KR20240057369A - Transmission - Google Patents

Abstract

(Project) To provide a transmission for a crawler vehicle that can suppress the enlargement of the transmission case by compactly arranging the gearbox gear mechanism and the slewing gear mechanism.
(Solution) The straight pump 31 and straight motor 32 of the straight HST 11, the swing pump 41 and swing motor 42 of the swing HST 12, and the planetary gear mechanism 13L· 13R), a straight gear mechanism 17 that transmits the power of the straight motor 32 to the straight line input unit, and a swing gear mechanism 18 that transmits the power of the swing motor 42 to the swing system input part are included in the transmission case. In the transmission (1) for a crawler traveling vehicle mounted on snow (16), the straight gear mechanism (17) has a plurality of power transmission shafts (54·57) for straight movement, and the turning gear mechanism (18) has a plurality of turning gear mechanisms. It is provided with power transmission shafts 92·96 for straight movement, and at least one of the power transmission shafts 54·57 for straight movement and at least one of the power transmission shafts 92·96 for turning are on the same axis, and also in the axis longitudinal direction. are juxtaposed.

Description

Transmission for driving vehicles {Transmission}

The present invention relates to a transmission for a driving vehicle.

Conventionally, traveling vehicles such as combines or tillage tractors that continuously harvest and thresh the grain stalks of a field have been known. In the transmission for the traveling vehicle, a linear pump and motor of a hydraulic continuously variable structure that drives the left and right traveling crawlers in the same direction, and a turning pump and motor of a hydraulic continuously variable structure that drive the left and right traveling crawlers in the reverse direction are comprised of a planetary gear mechanism. It is mounted on a transmission case that transmits the driving force to the traveling crawler through the, and by controlling the output of each pump and motor for straight movement and turning by operating the steering handle and shift lever, driving force is transmitted to both the left and right traveling crawlers, and the forward and backward Techniques for making forward and turning runs are known.

Japanese Patent Publication No. 2001-277898

However, in the mission case that stores the power transmission mechanism consisting of a power transmission shaft and gears that transmit power from the linear pump and motor to the planetary gear mechanism, the rotation speed from the variable speed motor to the linear system input portion of the planetary gear mechanism is adjusted. The transmission case tended to be large because the straight-line gear mechanism having a sub-transmission mechanism and the like and the swing-type gear mechanism that transmits power from the steering motor to the swing-type input part of the planetary gear mechanism are individually accommodated.

Therefore, the present invention was made in view of the above problems, and its purpose is to provide a transmission for a traveling vehicle that can suppress the enlargement of the transmission case by compactly arranging the straight-forward gear mechanism and the turning gear mechanism.

The problem to be solved by the present invention is as described above, and the means for solving this problem will be described next.

That is, the transmission for a driving vehicle disclosed herein includes a driving device for straight movement,

A swing drive device,

It is provided with a planetary gear mechanism that distributes and outputs power to the left and right driving wheels,

a straight-forward gear mechanism that transmits the power of the straight-forward driving device to a straight-forward input unit of the planetary gear mechanism;

A transmission for a traveling vehicle in which a swing gear mechanism that transmits the power of the swing drive device to a swing input portion of the planetary gear mechanism is built into the transmission case,

The straight forward gear mechanism includes a plurality of power transmission shafts for straight forward movement,

The turning gear mechanism includes a plurality of turning power transmission shafts,

At least one of the power transmission shafts for moving forward and at least one of the power transmission shafts for turning are on the same axis,

In addition, they are juxtaposed in the direction of the axis length.

In the transmission for a driving vehicle disclosed herein, the driving device for straight movement includes:

A straight-line pump and a straight-line motor constituting the first hydraulic continuously variable transmission device,

The swing driving device,

Preferably, it is a swing pump and a swing motor that constitute the second hydraulic continuously variable transmission device.

In the transmission for a driving vehicle disclosed herein, the plurality of straight-forward power transmission shafts include at least a straight-forward input shaft through which power is transmitted from the straight-forward motor, and a plurality of sub-transmission gear trains that are parallel to the straight-forward input shaft and have different reduction ratios. It is a straight output shaft that can be freely connected through,

The plurality of turning power transmission shafts are at least a turning input shaft through which power is transmitted from the turning motor, and a turning output shaft parallel to the turning input shaft and transmitted through an electric gear train,

The turning output shaft and the straight input shaft are disposed on the same axis and overlap in the axis length direction,

It is preferable that the turning input shaft and the straight output shaft are arranged on the same axis and overlap in the axis length direction.

In addition, the transmission for a driving vehicle disclosed herein includes a straight-line electric motor that supplies power for straight-line movement,

A turning electric motor that supplies turning power,

A planetary gear mechanism that distributes and outputs power to the left and right driving wheels,

a straight-line gear mechanism that transmits power of the straight-line electric motor to a straight-line input unit of the planetary gear mechanism;

A transmission for a traveling vehicle in which a swing gear mechanism that transmits the power of the swing electric motor to a swing input portion of the planetary gear mechanism is installed in a transmission case,

The straight forward gear mechanism includes a plurality of power transmission shafts for straight forward movement,

The turning gear mechanism includes a plurality of turning power transmission shafts,

At least one of the power transmission shafts for moving forward and at least one of the power transmission shafts for turning are on the same axis,

Additionally, they are juxtaposed in the axial direction.

In the transmission for a traveling vehicle disclosed herein, a planetary gear mechanism for straight forward movement is interposed between the straight forward electric motor and the straight forward gear mechanism,

It is preferable that a planetary gear mechanism for turning is interposed between the turning electric motor and the turning gear mechanism.

According to the present invention, it is possible to provide a crawler traveling vehicle that can suppress the enlargement of the transmission case by compactly arranging the transmission gear gear mechanism and the swing gear gear mechanism.

