drive gear 19A is connected to the output shaft 16. It is attached so that it can rotate freely. A second sync 23 for selectively connecting the first speed driven gear 20B and the third speed driven gear 19B to the output shaft 16 is disposed between the first speed driven gear 20B and the third speed driven gear 19B. Has been.

  Then, the first brake B1 for selectively fixing the motor shaft 9 connected to the rotor of the first pump motor 12 and the motor shaft 11 connected to the rotor of the second pump motor 13 are selectively fixed. A second brake B2 is provided. The other configuration is the same as the configuration shown in FIG. 1, and therefore, the same reference numerals as those in FIG. In the example shown in FIG. 3, the fourth speed gear pair is not provided. In FIG. 3, the power source and the electronic control device are omitted.

  In the power transmission device configured as shown in FIG. 3, when setting the second speed which is a fixed gear ratio, the motor shaft 9 is fixed by the first brake B <b> 1, and the first planetary planet is substituted for the first pump motor 12. A reaction force is applied to the sun gear 3S of the gear mechanism 3. This is the same state as fixing the first pump motor 12 with the first sync 22 in the example shown in FIG. 1 described above, and therefore, no high pressure is generated in each pump motor 12, 13. Power loss due to leakage or the like can be prevented or suppressed. When the first speed or the third speed, which is a fixed gear ratio, is set, the motor shaft 11 is fixed by the second brake B2 and is opposed to the sun gear 4S of the second planetary gear mechanism 4 in place of the second pump motor 13. Give power. This is the same state as fixing the second pump motor 13 with the R synchro 25 in the example shown in FIG. 1 described above, and therefore, no high pressure is generated in each pump motor 12, 13. It is possible to prevent or suppress power loss caused by the above.

  As described based on the above specific examples, the power transmission device of the present invention includes the variable displacement pump motors 12 and 13 that can be controlled in a locked state in which the rotation is stopped. When the rotation of the shafts 9 and 11 is stopped, it is configured to be fixed by a mechanical brake mechanism, so that a high pressure is generated in the pump motors 12 and 13 and a power caused by a fluid pressure leak or the like accordingly. It is possible to prevent or suppress the occurrence of loss. Further, as shown in FIG. 1, if the synchros 22 and 25 are configured to be engaged with the fixed hubs 26 and 28, the space on both sides of the synchro can be used effectively. Can be made more compact and the in-vehicle performance can be improved.

  Here, the relationship between the above specific example and the present invention will be briefly described. The planetary gear mechanisms 3 and 4 and the gear pairs 17, 18, 19, 20, and 21 correspond to the transmission mechanism of the present invention.

  The present invention is not limited to the specific examples described above, and the power from the power source is input to one of the rotor and casing of the pump motor and the power is output from the other to the motor shaft or the like. By configuring, the pump motor itself may be configured to perform a differential action. When configured in this manner, the above-described planetary gear mechanism can be saved. In the present invention, a mechanism such as a belt or a chain may be used instead of the gear pair. Further, when a gear mechanism having a differential action is used in the present invention, for example, a double pinion type planetary gear mechanism can be used in place of the single pinion type planetary gear mechanism, or a differential gear mechanism of another configuration is used. You can also Furthermore, the power source may be connected to the idle gear of the counter gear pair described above instead of being directly connected to one of the differential mechanisms.

It is a skeleton figure which shows typically an example of the power transmission device concerning this invention. It is a table | surface which shows collectively the operation state of each pump motor and each synchro at the time of setting each gear stage. It is a skeleton figure which shows typically the other example of the power transmission device which concerns on this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Power source (E / G), 2 ... Input member, 3 ... 1st planetary gear mechanism, 4 ... 2nd planetary gear mechanism, 3S, 4S ... Sun gear, 3R, 4R ... Ring gear, 3C, 4C ... Carrier, 8 1st intermediate shaft, 9 ... motor shaft, 10 ... 2nd intermediate shaft, 11 ... motor shaft, 12 ... variable displacement pump motor (first pump motor), 13 ... variable displacement pump motor (second pump motor) 16 ... output shaft 17, 18, 19, 20, 21 ... gear pair, 17A ... fourth speed drive gear, 18A ... second speed drive gear, 17B ... fourth speed driven gear, 18B ... second speed driven gear 19A ... 3rd speed drive gear, 21A ... Starting drive gear, 21B ... Starting driven gear, 22 ... First synchronizer (first synchronizer), 23 ... Second synchronizer (second synchronizer), 24 ... First. 3 Kuronaiza (Third synchronizer), 25 ... synchronizer for reverse (R synchro), 26, 28 ... fixed hub, 27 ... fixed portion, 39 ... electronic control unit (ECU), 40 ... fourth synchronizer.

Claims (4)

In the power transmission device that transmits the power output from the power source to the output member via the transmission mechanism,
The transmission mechanism has a mechanism for transmitting the power output from the power source to the output member by applying a reaction force;
A variable displacement fluid pressure pump motor that applies a reaction force to the transmission mechanism;
And a brake mechanism for selectively connecting and fixing a rotor of the variable displacement fluid pressure pump motor to a predetermined fixing portion. The transmission mechanism includes a rotary shaft connected to a rotor of the variable displacement fluid pressure pump motor, and is rotatably fitted to the rotary shaft and connected to the rotary shaft, thereby being connected to the output member. A transmission rotator for transmitting power, and a clutch mechanism for selectively connecting the transmission rotator to the rotating shaft;
The brake mechanism includes a fixed engagement portion that connects the rotation shaft to the predetermined fixed portion when the clutch mechanism is engaged in a state where the clutch mechanism is separated from the transmission rotating body. The power transmission device according to claim 1. The clutch mechanism includes a synchronous coupling mechanism that engages with the transmission rotating body by moving a sleeve in an axial direction of the rotating shaft and connects the rotating shaft and the transmission rotating body;
The fixed engaging portion is disposed on the opposite side of the transmission rotating body with the synchronous connecting mechanism interposed therebetween, and is fixed to selectively engage the sleeve and connect the rotating shaft to the predetermined fixing portion. The power transmission device according to claim 2, further comprising a hub. The transmission mechanism includes a planetary gear mechanism that performs a differential action using a sun gear, a carrier, and a ring gear as rotational elements,
One of these rotating elements is connected to the rotor of the variable displacement fluid pressure pump motor, and the other rotating element is connected to the transmission rotor directly or via the clutch mechanism. The power transmission device according to claim 2, wherein another rotating element is connected to the power source.

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