JP5248895B2 - Traveling work vehicle - Google Patents

Description

  The present invention relates to a traveling work vehicle such as a wheel loader, and more particularly to a traveling work vehicle that is hybridized by combining power from an engine and power from an electric motor as a drive source in the traveling work vehicle.

  2. Description of the Related Art Conventionally, in a traveling work vehicle such as a wheel loader, a configuration in which a working machine such as a boom or a bucket and a traveling body such as a wheel are operated using an engine as a driving source is known as a general configuration. For example, a wheel loader is used in a combination of a start / stop pattern in traveling, a soil sanding pattern by a work machine, and a pattern such as earth lifting and soil removal. Moreover, these combined patterns are repeated within a short time cycle.

  As a result, the engine as the power source is controlled in accordance with a severe variable load, and therefore the engine output torque and the engine speed are frequently adjusted. In addition, the engine rotational speed and the engine output torque must be adjusted in accordance with the severe fluctuating load, which hinders deterioration of fuel consumption and suppression of exhaust gas.

  On the other hand, in recent years, attempts have been made to reduce the load fluctuation applied to the engine by combining the power from the engine as the drive source of the traveling work vehicle with the power from the electric motor to achieve hybridization.

  As a hybrid work vehicle, the conventional wheel loader uses a torque converter or HST circuit to distribute power to the work machine pump and the drive transmission via a torque converter or HST circuit. In particular, there has been proposed a hybrid construction vehicle (see Patent Document 1) in which only the traveling side having a large required power is electrified. In addition, a hybrid drive type wheel system work vehicle (see Patent Document 2) in which an electric motor as a power source for a work machine and an electric motor as a power source for traveling are separately provided has been proposed. .

  Furthermore, the continuously variable transmission that changes the output from the engine is composed of two electric motors and three planetary speed reducers, and the power can be switched as required from low speed to high speed. A transmission (see Patent Document 3) and two electric motors that also act as a generator are arranged on the output shaft of the engine, and the two electric motors and one planetary speed reducer constitute a continuously variable transmission. Hybrid type vehicles (see Patent Document 4) have been proposed.

  The hybrid construction vehicle described in Patent Document 1 is shown as a conventional example 1 according to the present invention, and FIG. 9 shows an overall configuration diagram of the hybrid construction vehicle. As shown in FIG. 9, the power output from the engine 50 is distributed through a power distribution mechanism 55, and drives a hydraulic pump 51 for a work implement actuator and a generator 52 that converts it into electric energy.

  The electric energy generated by the generator 52 is charged in the battery 54, and the electric power from the battery 54 is supplied to the motor 53 as traveling power. Further, since the battery 54 can function as a buffer in the electric energy mode, the battery 54 can absorb a violent power fluctuation load required when the construction vehicle travels. Therefore, the output fluctuation of the engine 50 can be leveled. Further, by providing the clutch 56 on the output shaft of the engine 50, it is possible to perform idling stop.

  The hybrid drive wheel system work vehicle described in Patent Document 2 is shown as a conventional example 2 according to the present invention, and FIG. 10 shows an overall configuration diagram of the hybrid drive wheel system work vehicle. As shown in FIG. 10, an electric motor 61 as a power source for the work machine and an electric motor 62 as a power source for traveling are separately provided. Drive energy from the engine 60 is converted into electric energy by the generator 63 and the battery 64 is charged. The electric motor 61 and the electric motor 62 are driven by the electric energy charged in the battery 64.

  As described above, since the electric motor 61 for the working machine and the electric motor 62 for traveling can be controlled as completely independent power sources, only the necessary power is taken out from the battery 64 regardless of the operating conditions. Can be used. The engine 60 can be operated under optimum conditions both in terms of fuel consumption and exhaust gas. Further, the regenerative energy from the work machine and the regenerative energy from the traveling power can be stored in the battery 64 by using the electric motors 61 and 62 as generators.

  The electromechanical transmission described in Patent Document 3 is shown as a conventional example 3 according to the present invention, and FIG. 11 shows an overall configuration diagram of the electromechanical transmission. As shown in FIG. 11, the power from the engine 70 is taken out from the output shaft 71 via the continuously variable transmission and used as power for driving the vehicle. The continuously variable transmission consists of two generator-motors 72, 73 and three planetary speed reducers 74, 75, 76, allowing the vehicle to switch speeds as required from low speed to high speed. ing.

  The hybrid type vehicle described in Patent Document 4 is shown as a conventional example 4 according to the present invention, and FIG. 12 shows an overall configuration diagram of the hybrid type vehicle. As shown in FIG. 12, two electric motors 82 and 83 that also act as a generator are arranged on the output shaft 81 of the engine 80, and the two electric motors 82 and 83 and one planetary speed reducer 84 are stepless. It constitutes a transmission.

Since it is configured in this way, acceleration / deceleration control when the hybrid vehicle moves forward / backward is controlled freely by the control of the two electric motors 82 and 83 while maintaining a mode in which the engine speed is kept constant. It becomes possible to do.
JP 2005-133319 A JP 2006-233843 A JP 2000-108693 A JP 05-281542 A

  A traveling work vehicle such as a wheel loader requires a very large traveling power during excavation. That is, during digging, a large traction force with a large torque is required while running at a low speed. Therefore, in the hybrid construction vehicle and the wheel system work vehicle disclosed in Patent Documents 1 and 2, it is inevitable to increase the size of the electric motor when attempting to obtain a large traction force while performing medium / low speed traveling.

  Furthermore, in order to satisfy the demand for large torque, it is desirable to increase the size in the radial direction as compared with the size in the axial direction as the configuration of the rotor in the electric motor. However, on the other hand, it is necessary to rotate the electric motor at high speed when the traveling work vehicle is cruising. For this purpose, the rotor of the electric motor is configured to be long in the axial direction and small in the radial direction. This is a desirable configuration.

  In this way, contradictory circumstances occur which are mutually contradictory in the motor design. Therefore, in the hybrid construction vehicle and the wheel system work vehicle shown in Patent Documents 1 and 2, if priority is given to taking out large torque at medium and low speeds, it is difficult to satisfy the maximum speed during cruise traveling. I have a problem that becomes.

  That is, the hybrid construction vehicle of Patent Document 1 has a configuration in which traveling power is provided by a single electric motor 53. For this reason, the electric motor 53 must have both characteristics such that a large torque can be output at medium and low speeds and a high speed rotation can be performed at high speeds. In order to satisfy both of these characteristics, the electric motor 53 must have a very large configuration.

  Further, in the wheel system work vehicle disclosed in Patent Document 2, as in the case of the hybrid construction vehicle disclosed in Patent Document 1, the traveling power motor must be configured to be large. Moreover, since the electric motor 61 is separately provided for the work machine, the electric motor 61 that is not used at all other than when the work machine is driven is mounted. Furthermore, it is necessary to configure a wide space for mounting the electric motors 61 and 62, and the cost of the on-vehicle equipment is greatly increased.

  Furthermore, in the wheel system work vehicle of Patent Document 2, all of the drive output from the engine 60 is converted into electric energy by the generator 63 and the battery 64 is charged. The electric power charged in the battery 64 is used as electric power for driving the electric motor 61 for operating the work implement and the electric motor 62 for traveling. For this reason, when the wheel system work vehicle of patent document 2 is seen from the surface of the energy utilization efficiency in the whole system, the problem that the energy utilization efficiency in the whole system will fall has arisen. Moreover, this problem has become such a big problem that it cannot be ignored.