1 is a front view showing a transmission for a driving vehicle according to an embodiment of the present invention.
Fig. 2 is a partial plan cross-sectional view showing the transmission.
Figure 3 is a power transmission diagram showing the transmission.
Fig. 4 is a power transmission diagram showing the transmission according to the second embodiment of the present invention.
Fig. 5 is a power transmission diagram showing the transmission according to the third embodiment of the present invention.
Fig. 6 is a perspective view showing a transmission according to a third embodiment of the present invention.
Fig. 7 is a power transmission diagram showing the transmission according to the fourth embodiment of the present invention.
Fig. 8 is a schematic diagram showing the configuration of a crawler traveling vehicle using a transmission for a traveling vehicle according to an embodiment of the present invention.
Fig. 9 is a schematic diagram showing the configuration of a four-wheeled work vehicle using a transmission for a traveling vehicle according to an embodiment of the present invention.
Fig. 10 is a schematic diagram showing the configuration of a four-wheeled vehicle using a transmission for a traveling vehicle according to an embodiment of the present invention.
Fig. 11 is a schematic diagram showing the configuration of a three-wheeled vehicle using a transmission for a traveling vehicle according to an embodiment of the present invention.
Fig. 12 is a schematic diagram showing the configuration of an articulating type four-wheeled vehicle using a transmission for a traveling vehicle according to an embodiment of the present invention.

(First Embodiment)

A transmission for a driving vehicle according to an embodiment of the present invention will be described. As shown in Figs. 1 and 2, the transmission 1 that transmits power from the engine E to the sprockets 15L·15R for driving the traveling crawler includes a HST 11 for straight movement, which is the first hydraulic continuously variable transmission device, and , and is equipped with a second hydraulic continuously variable transmission device, the swing HST (12). In addition, the transmission 1 includes, within the transmission case 16, a straight gear mechanism 17 that transmits the power of the HST 11 for straight movement and a turning gear mechanism 18 that transmits the power of the HST 12 for turning. ) and a planetary gear mechanism (13L·13R) that distributes power to the left and right sprocket shafts (14L·14R) is formed. 15L·15R are sprockets arranged on the outer ends of the sprocket shafts 14L·14R, and are respectively linked to crawlers not shown in the drawing, which are the driving wheels of the vehicle.

As shown in FIG. 1, the variable displacement type straight forward pump 31 and the fixed displacement type straight forward motor 32 constituting the straight forward HST 11 are fluidly connected through a closed circuit outside the drawing, and the operator operates outside the drawing. By changing the capacity of the straight-forward pump 31 using a main speed operating tool consisting of a lever, pedal, etc., the straight-forward motor 32 is stopped and the output of the forward/reverse rotation is controlled.

In addition, as shown in FIG. 1, the swing HST 12 is also fluidly connected to the variable displacement type swing pump 41 and the fixed displacement type swing motor 42 through a closed circuit outside the drawing, and the operator is connected to the swing HST 12 in the drawing. By changing the capacity of the swing pump 41 using an external turning operation tool such as a steering handle, the stopping and forward/reverse output control of the turning motor 42 is performed.

As shown in FIG. 1, the HST 11 for straight progress and the HST 12 for turning are arranged side by side along the front-back direction on one side of the transmission case 16. In addition, in the HST 11 for straight movement, the straight pump 31 is disposed at the upper side, and the straight motor 32 is disposed at the lower side, and in the HST 12 for swing, the swing pump 41 is disposed at the upper side, The swing motor 42 is disposed on the lower side. The pump gear 31b driving the straight pump shaft 31a and the pump gear 41b driving the turning pump shaft 41a are meshed with each other with respect to a common engine gear Ea.

As shown in FIGS. 2 and 3, the transmission 1 is stored in the transmission case 16. The straight gear mechanism 17 has a subtransmission device 51 and a parking brake 52. The auxiliary transmission device 51 is a straight forward first axis 54, which is a straight forward input shaft that fixes an input gear 53 that meshes with a straight drive gear 32b formed on the straight forward motor shaft 32a of the straight forward motor 32. ) and a second axis for straight progression (57), which is a straight output axis parallel to the first axis for straight progression (54), and a shift gear mechanism (55) constituting a sub-shift gear train that allows free connection between the two axes. is provided.

The first shaft 54 for straight advancement is a straight input shaft, and a plurality of drive gears 55a·56a with different diameters constituting the transmission gear mechanism 55 are fixed and supported so that they cannot rotate relative to each other.

In addition, the second shaft 57 for straight forward movement is a straight forward output shaft, and is a driven gear ( 55b·56b) are formed to allow relative rotation. In addition, the second shaft 57 for straight movement is provided with a clutch slider 60 that cannot be relatively rotated but can freely slide in the axial direction, and is selectively engaged with any of the driven gears 55b and 56b. , it is possible to shift the rotational power from the first axis 54 for straight movement and transmit it to the second axis 57 for straight movement. The clutch slider 60 is linked with a shift operation lever (not shown), and the shift gear mechanism 55 is switched by operation of the operator. In addition, in this embodiment, the gear shift mechanism is a two-speed type, but it can also be configured as a three-speed changeable type depending on the specifications of the vehicle.

At approximately the middle position of the second shaft 57 for straight movement in the axial longitudinal direction, the large-diameter output gear 61 is fixed and supported so as not to rotate relative to it. The shifting gear mechanism 56 is disposed on one side of the large diameter gear 61. The large diameter gear 61 meshes with the input gear 63 of the sun gear shaft 62. The sun gear shaft 62 constitutes a straight-forward input unit of the left and right planetary gear mechanisms 13L·13R, and when the turning system input unit described later is not driven, the power of the straight-forward HST 11 is used to drive the left-right running crawler. It is transmitted to the sprocket (15L·15R) to drive forward or backward.

