JP7349962B2 - Composite planetary gear system - Google Patents

Description

The present invention relates to a composite planetary gear device.

The composite planetary gear device includes a first sun gear, a first planet gear that meshes with the first sun gear, and a first internal gear that meshes with the first planet gear.
a second sun gear whose axis is located on the axis of the first sun gear; a second planetary gear that meshes with the second sun gear; and a second planetary gear that has a second internal gear that meshes with the second planetary gear. Some are equipped with a device section. An example of this type of composite planetary gear device is one shown in Patent Document 1.

Patent Document 1 discloses a composite planetary transmission section as a composite planetary gear device. The composite planetary transmission section is equipped with two rows of planetary gear mechanisms, and each of the two rows of planetary gear mechanisms is equipped with a sun gear, a planetary gear, and an internal gear.

JP2019-95058 Publication

Some of the above-described composite planetary gear devices are configured such that the second planet gear revolves around the second sun gear in conjunction with the first planet gear revolves around the first sun gear. In this way, even in a composite planetary gear device in which the first planetary gear and the second planetary gear revolve in conjunction with each other, the first planetary gear and the second planetary gear are firmly supported by the carrier so that they do not shake, and A composite planetary gear device is desired in which the first planetary gear and the second planetary gear can be easily assembled into a carrier.

The present invention provides that although the first planetary gear and the second planetary gear revolve in conjunction with each other, the first planetary gear and the second planetary gear are firmly supported by the carrier, and the first planetary gear and the second planetary gear are firmly supported by the carrier. To provide a composite planetary gear device in which gears can be easily assembled into a carrier.

The composite planetary gear device according to the present invention includes:
a first planetary gear device section having a first sun gear, a first planetary gear that meshes with the first sun gear, and a first internal gear that meshes with the first planetary gear; a second planetary gear device having a second sun gear having an axis located at the second sun gear, a second planetary gear that meshes with the second sun gear, a second internal gear that meshes with the second planetary gear, and the first planetary gear. and the second planetary gear rotatably supports the second planetary gear, and together with the first planetary gear that revolves around the first sun gear and the second planetary gear that revolves around the second sun gear. a carrier that rotates around the axis of a first sun gear; the carrier includes a first planetary support shaft that supports the first planetary gear; and a second planetary shaft that supports the second planetary gear. a support shaft, and a first end of the first planetary support shaft that is closer to one end of the first planetary support shaft than the first planetary gear, and the second planetary support shaft of the second planetary support shaft; a first carrier part that supports a first end of a second planetary support shaft that is closer to one end of the second planetary support shaft than the planetary gear; and a first planetary support shaft that is closer to the first planetary gear of the first planetary support shaft; supports a second end on the other end side, and supports a second end of the second planetary support shaft on the other end side of the second planetary support shaft than the second planetary gear; a second carrier part, the second carrier part is configured to be separable from the first carrier part, and the first carrier part is separated from the first carrier part and the second carrier part. and integrally molded with one of the first carrier part and the second carrier part in a state of protruding toward the other of the second carrier part, and with respect to the other of the first carrier part and the second carrier part. and a reinforcing part that connects the first carrier part and the second carrier part, and the reinforcing part is located adjacent to the first planetary gear in the circumferential direction of the carrier. a wall surface of the reinforcing portion facing the first planetary gear when viewed in a direction along the axis of the first sun gear is an arcuate surface along an outer peripheral portion of the first planetary gear; The first carrier part is rotatably supported by a boss part formed in the second internal gear with the same axis as the second sun gear, and the second carrier part is rotatably supported by the boss part formed in the second internal gear. The first internal gear is rotatably supported by a boss portion formed on the first internal gear with the same axis as that of the first sun gear.

According to this configuration, both the first planetary gear and the second planetary gear are supported by the carrier, and the carrier revolves together with the first planetary gear that revolves around the first sun gear and around the second sun gear. Since the first planetary gear rotates with the second planetary gear around the axis of the first sun gear, the first planetary gear and the second planetary gear revolve in conjunction with each other.

The first planetary support shaft is supported by the carrier at a first end portion and a second end portion located separately on both sides of a portion that supports the first planetary gear, and the second planetary support shaft The second support shaft is supported by the carrier by a first end portion and a second end portion of the second support shaft, which are located separately on both sides of a portion that supports the gear.
In addition, a first carrier part that supports a first end of the first planetary support shaft and a first end of the second planetary support shaft of the second planetary support shaft; A second carrier part that supports the second end of the second planetary support shaft and supports the second end of the second support shaft of the second planetary support shaft is integrally molded with one of the first carrier part and the second carrier part. Since the first carrier part and the second carrier part are connected by a reinforcing part that is firmly supported by one of the carrier part and the second carrier part, and the position of the first carrier part and the second carrier part does not shift in the carrier circumferential direction, the space between the first planetary support shaft and the carrier is Moreover, no twisting occurs between the second planetary support shaft and the carrier, and the first planetary gear and the second planetary gear are firmly supported by the carrier so as not to rattle.

The first planetary gear and the second planetary gear can be assembled into the carrier with the carrier disassembled into the first carrier part and the second carrier part, so it is easy to assemble the first planetary gear and the second planetary gear into the carrier. .

In the present invention,
A transmission gear is provided which is meshed with the first planetary gear and transmits the rotation of the first planetary gear to the second planetary gear, the transmission gear is supported by the second planetary support shaft and is connected to the second planetary gear. The second support shaft first end of the support shaft is located closer to one end of the second planet support shaft than the transmission gear of the second planet support shaft, and Preferably, the second end of the shaft is located closer to the other end of the second planetary support shaft than the transmission gear.

According to this configuration, the second planetary support shaft has a first end of the second support shaft and a second end of the second support shaft, which are located separately on both sides of a portion that supports the second planetary gear and the transmission gear. Since the transmission gear is supported on the carrier by the second planetary support shaft, the transmission gear and the second planetary gear are firmly supported by the carrier so as not to rattle, and the transmission gear and the second planetary gear are supported by the carrier. 2.Easy to incorporate the planetary gear into the carrier.

In the present invention, it is preferable that the reinforcing part is integrally formed with the first carrier part and configured to be detachable from the second carrier part.

According to this configuration, since the shape of the second carrier part can be simplified, it is easy to manufacture the second carrier part.

