KR101401104B1 - Hydrostatic mechanical transmission - Google Patents

Abstract

The present invention relates to a hydrostatic mechanical transmission, and more specifically, to a hydrostatic mechanical transmission which reduces power loss and facilitates the security of a space. According to one embodiment of the present invention, a compound planetary gear (20) and a hydrostatic transmission (40) are connected to a drive shaft (10). Engine power is transmitted to a first sun gear (21a) and the hydrostatic transmission (40) through the drive shaft (10). The first sun gear (21a) is installed to the drive shaft (10) to rotate integrally. The output shaft (42) of the hydrostatic transmission (40) is connected to drive a second ring gear (24b).

Description

[0001] Hydrostatic Mechanical Transmission [

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to an hydraulic mechanical transmission, and more particularly, to a hydraulic mechanical transmission that includes a simple shifting structure to reduce power loss and facilitate installation space.

BACKGROUND ART [0002] A power-driven type speed-change device is utilized as a transmission device capable of continuously-variable shifting in a simple structure suitable for a shift device of a working vehicle such as a tractor or a combine.

The power split type transmission device is a multi-path transmission device having two or more power transmission paths using one or more planetary gear devices and a continuously variable transmission device, and a continuously variable transmission device is applied to one of the planetary gear devices, It is a transmission that synthesizes power to make the entire transmission unstable.

Hydro-mechanical transmission (HMT) of this power split type transmission uses a hydrostatic transmission (HST) as a variator, and uses a simple planetary gear system using one planetary gear device It can be divided into two or more compound eugenic gears. Further, a negative speed change portion formed of a gear mechanism is provided at the rear of the planetary gear set to have a plurality of speeds.

However, such an hydraulic mechanical transmission requires four sets of wet multi-plate clutches only in the case of a four-speed downshift, and since a wet multi-plate clutch is usually used in the range of six to eight sets, the power loss due to the clutch is large, A large space must be secured for Further, in addition to the auxiliary transmission, a pair of clutches for realizing the forward / backward movement is also required. Therefore, it is difficult to apply such a part in a tractor having a power of 100 horsepower or less because of a limited space.

In addition, the wet multi-plate clutch basically needs to lubricate for cooling, but also needs a hydraulic circuit because it operates with hydraulic pressure, so that the structure becomes complicated.

Open Patent Publication No. 10-2012-0065265 (June 20, 2012) Open Patent Publication No. 10-2012-0014060 (2012.02.15.) Open Patent Publication No. 10-2010-0026975 (2010.03.10.) Published Patent Publication No. 10-2009-0091105 (Feb.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a hydraulic mechanical transmission that is provided with a simple shifting structure to reduce power loss and facilitate the securing of an installation space.

In order to achieve the above object, in a hydraulic mechanical type transmission according to the present invention, a compound planetary gear and a hydrostatic transmission are connected to a drive shaft, the power of the engine is divided into a first sun gear and a hydrostatic transmission through a drive shaft, ; Wherein the compound planetary gear is provided so that the first sun gear rotates integrally with the drive shaft and a separate second sun gear is provided so as to slide on the drive shaft and the first pinion gear and the second pinion gear, And a second planetary gear set having a first ring gear and a second ring gear constituting a single body, the first pinion gear and the second pinion gear being engaged with each other in a circumscribed relationship with the second sun gear, The plurality of second pinion gears are configured to engage and engage with the ring gear; Wherein the output shaft of the forward hydraulic transmission is connected to drive the second ring gear; The power transmitted to the hydrostatic transmission is transmitted to the second ring gear of the complex planetary gear, combined with the power of the first sun gear by the drive shaft, and then divided into the second sun gear and the carrier and output; A first and second sun gear and a carrier are connected to the first and second stage speed change parts; And an L-H end speed change portion for shifting the power output from the negative speed first and second speed shafts of the first-second speed changing portion to the low-speed or high-speed secondarily.