The left and right planetary gear mechanisms 13L·13R include sun gears 81·81 formed on both ends of the sun gear shaft 62, and ring gears 82·82 loosely fitted and supported on the output shaft 19L·19R. and carriers 83·83 that are fixed to the output shafts 19L·19R so that they cannot rotate relative to each other, and planetary gears 84 that mesh with the inner gears 82a of each of the sun gears 81 and ring gears 82. ·84), and both ends of the sun gear shaft 62 are supported so as to rotate freely on the carriers 83·83. Additionally, the planet gears 84·84 are loosely supported by the pinion shaft 85 fixed to the carrier 83·83.

The rotational power for straight movement from the first shaft 54 for straight movement is transmitted from the sun gear shaft 62 to the sun gears 81 of the left and right planetary gear mechanisms 13L·13R, and rotates the planetary gear 84. (Rotate) Let me do it.

At this time, if the swing pump 41 assumes a neutral position and the swing motor 42 is stopped, the ring gear 82·82 cannot rotate, so the planet gear 84·84 revolves and moves the carriers 83 on the left and right. ·83) rotates in the same direction, and the straight-forward rotation power drives the pair of output shafts 19L·19R at the same rotation speed and in the same rotation direction to drive the sprocket shafts 14L·14R.

The turning rotational power output from the turning motor shaft 42a of the turning HST 12 via the turning drive gear 42b is transmitted to the turning gear mechanism 18.

The turning gear mechanism 18 is provided with a turning first axis 92, which is a turning input axis, and a turning second axis 96, which is a turning output axis, which are parallel to each other. The first shaft 92 for turning is a hollow shaft-shaped turning input shaft through which power is transmitted from the turning motor shaft 42a, and the second shaft 57 for straight movement is located on the other side of the large diameter gear 61. It is supported so as to be covered on the same axis. By configuring in this way, the space for arranging the first axis 92 for turning becomes unnecessary. Additionally, the transmission case 16 does not need a bearing to support the first axis 92 for turning. Accordingly, there is room in the layout of the mission case 16 and miniaturization can be achieved.

An input gear 93 is integrally formed on the other end of the first axis 92 for turning, and an output gear 95 is formed on one end thereof. The input gear 93 is meshed with the swing drive gear 42b, and the output gear 95 is meshed with the second axis-side input gear 97 of the second shaft 96 for swing.

The second axis 96 for turning is a turning output axis that distributes the power from the first axis 92 for turning to the left and right planetary gear mechanisms 13L·13R, and has the same axis as the first axis 54 for straight movement. They are arranged so that they overlap in the axial direction. By configuring in this way, the space for arranging the second axis 96 for turning is reduced. Accordingly, there is room in the layout of the mission case 16 and miniaturization can be achieved.

In addition, the second turning shaft 96 is provided with a first output gear 98 and a second output gear 99 for transmitting power to the left and right planetary gear mechanisms 13L·13R, and a large diameter gear 61. It is formed to be sandwiched between. The first output gear 98 meshes with the outer gear 82b of the left ring gear 82 via the idle gear 100. Additionally, the second output gear 99 is directly meshed with the outer gear 82b of the ring gear 82 on the right side.

Additionally, the idle gear 100 is adjacent to one side of the large diameter gear 61 and is loosely supported so as to overlap on the same axis as the second shaft 57 for straight advancement. By configuring in this way, the space for arranging the idle gear 100 is reduced. Accordingly, there is room in the layout of the mission case 16 and miniaturization can be achieved.

The turning power output from the turning motor shaft 42a of the turning HST 12 is transmitted from the turning drive gear 42b to the input gear 93 to the turning first shaft 92. The turning power output from the first turning axis 92 is transmitted to the second axis side input gear 97 which meshes with the first axis side output gear 95, and is transmitted to the turning second axis 96. do.

The turning power output from the second turning axis 96 is distributed to the left and right. The rotational power for turning on the left side is transmitted in the forward rotation direction to the planetary gear mechanism 13L on the left side by the first output gear 98, the idle gear 100, and the outer gear 82b of the ring gear 82. do. On the other hand, the rotational power for turning on the right side is directly transmitted from the second output gear 99 to the planetary gear mechanism 13R on the right side through the outer gear 82b of the ring gear 82.

Therefore, the turning rotational power output from the turning motor shaft 42a of the turning HST 12 moves the ring gears 82·82 of the pair of planetary gear mechanisms 13L·13R at the same rotational speed. As for the rotation direction, they are driven in a state where they are opposite to each other.

In the straight-ahead state, when a turning operation is performed using a steering operation tool (not shown), the ring gear 82 linked to the carrier 83 increases the speed of the carrier 83 on the side rotating in the same direction. Together with this, the carrier 83 on the side rotating in the reverse direction is decelerated. As the operating amount of the steering operation tool is increased and the output rotation of the turning HST (12) is increased, the differential rotation of both carriers (83·83) (output shafts (19L·19R)) increases and the turning radius of the vehicle can be reduced. there is.

As described above, the transmission 1 for a crawler traveling vehicle according to the present invention includes a straight-forward pump 31 and a straight-forward motor 32 of the straight-forward HST 11, which is a first hydraulic continuously variable transmission device, and a second hydraulic continuously variable transmission device. It is provided with a swing pump 41 and a swing motor 42 of the HST 12 for turning, and a planetary gear mechanism 13L·13R that distributes and outputs power to the left and right driving wheels, and the power of the straight motor 32 a straight gear mechanism 17 that transmits the power of the turning motor 42 to the turning system input part of the planetary gear mechanisms 13L·13R, and a turning gear mechanism ( In the transmission (1) for a crawler traveling vehicle in which 18) is installed in the transmission case (16), the straight gear mechanism (17) is provided with a plurality of power transmission shafts (54·57) for straight advance, and includes a turning gear mechanism ( 18) is provided with a plurality of power transmission shafts 92·96 for turning, and at least one of the power transmission shafts 54·57 for going straight and at least one of the power transmission shafts 92·96 for turning have the same axis and different centers. However, they are also juxtaposed in the direction of the axis length.