In the present invention, the shaft center has an axis in a direction along the direction of the shaft center of the first sun gear, and the second carrier section is attached to the first carrier section by being tightened by the second carrier section and the reinforcing section. Preferably, a connecting screw member is provided.

According to this configuration, since the reinforcing portion is utilized as a mounting member for the screw member, the second carrier portion can be firmly tightened and connected to the first carrier portion using the short screw member.

In the present invention,
The first planetary gears are provided at multiple locations around the first sun gear, the number of second planetary gears is the same as the number of first planetary gears, and the first carrier portion is provided at a plurality of locations around the first sun gear. It is preferable that the first carrier part is made by casting, and that the outer peripheral part of the first carrier part is turned.

According to this configuration, the mass of the first carrier part around the sun gear axis can be made uniform by turning the outer peripheral part of the first carrier part, so that the first carrier part can be made rigid by casting the first carrier part. This allows the first carrier portion to firmly support the plurality of planetary gears and the plurality of second planetary gears, while allowing the carrier to rotate smoothly without rotational vibration.

FIG. 2 is a left side view showing the entire tractor. FIG. 2 is a diagram showing a traveling transmission device. It is a sectional view showing a planetary gear device. It is a front view showing a first sun gear, a first planetary gear, a first internal gear, and a transmission gear. It is a rear view showing a 2nd sun gear, a 2nd planetary gear, and a 2nd internal gear. FIG. 3 is a perspective view showing the first planetary gear, second planetary gear, transmission gear, and carrier in an exploded state. FIG. 3 is a perspective view showing the carrier in a completed state. It is a front view which shows the 1st carrier part of the state in which the 1st planetary gear, the transmission gear, and the 2nd planetary gear are attached. It is a sectional view showing an oil supply structure. FIG. 3 is a longitudinal cross-sectional view of the second carrier part. It is a perspective view showing a part of a 2nd carrier part. FIG. 3 is an explanatory diagram showing the relationship between the speed change state of the continuously variable transmission, the speed range, and the rotational speed of the output shaft of the stepped transmission section.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment which is an example of this invention is described based on drawing.
In the following explanation, regarding the running vehicle body of the tractor, the direction of arrow F shown in FIG. The direction of ``vehicle body downward'', the direction of the front side of the page as ``vehicle body left'', and the direction of the back side of the page as ``vehicle body right''.

[Whole tractor]
The running body of the tractor includes an engine 1, a clutch housing 2 provided at the rear of the engine 1, a transmission case 3 connected to the clutch housing 2, and a body frame 5, which is composed of a front frame 4 and the like. It has a pair of left and right front wheels 6 that are steerably and drivably provided at the front, and a pair of left and right rear wheels 7 that are drivably provided at the rear of the vehicle body frame 5. A driving unit 8 having an engine 1 is formed at the front of the traveling vehicle body. A driving section 9 is formed at the rear of the traveling vehicle body. The driving section 9 is equipped with a driver's seat 10, a steering wheel 11 for steering the front wheels 6, and a cabin 12 that covers a passenger space. At the rear of the vehicle body frame 5, there is a link mechanism 13 that connects various working devices such as a rotary tiller (not shown) so that they can be raised and lowered. A power output shaft 14 for transmitting power is provided.

[Traveling transmission device]
It is configured such that power from the engine 1 is transmitted to the front wheels 6 and the rear wheels 7 by a traveling transmission device 15 shown in FIG.

As shown in FIG. 2, in the traveling transmission 15, power from the output shaft 1a of the engine 1 is transmitted to the input shaft 17 of the transmission case 3 via the main clutch 16. The power of the input shaft 17 is input to the main transmission section 18 that includes a planetary gear device 18A, etc., the output of the main transmission section 18 is input to the grading transmission section 19, and the output of the grading transmission section 19 is input to the forward/reverse switching device 20. is input. The output of the forward/reverse switching device 20 is transmitted to the input shaft 22a of the rear wheel differential mechanism 22 via the rear wheel gear interlocking mechanism 21. A steering brake 23 and a deceleration mechanism 24 are provided in a power transmission system that transmits the output of the rear wheel differential mechanism 22 to the rear wheels 7. The speed reduction mechanism 24 is constituted by a planetary gear mechanism. The power of the input shaft 22a of the rear wheel differential mechanism 22 is input to the front wheel transmission 26 via the front wheel gear interlocking mechanism 25, and is transmitted from the front wheel transmission 26 to the front wheel differential mechanism 28 via the rotating shaft 27. A parking brake 29 is provided in the front wheel gear interlocking mechanism 25.

30 shown in FIG. 2 is a working transmission. In the working transmission 30, the power of the input shaft 17 is input through the rotary shaft 31 and the rear rotary shaft 32, and the input power is changed in speed and transmitted to the power extraction shaft 14.

[Main transmission section]
As shown in FIG. 2, the main transmission section 18 includes a planetary gear device 18A and a continuously variable transmission 18B. The planetary gear device 18A includes two planetary gear device sections 50 and 60 arranged in the front-rear direction of the mission case 3. The previous planetary gear unit 50 of the two planetary gear units 50 and 60 and the input shaft 17 are connected via the first gear interlocking mechanism 34 . The continuously variable transmission 18B is constituted by a hydrostatic continuously variable transmission, and includes a variable displacement hydraulic pump P and a hydraulic motor M. The pump shaft of the continuously variable transmission 18B and the input shaft 17 are interlocked and connected via the second gear interlocking mechanism 35 and the rotating shaft 31. The motor shaft of the continuously variable transmission 18B and the previous planetary gear unit 50 of the two planetary gear units 50, 60 are connected via the third gear interlocking mechanism 36.

In the main transmission section 18, the power from the engine 1 is shifted by the continuously variable transmission 18B, and the shifted power and the power transmitted from the engine 1 via the third gear interlocking mechanism 36 are transferred to the planetary gear device 18A. The combined power is input to the two planetary gear units 50 and 60, and the combined power is output from the first output shaft 37a, the second output shaft 37b, and the third output shaft 37c, which are configured as a triple shaft.

[Graduation transmission part]
As shown in FIG. 2, the grading transmission section 19 has four grading clutches CL1 to CL4 into which the output of the planetary gear device 18A is input, and an output shaft 38 provided with the four grading clutches CL1 to CL4. We are prepared.