In one embodiment, the forward hydraulic transmission is configured to receive power from a drive shaft at a rear end of the compound planetary gear through a gear train.

In the above-mentioned first-second speed change portion, the negative speed first and second speed shafts are provided in parallel to the drive shaft, and a negative speed first and second speed shafts are provided in parallel with the drive shaft; The first stage gear driven by the carrier slidably rotates and the second stage gear driven by the second sun gear is provided for sliding rotation; The first speed change mechanism is operated between the first speed change stage first gear and the second speed gear in a direction to selectively connect either of the first speed reduction gears or the second speed gears to the reduction gears 1-2, And a second-stage clutch that takes a neutral state in which no transmission gear stage is connected.

In this case, the connection between the carrier and the first-stage gear is achieved by disposing a single-stage primary gear on the carrier shaft extending from the carrier and engaging with the first-stage gear; And the second sun gear is connected to the second gear in such a manner that a two-stage primary gear is integrally mounted on the second sun gear shaft extending from the second sun gear and is engaged with the second gear.

In one embodiment, it is preferable that the one-stage clutch is composed of a wet type multi-plate clutch using hydraulic pressure.

Further, a reverse speed change portion is provided in association with the carrier and the negative speed first and second speed shafts, wherein the reverse speed changing portion includes: a reverse primary gear installed as a single body on the carrier shaft; A reverse drive shaft disposed in parallel with the negative speed first-and second-stage shaft; A reverse drive gear installed in a single body in the input direction of the reverse drive shaft in a state of being engaged with the reverse primary gear of the carrier shaft and receiving power; A reverse output gear installed to rotate in a single body in the output direction of the reverse drive shaft; A reverse clutch installed between the reverse drive gear and the reverse output gear for connecting or disconnecting the reverse output gear to the reverse drive shaft; And a reverse backstop synchronous gear which is installed as a single body on the negative speed first and second speed shafts so as to be driven to engage with the reverse output gear from behind the second speed reduction gear.

In one embodiment of the present invention, the L-H speed shifting portion includes a negative shifting L-H shortshaft installed in a direction parallel to the negative speed first and second shortening shafts; A final output shaft for transmitting the output from the negative speed change L-H short shaft to an end reducer for transmitting to the drive wheels; A negative speed change top gear formed as a single body at a distal end of the negative speed first and second speed shafts; An L-H drive gear which is installed as a single body on the negative speed change L-H short shaft and engages with the speed change top gear to drive an auxiliary speed change L-H short shaft; An H-stage drive gear and an L-stage drive gear installed to be slidably rotated on the negative speed change L-H short axis; An L-H stage clutch installed between the H-stage drive gear and the L-stage drive gear to select and connect the H-stage drive gear or the L-stage drive gear to the negative speed change L-H short shaft or take a neutral state; And an H-stage output gear and an L-stage output gear which are integrally mounted on the final output shaft and meshed with the H-stage drive gear and the L-stage drive gear, respectively.

In one embodiment, the negative speed top gear is formed on a top gear shaft manufactured independently of the negative speed first and second speed shafts; The top gear shaft is connected to the negative speed first-and-second-stage shaft by a coupler; The final output shaft is connected to the end portion of the top gear shaft so as to rotate concentrically, so that the auxiliary transmission 1 - 2 and the final output shaft are provided on the same axis.

In this case, it is preferable that the L-H step clutch is composed of a synchronizer transmission mechanism, and the synchronizer transmission mechanism is structured to receive a shifting force by a separate actuator.

According to the hydraulic mechanical transmission according to the present invention, the first sun gear of the complex planetary gear and the forward hydraulic transmission are directly driven by the drive shaft, the output of the forward hydraulic transmission is received by the second ring gear of the compound planetary gear, And then output to the second sun gear and the carrier, thereby making it possible to configure the first-second speed change portion through the second sun gear and the carrier. Therefore, even if the negative speed change portion as the gear type transmission is simply constituted by only two speed change stages, the 1-2 speed transmission portion, which is a gear type transmission, receives the stepless speed change output of the positive pressure transmission and is steplessly changed at each speed change stage , It is possible to realize a sufficient shift output required for a working vehicle such as a tractor.