  As means for solving the problems in the hybrid construction vehicle and wheel work vehicle shown in Patent Documents 1 and 2, as shown in Patent Documents 3 and 4, the driving power from the engine is combined with the power from the electric motor. A continuously variable transmission has been proposed.

  In the traveling work vehicle equipped with the electromechanical transmission shown in Patent Document 3, it is inevitable that the clutch is engaged in the most frequently used low speed range to medium speed range, and the clutch engagement is performed every time the gear shift is performed. The number of times will increase. Further, since the clutch is frequently engaged during the work, the life of the clutch is deteriorated in addition to the shift shock. Or, in order to prevent the deterioration of the clutch life, an increase in the size of the clutch is inevitable.

  In the hybrid vehicle shown in Patent Document 4, when the high-speed cruise operation is performed with the hybrid vehicle, the number of rotations of the electric motors 82 and 83 to be mounted becomes extremely large. For this reason, it is necessary to increase the size of lubrication equipment and cooling devices. In addition, there are problems such as a reduction in the life of the rotating parts of the electric motors 82 and 83, a reduction in system efficiency due to loss of the rotating parts, and a reduction in the reliability of the electric motors 82 and 83.

  The present invention improves the energy efficiency of the entire system, makes it possible to control the acceleration / deceleration of the forward / rearward movement with a simple structure, enables the most efficient engine operation in terms of engine fuel consumption and exhaust gas, Equipped with a power transmission structure that can distribute the mechanical power and traveling power efficiently and without shifting shock in real time, and further switch the output shaft that selectively transmits the power to the wheel drive system at medium and low speeds and at high speeds A traveling work vehicle that can be used is proposed.

The object of the present invention can be achieved by the inventions described in claims 1 to 3.
That is, in the traveling work vehicle of the present invention, the first generator motor and actuator drive system connected in series to the output shaft of the engine, the speed reducer having a plurality of planetary gear mechanisms arranged in series, and the engine are different. A second generator motor connected to the drive source, a wheel drive system connected to the output shaft of the reduction gear to which the output shaft of the second generator motor is connected, the first generator motor and the second generator motor A power storage device connected via an inverter, and the output shaft of the second generator motor and the output shaft of the speed reducer are arranged on the same axis, and the output shaft of the engine and the speed reducer The output shaft and the input shaft of the wheel drive system are respectively arranged on different shaft cores, and the output shaft of the first generator motor and the second shaft are connected to different input portions of the reduction gear. An output shaft of the electric motor is connected to each other, the output shaft of the speed reducer is taken out from the output portion of the planetary gear mechanism in a different row, and one output shaft is used as an output shaft for medium and low speed, and the other The output shaft is configured as a high-speed output shaft, and the medium-low-speed output shaft and the high-speed output shaft are each connected to the input shaft of the wheel drive system via a pair of clutches. It is done.

In the traveling work vehicle of the present invention, the reduction gear is configured by a planetary gear mechanism having three rows, and the output shaft of the first generator-motor is the first row of planetary gear mechanisms and the second row of planets. Connected to the gear mechanism,
The medium-low speed output shaft in the reduction gear is taken out from the output part of the planetary gear mechanism in the first row or the planetary gear mechanism in the third row, and the output shaft for high speed is the planetary gear mechanism in the third row. Alternatively, the main feature is that it is taken out from the output portion of the planetary gear mechanism in the first row.
Furthermore, the traveling work vehicle of the present invention is mainly characterized in that the pair of clutches are provided on the input shaft of the wheel drive system.

The traveling working vehicle of the present invention, the power from the engine can be transmitted to the first generator-motor and the actuator drive system. Further, the power from the engine can be transmitted to a reduction gear configured by a plurality of planetary gear mechanisms via the first generator motor. In addition, power from the second generator motor connected to a drive source different from the engine can be transmitted to the same reduction gear. Then, two types of outputs for medium and low speed and high speed are extracted from the speed reducer, and the two types of extracted outputs are selected via a pair of clutches and transmitted to the input shaft of the wheel drive system. ing.

  Further, the input part of the reduction gear connected to the output shaft of the first generator motor and the input part of the reduction gear connected to the output shaft of the second generator motor are configured as different input parts. Thereby, the drive rotation speed output from the reduction gear can be controlled to an arbitrary rotation speed by the rotation speed at the output shaft of the first generator motor and the rotation speed at the output shaft of the second generator motor.

  Moreover, by taking out the output from the speed reducer from the planetary gear mechanisms in different rows among the planetary gear mechanisms constituting the speed reducer, one output shaft is configured as a medium / low speed output shaft, and the other The output shaft can be configured as a high-speed output shaft.

  With this configuration, when the energy required to drive the actuator drive system and the wheel drive system cannot be obtained only by driving the engine, the first generator motor and / or the second generator motor is appropriately used as the motor. By working, you can make up for the shortage of energy. Examples of the actuator drive system include a hydraulic pump drive system. In the following, description will be continued for a case where a hydraulic pump drive system is configured as the actuator drive system.

  When the energy required to drive the hydraulic pump drive system and wheel drive system is sufficient with only the power of the engine, the first generator motor is operated in a free mode so that the engine output shaft The first generator motor can be used as a kind of provided flywheel. Also, when the engine power is surplus or when power returns from the hydraulic pump drive system, the surplus energy and regenerative energy are converted into electrical energy by using the first generator-motor as a generator to store electricity. The device can be charged.

Further, during the forward / backward advance and acceleration / deceleration operations of the traveling work vehicle, the regenerative energy by the power returned from the wheel drive system side to the reduction gear is generated by the first generator motor and / or the second generator motor operated as a generator. Can be converted into electric energy and charged in the power storage device.
The electric energy charged in the power storage device in this way can be used as driving energy when the first generator motor and the second generator motor are operated as motors.

In addition, switching of each use mode in a 1st generator motor and a 2nd generator motor is controlled according to the rotation speed of an engine, the driving mode of a traveling work vehicle, and the rotation speed which drives the wheel in a wheel drive system. I can keep it.
The respective use modes in the first generator motor and the second generator motor can be a free rotation mode in which no torque is generated, a mode in which the motor operates as a generator, and a mode in which the motor operates as a motor.

  And each use mode in a 1st generator motor and a 2nd generator motor can be switched according to the rotation speed of an engine, the driving mode of a traveling work vehicle, and the rotation speed which drives the wheel in a wheel drive system. . In this way, by switching the respective use modes in the first generator motor and the second generator motor, it is possible to control the torque and the rotational speed applied to the wheel drive system to be optimum. In addition, in each of the first generator motor and the second generator motor, the power returning from the wheel drive system to the first generator motor and the second generator motor can be absorbed by the first generator motor and / or the second generator motor. The usage mode can be switched.

  Since the output from the speed reducer can be taken out separately for the medium-low speed output shaft and the high-speed output shaft, by selectively controlling the connection / disconnection of the pair of clutches, The required number of revolutions and the number of revolutions required for traveling in the low to medium speed range can be easily extracted.