In the staged transmission section 19, as shown in FIG. 3, by appropriately operating the continuously variable transmission 18B and the four staged clutches CL1 to CL4, the combined power from the planetary gear device 18A is divided into four stages. The speed is divided into stages and output from the output shaft 38.

FIG. 12 is an explanatory diagram showing the relationship between the speed change state of the continuously variable transmission 18B, the speed range, and the rotational speed V of the output shaft 38 of the stepped transmission section 19. The vertical axis in FIG. 12 indicates the rotational speed V of the output shaft 38. The horizontal axis in FIG. 12 indicates the shift state of the continuously variable transmission 18B, where "N" indicates a neutral state, and "-MAX" indicates the highest speed shift state in the reverse rotation direction. "+MAX" indicates the highest speed shift state in the forward rotation direction.

When the first clutch CL1 of the four staged clutches CL1 to CL4 is engaged and the continuously variable transmission 18B is operated to change the speed, the power of the first output shaft 37a is transferred to the first gear interlocking mechanism 39a and the first gear linkage mechanism 39a. The speed is changed by clutch CL1 and output from output shaft 38. As shown in FIG. 12, as the rotational speed of the output shaft 38 reaches the rotational speed of the 1st speed range and the continuously variable transmission 18B is shifted from "-MAX" to "+MAX", the output shaft 38 The rotational speed V increases steplessly from zero speed [0] to the highest speed [V1] in the first speed range.

When the second clutch CL2 of the four staged clutches CL1 to CL4 is engaged and the continuously variable transmission 18B is operated to change the speed, the power of the third output shaft 37c is transferred to the second gear interlocking mechanism 39b and the second gear interlocking mechanism 39b. The speed is changed by clutch CL2 and output from output shaft 38. As shown in FIG. 12, the rotational speed of the output shaft 38 becomes the rotational speed of the 2nd speed range, which is higher than the 1st speed range, and the continuously variable transmission 18B is shifted from "+MAX" to "-MAX". Accordingly, the rotational speed V of the output shaft 38 increases steplessly from the lowest speed [V1] of the second speed range to the highest speed [V2] of the second speed range.

When the third clutch CL3 among the four staged clutches CL1 to CL4 is put into the engaged state and the continuously variable transmission 18B is operated to change the speed, the power of the second output shaft 37b is transferred to the third gear interlocking mechanism 39c and the third gear linkage mechanism 39c. The speed is changed by clutch CL3 and output from output shaft 38. As shown in FIG. 12, the rotational speed of the output shaft 38 becomes the rotational speed of the 3rd speed range, which is higher than the 2nd speed range, and the continuously variable transmission 18B is shifted from [-MAX] to "+MAX". Accordingly, the rotational speed V of the output shaft 38 increases steplessly from the lowest speed [V2] of the third speed range to the highest speed [V3] of the third speed range.

When the fourth clutch CL4 among the four staged clutches CL1 to CL4 is put into the engaged state and the continuously variable transmission 18B is operated to change the speed, the power of the third output shaft 37c is transferred to the fourth gear interlocking mechanism 39d and the fourth clutch. The speed is changed by clutch CL4 and output from output shaft 38. As shown in FIG. 12, the rotational speed of the output shaft 38 becomes the rotational speed of the 4th speed range, which is higher than the 3rd speed range, and the continuously variable transmission 18B is shifted from "+MAX" to "-MAX". Accordingly, the rotational speed V of the output shaft 38 increases steplessly from the lowest speed [V3] of the 4th speed range to the highest speed [V4] of the 4th speed range.

[Forward/forward switching device]
As shown in FIG. 2, the forward/reverse switching device 20 includes an input shaft 40 interlockingly connected to the output shaft 38 of the stepped transmission section 19, a forward clutch CLF and a reverse clutch CLR provided on the input shaft 40, and a forward clutch. The output shaft 42 is connected to the CLF via a forward gear mechanism 41f and to the reverse clutch CLR via a reverse gear mechanism 41r.

In the forward/reverse switching device 20, when the forward clutch CLF is turned on, the power transmitted from the grading transmission section 19 to the input shaft 40 is converted into forward power by the forward clutch CLF and the forward gear mechanism 41f, and is output. It is output from the shaft 42. When the reverse clutch CLR is turned on, the power transmitted from the grading transmission section 19 to the input shaft 40 is converted into reverse power by the reverse clutch CLR and the reverse gear mechanism 41r, and is output from the output shaft 42.
Forward power and reverse power outputted from the output shaft 42 are transmitted to the rear gear interlocking mechanism 21, and by the rear gear interlocking mechanism 21 to the input shaft 22a of the rear wheel differential mechanism 22.

[Front wheel transmission]
As shown in FIG. 2, the front wheel transmission device 26 includes an input shaft 43 connected to the input shaft 22a of the rear wheel differential mechanism 22 via the front wheel gear interlocking mechanism 25, and a constant velocity clutch provided on the input shaft 43. The output shaft 45 is connected to the CLT, the speed increasing clutch CLH, and the constant velocity clutch CLT via a constant speed gear mechanism 44a, and the speed increasing clutch CLH via a speed increasing gear mechanism 44b.

In the front wheel transmission device 26, when the constant velocity clutch CLT is engaged, the power transmitted from the input shaft 22a of the rear wheel differential mechanism 22 to the input shaft 43 is transmitted to the constant velocity clutch CLT and the constant velocity gear mechanism 44a. The signal is transmitted to the output shaft 45 via the output shaft 45, and is transmitted from the output shaft 45 to the front wheel differential mechanism 28. In this case, the pair of left and right front wheels 6 and the pair of left and right rear wheels 7 are driven in a state where the average circumferential speed of the pair of left and right front wheels 6 and the average circumferential speed of the pair of left and right rear wheels 7 are approximately equal, so-called front and rear wheels. A four-wheel drive state with constant wheel speed is created. When the speed increasing clutch CLH is turned on, the power transmitted from the input shaft 22a of the rear wheel differential mechanism 22 to the input shaft 43 is transmitted to the output shaft 45 via the speed increasing clutch CLH and the speed increasing gear mechanism 44b. and is transmitted from the output shaft 45 to the front wheel differential mechanism 28. In this case, the pair of left and right front wheels 6 and the pair of left and right rear wheels 7 are driven in a state where the average circumferential speed of the pair of left and right front wheels 6 is higher than the average circumferential speed of the pair of left and right rear wheels 7, so-called. A four-wheel drive state with increased speed of the front wheels appears.