By configuring in this way, the space for arranging the first axis 92 for turning and the second axis 96 for turning is reduced. Accordingly, there is room in the layout of the mission case 16 and miniaturization can be achieved.

In addition, the plurality of power transmission shafts for straight ahead are at least parallel to the first axis 54 for straight forward, which is a straight forward input shaft through which power is transmitted from the straight forward motor 32, and the first axis 54 for straight forward, which is the straight forward input shaft. , a second axis 57 for straight forward, which is a straight forward output shaft that can be freely connected through a plurality of sub-transmission gear trains 55·56 with different reduction ratios,

The plurality of turning power transmission shafts are at least parallel to a turning first axis 92, which is a turning input axis through which power is transmitted from the turning motor 42, and a turning first axis 92, which is a turning input axis, It is a second axis for turning (96), which is a turning output axis transmitted through an electric gear train (95·97),

The second axis for turning (96), which is the turning output axis, and the first axis (54) for going straight, which is the input axis for going straight, are disposed so that they overlap in the axis longitudinal direction while being on the same axis,

The first axis 92 for turning, which is the turning input axis, and the second axis 57, which is the straight output axis, are disposed so as to overlap in the axis length direction while being on the same axis.

By configuring in this way, compared to the case where the first axis 92 for turning and the second axis 96 for turning are arranged separately, there is room in the layout of the mission case 16 and miniaturization can be achieved.

(Second Embodiment)

Additionally, the transmission for a traveling vehicle according to the second embodiment will be explained using FIG. 4.

As shown in FIG. 4 , the traveling vehicle is provided with a straight electric motor 111 that supplies power for straight movement and a turning electric motor 112 that supplies power for turning. In addition, the transmission 101 includes, within the transmission case 116, a straight gear mechanism 117 that transmits the power of the straight electric motor 111 and a turning gear mechanism 118 that transmits the power of the turning electric motor 112. ) and a planetary gear mechanism (113L·113R) that distributes power to the left and right drive shafts (114L·114R) is formed. 115L·115R are drive wheels disposed on the outer ends of the drive shafts 114L·114R, and are respectively connected to the driving device of the vehicle.

As shown in FIG. 4, the transmission 101 is stored in the transmission case 116. The straight gear mechanism 117 has a subtransmission device 151 and a parking brake 152. The auxiliary transmission device 151 is a straight-forward first axis ( 154), a second axis 157 for straight progress, which is a straight output axis parallel to the first axis 154, and a shift gear mechanism 155 that constitutes a sub-transmission gear train that allows free connection between the two axes. ) is provided.

The first shaft 154 for straight forward movement is a straight forward input shaft, and a plurality of drive gears 155a·156a with different diameters constituting the transmission gear mechanism 155 are fixed and supported so that they cannot rotate relative to each other.

In addition, the second shaft 157 for straight progress is a straight output shaft, and is a driven gear 155b that is always engaged with each of the drive gears 155a and 156a, which constitute the shift gear mechanism 156 constituting the auxiliary shift gear train. ·156b) is formed to allow relative rotation. In addition, the second shaft 157 for straight movement is provided with a clutch slider 160 that cannot be relatively rotated but can freely slide in the axial direction, and is selectively engaged with any of the driven gears 155b and 156b. , it is possible to change the rotational power from the first axis 154 for straight movement and transmit it to the second axis 157 for straight movement. The clutch slider 160 is linked with a shift operation lever (not shown), and the shift gear mechanism 155 is switched by operation of the operator. In addition, in this embodiment, the gear shift mechanism is a two-speed type, but it can also be configured as a three-speed changeable type depending on the specifications of the vehicle.

At approximately the middle position of the second shaft 157 for straight movement in the axial longitudinal direction, the large-diameter output gear 161 is fixed and supported so as not to rotate relative to it. The shifting gear mechanism 155 is disposed on one side of the large diameter gear 161. The large diameter gear 161 is engaged with the input gear 163 of the sun gear shaft 162. The sun gear shaft 162 constitutes a straight-line input unit of the left and right planetary gear mechanisms 113L·113R, and when the turning system input unit described later is not driven, the power of the straight-line electric motor 111 is applied to the drive wheels of the left and right traveling devices ( 115L·115R) to drive forward or backward.

The left and right planetary gear mechanisms 113L·113R include sun gears 181·181 formed on both ends of the sun gear shaft 162, and ring gears 182·182 that loosely fit and support the output shaft 119L·119R. and carriers 183·183 that are fixed to the output shafts 119L·119R so that they cannot rotate relative to each other, and planetary gears 184 that mesh with the inner gears 182a of each of the sun gears 181 and ring gears 182. ·184), and both ends of the sun gear shaft 162 are supported so that they can rotate freely on the carriers 183·183. Additionally, the planetary gears 184·184 are loosely fitted and supported on the pinion shaft 185 fixed to the carrier 183·183.

The rotational power for straight movement from the first shaft 154 for straight movement is transmitted from the sun gear shaft 162 to the sun gears 181 of the left and right planetary gear mechanisms 113L·113R, and rotates the planetary gear 184. (Rotate) Let me do it.

At this time, when the brake mechanism 112c directly connected to the swing electric motor 112 operates to stop the shaft rotation, the ring gears 182·182 become unable to rotate, so the planet gears 184·184 rotate left and right. The carriers 183·183 rotate in the same direction, and the straight-forward rotation power drives the pair of output shafts 119L·119R at the same rotation speed and in the same rotation direction, driving the drive shafts 114L·114R. I order it.

The turning rotational power output from the turning motor shaft 112a of the turning electric motor 112 via the turning drive gear 112b is transmitted to the turning gear mechanism 118. A brake mechanism 112c that enables stopping downstream rotation is formed in the middle portion of the swing motor shaft 112a.