  By arranging the output shaft of the engine, the output shaft of the speed reducer, and the input shaft of the wheel drive system on different shaft cores, the longitudinal dimensions of the first generator motor, the second generator motor, and the speed reducer can be adjusted. It can be made short. Thereby, a 1st generator motor, a 2nd generator motor, and a reduction gear device can be arranged between a wheel drive system and an engine.

  Since the first generator motor, the second generator motor, and the speed reducer can be made compact, without changing the layout dimension between the wheel drive system and the engine, which is configured in the conventional traveling work vehicle, The first generator motor, the second generator motor, and the speed reducer can be mounted. As a result, the traveling work vehicle can be easily hybridized.

  In addition, since the medium-low speed output shaft and the high-speed output shaft can extract the medium-low speed rotation and the high-speed rotation, the high-speed output shaft can be used as the input shaft of the wheel drive system when high-speed driving is required. By simply connecting, it is possible to give the wheel drive system the necessary number of revolutions only by controlling the first generator motor and the second generator motor without changing gear shifts including engagement of clutches and brakes. it can. For this reason, in order to give high-speed rotation to a wheel drive system, it is not necessary to enlarge the second generator motor and configure the rotational speed of the second generator motor to be extremely high.

  Furthermore, when obtaining a speed from low speed to medium speed range during normal work, simply connecting the output shaft for medium to low speed to the input shaft of the wheel drive system is necessary for the wheel drive system. The number of rotations to be given can be given. Therefore, there is no worry about shift shocks.

  Moreover, in the traveling work vehicle of this invention, it can comprise by the planetary gear mechanism which consists of three rows as a structure of a reduction gear. The output shaft of the first generator motor can be connected to the planetary gear mechanism in the first row and the planetary gear mechanism in the second row. Further, it is possible to adopt a configuration in which the medium / low speed output shaft is taken out from one of the first row planetary gear mechanism and the third row planetary gear mechanism, and the high speed output shaft is taken out from the other.

  By configuring in this way, it is possible to perform deceleration control by applying the rotation of the second generator motor where a small torque is applied in the reduction gear. Thereby, it is possible to prevent a high-load reaction force from acting on the second generator motor, and to extend the life of the second generator motor.

  In the traveling work vehicle of the present invention, a pair of clutches can be provided on the input shaft of the wheel drive system. By comprising in this way, even if a pair of clutch is arrange | positioned, the length dimension of the output direction in a reduction gear can be comprised short.

  In addition to the configuration in which the pair of clutches are provided on the input shaft of the wheel drive system, the respective clutches may be provided on the medium / low speed output shaft and the high speed output shaft.

  Preferred embodiments of the present invention will be specifically described below with reference to the accompanying drawings. The configuration of the traveling work vehicle of the present invention will be described below by taking a wheel loader as an example. However, as the traveling work vehicle of the present invention, the present invention can be suitably applied to a traveling work vehicle such as a forklift, for example, other than the wheel loader configuration described below. For this reason, this invention is not limited to the Example demonstrated below, A various change is possible.

  FIG. 1 is an overall configuration diagram showing an internal structure of a traveling work vehicle 1 according to an embodiment of the present invention. As shown in FIG. 1, power from the engine 2 is transmitted to the first generator motor 3 connected to the shaft A that is the output shaft of the engine 2, and the shaft B that is the output shaft of the first generator motor 3 is transmitted to the first generator motor 3. Via the shaft B and to the actuator drive system (not shown) connected to the shaft C via the shaft B.

  The power from the second generator motor 4 configured as a drive source different from the engine 2 is transmitted to the second input IN2 of the reduction gear 5 via the axis D which is the output shaft of the second generator motor 4. It has a configuration. That is, the axis B is connected to the first input IN1 of the speed reducer 5, and the axis D is connected to the second input IN2 of the speed reducer 5. The output shaft from the reduction gear 5 includes a high-speed output shaft 5a that outputs high-speed rotation and a medium-low speed output shaft 5b that outputs medium-low speed rotation. The high speed output shaft 5a is connected to the second output OUT2 of the speed reducer 5, and the medium / low speed output shaft 5b is connected to the first output OUT1 of the speed reducer 5.

  The rotation of the output shaft 5a for high speed and the output shaft 5b for medium / low speed is performed by transmission gears 8a and 8b, transmission gears 9a and 9b, and a first clutch CL1 and a second clutch CL2 provided on the input shaft 11 of the wheel drive system 10, respectively. It is configured to be transmitted to the input shaft 11 via That is, when the first clutch CL1 is connected and the second clutch CL2 is disconnected, the rotation of the high-speed output shaft 5a can be taken out by the input shaft 11 via the transmission gears 8a and 9a. Further, when the first clutch CL1 is disconnected and the second clutch CL2 is connected, the rotation of the medium / low speed output shaft 5b can be taken out by the input shaft 11 through the transmission gears 8b and 9b.

  The reduction gear 5 has a configuration in which a plurality of planetary gear mechanisms are arranged in series, as shown in the internal configuration of the reduction gear 5 in FIGS. Further, the configuration in which the first clutch CL1 and the second clutch CL2 are provided on the input shaft 11 has been described. However, the first clutch CL1 and the second clutch CL2 are respectively connected to the high-speed output shaft 5a and the medium-low speed output shaft 5b. It can also be set as the structure provided in.

  The plurality of planetary gear mechanisms constituting the reduction gear 5 are not limited to the three-row planetary gear mechanisms as shown in the fourth to sixth embodiments, and are configured as a plurality of two or more rows. Can be kept.

  When power returning from the wheel drive system 10 or power returning from an actuator drive system (not shown) connected to the shaft C acts on the shaft B, the shaft B does not become the output shaft of the first generator motor 3. In addition, the first generator motor 3 functions as an input shaft that works as a generator.

Similarly, when the engine 2 is not overloaded, or when the power returned from the wheel drive system 10 acts on the axis D, the axis D does not become the output shaft of the second generator motor 4. In addition, the second generator motor 4 functions as an input shaft that works as a generator.
At this time, the high-speed output shaft 5a or the medium / low-speed output shaft 5b, which is the output shaft of the speed reducer 5 to be described next, is used to input power returned from the wheel drive system 10 to the speed reducer 5. Will function as.

  The rotation from the high-speed output shaft 5a or the medium / low-speed output shaft 5b is introduced into the wheel drive system 10 by the input shaft 11. The wheel drive system 10 includes a power transmission mechanism 15 to which the output from the input shaft 11 is transmitted, a front differential 16a, a rear differential 16b, a front differential 16a and a rear differential 16b to which the output from the power transmission mechanism 15 is transmitted, respectively. In this configuration, a pair of front wheels 18a and a pair of rear wheels 18b that are rotationally driven by the rotation distributed by the motor are provided.

  Further, for the front wheel 18a and the rear wheel 18b, a front wheel brake 17a and a rear wheel brake 17b for applying braking to the respective wheels are provided. The front wheel brake 17a and the rear wheel brake 17b are operated by operating a brake pedal 27 described later.

  As shown in the second embodiment, the actuator drive system (not shown) to which the rotational force from the shaft C is transmitted includes a variable displacement hydraulic pump for driving the actuator, a pilot pressure supply, and a pressure oil for driving the auxiliary machine. It can be configured as a hydraulic pump drive system including a fixed displacement hydraulic pump to be supplied, or a drive system that outputs power other than traveling driving.