Further, by combining the reverse-speed shifting portion with the first-speed shifting portion, the first-speed shifting portion and the reverse shifting portion can be packed together in the same narrow space, thereby minimizing the space and modularizing the continuously variable transmission.

In addition, since only one reverse clutch is required as a clutch for realizing forward and rearward travel, the manufacturing cost is reduced and it is advantageous in securing the installation space.

In addition, the clutch of the LH step transmission portion is configured as a synchronizer automatic transmission mechanism to realize the 2x2-speed auxiliary transmission with the 1-2-speed transmission portion, and the 2x2-speed auxiliary transmission is provided with the wet multi- By implementing the transmission mechanism, it is possible to simplify the structure, reduce the installation space, and reduce the manufacturing cost, as compared with adopting the entire clutch as the wet multi-plate clutch system.

1 is a configuration diagram of an hydraulic mechanical transmission according to the present invention.
FIG. 2 is a view showing a power flow in the case of performing a 1-L speed change in an hydrostatic mechanical transmission according to the present invention. FIG.
3 is a view showing a power flow when 1-H step speed is performed in an hydraulic mechanical transmission according to the present invention.
4 is a view showing power flow in the case of performing a 2-L speed change in the hydrostatic mechanical transmission according to the present invention.
5 is a view showing a power flow in the case of performing a 2-H step speed change in the hydrostatic mechanical transmission according to the present invention.

Hereinafter, a hydraulic mechanical transmission according to the present invention will be described in detail with reference to the accompanying drawings.

1 is a configuration diagram of an hydraulic mechanical transmission according to the present invention.

Referring to FIG. 1, a hydrostatic mechanical transmission according to the present invention is provided with a compound planetary gear 20 mounted on a drive shaft 10 that receives power from an engine, and a gear train 30 is integrally rotated.

The complex planetary gear 20 is provided so that the first sun gear 21a rotates integrally with the drive shaft 10 and the other second sun gear 21b slidably rotates and the first pinion gear 22a And the second pinion gear 22b come into contact with the first sun gear 21a and the second sun gear 21b in a circumscribed state and the first pinion gear 22a and the second pinion gear 22b, A plurality of second pinion gears 22b and 22b are provided in the first ring gear 24a so that the first ring gear 24a and the second ring gear 24b constitute a single body, ) Are in contact with each other.

The gear train 30 is drawn out to one side of the drive shaft 10 and the input shaft 41 of the positive hydraulic transmission 40 is connected to the output side gear 33 of the gear train 30 and the input shaft 41 of the positive hydraulic transmission 40 An output gear 43 integrally provided on the output shaft 42 is connected to drive the second ring gear 24b.

In one embodiment, the gear train 30 includes a first gear 31 mounted on the drive shaft 10 as a single body, a second gear 32 engaged with the first gear 31 and idling, And a third gear 33 which is engaged with the second gear 32 and is united with the input shaft 41 of the hydraulic pressure transmission 40 in a single body.

Therefore, the power of the engine is divided into the first sun gear 21a and the forward hydraulic transmission 40 through the drive shaft 10, and the power transmitted to the forward hydraulic transmission 40 is transmitted to the second planetary gear 20 2 ring gear 24b and synthesized with the power of the first sun gear 21a and then divided into the second sun gear 21b and the carrier 23 and output.

In this embodiment, the forward hydraulic transmission 40 is disposed so as to connect the drive shaft 10 and the second ring gear 24b at the rear end of the compound planetary gear 20, The drive shaft 10 and the second ring gear 24b may be connected to each other.

That is, the gear train 30 for driving the hydrostatic transmission 40 is first installed on the drive shaft 10, and the gear train 30 is provided on the rear end side of the first gear 31 of the gear train 30, The output gear 43 of the positive pressure transmission 40 may be connected to the second ring gear 24b after the first sun gear 21a is installed.

