KR20200065944A - Power train for complex power transmission and control method thereof - Google Patents

Abstract

The present invention relates to a complex power transmission power train in which a second sun gear unit rotates by receiving power transmitted from a hydrostatic unit, and a forward clutch unit is coupled and a second ring gear unit rotates to transmit the power in a complex manner, while power is transmitted from an input gear unit at the same time, thereby outputting the power through a second carrier unit, and a control method thereof. To this end, the complex power transmission power train which shifts power output from an engine and transmits the same to an output drive shaft, comprises: an input gear unit connected to the engine; a hydrostatic unit connected to the input gear unit; a clutch unit connected to the input gear unit and transmitting or blocking power of the input gear unit; a second planetary gear unit connected to the clutch unit and the hydrostatic unit; a first planetary gear unit connected to the second planetary gear unit and the hydrostatic unit; and a brake unit connected to the first planetary gear unit.

Description

Power train for complex power transmission and control method thereof

The present invention relates to a combined power transmission power train and a control method thereof, and more specifically, includes a hydraulic continuously variable transmission device (HSU, Hydrostatic Transmission Unit, hereinafter referred to as a hydrostatic unit) that performs transmission by power branching and synthesis. When shifting in a mechanical hydraulic transmission, power is transmitted from the hydrostatic unit to rotate the second sun gear unit, power is transmitted from the input gear unit, and at the same time, the forward clutch unit is coupled to rotate the second ring gear unit to transmit power in a complex manner. It relates to a combined power transmission power train that outputs power through the second carrier portion and a control method thereof.

In general, a work vehicle such as a forklift, a tractor, or the like, is a special vehicle used to carry cargo, and a hydraulic mechanical transmission (HMT, Hydromechanical Transmission) combining a hydrostatic unit and a mechanical gear is used.

The hydraulic mechanical transmission is a transmission for maximizing the advantages of both a hydrostatic unit having excellent operability and a mechanical gear device having excellent transmission efficiency.

In addition, in the case of a hydraulic mechanical transmission used in a work vehicle, a multipath transmission having two or more power transmission paths may be used by using a planetary gear set composed of a pair or more planetary gear units and a hydraulic continuously variable transmission.

In this case, the power of the engine continuously changed by the hydraulic continuously variable transmission and the power of the engine not changed by the continuously variable transmission are synthesized using a planetary gear device, and the combined power is selectively transmitted to the axle using a clutch. do.

In developing the power train using the planetary gear set as described above, rather than developing a new planetary gearset, a combination of the existing simple planetary gearset or the complex planetary gearset can be combined in any way without any possible power loss, and the desired shift stage is followed without any possible power loss. The goal is to realize the transmission ratio, and various studies are actively conducted for this purpose.

The combination of the planetary gear sets has different operation mechanisms depending on the connection configuration of the rotating elements (sun gear, planet carrier, ring gear).

In addition, characteristics such as durability, power transmission efficiency, size, and the like vary according to the connection configuration, and at this time, power loss may occur, and a problem arises in that the volume of the configuration increases.

Republic of Korea Patent Publication No. 1020130097120 (Invention name: Multi-speed transmission drive system with a planetary gear set, Publication date: September 02, 2013)

The problem to be solved in the present invention is when the power is shifted in a mechanical hydraulic transmission that includes a hydraulic stepless transmission device (HSU, Hydrostatic Transmission Unit, hereinafter referred to as a hydrostatic unit) to perform transmission by a branch and synthesis, power from the hydrostatic unit This is transmitted, the second sun gear part rotates, power is transmitted from the input gear unit, and at the same time, the forward clutch unit is coupled, and the second ring gear part rotates to transmit power in a complex manner, thereby outputting power through the second carrier part. It is to provide a train and its control method.