  The first generator motor 3 is connected to a battery 21 that is a power storage device via a first inverter 20a, and the second generator motor 4 is connected to the battery 21 that is a power storage device via a second inverter 20b. Yes. The first inverter 20a and the second inverter 20b are, according to the control signal from the controller 25, the first generator motor 3 and the second generator motor 4 in a free rotation mode, a mode in which the motor operates as a generator, and a mode in which the motor operates as a motor. Can be switched to.

  When the first generator motor 3 and the second generator motor 4 are operated as generators, the battery 21 can be charged with the electric energy generated by the first generator motor 3 and the second generator motor 4. . Further, when the first generator motor 3 and the second generator motor 4 are operated as electric motors, the first generator motor 3 and the second generator motor 4 can be operated as electric motors with the electric power charged in the battery 21.

  The controller 25 receives a detection signal from a speed sensor 30 that detects the number of rotations in the input shaft 11, and also includes an operation amount of an accelerator pedal 26, an operation amount of a brake pedal 27, a switching position in a forward / reverse switching lever 28, and the like. The signal concerning is input. The controller 25 controls the amount of fuel to the engine 2 with respect to a fuel injection device (not shown) based on the values of these input signals and the like, the control signal for the first inverter 20a and the second inverter 20b, the first A connection / disconnection control signal for the clutch CL1 and the second clutch CL2 is output.

  That is, when the controller 25 determines that the power from the engine 2 is insufficient, the first inverter 20a and / or the second inverter is used so that the first generator motor 3 and / or the second generator motor 4 are operated as a motor. Control 20b. Also, when it is determined that there is power returned from the wheel drive system 10 or an actuator drive system (not shown) connected to the axis C, or when it is determined that the power from the engine 2 is surplus, or the engine 2 is excessive. For example, when it is determined that an overload is applied, the first inverter 20a and / or the second inverter 20b is used so that the first generator motor 3 and / or the second generator motor 4 function as a generator. Control.

Since the axis B of the first generator motor 3 is connected to the first input IN1 of the speed reducer 5 and the axis D of the second generator motor 4 is connected to the second input IN2 of the speed reducer 5, the rotational speed of the engine 2 Even in the mode in which the constant speed is maintained, by controlling the rotational speed of the first generator motor 3 on the axis B and the rotational speed of the second generator motor 4 on the axis D, the high-speed output shaft 5a and the medium-low speed Each rotation speed output from the output shaft 5b can be controlled to be a desired rotation speed.
Then, by controlling the rotational speed of the engine 2 with the controller 25, the rotational speeds output from the high-speed output shaft 5a and the medium-low speed output shaft 5b can be controlled more finely.

  That is, the rotational fluctuation amount of the shaft B interlocked with the engine 2 is suppressed so as to be minimized, and the rotational speed of the second generator motor 4 operated as an electric motor is greatly varied, so that the traveling work vehicle is Thus, it is possible to perform a necessary traveling operation. In addition, since the first generator motor 3 is provided on the shaft B interlocked with the engine 2, the mode and motor in which the first generator motor 3 is used as a generator so that the amount of rotational fluctuation of the shaft B is minimized. It is possible to control the mode to be used or a free mode that does not generate torque.

  In addition, when the first generator motor 3 and the second generator motor 4 are operated by the IV quadrant operation of forward / reverse rotation, power running and regeneration, respectively, the power from the engine is used as in the past. With the same operation as the operation, it is possible to perform forward / backward movement and acceleration / deceleration operations on the traveling work vehicle. The power necessary to perform each operation can be uniformly applied to the wheel drive system 10.

  Further, the power returned from the wheel drive system 10 can be absorbed by the first generator motor 3 and the second generator motor 4. Moreover, since the power returned from the wheel drive system 10 can be absorbed by the first generator motor 3 and the second generator motor 4, the engine 2 is overloaded by the power returned from the wheel drive system 10. It can be prevented from joining.

  Here, the IV quadrant operation described above will be explained. The IV quadrant here refers to the direction of rotation and the sign of torque in the axis B of the first generator motor 3, the axis D of the second generator motor 4, the output shaft 5a for high speed and the output shaft 5b for medium and low speed of the speed reducer 5. It is defined as a quadrant to show the relative relationship with.

  That is, the case where both the rotational speed and the torque have a plus sign is the first quadrant, the case where the rotational speed is a negative sign and the torque is a positive sign, the second quadrant, and the case where both the rotational speed and the torque are negative signs. The fourth quadrant is the case where the rotation number is positive and the torque is negative. The quadrants I and III in which the second generator motor 4 is used as a motor are referred to as power running, and the II and IV quadrants in which the second generator motor 4 is used as a generator are referred to as regeneration. This is illustrated in FIG.

  The description of the IV quadrant operation will be described by taking as an example a case where a V-shape operation, which is a representative operation in the wheel loader used as the traveling work vehicle 1, is performed. V-shape operation is a series of operations that excavate piled sediment, load the sediment into the wheel loader bucket, reload the loaded sediment into a dump truck, and return to the original standby position after the replacement. This is the work (operation) for one cycle.

  When this series of cycle operations is performed only with the power from the engine as in the prior art, the time variation of the rotational speed and torque input to and output from the wheel drive system 10 is as shown in the graph of FIG. . Also in the hybrid traveling work vehicle 1 according to the present invention, the drive source of the engine 2, the first generator motor 3, and the second generator motor 4 is controlled as described below, so that the wheel drive system 10 is input and output. The graph of the change over time in the rotational speed and torque on the input shaft 11 can be drawn so as to be the same graph as the graph shown in FIG.

Therefore, in the following description, the graph shown in FIG. 3 will be described as being also a graph obtained by the present invention.
In the V-shape operation, since the wheel loader is traveling in a medium / low speed state, the first clutch CL is disengaged and the second clutch CL2 is connected as the input shaft 11 at this time. It is in a state connected to the shaft 5b.

  In FIG. 3, the thick line indicates the rotational speed input / output to / from the input shaft 11 of the wheel drive system 10, and the dotted line indicates the torque input / output to / from the input shaft 11 of the wheel drive system 10. The number of rotations and torque are given plus and minus signs.

  When the input shaft 11 of the traveling work vehicle 1 rotates in the forward direction, a plus sign is attached as the sign of the rotational speed, and the input shaft 11 of the traveling work vehicle 1 rotates in the reverse direction. In this case, a minus sign is attached as a sign of the rotational speed. In addition, when the signs of the rotational speed and torque are both positive and negative, the drive sources of the engine 2, the first generator motor 3 and the second generator motor 4 perform power running to indicate the state. When the signs of the torques are opposite to each other, a state is shown in which regeneration is performed by the power returned from the wheel drive system 10.

3 will be described with reference to FIG.
The stop mode “1” in the table of FIG.

  In the stop mode in which the wheel loader is stopped in an empty state, the brake is depressed, and the rotation of the output shaft 5b for the medium / low speed of the speed reducer 5 is stopped. For this reason, the rotational speed from the engine 2 is transmitted to the axis D of the second generator motor 4 via the reduction gear 5. Then, the second generator motor 4 idles in the minus direction and absorbs the rotational speed from the engine. At this time, the second generator motor 4 is in a free mode in which torque is not generated and is not a load on the engine 2.