A second sun gear 21b and a carrier 23 are provided between the complex planetary gear 20 and the gear train 30 for outputting a combined power of the compound planetary gear 20 and the positive hydraulic transmission 40, And a first-speed shifting portion 50 that is driven with power is provided.

The first sun gear 21a of the compound planetary gear 20 and the positive hydraulic transmission 40 are directly driven by the drive shaft 10 to connect the output of the positive hydraulic transmission 40 to the compound planetary gear 20, Through the second sun gear 21b and the carrier 23 so as to be output to the second sun gear 21b and the carrier 23 after being synthesized by the second ring gear 24b of the first sun gear 21b and the carrier 23, 50). Therefore, even if the transmission portion 50 which is a gear type transmission is simply constituted by only two transmission gears, the 1-2 speed transmission portion 50, which is a gear type transmission, is connected to the stepless speed change output So that the shifting output required for the working vehicle such as the tractor can be realized.

In one embodiment, the one-to-one speed change section 50 is provided with a reduction gear 1-2 axis 50a in parallel with the drive shaft 10, A first stage gear 51 driven by the carrier 23 and a second stage gear 52 connected to the second sun gear 21b are provided so as to be slid on the first stage gear 51, Stage clutch 53 is provided between the first and second gears 52,

The 1-2 step clutch 53 is composed of a wet type multi-plate clutch using a hydraulic pressure and connects the first stage gear 51 to the second speed change shaft 50a or the first speed gear 51 The second-stage gear 52 is selectively connected to a neutral state in which no gearbox is connected.

A single-stage primary gear 23b is provided on the shaft 23a of the carrier 23 so as to be engaged with the first gear 51 and the shaft 21c of the second sun gear 21b And a two-stage primary gear 23b for meshing with the second gear 52 is provided.

Further, the reverse transmission portion 60 is provided between the shaft 23a of the carrier 23 and the reduction gears 1-2 and 50a.

The reverse transmission portion 60 is disposed so that the reverse drive shaft 61 is disposed in parallel to the negative speed first-and-second-stage shaft 50a and is connected to the carrier shaft 23a in the input direction of the reverse drive shaft 61, And a reverse output gear 63 for driving the auxiliary speed-first and second-speed shaft 50a is slidably provided in the output direction, and the reverse drive gear 62 A reverse clutch 64 is provided between the reverse output gear 63 and the reverse output gear 63 to connect or disconnect the reverse output gear 63 to or from the reverse drive shaft 61.

In the embodiment, the carrier shaft 23a is provided with a reverse primary gear (not shown) driven to engage with the reverse drive gear 62 of the reverse shift portion 60, for driving the reverse shift portion 60 by the carrier shaft 23a. And a reverse driven gear 65 which is driven to engage with the reverse output gear 63 is provided on the auxiliary shift stage 1-2 of the auxiliary shift second stage gear 52, Is installed as a single body.

Thus, by combining the reverse transmission portion 60 with the one-step transmission portion 50, the 1-2nd transmission portion 50 and the reverse transmission portion 60 are packaged together in the same (adjacent) Which minimizes the space and enables the modularization of the continuously variable transmission.

In addition, since only one clutch for backward movement is required as a clutch for realizing the forward / rearward movement, the manufacturing cost is reduced and the installation space is advantageously secured.

Further, in one embodiment of the present invention, an L (low speed) -H (high speed) speed changing portion 70 for switching the output of the 1-2 speed shifting portion 50 back to two stages is further installed do.

The LH step-variable shifting portion 70 is provided at the end of the negative speed alternate-first-speed shaft 50a to switch the output speed of the negative speed alternate-speed shaft 50a to low speed and high speed, And to implement the downshift.