In order to solve the above-described problems, the present invention is a complex power transmission power train that transmits power output from an engine to an output driving shaft, and an input gear unit connected to the engine and a hydro connected to the input gear unit. A static unit, a clutch unit connected to the input gear unit to transmit or block power of the input gear unit, a second planetary gear unit connected to the clutch unit and the hydrostatic unit, and the second planetary gear A first planetary gear unit connected to the unit and the hydrostatic unit, and a brake unit connected to the first planetary gear unit, wherein the clutch unit includes a forward clutch unit and a reverse clutch unit, and the second planetary unit The gear unit includes an input shaft rotating by receiving power from the hydrostatic unit, a second sun gear unit rotating by being coupled to the input shaft, and the input shaft passing through the center, rotating by receiving power from the outside. A clutch gear, and a hub shaft through which the input shaft passes through, and at least a portion is disposed between the clutch gear and the input shaft, and a hub shaft receiving power from the forward clutch unit, and a hub shaft connected to the hub shaft, A second ring gear part receiving power, and a second carrier part connected to the second sun gear part, the second ring gear part and the first planetary gear unit, wherein the forward clutch unit is between the hub shaft and the clutch gear. Interposed in, it provides a composite power transmission power train, characterized in that for transmitting or blocking the power of the clutch gear to the hub shaft.

Here, the brake unit is connected to the first ring gear portion of the first planetary gear unit, in the first-stage mode, the brake unit is engaged, the clutch unit is released, and in the second-stage mode, the brake unit is released and the forward movement. Either the clutch unit or the reverse clutch unit may be combined.

In addition, the first planetary gear unit includes a first sun gear unit connected to the hydrostatic unit, a first ring gear unit connected to the second carrier unit, the first sun gear unit, the first ring gear unit and the output. It may include a first carrier portion connected to the drive shaft.

In addition, the present invention is a method for controlling a complex power transmission power train that transmits power output from an engine to an output driving shaft, wherein the complex power transmission power train includes an input gear unit connected to the engine, and the input gear unit. A hydrostatic unit connected to the, and a clutch unit connected to the input gear unit to transmit or block power of the input gear unit, a second planetary gear unit connected to the clutch unit and the hydrostatic unit, and A second planetary gear unit and a first planetary gear unit connected to the hydrostatic unit, and a brake unit connected to the first planetary gear unit, wherein the clutch unit includes a forward clutch unit and a reverse clutch unit, The second planetary gear unit includes an input shaft that receives power from the hydrostatic unit and rotates, a second sun gear unit that rotates in combination with the input shaft, and the input shaft penetrates the center, and transmits power from the outside. A clutch gear that rotates upon transmission, and the input shaft passes through the center, and at least a portion is disposed between the clutch gear and the input shaft, and a hub shaft receiving power from the forward clutch unit and connected to the hub shaft It includes a second ring gear portion receiving the power of the hub shaft, the second sun gear portion, the second ring gear portion and a second carrier portion connected to the first planetary gear unit, power is transmitted from the hydrostatic unit As the second sun gear part rotates and power is transmitted from the input gear unit and the forward clutch unit is coupled, the second ring gear part rotates and power is transmitted through the second carrier part, so that power can be output through the second carrier part. .

Here, when power is transmitted only from the hydrostatic unit and the second sun gear unit rotates, the second ring gear unit and the second carrier unit may rotate in an idle state.

In the combined power transmission power train and control method according to the present invention, power is transmitted from the hydrostatic unit to rotate the second sun gear unit, power is transmitted from the input gear unit, and the forward clutch unit is coupled to rotate the second ring gear unit. The second planetary gear portion rotates and the second planetary gear portion rotates to output power through the first carrier portion, thereby minimizing the loss of power and having a compact structure.

1 is a block diagram showing a state in which a complex power transmission power train according to an embodiment of the present invention is arranged.
FIG. 2 is a view schematically showing the configuration of the second planetary gear unit of the combined power transmission power train of FIG. 1.
3 is a view showing a case in which only the second sun gear portion of the second planetary gear unit of FIG. 2 rotates.
FIG. 4 is a view showing a case where the second sun gear portion of the second planetary gear unit of FIG. 2 rotates and power is transmitted from the input gear unit while the forward clutch unit is in the released state.
FIG. 5 is a view showing a case in which the first sun gear portion of the first planetary gear unit of FIG. 2 rotates, and power is transmitted from the input gear unit while the forward clutch unit is engaged.

Hereinafter, preferred embodiments of the present invention in which the above-described problem to be solved can be realized in detail will be described with reference to the accompanying drawings. In describing the embodiments, the same name and the same code are used for the same configuration, and additional descriptions thereof are omitted below.

The complex power transmission power train according to the present invention will be described with reference to FIGS. 1 to 5 as follows.

1 is a block diagram showing a state in which a complex power transmission power train according to an embodiment of the present invention is arranged.