  When the description of the table shown in FIG. 3 is added, the operation modes of “1” to “10” are arranged as items on the horizontal axis, and the second generator motor 4 and the first generator motor 3 are arranged as columns. The engine 2, shaft B, shaft C, accelerator pedal 26, brake pedal 27, and forward / reverse switching lever 28 are arranged in this order. And the place where the item on the vertical axis overlaps with the item on the horizontal axis shows the mode state of the member indicated by the item on the vertical axis in the operation mode set as the item on the horizontal axis.

  For example, in the stop mode “1”, the second generator motor 4 is in the second quadrant operation and is in a free mode in which torque is not generated. The first generator motor 3 and the engine 2 and the shaft B are all in the quadrant I operation. The axis C is in a “−” state that is not related to the traveling of the wheel loader. The accelerator pedal 26 is in the “OFF” state where it is not operated, the brake pedal 27 is in the “ON” state where it is operating, and the forward / reverse switching lever 28 is in the neutral position “N” position. Indicates that it is placed.

  The Roman numerals “I”, “II”, “III”, and “IV” represent the quadrants shown in FIG. 2, and “N”, “F”, “ “B” indicates that the switching positions of the forward / reverse switching lever 28 are a neutral position, a forward position, and a reverse position, respectively.

  The forward start mode of “2” in the table of FIG.

  In this forward start mode, the forward / reverse switching lever 28 enters the forward position “F”, the brake pedal 27 is changed from the “ON” state to the “OFF” state, and the accelerator pedal 26 is depressed from the “OFF” response to the “ON” state. Will be. The first generator motor 3, the second generator motor 4, or the shaft A of the engine 2 generates torque so that torque proportional to the amount of depression of the accelerator pedal 26 is generated at the medium / low speed output shaft 5b of the speed reducer 5. Let At this time, the torque distribution is determined by the second generator motor 4 and the first generator motor 3 or the axis A of the engine 2 according to the planetary gear coupling method in the planetary gear mechanism constituting the reduction gear 5 and the gear ratio at that time. Will be allocated.

  When the accelerator pedal 26 is depressed, a throttle (not shown) for supplying fuel to the engine 2 opens, and the engine 2 tries to increase the rotational speed together with the torque output. At this time, the medium-low speed output shaft 5b is rotated by the rotation of the engine 2.

  However, in order to run the wheel loader, a drive torque of a predetermined value or more is required. However, when the drive torque for rotating the medium / low speed output shaft 5b is equal to or less than the predetermined drive torque, the wheel loader is stopped. It is inside. For this reason, the reaction torque to be returned to the engine 2 from the stopped output shaft 5b for medium and low speed flows toward the axis D of the second generator motor 4.

At this time, the first generator motor 3 is controlled so as to rotate the medium / low speed output shaft 5b in the forward direction of the wheel loader while keeping the rotation speed output from the engine 2 constant.
The rotation speed of the second generator motor 4 is controlled by the controller 25 that monitors the rotation speed of the engine 2 so that the rotation speed of the medium / low speed output shaft 5b becomes a predetermined rotation speed. It can be detected by the speed sensor 30 provided on the input shaft 11 whether or not the rotation speed for medium and low speed has reached a predetermined rotation speed.

In the starting stage, the second generator motor 4 that has been idly reversed in the minus direction is controlled at a predetermined number of revolutions while generating electricity by rotating in the minus direction so as to satisfy the relational expression of the torque and the number of revolutions described above. (Second quadrant operation). As a result, a large torque required to advance the wheel loader can be output from the medium / low speed output shaft 5b of the speed reduction device 5 while keeping the engine rotation speed constant.
In this mode, the second generator motor 4 will act as a generator, and the generated energy will be charged to the battery 21 or consumed by the first generator motor 3 acting as a motor. Become.

  The forward mode “3” in the table of FIG.

  When the wheel loader starts moving forward in the forward mode, the second generator motor 4 gradually decreases the rotational speed and finally reaches zero speed. Since the medium / low speed output shaft 5b of the speed reducer 5 rotates based on the relative rotational speed between the shaft B and the shaft D, the second generator motor 4 The vehicle reaches the zero speed and further accelerates the vehicle by reversing the sign of the rotational speed from the negative rotation to the positive rotation.

  At this time, since the accelerator pedal 26 remains in the depressed “ON” mode, the rotation speed of the second generator motor 4 is successively increased in the output shaft 5b for the medium / low speed of the speed reducer 5 in an attempt to continue acceleration. In accordance with the rotational speed and the engine rotational speed, control is performed so as to obtain a desired rotational speed.

  When the sign of the rotation speed of the second generator motor 4 is reversed from minus to plus, the second generator motor 4 shifts from the power generation mode to the power running mode (first quadrant). That is, when the sign of the rotation speed of the second generator motor 4 is reversed to plus, the second generator motor 4 functions as an electric motor.

  As a result, the second generator motor 4 has so far supplied power generation energy for supplying power to the first generator motor 3, but energy is required for the second generator motor 4 to function as a motor. Since the engine 2 is also operating in the first quadrant simultaneously with the second generator motor 4, the first generator motor 3 becomes a generator (fourth IV quadrant) and supplies energy to the second generator motor 4. become. In this way, the same graph as the graph at the time of forward movement in FIG. 3 can be drawn as the rotational speed and torque of the medium-low speed output shaft 5b of the speed reducer 5.

  The forward and excavation modes of “4” and “5” in the table of FIG.

  In this forward / excavation mode, the soil moves forward while excavating soil. In this mode, the output from the output shaft 5b for medium / low speed of the speed reducer 5 requires that the wheel loader travels at medium / low speed and that a large torque is obtained. In this mode, the wheel loader receives a reaction force from the earth and sand, so the vehicle speed tends to become unstable.

  As a result, the wheel loader repeats start, stop, and advance in small steps, and the forward start mode and the forward mode described above are sequentially switched according to the travel mode of the wheel loader. At this time, it is the second generator motor 4 that needs to switch the operation most frequently.

  However, when the second generator motor 4 whose operation is switched most frequently is examined and examined, the rotational speed of the shaft A of the engine 2 or the shaft B of the first generator motor 3 and the output shaft 5b for the medium / low speed of the speed reducer 5 By constantly monitoring the rotational speed (in this application, detected by the speed sensor 30 as the rotational speed of the input shaft 11 of the wheel drive system 10), the accelerator opening by the accelerator pedal 26 and the vehicle speed of the wheel loader are determined. Thus, it can be seen that the rotation of the second generator motor 4 is only controlled so that the optimum torque and rotation speed can be drawn from the second generator motor 4.

  Also at this time, by controlling the first generator motor 3 and the second generator motor 4, the same graph as the graph at the time of forward excavation in FIG. Can be drawn.

  “6” reverse (sediment transport) mode in the table of FIG.

  In this reverse (sediment transport) mode, when the forward / reverse switching lever 28 is switched to the reverse position, the first generator-motor 3 is adapted to reverse the direction of the rotational speed of the medium / low speed output shaft 5b of the speed reducer 5. And the second generator motor 4 work together to change the control scheme.

  That is, the first generator motor 3 and the second generator motor 4 are controlled by the accelerator pedal opening of the accelerator pedal 26 so that the medium / low speed output shaft 5b of the speed reducer 5 rotates in the reverse direction. The second generator motor 4 is in the third quadrant operation mode in which the signs of the rotation speed and torque are reversed, and the first generator motor 3 is coaxial with the engine 2, so the rotation speed is constant, but the sign of torque is reversed. The fourth quadrant operation mode is set.