[Planetary gear device]
As shown in FIGS. 2 and 3, the planetary gear device 18A includes two planetary gear device sections 50 and 60 arranged in the front-rear direction of the mission case 3. The planetary gear device 18A is configured as a composite planetary gear device. In the following, the previous planetary gear unit 50 of the two planetary gear units 50, 60 will be referred to as a first planetary gear unit 50, and the latter planetary gear unit 50 of the two planetary gear units 50, 60 will be referred to as a first planetary gear unit 50. The section 60 will be described as a second planetary gear device section 60.

[First planetary gear unit]
As shown in FIGS. 2 and 3, the first planetary gear unit 50 includes a first sun gear 51, a first planet gear 52 that meshes with the first sun gear 51, and a first planet gear 52 that meshes with the first planet gear 52. The first internal gear 53 and the first planetary gear 52 rotatably support the first planetary gear 52 and revolve around the first sun gear 51 together with the axis X of the first sun gear 51 (see FIG. 4). ), and a carrier 70 that rotates around the center of rotation.

As shown in FIG. 3, the first sun gear 51 is rotatably supported by a sun support shaft constituted by the rotating shaft 31. Hereinafter, the rotation shaft 31 will be referred to as the sun support shaft 31. The first sun gear 51 is operatively connected to the third gear interlocking mechanism 36, as shown in FIG. Specifically, as shown in FIG. 3, the boss portion 51a provided on the first sun gear 51 is extended to the front side of the carrier 70, and the third gear interlocking mechanism 36 is attached to the extending portion of the boss portion 51a. The transmission gears 36a are interlocked and connected. The interlocking connection between the boss portion 51a and the transmission gear 36a is achieved by spline engagement.

The first planetary gears 52 are provided at three locations around the first sun gear 51, as shown in FIG. Each first planetary gear 52 is rotatably supported by a first planetary support shaft 54, as shown in FIG. A bush 55 is provided between the first planetary gear 52 and the first planetary support shaft 54.

The first internal gear 53 is rotatably supported by the boss portion 51a of the first sun gear 51, as shown in FIG. Specifically, the boss portion 53a provided on the first internal gear 53 is externally fitted onto the boss portion 51a via the cylindrical member 56 located between the boss portion 53a and the boss portion 51a of the first sun gear 51. has been done. The first internal gear 53 is operatively connected to the first gear interlocking mechanism 34, as shown in FIG. Specifically, as shown in FIG. 3, the boss portion 53a of the first internal gear 53 and the cylindrical member 56 are interlocked and connected by spline engagement, and the transmission of the cylindrical member 56 and the first gear interlocking mechanism 34 is achieved. The gear 34a is interlocked and connected by spline engagement.

[Second planetary gear unit]
As shown in FIGS. 2 and 5, the second planetary gear unit 60 includes a second sun gear 61, a second planet gear 62 that meshes with the second sun gear 61, and a second planet gear 62 that meshes with the second planet gear 62. 2 internal gear 63, a transmission gear 64 (see FIG. 4) that meshes with the first planetary gear 52 and transmits the rotation of the first planetary gear 52 to the second planetary gear 62, and the second planetary gear 62 can be rotated. and a carrier 70 that rotates around the axis Z (see FIG. 5) of the second sun gear 61 together with the second sun gear 61 that revolves around the second sun gear 61. There is.

As shown in FIG. 3, the second sun gear 61 is supported by a portion of the third output shaft 37c that extends inside the carrier 70. The axis Z of the second sun gear 61 is located on the axis of the first sun gear 51. The axis Z of the second sun gear 61 and the axis X of the first sun gear 51 are the same axis. The second sun gear 61 is operatively connected to the third output shaft 37c, as shown in FIG. As shown in FIG. 3, the second sun gear 61 and the third output shaft 37c are interlocked and connected by spline engagement.

The second planetary gears 62 are provided at three locations around the second sun gear 61, as shown in FIG. The number of second planetary gears 62 is the same as the number of first planetary gears 52. Each second planetary gear 62 is rotatably supported by a second planetary support shaft 65, as shown in FIG.

As shown in FIG. 4, the transmission gears 64 are provided corresponding to the first planetary gears 52 at three locations and the second planetary gears 62 at three locations. The number of transmission gears 64 is the same as the number of first planetary gears 52 and the number of second planetary gears 62. As shown in FIG. 3, the transmission gear 64 is supported by a portion of the second planetary support shaft 65 that is located in front of the second planetary gear 62. The transmission gear 64 is operatively connected to the second planetary gear 62 and transmits input rotation of the first planetary gear 52 to the second planetary gear 62 by meshing with the first planetary gear 52 . Bushes 66 are provided between the second planetary gear 62 and the second planetary support shaft 65 and between the transmission gear 64 and the second planetary support shaft 65. In this embodiment, the transmission gear 64 and the second planetary gear 62 are interlocked and connected by integrally forming the transmission gear 64 and the second planetary gear 62. The transmission gear 64 and the second planetary gear 62 may be interlocked and connected by a second planetary support shaft 65.

As shown in FIGS. 2 and 3, the second internal gear 63 is supported by the front part of the first output shaft 37a, and is operatively connected to the first output shaft 37a. Specifically, the interlocking connection between the second internal gear 63 and the first output shaft 37a is achieved by spline engagement between the boss portion 63a provided in the second internal gear 63 and the first output shaft 37a. It is being said.

[Carrier composition]
The carrier 70 of the first planetary gear device section 50 and the carrier 70 of the second planetary gear device section 60 are constituted by the same carrier 70. The carrier 70 is constructed as follows.

The carrier 70 is supported by the boss portion 53a of the first internal gear 53 and the boss portion 63a of the second internal gear 63, as shown in FIG. A ball bearing 71 is provided between the carrier 70 and the boss portion 53a, and a ball bearing 72 is provided between the carrier 70 and the boss portion 63a. The carrier 70 is rotatably supported by the boss portion 53a and the boss portion 63a, and rotates about the axis X of the first sun gear 51 together with the first planetary gear 52 that revolves around the first sun gear 51. (See FIG. 4), and rotates about the axis Z of the second sun gear 61 together with the second planetary gear 62 that revolves around the second sun gear 61 (see FIG. 5).