This LH-stage speed change section 70 includes an auxiliary speed-change LH short-axis shaft 71 provided in a direction parallel to the auxiliary speed-first-speed short-axis shaft 50a, To a reduction gear mechanism for transmitting the reduction gear LH to the reduction gear mechanism for transmission to the reduction gear LH shaft And an LH drive gear 73 installed as a single body on the auxiliary speed change LH short shaft 71 to be engaged with the auxiliary speed change top gear 72 to drive the auxiliary speed change LH short shaft 71, Stage driving gear 74 and an L-stage driving gear 75 installed between the H-stage driving gear 74 and the L-stage driving gear 75, Stage drive gear 74 and the L-stage drive gear 75 are selectively connected to the LH stage clutch 71 or the LH stage clutch 76 that takes the neutral state.

An H-stage output gear 81 and an L-stage output gear 82, which mesh with the H-stage drive gear 74 and the L-stage drive gear 75, respectively, Respectively.

In one embodiment, the auxiliary speed change top gear 72 is formed separately from the auxiliary speed-first and second-speed shafts 50a in place of the configuration in which the auxiliary speed- In this case, the top gear shaft 72a can be connected to the negative speed first-and second-stage shaft 50a by a coupler 72b.

In addition, the final output shaft 80 may be connected to the end of the top gear shaft 72a so as to rotate in a concentric manner (i.e., relatively rotatably). With such a configuration, the auxiliary transmission 1 - 2 shaft 50a and the final output shaft 80 can be provided on the same axis, thereby reducing the size of the transmission and occupying a small space.

In one embodiment, the L-H stage clutch 76 is configured as a synchronizer transmission mechanism as shown in the drawing.

As is well known in the field of the present invention, the LH stage clutch 76 is a synchronized transmission, which includes a hub integrally mounted on the reduction gear LH short shaft 71, and a spline- A synchronizer ring for synchronizing the H-stage drive gear 74 and the L-stage drive gear 75 with the auxiliary speed change LH shaft 71 by the movement of the sleeve, and a friction surface and a dog clutch And a dog clutch (Dog Clutch).

In the present embodiment, the sleeve of the LH step clutch 76 comprising the synchronizer transmission mechanism is subjected to AMT (Automatic Manual Transmission), which is automated by the automatic shifting force by the actuator without depending on the manual shifting force by the lever operation of the driver This eliminates the wet multi-plate clutch system having an expensive and complicated structure. Even if a synchronizer transmission mechanism is employed, automatic shifting is enabled, thereby simplifying the structure, reducing installation space, and reducing manufacturing cost.

The drive gear 90 for four-wheel drive (that is, for driving the front wheels) is connected to the L-stage drive gear 75 of the L-H speed shift portion 70.

A PTO (Power Take Off) clutch 95 and a PTO shaft 96 may be connected to the end of the drive shaft 10 to drive a separate operation unit such as a working machine.

Hereinafter, the operation of the hydraulic mechanical transmission according to the present invention will be described.

The power of the engine is transmitted through the drive shaft 10 dividedly divided into the first sun gear 21a and the gear train 30 of the compound planetary gear 20 and the gear train 30 Is transmitted to the hydrostatic transmission 40. In this case,

The power of the engine is synthesized by the first sun gear 21a of the compound planetary gear 20 and the second ring gear 24b connected to the positive hydraulic transmission 40 and then transmitted to the second sun gear 21b Carrier 23 and output.

The operation state of the accelerator pedal or the acceleration lever by the driver is reflected on the variable displacement hydraulic pump 40a of the constant hydraulic transmission 40 to steplessly change the operation speed of the constant displacement hydraulic motor 40b.

The power transmitted to the second sun gear 21b and the carrier 23 of the compound planetary gear 20 is transmitted to the final output shaft 80 through the 1-2nd speed change portion 50 and the LH end speed change portion 70, And is transmitted from the final output shaft 80 to the drive wheel through a longitudinal reduction gear such as a differential gear.

The power transmission operation by the shifting of the 1-2 step transmission portion 50 and the L-H speed portion 70 is as follows.