  As with the forward movement, the second generator motor 4 sets the output shaft 5b for the medium / low speed of the speed reducer 5 to a predetermined speed based on the speed of the engine 2 and the speed of the output shaft 5b for the medium / low speed of the speed reducer 5. Rotational speed control is performed. The first generator motor 3 is subjected to torque control for absorbing torque distributed from the medium / low speed output shaft 5b of the reduction gear 5 by the accelerator opening degree by the accelerator pedal 26. At this time, the reference rotational speed is determined by the rotational speed of the engine 2.

  Also at this time, by controlling the first generator motor 3 and the second generator motor 4, the rotation speed and torque at the medium / low speed output shaft 5 b of the speed reducer 5 can be obtained as a graph during reverse travel (sediment transport) in FIG. The same graph can be drawn.

  The “7” forward start mode, “8” forward mode, “9” forward / load mode, and “10” reverse mode in the table of FIG. The same control as in the mode is repeated.

  As described above, in the present invention, the engine 2, the first generator motor 3, and the second generator motor 4 are controlled corresponding to each work mode in the wheel loader while taking advantage of the hybrid of the traveling work vehicle. Thus, the same rotational speed and torque as those performed by the engine alone can be applied to the medium / low speed output shaft 5b of the reduction gear 5. That is, it is possible to operate a traveling work vehicle such as a hybrid wheel loader by the same operation as that performed by the engine alone.

  Returning to FIG. 1 and continuing the description, as the wheel loader, the traveling speed required for excavation / loading work is only required for the speed range from the low speed range to the medium speed range. However, on the other hand, it is necessary to be able to run at high speed when moving in the workplace.

  Therefore, when performing high-speed running, disconnect the connection between the output shaft 5b for medium and low speed and the input shaft 11, and connect the output shaft 5a for high speed to the input shaft 11, thereby reducing the number of revolutions required for high-speed running. Can be given to the wheel. For this reason, it is not necessary to enlarge the second generator motor 4 and to configure the rotational speed of the second generator motor 4 to be extremely high.

Further, during normal work, as described above, the speed is limited to the speed range from the low speed range to the medium speed range, so it is only necessary to connect the output shaft 5b for medium / low speed and the input shaft 11, such as a shift shock. No worries. Furthermore, when high-speed traveling is required, the vehicle starts off in an unloaded state where dirt or the like is not loaded in the bucket or other work machine, so the first clutch CL1 and the second clutch CL2 must be connected and disconnected. At the time of switching, since the medium speed is switched to the high speed traveling, the shift shock is not a big problem.
Since the present invention is configured as described above, the hybrid traveling work vehicle can be operated in the same operation as that performed by a conventional engine alone in the entire range from low speed to high speed.

  Further, the shaft B that is the input shaft of the reduction gear 5 that rotates in conjunction with the shaft A of the engine 2 can be rotated so that the fluctuation of the rotational speed is minimized. Alternatively, the rotational speed of the engine 2 can be controlled so that the engine rotational speed is most suitable for fuel consumption and exhaust gas reduction corresponding to the load required for the engine 2.

In the present invention, the functions of the engine 2, the first generator motor 3, the speed reducer 5, the second generator motor 4, the output shaft 5b for medium and low speed, the input shaft 11, and the output shafts 5a and 5b of the speed reducer 5 Can be summarized as follows.
That is, the engine 2 is required to output an optimum rotational speed in accordance with the required load, and further, is required to have an engine rotational speed most suitable for fuel consumption and exhaust gas reduction. That is, the engine 2 has a rotational speed required for the output shafts 5a and 5b of the speed reducer 5 required to obtain traveling power for running the wheel loader, and a rotational speed required for the output shafts 5a and 5b of the speed reducer 5. And the optimum rotational speed required for the engine 2 is required.

The second generator motor 4 adjusts the rotational speed from the engine 2 via the speed reducer 5 so that the speed required for the output shafts 5a and 5b of the speed reducer 5 can be output.
As the first generator motor 3, when the output required from the engine 2 and the optimal engine speed cannot be adjusted from the output from the engine 2 and the output from the second generator motor 4, The first generator motor 3 works as a motor to assist the shortage. As a result, the load on the engine 2 can be reduced. Further, in order to rotate the engine 2 at the optimum rotational speed, it may function as a load on the engine 2 or may function as a generator that supplies electric power to the battery 21.

Then, by generating electricity by using the first generator motor 3 as a generator, it is possible to brake the rotation of the engine 2 and to increase the load applied to the engine 2.
However, the amount of power stored when the first generator-motor 3 is operated as a generator is also limited by the amount of power stored in the battery 21 that is the power source of the second generator-motor 4.

As the speed reducer 5, the speed and torque input from the shaft B from the engine 2 and the first generator motor 3 and the axis D of the second generator motor 4 are adjusted in the speed reducer 5 to reduce the speed reducer. It can output to five output shafts 5a and 5b.
As the output shafts 5a and 5b of the speed reducer 5, it is possible to output rotation in accordance with the traveling speed of the wheel loader. Then, by connecting / disconnecting the first clutch CL1 and the second clutch CL2, high speed rotation or medium / low speed rotation can be supplied to the wheel drive system 10.

  FIG. 4 shows a second embodiment according to the present invention and shows an example in which a hydraulic pump drive system 6 is configured as an actuator drive system. Other configurations are the same as those in the first embodiment. Therefore, regarding the same members, the same reference numerals as those used in Example 1 are used, and the description thereof is omitted. Further, regarding the configuration of a part of the controller 25, the speed sensor 30, the accelerator pedal 26, etc. shown in FIG. 1, those members are not shown in FIG.

  Moreover, also in FIGS. 5-8 which each demonstrate the structure of Example 3 to Example 6 demonstrated below, about the same member, the description is used by using the same code | symbol as the member code | symbol used in Example 1. FIG. The components of the controller 25, the speed sensor 30, the accelerator pedal 26, etc. shown in FIG. 1 are also omitted, and the members are not shown in FIGS.

  As shown in FIG. 4, the hydraulic pump drive system 6 to which the rotational force from the shaft C directly connected to the shaft B is transmitted includes a first hydraulic pump 6a and a second hydraulic pump 6b. The first hydraulic pump 6a is configured as a variable displacement hydraulic pump that supplies pressure oil to a working machine actuator, etc., and the second hydraulic pump 6b is a fixed displacement type for driving auxiliary equipment that discharges pilot pressure, etc. It is configured as a pump.

  In the second embodiment, the first hydraulic pump 6a has an arrangement configuration in which the first hydraulic pump 6a is directly coupled to the engine shaft or coupled to an interlocked shaft. The shaft B of the first generator motor 3 is connected to the first input IN1 of the reduction gear 5. With this configuration, the shaft C of the first hydraulic pump 6a has a configuration in which the rotation fluctuation is small and rotates only in one direction, and the pump load can be efficiently driven at any time.

  Next, the operation of the hydraulic pump drive system 6 that drives the work machine actuator during excavation work at medium to low speed will be described. At this time, the number of revolutions of the engine 2 is set to be lower in accordance with a request for traveling power supplied to the wheel loader. On the other hand, since the first hydraulic pump 6a that drives the work implement actuator requires a large amount of power, the discharge flow rate from the first hydraulic pump 6a is increased.