As shown in FIG. 3, the carrier 70 includes a first planetary support shaft 54, a second planetary support shaft 65, a first sun gear 51, a second sun gear 61, a first planetary gear 52, and a second planetary gear. 62 and a transmission gear 64, and a second carrier part 70B that constitutes a lid for the first carrier part 70A.

The first carrier section 70A and the second carrier section 70B are configured to be separable in the axial direction of the first sun gear 51 and the axial direction of the second sun gear 61, as shown in FIG.

As shown in FIG. 6, the sun support shaft 31 is inserted into the center of the first carrier part 70A, and the front part of the second output shaft 37b is inserted, and further the front part of the third output shaft 37c is inserted. A first through hole 73 is provided. The first through hole 73 is configured as a spline hole that engages with the spline shaft portion 37s (see FIG. 3) of the second output shaft 37b. A sun gear accommodation space 74 for accommodating the first sun gear 51 and the second sun gear 61 is provided at a location closer to the second carrier section (front side) than the first through hole 73 so as to communicate with the first through hole 73. It is being The sun gear accommodating space 74 is open toward the second carrier section, and allows the first sun gear 51 and the second sun gear 61 to be incorporated into the sun gear accommodating space 74 from the second carrier section side (front side). configured to be possible.

Around the sun gear housing space 74, there are three first gear housing spaces 75 that individually house the three first planetary gears 52, and three second gear housing spaces 75 that house the three second planetary gears 62, respectively. A gear housing space 76 is provided. The three first gear accommodating spaces 75 and the three second gear accommodating spaces 76 are lined up in the carrier circumferential direction with one second gear accommodating space 76 located between the first gear accommodating spaces 75 .

The second gear accommodating space 76 is configured to be able to accommodate the transmission gear 64. The depth of the second gear accommodation space 76 in the direction along the axis of the first sun gear 51 is deeper than the depth of the first gear accommodation space 75 in the direction along the axis of the first sun gear 51. has been done. As shown in FIG. 8, the first gear housing space 75 and the second gear housing space 76 communicate in the carrier circumferential direction so that the first planetary gear 52 and the transmission gear 64 can mesh with each other. .

As shown in FIGS. 7 and 8, the first gear housing space 75 has a portion of the first planetary gear 52 that meshes with the first internal gear 53 that protrudes from the first gear housing space 75 toward the outer peripheral side of the carrier. It is configured as follows. The second gear accommodating space 76 is configured such that a portion of the second sun gear 61 that meshes with the second internal gear 63 protrudes from the second gear accommodating space 76 toward the outer peripheral side of the carrier.

As shown in FIG. 6, the first gear accommodating space 75 is opened toward the second carrier section 70B at the second carrier section side end (front end), and the first gear accommodating space 75 is opened toward the second carrier section 70B. A first opening 77 is provided that allows the first planetary gear 52 to be assembled into the gear housing space 75 .
A portion of the first carrier portion 70A that is opposite to the first opening 77 with respect to the first gear housing space 75 is provided with a portion of the first planetary support shaft 54 that is smaller than the first planetary gear 52. A first support hole 78 for supporting the first support shaft first end 54a (see FIGS. 3 and 6) located on one end side of the planetary support shaft is provided. The first support shaft first support hole 78 is provided so as to communicate with the first gear housing space 75 .

As shown in FIG. 6, the second gear housing space 76 is opened toward the second carrier part 70B at the second carrier part side end (front end) of the second gear housing space 76, and the second gear housing space 76 is opened toward the second carrier part 70B. A second opening 79 is provided that allows the second planetary gear 62 and transmission gear 64 to be assembled into the gear housing space 76 . Of the second planetary support shaft 65, a second planetary support shaft is provided in a portion of the first carrier portion 70A on the opposite side to the side where the second opening 79 is located with respect to the second gear housing space 76. A second support shaft first supporting a second support shaft first end 65a (see FIGS. 3 and 6) located on one end of the shaft and closer to one end of the second planetary support shaft than the second planetary gear 62; A support hole 80 is provided. The second support shaft first support hole 80 is provided so as to communicate with the second gear housing space 76 .

As shown in FIG. 6, reinforcement is provided between a portion of the first carrier portion 70A on the outside in the carrier radial direction in the first gear housing space 75 and a portion on the outside in the carrier diameter direction in the second gear housing space 76. A section 81 is provided. The reinforcing portions 81 are provided at six locations. Each reinforcing portion 81 is integrally molded with the first carrier portion 70A. The reinforcing portion 81 is located between the outer peripheral side of the first planetary gear 52 and the outer peripheral side of the transmission gear 64, as shown in FIG.

As shown in FIG. 3, in the rear part of the first carrier part 70A, the front part of the first output shaft 37a and the boss part of the second internal gear 63 are located at the rear side of the sun gear housing space 74. 63a, and a recessed portion 82 into which the ball bearing 72 is inserted.

The first carrier part 70A is manufactured by casting, and after casting, the outer peripheral part 84 (see FIG. 6) of the first carrier part 70A is turned. The mass of the first carrier portion 70A around the axis X of the first sun gear 51 and the axis Z of the second sun gear 61 becomes uniform, and rotational vibration of the carrier 70 can be prevented.

The second carrier portion 70B includes an outer wall portion 85 and an inner wall portion 86, as shown in FIGS. 6, 10, and 11. The outer wall portion 85 and the inner wall portion 86 are connected at the outer peripheral portion of the second carrier portion 70B. As shown in FIGS. 3, 6, and 10, a second through hole 87 is provided in the center of the inner wall portion 86, through which the boss portion 51a of the first sun gear 51 is inserted. A third through hole into which the boss portion 51a of the first sun gear 51 is inserted into the center of the outer wall portion 85, and into which the rear portion of the cylindrical member 56, the boss portion 53a of the first internal gear 53, and the ball bearing 71 are inserted. 88 are provided. Around the second through hole 87 in the second carrier part 70B, a first lid part 89 that closes the first opening 77 of the first gear accommodating space 75 and a second lid part 89 that closes the second opening 79 of the second gear accommodating space 76 are provided. Two lid portions 90 are provided.