Referring to FIG. 1, a combined power transmission power train according to an embodiment of the present invention is installed in a work vehicle such as a forklift, a tractor, etc., and transmits power output from an engine (E/G) to an output driving shaft (OUTPUT) The continuously variable transmission includes an input gear unit, a hydrostatic unit (HSU), a second planetary gear unit, a clutch unit, a first planetary gear unit, and a brake unit (B1).

The input gear unit is coupled to the engine (E/G).

The input gear unit includes a first input gear portion G1 coupled to the output shaft of the engine E/G, and a second input gear portion G13 coupled to the rotation axis of the first input gear portion G1 and coaxial. The third input gear unit G3 may be further included. Here, the second input gear part G13 and the third input gear part G3 have the same rotational speed as the first input gear part G1.

The second input gear unit G13 prevents interference between the input gear unit and the reverse clutch unit in combination with the reverse clutch unit C2, which will be described later, and can reduce the size of the continuously variable transmission.

In this way, the hydrostatic unit (HSU) is coupled to the input gear unit described above, and the hydrostatic unit (HSU) continuously transmits power to the input gear unit to transmit it to the output drive shaft (OUTPUT).

Although not shown, the hydrostatic unit (HSU) includes a hydraulic pump that generates hydraulic pressure with power transmitted from the input gear unit and a hydraulic motor that generates power with hydraulic pressure by the hydraulic pump.

Here, the hydraulic pump can control the hydraulic pressure by adjusting the inclination angle of the inclined plate provided therein, and the hydraulic motor is regulated in power according to the transmitted hydraulic pressure.

In addition, the hydrostatic unit (HSU) may be connected to the first gear portion (G2) coupled to the first input gear portion (G1) of the input gear unit while being coupled to the input shaft of the hydraulic pump. In addition, the hydrostatic unit (HSU) may be connected to the second gear portion G5 coupled to the transmission gear unit described later in a state coupled to the output shaft of the hydraulic motor.

The second planetary gear unit includes a second ring gear part R2 connected to the input gear unit, a second sun gear part S2 connected to the hydrostatic unit HSU, a second ring gear part R2 and a second It includes a plurality of second planetary gear portion (P2) coupled between the sun gear portion (S2), and a second carrier portion (PC2) for outputting the power converted according to the operation of the second planetary gear portion (P2).

The second planetary gear unit may synthesize or branch power according to the rotation ratio between the second ring gear part R2 and the second sun gear part S2 and the second carrier part PC2.

The clutch unit includes a forward clutch unit and a reverse clutch unit.

The forward clutch unit connects the input gear unit and the second planetary gear unit. The forward clutch unit is connected through the second ring gear unit R2 when the power of the input gear unit is transmitted to the second planetary gear unit in the forward two-stage mode.

In addition, the forward clutch unit is coupled to the forward clutch part (C1) and the input shaft of the forward clutch part (C1), and coupled to the third input gear part (G3) of the input gear unit while being separated from the hydrostatic unit (HSU) It comprises a forward gear portion (G4), the output shaft of the forward clutch portion (C1) is coupled to the rotation axis of the second ring gear portion (R2).

The reverse clutch unit connects the input gear unit and the second planetary gear unit. The reverse clutch unit is connected to the second ring gear unit R2 when power of the input gear unit is transmitted to the second planetary gear unit in the reverse two-stage mode.

In addition, the reverse clutch unit includes a reverse clutch part C2 connected to the second ring gear part R2 in the reverse two-stage mode, and a first reverse gear part G14 coupled to the input shaft of the reverse clutch part C2. And further includes a second reverse gear portion G15 coupled to the output shaft of the reverse clutch portion C2.

Here, the first reverse gear unit G14 is coupled to the second input gear unit G13 in a spaced state from the hydrostatic unit HSU and the forward clutch unit, respectively.

In addition, the second reverse gear unit G15 is coupled to the rotation shaft of the second ring gear unit R2 via the reverse rotation transmission unit described later.

The first planetary gear unit includes a first ring gear portion R1 connected to a second carrier portion PC2, a first sun gear portion S1 connected to a hydrostatic unit HSU, and a first ring gear portion R1. ) And a first planetary gear portion P1 coupled between the first sun gear portion S1 and a first carrier that transmits power converted according to the operation of the first planetary gear portion P1 to the output drive shaft OUTPUT It includes a part (PC1).

Here, the first sun gear unit S1 is connected to the second gear unit G5 provided on the output shaft of the hydrostatic unit HSU via the transmission gear unit described later.