  Therefore, by configuring the first hydraulic pump 6a as a variable displacement hydraulic pump, the pump discharge capacity per one rotation of the first hydraulic pump 6a can be controlled only by controlling the swash plate angle of the first hydraulic pump 6a. Can be increased. In addition, the discharge flow rate from the first hydraulic pump 6a can be increased even when the rotational speed of the engine 2 is kept low, so that the operating speed and power of the work implement actuator do not decrease. That is, the range in which the power in the work implement actuator can be adjusted is expanded regardless of the rotational speed of the engine 2.

  It should be noted that both the traveling power of the wheel loader and the power of the work implement actuator must be ensured during the excavation work at the medium to low speed. For this reason, it is necessary to increase the amount of power stored in the battery 21 in advance, and when the work implement actuator needs instantaneous power, the shaft C that supplies the power of the hydraulic pump drive system 6 It is possible to monitor and control the electric power supplied from the battery 21 to the first generator motor 3 that is working as an electric motor.

  In other words, the power from the engine 2 can be distributed to the wheel drive system 10, and the power to the hydraulic pump drive system 6 can be driven by the first generator motor 3 that serves as an electric motor.

  Therefore, in the present invention, it is possible to perform a greater work than the engine 2 is outputting. As a result, it is possible to configure the engine 2 with a smaller capacity, and it is possible to output more power than the power of the engine mounted on the conventional traveling work vehicle.

  However, the work machine actuator requires a large amount of power for a time of only a few seconds for scooping earth and sand, and is an intermittent operation. On the other hand, the electric power required to be generated by the first generator motor 3 or the second generator motor 4 that has worked as a generator is always required to be used as power for running the wheel loader. It is what. For this reason, even if the working machine actuator as described above requests the necessary power instantaneously, the energy consumed by the first generator motor 3 at this time is the amount of power generated by the second generator motor 4 Will be better.

  Like the rotation of the engine 2, the second hydraulic pump 6b for driving the auxiliary machinery and the first hydraulic pump 6a for the work machine need to be driven only in a certain rotational direction and always be rotated. Become. For this reason, the axis C that is the input shaft of the hydraulic pump drive system 6 is a member that has the smallest fluctuation in the number of rotations among the members that are the input and output shafts in the reduction gear 5, and is linked to the axis A of the engine 2. The most preferable configuration is to extract the rotation from the member coupled to the shaft B. That is, it is desirable to arrange the hydraulic pump drive system 6 on the rotating shaft close to the engine 2 in the entire vehicle.

  In the second embodiment, since the first hydraulic pump 6a for the work machine actuator is directly connected to the engine 2 and the first generator motor 3, even when a large work machine power is instantaneously required, One generator motor 3 can direct a large amount of power to the work machine actuator without delay in response. And it becomes possible to perform the agile operation | movement of a working machine actuator.

FIG. 5 shows a third embodiment according to the present invention. The first generator motor 3 is not directly connected to the shaft A of the engine 2 but is directly connected to the first input IN1 of the reduction gear 5. The shaft A of the engine 2 is driven through meshing of transmission gears 7a and 7b.
Other configurations are the same as those in the second embodiment. Therefore, regarding the same member, the same reference numerals as those used in the first and second embodiments are used, and the description thereof is omitted.

  Since the first generator motor 3 is configured to transmit the rotation of the engine 2 through the meshing of the transmission gears 7a and 7b, the first generator motor 3 can be rotated at a higher speed than the shaft A of the engine 2. Can do. Thereby, the power generation efficiency in the first generator motor 3 can be increased. Moreover, since the axis D of the second generator motor 4 is directly connected to the second input IN2 of the speed reducer 5, the speed controllability for the plurality of rows of planetary gear mechanisms constituting the speed reducer 5 is It is easily increased by controlling the second generator motor 4.

  Further, the second hydraulic pump 6b for driving the auxiliary machine and the first hydraulic pump 6a for the working machine need to be driven to rotate only in a certain rotational direction and to always rotate, like the rotation of the engine 2. There is. In both the second and third embodiments, the first hydraulic pump 6a and the second hydraulic pump 6b are linked to the axis A of the engine 2 with the smallest fluctuation in the rotational speed among the input / output shafts of the speed reducer 5. Since the configuration is coupled to the shaft C, the first hydraulic pump 6a and the second hydraulic pump 6b can always be rotated and driven to rotate only in a certain rotational direction.

  FIG. 6 shows a fourth embodiment according to the present invention. In the planetary gear mechanism 32 in the first row constituting the reduction gear 5 by the axis B of the first generator motor 3 rotating in conjunction with the axis A of the engine 2. The ring gear 32d and the ring gear 33d in the planetary gear mechanism 33 in the second row are configured to be directly connected to each other.

  The axis D of the second generator motor 4 is configured to drive the sun gears 32a and 33a in the first and second planetary gear mechanisms 32 and 33, respectively. Further, the sun gear 34a of the planetary gear mechanism 34 in the third row is coupled to the carrier 33c in the planetary gear mechanism 33 of the second row, and the ring gear 34d in the planetary gear mechanism 34 of the third row is fixed. It has become.

  The carrier 34c in the planetary gear mechanism 34 in the third row is coupled to the medium / low speed output shaft 5b. The high-speed output shaft 5a is coupled to the carrier 32c in the planetary gear mechanism 32 in the first row. The high-speed output shaft 5a is provided with a transmission gear 8a, and the transmission gear 8a meshes with a transmission gear 9a supported via a first clutch CL1 provided on the input shaft 11. The medium / low speed output shaft 5b is provided with a transmission gear 8b, and the transmission gear 8b meshes with a transmission gear 9b supported via a second clutch CL2 provided on the input shaft 11. .

  When the first clutch CL1 is connected and the second clutch CL2 is disconnected, the high-speed running power output from the reduction gear 5 is transmitted from the high-speed output shaft 5a to the input shaft 11 of the wheel drive system 10. become. Further, when the first clutch CL1 is disconnected and the second clutch CL2 is connected, the traveling power of medium / low speed rotation output from the reduction gear 5 is transferred from the medium / low speed output shaft 5b to the input shaft 11 of the wheel drive system 10. Will be communicated.

  In the configuration of the fourth embodiment, an example of the arrangement configuration of the dual pumps is shown with respect to the arrangement of the first hydraulic pump 6a and the second hydraulic pump 6b. Variations such as a configuration for driving the pump are also conceivable. What kind of variation arrangement is adopted can be selected depending on the vehicle structure of the traveling work vehicle.

  FIG. 7 shows a fifth embodiment according to the present invention. In the planetary gear mechanism 32 in the first row constituting the reduction gear 5, the shaft B of the first generator motor 3 that rotates in conjunction with the shaft A of the engine 2 is used. The ring gear 32d and the carrier 33c in the second row planetary gear mechanism 33 are configured to be directly coupled to each other.

  The axis D of the second generator motor 4 is configured to drive the sun gears 32a and 34a in the first and third planetary gear mechanisms 32 and 34, respectively. Further, the ring gear 34d of the planetary gear mechanism 34 in the third row is coupled to the sun gear 33a in the planetary gear mechanism 33 in the second row, and the ring gear 33d in the planetary gear mechanism 33 in the second row is fixed. It has a configuration.