As shown in FIGS. 10 and 11, a second support shaft of the first planet support shaft 54 located on the other end side of the first planet support shaft with respect to the first planet gear 52 is attached to the first lid portion 89. A first support shaft second support hole 91 is provided to support the end portion 54b (see FIGS. 3 and 6). The first support shaft second support hole 91 is open toward the first gear housing space 75, and communicates with the first gear housing space 75 by connecting the second carrier portion 70B to the first carrier portion 70A. do. The second lid part 90 is located on the other end side of the second planetary support shaft of the second planetary support shaft 65 than the second planetary gear 62, and is located on the other end side of the second planetary support shaft than the transmission gear 64. A second support hole 92 for supporting the second support shaft second end 65b (see FIGS. 3 and 6) located at is provided. The second support shaft second support hole 92 is open toward the second gear housing space 76, and communicates with the second gear housing space 76 by connecting the second carrier portion 70B to the first carrier portion 70A. do.

As shown in FIGS. 6 and 11, a connecting portion 93 connecting the second carrier portion 70B to the first carrier portion 70A is provided in a portion of the second carrier portion 70B around the third through hole 88. There is. The connecting portions 93 are provided corresponding to the six reinforcing portions 81 and are located at six locations. As shown in FIG. 7, each connecting portion 93 has a screw member inserted into a bolt hole 94 (see FIG. 6) provided in the connecting portion 93 and a screw hole 95 (see FIG. 6) provided in the reinforcing portion 81. A connecting bolt 96 (see FIG. 6) is attached and tightened to the reinforcing portion 81 by the connecting bolt 96. The connecting bolt 96 has an axis extending along the axial direction of the first sun gear 51 . The reinforcing portion 81 is tightly connected to the first carrier portion 70A in a direction along the axial direction of the first sun gear 51, thereby connecting the second carrier portion 70B to the first carrier portion 70A.

The carrier 70 can be obtained based on the following assembly method.
As shown in FIG. 6, the first planetary gear 52 attached to the first planetary support shaft 54 is inserted into the first gear housing space 75 through the first opening 77, and the first planetary gear 52 is inserted into the first support shaft of the first planetary support shaft 54. The end portion 54a is inserted into the first support hole 78 of the first support shaft. Then, the first support shaft first end 54a is supported in the first support hole 78 of the first support shaft. The first end portion 54a of the first support shaft is supported by the first carrier portion 70A.

As shown in FIG. 6, the second planetary gear 62 and the transmission gear 64 are inserted into the second gear housing space 76 through the second opening 79 with the second planetary gear 62 and the transmission gear 64 attached to the second planetary support shaft 65. The support shaft first end 65a is inserted into the second support shaft first support hole 80. Then, the second support shaft first end 65a is supported by the second support shaft first support hole 80. That is, the second support shaft first end portion 65a is supported by the first carrier portion 70A.

In this way, the three first planetary gears 52 are inserted into the first gear housing space 75, and the first support shaft first ends 54a of the three first planetary support shafts 54 are inserted into the first support shaft first support hole 78. The three second planetary gears 62 and the three transmission gears 64 are inserted into the second gear housing space 76, and the second support shaft first ends 65a of the three second planetary support shafts 65 are connected to the second support shafts. It is supported by the first support hole 80.

Next, the first support shaft second support hole 91 faces the first support shaft second end 54b of the first planet support shaft 54, and the second support shaft second support hole 92 faces the second planet support shaft The second carrier portion 70B is aligned with the first planetary support shaft 54 and the second planetary support shaft 65 so as to face the second end portion 65b of the second support shaft 65, and the bolt hole 94 is inserted into the connecting portion 93. and tighten the connecting bolt 96 installed in the screw hole 95. As the connecting portion 93 is tightened to the reinforcing portion 81 (first carrier portion 70A), the first support shaft second end portion 54b of each first planetary support shaft 54 is inserted into the first support shaft second support hole 91. The second end portion 65b of each second planetary support shaft 65 enters into the second support hole 92 of the second support shaft.

When the tightening of the connecting bolt 96 is completed, the connecting portion 93 is tightened and connected to the reinforcing portion 81, and the first planetary gear 52 is housed in the first gear housing space 75, and the second planetary gear 62 and the transmission gear 64 are housed in the first gear housing space 75. The first sun gear 51 is housed in the second gear housing space 76, and the first opening 77 and second opening 79 are closed by the second carrier part 70B, and the first carrier part 70A and the second carrier part 70B interlock with each other to close the first sun gear 51. The carrier 70 is in a state of rotating around the axis X of the second sun gear 61 and around the axis Z of the second sun gear 61. Moreover, the first carrier part 70A and the second carrier part 70B are connected by the reinforcing part 81, and the carrier 70 is in a state where it is reinforced by the reinforcing part 81.

[Lubricating oil supply configuration]
As shown in FIGS. 3 and 9, a solar oil supply path 100 supplies lubricating oil between the sun support shaft 31 and the first sun gear 51 to the outer circumference of the sun support shaft 31 that supports the first sun gear 51. is provided. The solar oil supply path 100 is provided at two locations in the circumferential direction of the solar support shaft 31. The solar oil supply path 100 is provided to extend linearly between the third output shaft 37c and the sun support shaft 31 along the axis of the sun support shaft 31, and is provided between the third output shaft 37c and the sun support shaft 31. The structure also allows for oil supply between the two. As shown in FIG. 3, the solar oil supply passage 100 is supplied with oil from an oil supply passage 101 that is bored in a cylindrical portion 17a that is fitted onto the front end of the sun support shaft 31. The cylindrical portion 17a is provided at the rear of the input shaft 17.

As shown in FIGS. 3 and 9, the first planetary support shaft 54 is provided with a first planetary oil supply path 102 that supplies lubricating oil between the first planetary support shaft 54 and the first planetary gear 52. . The first planetary oil supply path 102 is provided on the three first planetary support shafts 54 . Specifically, as shown in FIG. 9, the first planetary oil supply path 102 is an upstream oil path section 102a that is bored in the first planetary support shaft 54 along the axial direction of the first planetary support shaft 54. and is bored in the first planetary support shaft 54 in a state perpendicular to the axis of the first planetary support shaft 54, and connects the upstream oil passage portion 102a to two locations around the outer circumference of the first planetary support shaft 54. A downstream oil passage section 102b is provided.