(1-L step speed)

FIG. 2 is a view showing a power flow in the case of performing a 1-L speed change in an hydrostatic mechanical transmission according to the present invention. FIG.

2, the 1 < st > -to-1 speed clutch 53 operates to connect the first stage gear 51 to the reduction gear 1 - 2 shaft 50a, and the LH Stage LH step clutch 76 is operative to connect the L-stage drive gear 75 and the negative speed LH short shaft 71 to each other.

Thereby, the power output through the carrier 23 is transmitted to the first-stage primary gear 23b, the first-stage gear 51, the 1-2 -step clutch 53, the reduction gear 1-2, Stage gear 72 to the negative speed LH short shaft 71 to the L-stage drive gear 75 to the L-stage output gear 82 to the final output shaft 80, as shown in Fig.

(1-H step speed)

3 is a view showing power flow when 1-H step speed is performed in an hydraulic mechanical transmission according to the present invention.

3, the 1 < st > -to-1 speed clutch 53 operates to connect the first stage gear 51 to the reduction gear 1 - 2 shaft 50a, and the LH Stage LH step clutch 76 is operative to connect the H-stage drive gear 74 and the negative speed LH short shaft 71 to each other.

Thereby, the power output through the carrier 23 is transmitted to the first-stage primary gear 23b, the first-stage gear 51, the 1-2 -step clutch 53, the reduction gear 1-2, Stage reduction gear LH short shaft 71 → the H-stage drive gear 74 → the H-stage output gear 81 → the final output shaft 80, as shown in FIG.

(2-speed step speed)

4 is a view showing power flow in the case of performing a 2-L speed change in the hydrostatic mechanical transmission according to the present invention.

4, the 2 < st > -to-1 step clutch 53 operates to connect the second stage gear 52 to the reduction gear 1 - 2 shaft 50a, and the LH Stage LH step clutch 76 is operative to connect the L-stage drive gear 75 and the negative speed LH short shaft 71 to each other.

Thus, the power output through the second sun gear 21b is transmitted via the two-stage primary gear 21d, the second-stage gear 52, the one-step clutch 53, Speed drive gear 75 to the L-stage output gear 82 to the final output shaft 80 in the following manner.

(2-speed shift)

5 is a view showing a power flow in the case of performing a 2-H step speed change in the hydrostatic mechanical transmission according to the present invention.

5, the first-second-stage clutch 53 operates to connect the second-stage gear 52 to the negative speed-first and second-speed shaft 50a during 2-H speed change, and LH Stage LH step clutch 76 is operative to connect the H-stage drive gear 74 and the negative speed LH short shaft 71 to each other.

Thus, the power output through the second sun gear 21b is transmitted via the two-stage primary gear 21d, the second-stage gear 52, the one-step clutch 53, Stage drive gear 74 to the H-stage output gear 81 to the final output shaft 80. The output shaft 80 is connected to the output side of the reduction gear LH.

(Reverse L-speed)

1, the 1 < st > -shift transmission portion 50 assumes a neutral state and the reverse clutch 64 is engaged with the reverse output gear 63 and the reverse drive shaft 61 And the LH stage clutch 76 of the LH stage is operated to connect the L-stage drive gear 75 and the negative speed LH short shaft 71. [

Thus, the power output through the carrier 23 is transmitted via the reverse primary gear 23c, the reverse drive gear 62, the reverse drive shaft 61, the reverse clutch 64, the reverse output gear 63, Gear 65 → Secondary speed 1st-2nd stage shaft 50a (reverse rotation) → Second speed change top gear 72 → Second speed reduction LH short shaft 71 → L-stage drive gear 75 → L- And is output to the final output shaft 80 from the gear 82.