The turning gear mechanism 118 includes a first turning axis 192, which is a turning input axis, and a turning second axis 196, which is a turning output axis, which are parallel to each other. The first shaft 192 for turning is a hollow shaft-shaped turning input shaft through which power is transmitted from the turning motor shaft 112a, and the second shaft 157 for straight movement is located on the other side of the large diameter gear 161. It is supported so as to be covered on the same axis. By configuring in this way, the space for arranging the first axis 192 for turning becomes unnecessary. Additionally, there is no need for a bearing in the transmission case to support the first axis 192 for turning. Therefore, there is room in the layout of the mission case and miniaturization can be achieved.

An input gear 193 is integrally formed on the other end of the first turning shaft 192, and an output gear 195 is formed on one end thereof. The input gear 193 is meshed with the swing drive gear 112b, and the output gear 195 is meshed with the second axis side input gear 197 of the second shaft 196 for swing.

The second axis 196 for turning is a turning output axis that distributes the power from the first axis 192 for turning to the left and right planetary gear mechanisms 113L·113R, and has the same axis as the first axis 154 for straight movement. They are arranged so that they overlap in the axial direction. By configuring in this way, the space for arranging the second axis 196 for turning is reduced. Therefore, there is room in the layout of the mission case and miniaturization can be achieved.

In addition, the second turning shaft 196 includes a first output gear 198 and a second output gear 199 for transmitting power to the left and right planetary gear mechanisms 113L·113R, and a large diameter gear 161. It is formed to be sandwiched between. The first output gear 198 meshes with the outer gear 182b of the left ring gear 182 via the idle gear 200. Additionally, the second output gear 199 is directly meshed with the outer gear 182b of the ring gear 182 on the right side.

Additionally, the idle gear 200 is adjacent to one side of the large-diameter gear 161 and is loosely supported so as to overlap on the same axis as the second axis 157 for straight advancement. By configuring in this way, the space for arranging the idle gear 200 is reduced. Accordingly, there is room in the layout of the mission case 116 and miniaturization can be achieved.

The turning rotational power output from the turning motor shaft 112a of the turning electric motor 112 is transmitted to the turning first shaft 192 from the turning drive gear 112b to the input gear 193. The turning power output from the first turning axis 192 is transmitted to the second axis side input gear 197 which meshes with the first axis side output gear 195, and is transmitted to the turning second axis 196. do.

The turning power output from the second turning axis 196 is distributed to the left and right. The rotational power for turning on the left side is transmitted in the forward rotation direction to the planetary gear mechanism 113L on the left side by the first output gear 198, the idle gear 200, and the outer gear 182b of the ring gear 182. do. On the other hand, the rotational power for turning on the right side is directly transmitted from the second output gear 199 to the planetary gear mechanism 113R on the right side through the outer gear 182b of the ring gear 182.

Therefore, the turning rotational power output from the turning motor shaft 112a of the turning electric motor 112 moves the ring gears 182·182 of the pair of planetary gear mechanisms 113L·113R at the same rotation speed. As for the rotation direction, they are driven in a state where they are opposite to each other.

In the straight-ahead state, when a turning operation is performed using a steering operation tool (not shown), the ring gear 182 linked to the carrier 183 increases the speed of the carrier 183 on the side rotating in the same direction. Together with this, the carrier 183 on the side rotating in the reverse direction is decelerated. As the operation amount of the steering operation tool is increased and the output rotation of the turning electric motor 112 is increased, the differential rotation of both carriers 183·183 (output shafts 119L·119R) increases and the turning radius of the vehicle can be reduced. there is.

(Third Embodiment)

In addition, as a third embodiment, as shown in FIGS. 5 and 6, a planetary gear mechanism 211 is formed between the straight electric motor 111 that supplies power for straight forward movement and the straight forward gear mechanism 117. Alternatively, the planetary gear mechanism 212 may be formed between the turning electric motor 112 that supplies turning power and the turning gear mechanism 118.

As shown in FIG. 6 , the straight electric motor 111 is arranged on the right side of the transmission 101, and the turning electric motor 112 is arranged on the left side of the transmission 101. In this way, by arranging the straight electric motor 111 and the turning electric motor 112 on the left and right with the transmission 101 as the center, the left and right are balanced and mountability is improved.

The planetary gear mechanism 211 is rotationally supported by a sun gear 223 formed at the end of the sun gear shaft 222 connected to the straight motor shaft 111a of the straight electric motor 111 and the output shaft 224. , a ring gear 225 fixed in the case so as not to rotate relative to the axial direction, a carrier 226 fixed not to rotate relative to the output shaft 224, the sun gear 223, and the ring gear 225. It is provided with a planetary gear 227 that engages the inner gear 225a, and the other end of the sun gear shaft 222 is supported on the carrier 226 so that it can rotate freely. Additionally, the planetary gear 227 is loosely supported by the pinion shaft 228 fixed to the carrier 226.

The driving force of the straight-line electric motor 111 is transmitted from the sun gear shaft 222 connected to the straight-line motor shaft 111a to the sun gear 223 to rotate the planetary gear 227. The planetary gear 227 is meshed with the inner gear 225a of the ring gear 225, and rotates around the fixed output shaft 224 of the carrier 226. As a result, the driving force of the straight-line electric motor 111 is decelerated and transmitted to the output shaft 224. The straight drive gear 224a formed on the output shaft 224 is meshed with the input gear 229 formed on the third axis 230 for straight drive. The output gear 231 of the third axis 230 for straight movement is meshed with the input gear 153.

By configuring in this way, the output from the output shaft 224 can realize high torque, so even if the linear electric motor 111 is made small, high torque output can be realized.

Additionally, the planetary gear mechanism 212 is provided with a sun gear shaft 242 connected to the swing motor shaft 112a of the swing electric motor 112. The planetary gear mechanism 212 includes a sun gear 243 formed at the end of the sun gear shaft 242, and a ring gear 245 supported on the output shaft 244 and fixed in the case so that it cannot rotate relative to the axial direction. ) and a carrier 246 that is fixed so as not to rotate relative to the output shaft 244, and a planetary gear 247 that engages the inner gear 245a of the sun gear 243 and the ring gear 245. Together, the other end of the sun gear shaft 242 is supported so that it can rotate freely on the carrier 246. Additionally, the planetary gear 247 is loosely supported by the pinion shaft 248 fixed to the carrier 246.