In the first planetary oil supply path 102, lubricating oil is supplied to the upstream oil path section 102a, flows from the upstream oil path section 102a to the downstream oil path section 102b, and from the downstream oil path section 102b, the lubricating oil is supplied to the first planetary support shaft 54 and the first planetary support shaft 54. It is supplied between the first planetary support shaft 54 and the first planetary gear 52 by being supplied to the bush 55 located between the first planetary gears 52 .

As shown in FIGS. 3 and 9, the first planetary oil supply passage 102 is connected to the solar oil supply passage 100 by a first supply oil passage 103 provided inside the carrier 70. As shown in FIGS. The first supply oil passage 103 extends along the radial direction of the carrier 70 and is provided along the carrier 70 (second carrier part 70B), and takes in lubricating oil from the solar oil supply passage 100 as the carrier 70 rotates. The lubricating oil is supplied to the first planetary oil supply path 102. That is, the lubricating oil located in the first oil supply path 103 is applied with centrifugal force by the rotation of the carrier 70 and flows toward the first planetary oil supply path 102, and this flow causes the lubricating oil in the solar oil path 100 to flow toward the first planetary oil supply path 102. The oil is taken into the first supply oil passage 103 and is supplied from the first supply oil passage 103 to the first planetary oil supply passage 102 .

The first supply oil passage 103 includes a first upstream oil passage part 103a that opens to the solar oil supply passage 100, a first downstream oil passage part 103b that opens to the first planetary oil supply passage 102, and a first upstream oil passage part 103b that opens to the first planetary oil supply passage 102. A first connecting oil passage portion 103c is provided that connects the oil passage portion 103a and the first downstream oil passage portion 103b. The first upstream oil passage portion 103a is formed by the front end portion of the first sun gear 51 and the rear end portion of the cylindrical member 56, and is formed through a through hole 51b provided in the boss portion 51a of the first sun gear 51. It opens to the solar oil supply path 100. The first downstream oil passage section 103b is formed by the first support shaft second support hole 91, the inner wall section 86, and the ball bearing 71 of the second carrier section 70B. The width of the first downstream oil passage section 103b in the axial direction of the first sun gear 51 is narrower than the width of the first upstream oil passage section 103a in the axial direction of the first sun gear 51. has been done. The first connection oil passage portion 103c is formed by an inclined portion 104 provided in a portion of the inner wall portion 86 near the second through hole 87, and a boss portion 53a of the first internal gear 53. The width of the first connection oil passage portion 103c in the direction along the axial direction of the first sun gear 51 becomes narrower toward the first downstream oil passage portion due to the action of the inclined portion 104. The first connecting oil passage part 103c acts to throttle the lubricating oil flowing from the first upstream oil passage part 103a toward the first downstream oil passage part 103b, and the first downstream oil passage part 103b It is narrower than the side oil passage section 103a, and even if the oil amount in the first upstream oil passage section 103a changes, the oil amount in the first downstream oil passage section 103b is stabilized.

As shown in FIGS. 3 and 9, the second planetary support shaft 65 is lubricated between the second planetary support shaft 65 and the transmission gear 64, and between the second planetary support shaft 65 and the second planetary gear 62. A second planetary oil supply path 105 for supplying oil is provided. The second planetary oil supply path 105 is provided on the three second planetary support shafts 65. Specifically, as shown in FIG. 9, the second planetary oil supply path 105 is an upstream oil path section 105a that is bored in the second planetary support shaft 65 along the axial direction of the second planetary support shaft 65. , is bored in the second planetary support shaft 65 in a state perpendicular to the axis of the second planetary support shaft 65, and connects the upstream oil passage portion 105a to the transmission gear 64 on the outer periphery of the second planetary support shaft 65. Two downstream oil passage portions 105b are provided which are respectively connected to corresponding portions and portions of the outer periphery of the second planetary support shaft 65 that correspond to the second planetary gears 62. The downstream oil passage portion 105b opens at two locations around the outer circumference of the second planetary support shaft 65.

In the second planetary oil supply path 105, lubricating oil is supplied to the upstream oil path section 105a, flows from the upstream oil path section 105a into two downstream oil path sections 105b, and from one downstream oil path section 105b to the second planetary oil path section 105b. It is supplied between the second planetary support shaft 65 and the transmission gear 64 by being supplied to the bush 66 located between the shaft 65 and the transmission gear 64, and the second planetary support shaft 65 and the second planetary support shaft 65 are supplied from the other downstream oil passage section 105b. It is supplied between the second planetary support shaft 65 and the second planetary gear 62 by being supplied to the bush 55 located between the second planetary gears 62 .

As shown in FIGS. 3 and 9, the second planetary oil supply passage 105 is connected to the solar oil supply passage 100 by a second supply oil passage 106 provided inside the carrier 70. The second supply oil passage 106 extends along the radial direction of the carrier 70 and is provided along the carrier 70 (second carrier portion 70B), and takes in lubricating oil from the solar oil supply passage 100 as the carrier 70 rotates. The lubricating oil is supplied to the second planetary oil supply path 105. That is, the lubricating oil located in the second oil supply path 106 is applied centrifugal force by the rotation of the carrier 70 and flows toward the second planetary oil supply path 105, and this flow causes the lubricating oil in the solar oil path 100 to flow toward the second planetary oil supply path 105. The oil is taken into the second supply oil passage 106 and is supplied from the second supply oil passage 106 to the second planetary oil supply passage 105.

The second supply oil passage 106 includes a second upstream oil passage part 106a that opens to the solar oil supply passage 100, a second downstream oil passage part 106b that opens to the second planetary oil supply passage 105, and a second upstream oil passage part 106b that opens to the second planetary oil supply passage 105. A second connecting oil passage portion 106c is provided that connects the oil passage portion 106a and the second downstream oil passage portion 106b. The second upstream oil passage portion 106a is formed by the front end portion of the first sun gear 51 and the rear end portion of the cylindrical member 56, and is formed through a through hole 51b provided in the boss portion 51a of the first sun gear 51. It opens to the solar oil supply path 100. The second downstream oil passage section 106b is formed by the second support shaft second support hole 92 of the second carrier section 70B, the inner wall section 86, and the ball bearing 71. The width of the second downstream oil passage section 106b in the axial direction of the first sun gear 51 is narrower than the width of the second upstream oil passage section 106a in the axial direction of the first sun gear 51. has been done. The second connection oil passage portion 106c is formed by an inclined portion 104 provided in a portion of the inner wall portion 86 near the second through hole 87, and a boss portion 53a of the first internal gear 53. The width of the second connection oil passage portion 106c in the direction along the axis of the first sun gear 51 becomes narrower toward the second downstream oil passage portion due to the action of the inclined portion 104. The second connecting oil passage part 106c acts to throttle the lubricating oil flowing from the second upstream oil passage part 106a toward the second downstream oil passage part 106b, and the second downstream oil passage part 106b The width is narrower than that of the side oil passage portion 106a, and even if the oil amount in the second upstream oil passage portion 106a changes, the oil amount in the second downstream oil passage portion 106b is stabilized.