The brake unit B1 intermittently rotates the first ring gear portion R1. The brake unit B1 may control the rotation of the first ring gear part R1 through various types of well-known such as a wet multi-plate brake or a drum brake.

Then, in the first stage mode, the brake unit B1 is operated to brake the rotation of the first ring gear portion R1, and in the second stage mode, the operation of the brake unit B1 is released and the first ring gear portion R1 is rotated. As much as possible.

The continuously variable transmission according to an embodiment of the present invention may further include a transmission gear unit and a connection gear unit.

The transmission gear unit connects the hydrostatic unit (HSU) and the first sun gear unit (S1). The transmission gear unit includes a first transmission gear part G6 coupled to the coaxial axis of the first sun gear part S1 and coupled to the second gear part G5, and of the first transmission gear part G6. A second transmission gear portion G8 coupled to the rotation shaft and the coaxial shaft may be further included.

Here, the second transmission gear portion G8 has the same number of revolutions as the first transmission gear portion G6. The second transmission gear unit G8 prevents interference between the connection gear unit and the transmission gear unit in connection with the connection gear unit, and can reduce the size of the continuously variable transmission.

The connecting gear unit connects the second sun gear unit S2 and the transmission gear unit.

The connecting gear unit includes a first connecting gear part G9 coupled to the second transmission gear part G8, and a second coupled to the first connecting gear part G9 while being coupled to the rotation axis of the second sun gear part S2. It may include a connecting gear portion (G11), and may further include a third connecting gear portion (G10) coupled to the second connecting gear portion (G11) in a state coupled to the rotation axis of the first connecting gear portion (G9).

Here, the first connecting gear portion G9 and the third connecting gear portion G10 have the same number of revolutions. In addition, the second sun gear portion S2 and the second connection gear portion G11 have the same number of revolutions.

The continuously variable transmission according to an embodiment of the present invention may further include an output gear unit.

The output gear unit connects the second carrier portion PC2 and the first ring gear portion R1. The output gear unit includes a first output gear portion G12 connected to the first ring gear portion R1 in a state coupled to the rotation axis of the second carrier portion PC2.

The continuously variable transmission according to an embodiment of the present invention may further include a reverse rotation transmission unit.

The reverse rotation transmission unit connects the reverse clutch unit C2 and the second ring gear unit R2 among the clutch units. The reverse rotation transmission unit may include a reverse rotation gear portion G16 coupled to the second reverse gear portion G15 in a state coaxially coupled to the rotation axis of the second ring gear portion R2.

Each of the gear units described above may be configured as one gear. In addition, each of the gear units described above may have a configuration in which two or more gears mesh with each other.

Although not shown, a power take-off unit may be coupled to the output shaft or input gear unit of the engine E/G.

Here, referring to FIGS. 2 to 5, the specific configuration of the second planetary gear unit and the method for controlling the complex power transmission power train according to the present invention by driving the second planetary gear unit will be described in detail as follows.

2 is a view showing a configuration connected to the second planetary gear unit and the second planetary gear unit of the combined power transmission power train.

First, as shown in FIG. 2, the second planetary gear unit includes a second ring gear portion R2, a second sun gear portion S2, and a plurality of second planetary gear portions P2 and a second carrier portion PC2. ), which is the same as the second planetary gear unit described with reference to FIG. 1.

In addition, the second planetary gear unit further includes an input shaft 100, a clutch gear 400, a hub shaft 600, and a needle bearing 700.

The input shaft 100 is rotated by receiving power from the hydrostatic unit (HSU) from the input gear 800 coupled with a portion of the input shaft 100, and the second sun gear unit S2 is the input It is coupled to the other part of the shaft.

In addition, the plurality of second planetary gear portion P2 includes a plurality of planetary gears, meshes with the second sun gear portion S2, and the second carrier portion PC2 includes a body portion 311 and a rotating shaft portion ( 312).

The body portion 311 is formed in an annular shape that surrounds the outer portion of the input shaft 100, the outer peripheral surface of the body portion 311 is formed of a gear-shaped output gear portion 313, the output gear The unit 313 transmits power to the output driving shaft OUTPUT.

The rotating shaft portion 312 is formed to protrude in a direction parallel to the second sun gear portion S2 from a surface facing the second sun gear portion S2 of the body portion 311.

The plurality of second planetary gear portions P2 are engaged with the second sun gear portion S2, and each of the second planetary gear portions P2 is coupled to the rotation shaft portion 312, respectively, so that the rotation shaft portion 312 ).