The driving force of the turning electric motor 112 is transmitted from the sun gear shaft 242 connected to the turning motor shaft 112a to the sun gear 243 to rotate the planetary gear 247. The planetary gear 247 is meshed with the inner gear 245a of the ring gear 245, and rotates around the fixed output shaft 244 of the carrier 246. As a result, the driving force of the swing electric motor 112 is decelerated and transmitted to the output shaft 244. The turning drive gear 244a formed on the output shaft 244 is meshed with the input gear 249 formed on the third turning axis 250. The output gear 251 of the third turning axis 250 is meshed with the input gear 193. Additionally, a turning brake 252 for stopping the rotation of the turning third axis 250 is provided on the turning third axis 250.

With this configuration, the output from the output shaft 244 can realize high torque, so even if the swing electric motor 112 is made small, high torque output can be realized.

(Fourth Embodiment)

In addition, as another embodiment, a planetary gear mechanism 211 is formed between the straight electric motor 111 that supplies power for straight movement and the straight gear mechanism 117, and a turning gear mechanism 211 that supplies power for turning is provided. A planetary gear mechanism 212 is formed between the electric motor 112 and the turning gear mechanism 118. In addition, the ring gear 225 of the planetary gear mechanism 211 is loosely supported by the output shaft 244, and the power from the working prime mover 261 is transmitted to the outer gear 245b of the ring gear 245. You can do it as a configuration.

The planetary gear mechanism 211 is loosely fitted with respect to the output shaft 244 and the sun gear 223 formed at the end of the sun gear shaft 222 connected to the straight motor shaft 111a of the straight electric motor 111. A supported ring gear 225, a carrier 226 fixed to prevent relative rotation with respect to the output shaft 224, and a planetary gear meshed with the inner gear 225a of the sun gear 222 and the ring gear 225 ( 227), and the other end of the sun gear shaft 222 is supported on the carrier 226 so that it can rotate freely. Additionally, the planetary gear 227 is loosely supported by the pinion shaft 228 fixed to the carrier 226.

The driving force of the straight-line electric motor 111 is transmitted from the sun gear shaft 222 connected to the straight-line motor shaft 111a to the sun gear 223 to rotate the planetary gear 227. The planetary gear 227 is meshed with the inner gear 225a of the ring gear 225, and rotates around the fixed output shaft 224 of the carrier 226. As a result, the driving force of the straight-line electric motor 111 is decelerated and transmitted to the output shaft 224. The straight drive gear 224a formed on the output shaft 224 is meshed with the input gear 229 formed on the third axis 230 for straight drive. The output gear 231 of the third axis 230 for straight movement is meshed with the input gear 153.

Meanwhile, the power from the prime mover 261 for work is transmitted through the output pulley 262, the output belt 263, and the input pulley 264 to the outer gear of the ring gear 225 that meshes with the power input gear 265 for work ( 225b). The rotation of the ring gear 225 increases the speed of the carrier 226 on the side rotating in the same direction. As a result, the driving force of the work prime mover 261 can be used as auxiliary power for straight movement.

Additionally, the planetary gear mechanism 212 is provided with a sun gear shaft 242 connected to the swing motor shaft 112a of the swing electric motor 112. The planetary gear mechanism 212 includes a sun gear 243 formed at the end of the sun gear shaft 242, a ring gear 245 loosely fitted and supported on the output shaft 224, and relative rotation with respect to the output shaft 244. The other end of the sun gear shaft 242 is provided with a carrier 246 that makes it impossible to fix it, and a planetary gear 247 that meshes with the inner gear 245a of the sun gear 243 and the ring gear 245. It is supported so that it can rotate freely on the carrier 246. Additionally, the planetary gear 247 is loosely supported by the pinion shaft 248 fixed to the carrier 246.

The driving force of the turning electric motor 112 is transmitted from the sun gear shaft 242 connected to the turning motor shaft 112a to the sun gear 243 to rotate the planetary gear 247. The planetary gear 247 is meshed with the inner gear 245a of the ring gear 245, and rotates around the fixed output shaft 244 of the carrier 246. As a result, the driving force of the swing electric motor 112 is decelerated and transmitted to the output shaft 244. The straight drive gear 244a formed on the output shaft 244 is meshed with the input gear 249 formed on the third axis 250 for turning. The output gear 251 of the third turning axis 250 is meshed with the input gear 193.

With this configuration, the output from the output shaft 244 can realize high torque, so even if the swing electric motor 112 is made small, high torque output can be realized.

Next, an embodiment of a traveling vehicle equipped with the traveling vehicle transmission 1, 101 will be described below.

The traveling vehicle in this embodiment may be the crawler traveling vehicle 301 shown in FIG. 8. The crawler traveling vehicle 301 shown in FIG. 8 is equipped with the transmission 101 according to the second embodiment.

The crawler traveling vehicle 301 includes sprockets (115L·115R) and driven sprockets (303), which are driving wheels arranged on the left and right sides of the vehicle body, and an endless crawler (304) wound around the sprockets (115L·115R) and driven sprockets (303). ) has. The sprockets 115L·115R are driven by a straight electric motor 111 and a turning electric motor 121, which are drive sources. The straight electric motor 111 and the turning electric motor 112 are arranged one on each side.

The straight electric motor 111 and the turning electric motor 112 are connected to a battery 310 disposed in the front center of the vehicle. An inverter 311·311 is formed between the battery 310 and the straight electric motor 111 and the turning electric motor 112 to convert direct current into alternating current. By supplying alternating current from the battery 310 to the straight electric motor 111 and the turning electric motor 112 through the inverters 311·311, the straight electric motor 111 and the turning electric motor 112 are driven.