  The carrier 34c in the planetary gear mechanism 34 in the third row is coupled to the high-speed output shaft 5a. The medium / low speed output shaft 5b is coupled to the carrier 32c in the planetary gear mechanism 32 in the first row. The high-speed output shaft 5a is provided with a transmission gear 8a, and the transmission gear 8a meshes with a transmission gear 9a supported via a first clutch CL1 provided on the input shaft 11. The medium / low speed output shaft 5b is provided with a transmission gear 8b, and the transmission gear 8b meshes with a transmission gear 9b supported via a second clutch CL2 provided on the input shaft 11. .

  In FIG. 7, the high-speed output shaft 5a, the transmission gears 8a, 9a, and the first clutch CL1 are disposed on the right side of FIG. 8b and 9b and the second clutch CL2 are disposed on the left side in FIG. For this reason, the arrangement of the output shafts 5a, 5b, the transmission gears 8a, 8b, 9a, 9b and the clutches CL1, CL2 is opposite to that shown in FIG. 6 showing the arrangement of the fourth embodiment. Yes.

  When the first clutch CL1 is connected and the second clutch CL2 is disconnected, the high-speed running power output from the reduction gear 5 is transmitted from the high-speed output shaft 5a to the input shaft 11 of the wheel drive system 10. become. Further, when the first clutch CL1 is disconnected and the second clutch CL2 is connected, the traveling power of medium / low speed rotation output from the reduction gear 5 is transferred from the medium / low speed output shaft 5b to the input shaft 11 of the wheel drive system 10. Will be communicated.

  FIG. 8 shows a sixth embodiment according to the present invention. The first generator motor 3 is not directly connected to the shaft A of the engine 2 but is connected to the shaft A of the engine 2 via transmission gears 7a and 8a. It has become the composition. The shaft B of the first generator motor 3 is directly connected to the ring gear 32d in the first row planetary gear mechanism 32 constituting the reduction gear 5 and the ring gear 33d in the second row planetary gear mechanism 33, respectively. .

  The axis D of the second generator motor 4 is configured to drive the sun gears 32a and 34a in the first and third planetary gear mechanisms 32 and 34, respectively. The ring gear 34d of the planetary gear mechanism 34 in the third row is coupled to the sun gear 33a in the planetary gear mechanism 33 in the second row, and the carrier 33c in the planetary gear mechanism 33 in the second row is fixed. It has become.

The carrier 34c in the planetary gear mechanism 34 in the third row is coupled to the high-speed output shaft 5a. The medium / low speed output shaft 5b is coupled to the carrier 32c in the planetary gear mechanism 32 in the first row. The high-speed output shaft 5a is provided with a transmission gear 8a, and the transmission gear 8a meshes with a transmission gear 9a supported via a first clutch CL1 provided on the input shaft 11. The medium / low speed output shaft 5b is provided with a transmission gear 8b, and the transmission gear 8b meshes with a transmission gear 9b supported via a second clutch CL2 provided on the input shaft 11. .
Note that the arrangement of the output shafts 5a, 5b, the transmission gears 8a, 8b, 9a, 9b and the clutches CL1, CL2 in FIG. 8 is the same as the arrangement in FIG.

  When the first clutch CL1 is connected and the second clutch CL2 is disconnected, the high-speed running power output from the reduction gear 5 is transmitted from the high-speed output shaft 5a to the input shaft 11 of the wheel drive system 10. become. Further, when the first clutch CL1 is disconnected and the second clutch CL2 is connected, the traveling power of medium / low speed rotation output from the reduction gear 5 is transferred from the medium / low speed output shaft 5b to the input shaft 11 of the wheel drive system 10. Will be communicated.

  The technical idea of the present invention can be applied to a device or the like to which the technical idea of the present invention can be applied.

1 is an overall configuration diagram of a traveling work vehicle according to an embodiment of the present invention. Example 1 It is explanatory drawing of IV quadrant. (Explanation) It is the figure which showed the state of each structural member corresponding to the operation | movement pattern of a traveling work vehicle. (Example) It is another whole block diagram of a traveling work vehicle. (Example 2) It is another whole block diagram of a traveling work vehicle. (Example 3) It is another whole block diagram of a traveling work vehicle. Example 4 FIG. 10 is still another overall configuration diagram of the traveling work vehicle. (Example 5) It is another whole block diagram of a traveling work vehicle. (Example 6) 1 is an overall configuration diagram of a traveling work vehicle. (Conventional example 1) 1 is an overall configuration diagram of a traveling work vehicle. (Conventional example 2) 1 is an overall configuration diagram of a traveling work vehicle. (Conventional example 3) 1 is an overall configuration diagram of a traveling work vehicle. (Conventional example 4)

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Travel work vehicle, 3 ... 1st generator motor, 4 ... 2nd generator motor, 5 ... Reduction gear, 6 ... Hydraulic pump drive system, 10 ... Wheel drive system, DESCRIPTION OF SYMBOLS 11 ... Input shaft, 20a ... 1st inverter, 20b ... 2nd inverter, 21 ... Battery, 25 ... Controller, 32 ... Planetary gear mechanism of the 1st row, 33 ... Second row planetary gear mechanism, 34 ... third row oil gear mechanism, 50 ... engine, 51 ... hydraulic pump, 52 ... generator, 53 ... motor, 54 ... Battery, 60 ... Engine, 61, 62 ... Generator motor, 63 ... Generator, 64 ... Battery, 70 ... Engine, 72, 73 ... Generator motor, 74-76 ..Planet reducer, 80 ... Engine, 82, 83 ... Dynamic motor, 84 ... planetary reduction gear.

Claims (3)

A first generator motor and actuator drive system connected in series to the output shaft of the engine;
A reduction gear having a plurality of planetary gear mechanisms arranged in series;
A second generator motor connected to a drive source different from the engine ;
A wheel drive system connected to the output shaft of the speed reducer to which the output shaft of the second generator motor is connected;
A power storage device connected to each of the first generator motor and the second generator motor via an inverter ,
The output shaft of the second generator motor and the output shaft of the speed reducer are arranged on the same axis,
The output shaft of the engine, the output shaft of the speed reducer, and the input shaft of the wheel drive system are arranged on different shaft cores, respectively.
The output shaft of the first generator motor and the output shaft of the second generator motor are respectively connected to different input parts in the speed reducer,
The output shaft of the speed reducer is respectively taken out from the output part of the planetary gear mechanism in a different row,
One output shaft is configured as a medium-low speed output shaft, and the other output shaft is configured as a high-speed output shaft, and the medium-low speed output shaft and the high-speed output shaft are respectively connected to the wheel drive system via a pair of clutches. A traveling work vehicle characterized by being connected to an input shaft. The reduction gear is constituted by a planetary gear mechanism consisting of three rows,
The output shaft of the first generator motor is connected to the planetary gear mechanism in the first row and the planetary gear mechanism in the second row,
The medium-low speed output shaft in the reduction gear is taken out from the output part of the planetary gear mechanism in the first row or the planetary gear mechanism in the third row, and the output shaft for high speed is the planetary gear mechanism in the third row. The traveling work vehicle according to claim 1, wherein the traveling work vehicle is taken out from an output portion of the planetary gear mechanism in the first row.   The traveling work vehicle according to claim 1 or 2, wherein the pair of clutches are provided on an input shaft of the wheel drive system.

Images