The clutch gear 400 is disposed between the input gear 800 and the second sun gear part S2, the input shaft 100 passes through the center, and rotates by receiving power from the outside. In the clutch gear 400 in Figure 1 corresponds to the forward gear portion (G4).

The hub shaft 600 is connected to the clutch gear 400 by the forward clutch unit C1 to receive power and is formed in a U-shape, and specifically, the hub shaft 600 is a hub boss 610 (( hub both) and the clutch coupling portion 620.

The hub boss 610 is formed in a T-shape, at least a portion of a body part (not shown in the drawing) region surrounding the outer surface of the input shaft 100 is the clutch gear 400 and the input shaft 100 Is placed between.

The clutch coupling portion 620 is formed to protrude from the outer surface of the body portion, one surface of the protrusion (not shown in the figure) perpendicular to the input shaft 100 and the body portion of the hub boss 610 Phosphorus is formed to extend so that the cross section has an annular shape toward the forward clutch unit C1, and is coupled with the forward clutch unit C1.

The second ring gear portion R2 is formed to extend from the other surface of the protruding portion of the hub shaft 600, a cross section is formed in an annular shape, and a thread is formed so that the inner circumferential surface meshes with the second planetary gear portion P2.

The needle bearing 700 is disposed between the input shaft 100 and the hub shaft 600, thereby supporting the Huff shaft 600, so that the input shaft 100 and the second ring gear part R2 are When a relative motion occurs, power of the second ring gear portion R2 is transmitted to the second planetary gear portion P2, that is, the second carrier portion PC2.

3 to 5, the driving example of the second planetary gear unit will be described as follows.

First, referring to FIG. 3, a case in which power is transmitted only from the hydrostatic unit (HSU) and only the input shaft 100 rotates is described as follows.

As shown in FIG. 3, power is transmitted from the hydrostatic unit (HSU) and the input shaft 100 rotates, so that the second sun gear unit S2 rotates. At this time, as the power is not transmitted from the clutch gear 400, the second ring gear part R2 and the plurality of second planetary gear parts P2 are rotated in an idle state so that power is not output. .

Next, referring to Figure 4, the power is transmitted from the hydrostatic unit, the second shaft (S2) is rotated by the rotation of the input shaft 100, the power is transmitted from the input gear unit at the same time the forward clutch The case where the unit C1 is in the released state is as follows.

As illustrated in FIG. 4, power is transmitted from the hydrostatic unit (HSU) and the input shaft 100 rotates, so that the second sun gear unit S2 rotates. In addition, the engine (E/G) is driven to transmit power to the clutch gear 400 so that the clutch gear 400 rotates.

At this time, when the forward clutch unit C1 is in the released state, that is, when the clutch plate and the clutch disk included in the forward clutch unit C1 are not contacted and spaced apart, the power of the clutch gear 400 is the It is not transmitted to the hub shaft 600.

Accordingly, the clutch gear 400, the second ring gear part R2, and the plurality of second planetary gear parts P2 are rotated in an idle state so that no power is output.

Referring to Figure 5, the power is transmitted from the hydrostatic unit, the input shaft 100 is rotated, the second sun gear unit S2 is rotated, power is transmitted from the input gear unit, and at the same time, the forward clutch unit C1 ) Is as follows.

As shown in FIG. 5, power is transmitted from the hydrostatic unit (HSU) and the input shaft 100 rotates, so that the second sun gear unit S2 rotates. In addition, the engine (E/G) is driven to transmit power to the clutch gear 400 so that the clutch gear 400 rotates.

At this time, when the forward clutch unit (C1) is engaged, that is, the clutch plate and the clutch disk included in the forward clutch unit (C1) are in contact, the power of the clutch gear 400 is the forward clutch unit (C1) ) Is transmitted to the hub shaft 600 so that the second ring gear part R2 rotates.

As a result, power is transmitted from the input shaft 100, the second sun gear part S2 rotates, power is transmitted from the clutch gear 400, and the forward clutch unit C1 is coupled to the second ring machine. The second planetary gear portion P2 rotates as the fisherman R2 rotates and power is transmitted to the second planetary gear portion P2, so that power can be output from the second carrier portion PC2. There will be.