In addition, the traveling vehicle in this embodiment may be a four-wheeled work vehicle 321 having a work unit 331 shown in FIG. 9. The four-wheeled work vehicle 321 shown in FIG. 9 is equipped with a transmission 101 according to the third embodiment. The working part 331 is formed in the front part of the vehicle and is composed of a mechanism for transporting earth and sand, such as a bucket. The working section 331 may be a topping board in addition to a bucket.

The four-wheeled work vehicle 321 has drive wheels 332 arranged at four locations on the front, rear, and left sides of the vehicle body. The drive wheel 332 is driven by a straight-line electric motor 111 and a turning electric motor 112, which are drive sources. A power transmission mechanism 333 is formed between the front and rear drive wheels 332 arranged on the left and right sides of the vehicle body. The power transmission mechanism 333 is disposed at the center in the front-back direction and includes sprockets 115L·115R that output the driving force from the transmission 101, and a driven sprocket 332b formed on the drive shaft 332a of the front and rear drive wheels 332. ) and a chain 335 wound between the sprockets 115L·115R and the driven sprocket 332b. The output of the transmission 101 is transmitted to the sprockets 115L·115R, and is transmitted from the sprockets 115L·115R through the chain 335 to the front and rear drive wheels 332 as rotational force in the same direction.

In addition, the straight electric motor 111 and the turning electric motor 112 are arranged one on the left and right. In this embodiment, the straight electric motor 111 and the turning electric motor 112 are connected to a battery not shown. By supplying alternating current from the battery to the straight electric motor 111 and the turning electric motor 112 through the inverter, the straight electric motor 111 and the turning electric motor 112 are driven. In addition, a planetary gear mechanism 211 is formed between the straight electric motor 111 and the straight gear mechanism 117, and a planetary gear mechanism is formed between the turning electric motor 112 and the turning gear mechanism 118. It is configured to form (212). As a result, the output from the sprockets 115L·115R can realize high torque, so even if the straight electric motor 111 and the turning electric motor 112 are made small, high torque output can be realized.

The traveling vehicle in this embodiment may be a four-wheeled vehicle 341 shown in FIG. 10 . The four-wheeled vehicle 341 shown in FIG. 10 is equipped with a transmission 101 according to the second embodiment.

The four-wheeled transport vehicle 341 has rear wheels 351 and front wheels 352 arranged at four locations on the left and right sides of the front and back of the vehicle body. Four-wheeled vehicle 341 is four-wheel drive. The four-wheeled vehicle 341 has sprockets (115L·115R) and driven sprockets 353 arranged on the left and right sides of the vehicle body, and a chain 354 wound around the sprockets (115L·115R) and driven sprockets 353. . The sprockets 115L·115R are driven by a straight electric motor 111 and a turning electric motor 121, which are drive sources. The straight electric motor 111 and the turning electric motor 112 are arranged one on the left and right.

Sprockets 115L·115R are directly connected to the drive wheel 351 and drive the rear wheel 351. Additionally, the driven sprocket 353 is connected to the axle 352a of the front wheel 352.

The straight electric motor 111 and the turning electric motor 112 are connected to a battery 310 disposed in the front center of the vehicle. An inverter 311·311 is formed between the battery 310 and the straight electric motor 111 and the turning electric motor 112 to convert direct current into alternating current. By supplying alternating current from the battery 310 to the straight electric motor 111 and the turning electric motor 112 through the inverters 311·311, the straight electric motor 111 and the turning electric motor 112 are driven.

The traveling vehicle in this embodiment may be a three-wheeled vehicle 361 shown in FIG. 11 . The three-wheeled vehicle 361 shown in FIG. 11 is equipped with a transmission 101 according to the second embodiment.

The three-wheeled transport vehicle 361 has two rear wheels 371 arranged in the rear part of the car body, and a front wheel 372 arranged in one place in the front part of the car body. The three-wheeled vehicle 361 is rear-wheel drive. The three-wheeled vehicle 361 is driven by a straight-line electric motor 111 and a turning electric motor 112, which are drive sources. The straight electric motor 111 and the turning electric motor 112 are arranged one on each side.

The output from the transmission 101 is transmitted directly to the rear wheel 371 from the left and right drive shafts 373L·373R, and drives the rear wheel 371. Additionally, the front wheel 372 is able to swing freely by the axle support portion 374.

The straight electric motor 111 and the turning electric motor 112 are connected to a battery 310 disposed in the front center of the vehicle. An inverter 311·311 is formed between the battery 310 and the straight electric motor 111 and the turning electric motor 112 to convert direct current into alternating current. By supplying alternating current from the battery 310 to the straight electric motor 111 and the turning electric motor 112 through the inverters 311·311, the straight electric motor 111 and the turning electric motor 112 are driven.

The traveling vehicle in this embodiment may be a four-wheeled vehicle 381 shown in FIG. 12 . The four-wheeled vehicle 381 shown in FIG. 12 is equipped with two transmissions 101 at the front and rear according to the second embodiment.

The four-wheeled vehicle 381 is an articulating type vehicle and has a joint portion 391 between the front and rear vehicle bodies, and the front vehicle body 392A and the rear vehicle body 392B are centered on the joint section. It is designed to be moved independently. The front car body 392A and the rear car body 392B are connected by a connecting cylinder 393 to enable relative movement. Additionally, the joint portion 391 has a rotation axis 391a, and the front vehicle body 392A and the rear vehicle body 392B can be moved around the rotation axis 391a. The front body 392A and the rear body 392B have rear wheels 394 and front wheels 395. Four-wheeled vehicle 381 is four-wheel drive. The four-wheeled vehicle 381 has a total of two driving sources, a straight electric motor 111 and a turning electric motor 112, one at the front and the other at the rear.