(Reverse H-speed)

1, the first-speed shifting portion 50 assumes a neutral state, and the reverse clutch 64 is engaged with the reverse output gear 63 and the reverse drive shaft 61 And the LH stage clutch 76 of the LH stage is operated to connect the H-stage drive gear 74 and the negative speed LH short shaft 71. [

Thus, the power output through the carrier 23 is transmitted via the reverse primary gear 23c, the reverse drive gear 62, the reverse drive shaft 61, the reverse clutch 64, the reverse output gear 63, Gear 65 → Secondary speed 1st-2nd stage shaft 50a (reverse rotation) → Second speed change top gear 72 → Second speed reduction LH end shaft 71 → H-stage drive gear 74 → H- And is output to the final output shaft 80 from the gear 81.

The foregoing is a description of certain preferred embodiments of the present invention. The present invention may, however, be embodied in many different forms and should not be construed as being limited to the embodiments set forth herein, but may be modified and altered without departing from the spirit and scope of the invention as defined in the appended claims.

10:
20: Compound planetary gear
21a: First sun gear
21b: second sun gear
21c: second sun gear shaft
21d: Two-speed primary gear
22a: first pinion gear
22b: second pinion gear
23: Carrier
23a: carrier shaft
23b: 1st stage primary gear
23c: Reverse primary gear
24a: a first ring gear
24b: a second ring gear
30: gear train
31: First gear
32: second gear
33: Third gear
40: Hydrostatic transmission
40a: Hydraulic pump
40b: Hydraulic motor
41: input shaft
42: Output shaft
43: Output gear
50: 1-2 step transmission portion
50a: Secondary speed reduction shaft
51: first gear
52: Second gear
53: 1-2 stepped clutch
60: Reverse transmission portion
61: reverse drive shaft
62: Reverse drive gear
63: Reverse output gear
64: Reverse clutch
65: Reverse gear
70: LH terminal transmission section
71: Negative speed LH Short shaft
72: Reduction top gear
72a: Top gear shaft
72b: Coupler
73: LH drive gear
74: H-stage drive gear
75: L-stage drive gear
76: LH stage clutch
80: final output shaft
81: H-stage output gear
82: L-stage output gear
90: Drive gear for 4-wheel drive
95: PTO clutch
96: PTO shaft

Claims (9)