In this embodiment, the first oil supply passage 103 that supplies oil to the three first planetary oil supply passages 102 and the second oil supply passage 106 that supplies oil to the three second planetary oil supply passages 105 are arranged in the circumferential direction of the carrier 70. They are placed in communication with each other.

The lubricating oil supplied from the oil supply path 101 to the solar oil supply path 100 is supplied between the sun support shaft 31 and the first sun gear 51 from the solar oil supply path 100 . Further, oil is supplied from the solar oil supply path 100 between the solar support shaft 31 and the third output shaft 37c. As the carrier 70 rotates, the lubricating oil located in the solar oil supply passage 100 is taken into the first oil supply passage 103 and is supplied from the first oil supply passage 103 to the first planetary oil supply passage 102. 102 and is supplied between the first planetary support shaft 54 and the first planetary gear 52 . Further, as the carrier 70 rotates, the lubricating oil located in the solar oil supply path 100 is taken into the second oil supply path 106 and is supplied from the second oil supply path 106 to the second planetary oil path 105, and The oil is supplied from the oil supply path 105 between the second planetary support shaft 65 and the transmission gear 64 and between the second planetary support shaft 65 and the second planetary gear 62 .

[Another embodiment]
(1) In the embodiment described above, three first planetary gears 52 and three second planetary gears 62 are provided, but two or four or more first planetary gears and second planetary gears may be provided. There may be.

(2) In the embodiment described above, the first carrier part 70A is made of cast material, and the outer peripheral part of the first carrier part 70A is turned. However, the present invention is not limited to this. For example, it may be made by casting without turning, or it may be made by a manufacturing method other than casting.

INDUSTRIAL APPLICATION This invention is applicable to the compound planetary gear apparatus equipped with various vehicles, such as a combine harvester and a multi-purpose vehicle, in addition to a tractor.

50 First planetary gear unit 51 First sun gear 52 First planetary gear 53 First internal gear
53a boss part
54 First planetary support shaft 54a First end 54b Second end 60 Second planetary gear unit 61 Second sun gear 62 Second planetary gear 63 Second internal gear
63a boss part
64 Transmission gear 65 Second planetary support shaft 65a Second support shaft first end 65b Second support shaft second end 81 Reinforcement portion 96 Screw member (connection bolt)
X axis (axis of 1st sun gear)
Z axis (axis of second sun gear)

Claims (5)

a first planetary gear device having a first sun gear, a first planetary gear that meshes with the first sun gear, and a first internal gear that meshes with the first planetary gear;
a second sun gear whose axis is located on the axis of the first sun gear; a second planetary gear that meshes with the second sun gear; and a second planetary gear that has a second internal gear that meshes with the second planetary gear. equipment section;
The second planet gear rotatably supports the first planet gear and the second planet gear, and revolves around the second sun gear together with the first planet gear that revolves around the first sun gear. a carrier that rotates around the axis of the first sun gear together with the planet gear;
The carrier includes a first planetary support shaft that supports the first planetary gear, a second planetary support shaft that supports the second planetary gear, and a second planetary support shaft that supports the first planetary gear. A first end portion of a second planetary support shaft that supports a first end portion on one end side of the first planetary support shaft, and that is closer to one end side of the second planetary support shaft than the second planetary gear of the second planetary support shaft. a first carrier portion that supports a second planetary support shaft, and a second end portion of the first planetary support shaft that is closer to the other end of the first planetary support shaft than the first planetary gear; a second carrier part that supports a second end of the second planetary support shaft on the other end side of the second planetary support shaft than the second planetary gear;
The second carrier part is configured to be separable from the first carrier part,
integrally formed on one of the first carrier part and the second carrier part in a state of protruding from one of the first carrier part and the second carrier part toward the other of the first carrier part and the second carrier part; and a reinforcing part that is configured to be detachable from the other of the first carrier part and the second carrier part, and connects the first carrier part and the second carrier part,
The reinforcing portion is provided adjacent to the first planetary gear in the circumferential direction of the carrier,
A wall surface of the reinforcing portion facing the first planetary gear when viewed in a direction along the axis of the first sun gear is an arcuate surface along an outer peripheral portion of the first planetary gear,
The first carrier portion is rotatably supported by a boss portion formed on the second internal gear with the same axis as the second sun gear,
The second carrier portion is rotatably supported by a boss portion formed on the first internal gear, with the second carrier portion having the same axis as the first sun gear. a transmission gear that meshes with the first planetary gear and transmits rotation of the first planetary gear to the second planetary gear;
The transmission gear is supported by the second planetary support shaft,
The second planetary support shaft first end portion of the second planetary support shaft is located closer to one end of the second planetary support shaft than the transmission gear of the second planetary support shaft,
The compound according to claim 1, wherein the second end of the second planetary support shaft is located closer to the other end of the second planetary support shaft than the transmission gear of the second planetary support shaft. Planetary gear system. The composite planetary gear device according to claim 1 or 2, wherein the reinforcing portion is integrally molded with the first carrier portion and is configured to be detachable from the second carrier portion. a screw member having an axial center in a direction along the axial direction of the first sun gear and connecting the second carrier part to the first carrier part by being tightened by the second carrier part and the reinforcing part; A compound planetary gear device according to any one of claims 1 to 3, further comprising: The first planetary gear is provided at multiple locations around the first sun gear,
The second planetary gears are provided in the same number as the first planetary gears,
The first carrier part is made of casting,
The composite planetary gear device according to any one of claims 1 to 4, wherein an outer peripheral portion of the first carrier portion is machined by turning.

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