As described above, the present invention is not limited to the specific preferred embodiments described above, and various modifications can be carried out by those skilled in the art to which the present invention pertains without departing from the gist of the invention as claimed in the claims. It is possible and such modifications are within the scope of the present invention.

E/G: engine
OUTPUT: Output drive shaft
G1: first input gear unit
G13: Second input gear unit
G3: Third input gear unit
HSU: Hydrostatic unit
G2: Gear 11
G5: second gear
R1: 1st ring gear part
S1: First line gear part
PC1: first carrier
P1: 1st planetary gear part
C1: Forward clutch part
G4: Forward gear fisherman
C2: Reverse clutch part
G14: First reverse gear part
G15: Second reverse gear part
R2: Second ring gear part
S2: second sun gear part
PC2: second carrier
P2: second planetary gear part
B1: Brake unit
G6: First transmission gear fisherman
G8: Second transmission gear fisherman
G9: First connecting gear
G11: Second connecting gear part
G10: 3rd connection gear part
G12: First output gear unit
G16: Reverse rotation gear part

Claims (5)

In the complex power transmission power train for transmitting the power output from the engine to the output drive shaft,
An input gear unit connected to the engine;
A hydrostatic unit connected to the input gear unit;
A clutch unit connected to the input gear unit to transmit or block power of the input gear unit;
A second planetary gear unit connected to the clutch unit and the hydrostatic unit;
A first planetary gear unit connected to the second planetary gear unit and the hydrostatic unit; And
It includes a brake unit connected to the first planetary gear unit,
The clutch unit includes a forward clutch unit and a reverse clutch unit,
The second planetary gear unit,
An input shaft rotating by receiving power from the hydrostatic unit;
A second sun gear unit coupled to and rotated with the input shaft;
A clutch gear that passes through the input shaft at the center and rotates by receiving power from the outside;
A hub shaft through which the input shaft passes through, and at least a portion is disposed between the clutch gear and the input shaft, and receives power from the forward clutch unit;
A second ring gear part connected to the hub shaft to receive power of the hub shaft; And
And a second carrier part connected to the second sun gear part, the second ring gear part, and the first planetary gear unit,
The forward clutch unit is interposed between the hub shaft and the clutch gear, the power transmission of the complex power transmission, characterized in that for transmitting or blocking the power of the clutch gear to the hub shaft. According to claim 1,
The brake unit is connected to the first ring gear portion of the first planetary gear unit,
In the first stage mode, the brake unit is engaged and the clutch unit is released,
In the second-stage mode, the brake unit is released and the combined power transmission power train, characterized in that any one of the forward clutch unit or the reverse clutch unit is combined. According to claim 1,
The first planetary gear unit includes a first sun gear unit connected to the hydrostatic unit, a first ring gear unit connected to the second carrier unit, the first sun gear unit, the first ring gear unit and the output driving shaft. A complex power transmission power train comprising a first carrier portion connected. In the control method of a complex power transmission power train for transmitting the power output from the engine to the output drive shaft,
The complex power transmission power train,
An input gear unit connected to the engine;
A hydrostatic unit connected to the input gear unit;
A clutch unit connected to the input gear unit to transmit or block power of the input gear unit;
A second planetary gear unit connected to the clutch unit and the hydrostatic unit;
A first planetary gear unit connected to the second planetary gear unit and the hydrostatic unit; And
It includes a brake unit connected to the first planetary gear unit,
The clutch unit includes a forward clutch unit and a reverse clutch unit,
The second planetary gear unit,
An input shaft rotating by receiving power from the hydrostatic unit;
A second sun gear unit coupled to and rotated with the input shaft;
A clutch gear that passes through the input shaft at the center and rotates by receiving power from the outside;
A hub shaft through which the input shaft passes through, and at least a portion is disposed between the clutch gear and the input shaft, and receives power from the forward clutch unit;
A second ring gear part connected to the hub shaft to receive power of the hub shaft; And
And a second carrier part connected to the second sun gear part, the second ring gear part, and the first planetary gear unit,
Power is transmitted from the hydrostatic unit to rotate the second sun gear unit, power is transmitted from the input gear unit, and the second ring gear unit rotates to transmit power in a complex manner as the forward clutch unit is coupled. Control method of a complex power transmission power train, characterized in that power is output through the carrier portion. The method of claim 4,
When power is transmitted only from the hydrostatic unit and the second sun gear part rotates, the second ring gear part and the second carrier part rotate in an idle state, thereby controlling the complex power transmission power train .

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