The compound planetary gear 20 and the hydraulic pressure transmission 40 are connected to the drive shaft 10 so that the power of the engine is divided into the first sun gear 21a and the forward hydraulic transmission 40 through the drive shaft 10,
The compound planetary gear 20 is provided so that the first sun gear 21a rotates integrally with the drive shaft 10 and another second sun gear 21b slides on the drive shaft 10, The first pinion gear 22a and the second pinion gear 22b are engaged with the first sun gear 21a and the second sun gear 21b in a circumscribed state to form a plurality of single pinion gears 22a, A first ring gear 24a and a second ring gear 24b constituting a single body are provided so as to connect the two pinion gears 22b to each other, The second pinion gears 22b of the first pinion gear 22 are in contact with each other,
The forward hydraulic transmission 40 is connected such that its output shaft 42 drives the second ring gear 24b,
The power transmitted to the positive hydraulic transmission 40 is transmitted to the second ring gear 24b of the compound planetary gear 20 and synthesized with the power of the first sun gear 21a by the drive shaft 10, The sun gear 21b and the carrier 23 are divided and output,
The second-speed gear 21b and the carrier 23 are connected to the first-speed shifting portion 50,
And an LH step speed change portion 70 for shifting the power output from the auxiliary speed change / first-speed / second-speed shaft 50a of the first-second speed change portion 50 to the low-speed or high- Hydraulic mechanical transmission. The method according to claim 1,
Wherein the forward hydraulic transmission (40) receives power from the drive shaft (10) through the gear train (30) at a rear end of the compound planetary gear (20). The method according to claim 1,
The 1-2 step transmission portion (50)
The negative speed alternate first-speed and second-speed shaft 50a is installed in parallel with the drive shaft 10,
The first stage gear 51 driven by the carrier 23 slides on the auxiliary speed-first and second shaft 50a and the second stage driven by the second sun gear 21b. The gear 52 is provided so as to rotate in a sliding manner,
The first reduction gear 51 and the second reduction gear 52 are provided between the reduction gear first stage gear 51 and the second gear 52 so that the reduction gear first stage gear 51 and the second gear gear 52 And a second-stage clutch (53) which is operated in a direction to select any one of the first and second shift stages and to take a neutral state in which no shift stage is connected. The method of claim 3,
The carrier 23 and the first stage gear 51 are connected by a single stage primary gear 23b provided on the carrier shaft 23a extending from the carrier 23, (51) so as to be engaged with each other,
The connection between the second sun gear 21b and the second stage gear 52 is achieved by installing a two-stage primary gear 21d as a single body on the second sun shaft 21c extending from the second sun gear 21b (52) so as to engage with said second gear (52). The method according to claim 3 or 4,
Wherein the 1-2 step clutch (53) comprises a wet type multi-plate clutch using hydraulic pressure. The method according to claim 3 or 4,
The reverse transmission portion 60 is provided in association with the carrier 23 and the auxiliary transmission 1 - 2 shaft 50a,
The reverse speed change portion (60)
A reverse primary gear 23c provided as a single body on the carrier shaft 23a,
A reverse drive shaft 61 disposed in parallel with the auxiliary speed first-second stage shaft 50a,
A reverse drive gear 62 installed as a single body in the input direction of the reverse drive shaft 61 in a state of being engaged with the reverse primary gear 23c of the carrier shaft 23a and receiving power,
A reverse output gear (63) provided so as to be slid in a single body in the output direction of the reverse drive shaft (61)
A reverse clutch 64 provided between the reverse drive gear 62 and the reverse output gear 63 to connect or disconnect the reverse output gear 63 to the reverse drive shaft 61,
And a reverse driven gear (65) which is provided as a single body to the reduction gears 1-2 and 50a so as to be driven to engage with the reverse output gear (63) from the rear of the reduction gear second gear (52) Hydraulic mechanical transmission. The method according to claim 1,
The LH step speed change portion 70,
A negative speed change LH short shaft 71 installed in a direction parallel to the negative speed first-second speed shaft 50a,
A final output shaft 80 for transmitting the output from the auxiliary speed change LH short shaft 71 to an end reduction gear for transmitting to the drive wheels,
A negative speed change top gear 72 formed as a single body at a distal end of the negative speed alternate first and second shaft 50a,
An LH drive gear 73 which is provided as a single body on the negative speed change LH short shaft 71 and meshes with the negative speed change top gear 72 to drive the negative speed change LH short shaft 71,
An H-stage drive gear 74 and an L-stage drive gear 75 which are slidably mounted on the negative speed LH short shaft 71, respectively,
Stage drive gear 74 and an L-end drive gear 75 are provided on the negative speed change-speed LH short shaft 71 and the H-end drive gear 74 and the L- An LH stage clutch 76 that selectively connects and takes a neutral state,
An H-stage output gear 81 and an L-stage output gear 82 which are integrally provided on the final output shaft 80 and meshed with the H-stage drive gear 74 and the L-stage drive gear 75, respectively, Wherein the transmission mechanism is a transmission mechanism. 8. The method of claim 7,
The auxiliary speed change top gear 72 is formed on a top gear shaft 72a which is manufactured independently of the auxiliary speed-first and second-speed shaft 50a,
The top gear shaft 72a is connected to the negative speed first-and second-stage shaft 50a by a coupler 72b,
The final output shaft 80 is connected to the end of the top gear shaft 72a so as to rotate concentrically and is provided on the same axis as the auxiliary speed change shaft 1-2 and the final output shaft 80. [ Hydraulic mechanical transmission. 9. The method according to claim 7 or 8,
Wherein the LH step clutch (76) is composed of a synchronizer transmission mechanism, and the synchronizer transmission mechanism is provided with a shifting force by a separate actuator.

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