The output from the transmission 101 disposed on the rear body 392B is directly connected to the rear wheel 394 through the left and right drive shafts 396L·396R, and drives the rear wheel 394. Additionally, the output from the transmission 101 disposed on the front vehicle body 392A is directly connected to the front wheels 395 through the left and right drive shafts 397L·397R, and drives the front wheels 395.

The straight electric motor 111 and the turning electric motor 112 arranged front and rear are connected to batteries 398 and 398 arranged on the front car body 392A and the rear car body 392B, respectively. Inverters 399·399 for converting direct current to alternating current are formed between the batteries 398 and 398 and the straight electric motor 111 and the turning electric motor 112, respectively. By supplying alternating current from the battery 398 to the straight electric motor 111 and the turning electric motor 112 through the inverters 399·399, the straight electric motor 111 and the turning electric motor 112 are driven. Additionally, the battery 398 and the inverter 399 may be common to the front and rear straight electric motors 111 and turning electric motors 112 by using one device.

1: Transmission
11: HST for going straight
12: HST for turning
13L·13R: Planetary gear mechanism
14L·14R: Sprocket axis
16: Mission case
17: straight gear mechanism
18: Swivel gear mechanism
19L·19R: Output shaft
31: straight pump
32: straight motor
32a: Shift motor shaft
41: Swivel pump
42: slewing motor
42a: Swivel motor shaft
51: Sub-transmission device
54: 1st axis for going straight (going straight input axis)
55: Shift gear mechanism (sub-shift gear train)
56: Shift gear mechanism (sub-shift gear train)
57: 2nd axis for straight movement (straight output axis)
62: Sun gear shaft
81: sun gear
82: ring gear
83: carrier
84: planetary gear
92: 1st axis for turning (turning input axis)
96: 2nd axis for turning (swivel output axis)
101: Transmission
111: straight electric motor
111a: straight motor shaft
111b: straight drive gear
112: Swivel electric motor
112a: Swivel motor shaft
112b: slewing drive gear
112c: Brake mechanism
113L·113R: Planetary gear mechanism
114L·114R: Drive shaft
116: Mission case
117: straight gear mechanism
118: Swivel gear mechanism
119L·119R: Output shaft
151: Sub-transmission device
154: 1st axis for going straight (going straight input axis)
155: Shift gear mechanism (sub-shift gear train)
156: Shift gear mechanism (sub-shift gear train)
157: 2nd axis for straight movement (straight output axis)
162: Sun gear shaft
181: sun gear
182: ring gear
183: carrier
184: planetary gear
192: 1st axis for turning (swing input axis)
196: 2nd axis for turning (swivel output axis)
211: Planetary gear mechanism
212: Planetary gear mechanism
222: Sun gear shaft
223: sun gear
225: ring gear
226: carrier
227: planetary gear
230: 3rd axis for going straight
242: Sun gear shaft
243: sun gear
245: ring gear
246: carrier
247: planetary gear
250: 3rd axis for turning
252: Swivel brake
261: Work prime mover
262: output pulley
263: output belt
264: input pulley
301: Crawler driving car
321: 4-wheeled work vehicle
341: Four-wheeled transport vehicle
361: three-wheeled transport vehicle
381: Four-wheeled transport vehicle

Claims (5)

A driving device for going straight,
A swing drive device,
It is provided with a planetary gear mechanism that distributes and outputs power to the left and right driving wheels,
A straight gear mechanism that transmits the power of the straight drive drive device to a straight line input unit of the planetary gear mechanism,
In a transmission for a traveling vehicle in which a swing gear mechanism that transmits the power of the swing drive device to a swing input portion of the planetary gear mechanism is installed in a transmission case,
The straight forward gear mechanism includes a plurality of power transmission shafts for straight forward movement,
The turning gear mechanism includes a plurality of turning power transmission shafts,
At least one of the power transmission shafts for moving forward and at least one of the power transmission shafts for turning are on the same axis,
In addition, a transmission for a driving vehicle characterized in that it is juxtaposed in the axis length direction. According to claim 1,
The driving device for going straight,
A straight-line pump and a straight-line motor constituting the first hydraulic continuously variable transmission device,
The swing driving device,
A transmission for a driving vehicle that is a swing pump and a swing motor constituting a second hydraulic continuously variable transmission. According to claim 2,
The plurality of straight-forward power transmission shafts are at least a straight-forward input shaft through which power is transmitted from the straight-forward motor, and a straight-forward output shaft that can be freely connected via a plurality of sub-transmission gear trains that are parallel to the straight-forward input shaft and have different reduction ratios,
The plurality of power transmission shafts for turning are at least a turning input shaft through which power is transmitted from the turning motor, and a turning output shaft parallel to the turning input shaft and transmitted through an electric gear train,
The turning output shaft and the straight input shaft are disposed on the same axis and overlap in the axis length direction,
A transmission for a driving vehicle, wherein the turning input shaft and the straight output shaft are disposed on the same axis and overlap in the axis length direction. A straight-line electric motor that supplies power for straight-line movement,
A turning electric motor that supplies turning power,
A planetary gear mechanism that distributes and outputs power to the left and right driving wheels,
a straight-line gear mechanism that transmits the power of the straight-line electric motor to a straight-line input unit of the planetary gear mechanism;
A transmission for a traveling vehicle in which a swing gear mechanism that transmits the power of the swing electric motor to a swing input portion of the planetary gear mechanism is installed in a transmission case,
The straight forward gear mechanism includes a plurality of power transmission shafts for straight forward movement,
The turning gear mechanism includes a plurality of turning power transmission shafts,
At least one of the power transmission shafts for moving forward and at least one of the power transmission shafts for turning are on the same axis,
In addition, a transmission for a driving vehicle characterized in that it is juxtaposed in the axis length direction. According to claim 4,
A planetary gear mechanism for straight forward movement is interposed between the straight forward electric motor and the straight forward gear mechanism,
A transmission for a traveling vehicle, characterized in that a turning planetary gear mechanism is interposed between the turning electric motor and the turning gear mechanism.

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