JPS605817B2 - transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a traveling system transmission device for traveling work vehicles such as agricultural, civil engineering, and construction tractors.

The present invention provides a planetary transmission between an input shaft receiving rotational power of an engine and an output shaft of a coaxial core, in which an inner ring transmission body on the input shaft side and a solar transmission body on the output shaft side are connected. For example, by providing a hydraulic clutch that can be disengaged, the solar power transmission body is provided with a one-way clutch that can be freely engaged and disengaged from a fixed member, so that the vehicle speed can be increased or decreased by disengaging the hydraulic clutch under any conditions. It is possible to change the speed to
The aim is to speed up work and improve safety.

In addition, in the present invention, when the above-mentioned object is achieved, it is possible to prevent the inevitable loss of the engine braking action when driving downhill, and the loss of the push-pull starting operation of the vehicle steel in the event of engine failure. The purpose is to provide equipment.

In order to achieve the above object, the present invention provides an inner ring transmission body on an input shaft that receives rotational power of an engine, a planetary carrier and a solar transmission body on an output shaft coaxial with the input shaft, and an inner ring transmission body on the planetary carrier. In a planetary transmission device comprising a planetary transmission body interlocked with a ring transmission body and a sun transmission body,
A clutch is provided that engages and disengages the sun transmission body and the inner ring transmission body, and a clutch that engages only in the reverse rotation direction of the output shaft is provided between the sun transmission body and the fixed member, and the planetary carrier is connected to the input shaft. It is characterized by being equipped with a clutch that engages the shaft only in the normal rotation direction. Hereinafter, a preferred embodiment of the present invention will be described in detail in the case where it is adopted as a transmission for a tractor, but the present invention can be used as a transmission device in various industrial fields including those for agricultural work such as tillers and the like.

In the drawings, especially in FIG. 1, 1 is the engine crankshaft, 2 is a double clutch device consisting of a primary clutch 3 and a secondary clutch 4, and when each clutch 3, 4 is disengaged, the running system and PTO system are connected. Engine power can be intermittent to each propulsion shaft.

The propulsion shaft has a so-called double shaft structure in which the traveling system is a cylindrical shaft 5 and a PTO system propulsion shaft 6 is inserted into the cylindrical shaft 5.

The cylindrical shaft 5 is an input shaft 5 that receives rotational power from the engine and rotates normally in a counterclockwise direction when viewed from the rear, as shown in Fig. 2 and below.
A, and an output shaft 5B coaxial with this input shaft 5A, and the input shaft 5A is separated from the clutch housing 7 by a partition wall 8.
The end of the shaft is supported by a bearing 9 shown in FIG.

A propulsion shaft case 10 integral with or supported by the partition wall 8 is encased on the input shaft 5A, and the propulsion shaft case 10 is provided with clutch release hub devices 11 and 12 for disengaging the double clutch 2, respectively. be.

The output shaft 5B is connected to the front and rear partition walls 14A of the mission case 13,
14B via bearings 16B, 16B, respectively, and the output shaft 5B is provided with four transmission gears 17 of different diameters in the figure at intervals in the axial direction.

A transmission shaft 19 is mounted parallel to and below the output shaft 5B on the front and rear partition walls 14A, 148 of the transmission case 13 via a pair of bearings 18A, 18B. Gears 20 are provided which are always in gear with the gears 17, and constitute a main transmission device A which is always in gear as a main gear.

Reference numeral 21 denotes a differential gear, in which the differential drive shaft 22 and the speed change shaft 19 are on the same axis, and a super reduction gear B and a sub-transmission C are provided between the two shafts 19 and 22.

Reference numeral 23 denotes a PTO gear shift shaft, which is provided on the extension of the axial center of the propulsion shaft 6 so as to be freely engageable and detachable via a locking and disengaging body 23A, and a PTO gear gear shift device 25 is provided between the shift shaft 23 and the PTO shaft 24. There is.

The transmission D of the present invention is provided between the input shaft 5A and the output shaft 5B, that is, in front of the main transmission A.

Referring to FIGS. 2 to 4, 26 is an inner ring transmission body;
The cylindrical boss portion of the sleeve 27 is fixed to the shaft end of the input shaft 5A.

The inner power transmission body 26 has an internal gear 26A in the figure, which surrounds the axis 0 of the output shaft 5B. Reference numeral 28 denotes a planetary carrier, which is fixed to the shaft end of the output shaft 5B by a spline in the figure, and three planetary transmission bodies 30, which are shown as gears in the embodiment, are attached to the carrier 28 via a support shaft 29. It is installed so that it can rotate freely.

In addition, each planetary transmission body 30 is connected to the internal gear 26A and is also connected to a sun transmission body 31 shown as a gear, thereby forming a planetary transmission device E. Of course, the planetary transmission E is preferably of the gear type shown, but it can also be of a roller type.

Furthermore, the carrier 28 of the planetary transmission device E has an inner transmission body 26.
It is supported by a rising wall 26B via a bearing 32 so as to be relatively rotatable.

33 is a fixing member, and the wall 14 of the mission case 13
A is attached via bolts, and this fixing member 3
3 is a holding case for the bearing 16A, and has an oil passage 34 opened in the wall 14A and an oil passage 35 extending through the output shaft 5.
It is mounted on A so that it can rotate freely.

37 is a one-way clutch on the output side, especially the fourth one in the figure.
As shown in the figure, a plurality of sprag type clutch bodies 37A are provided between the solar power transmission body 31 and the fixing member 33.

That is, the clutch 37 allows the solar transmission body 31 to freely rotate in the normal rotation direction of the counterclockwise hand in FIG. 3, but restrains it from rotating in the opposite direction. Body 31 and fixing member 3
3, and engages only in the reverse rotation direction of the output shaft 5B. In order to provide such a one-way clutch, the solar power transmission body 31 has a ring portion 31A through a stepped portion, and the fixed member 33 has a cylindrical boss portion 33 through a stepped portion.
A, and a clutch body 37A is interposed between the ring portion 31A and the cylindrical boss portion 33A. 38 is a clutch body using a fluid pressure cylinder, and the ring portion 31 of the solar transmission body 31
The body 38 has a post part 38A fixed to the mantle A by a spline and rotatably relative to the fixed member 33.
A ring-shaped piston or a plurality of pistons 39 in the circumferential direction compete with each other in the cylinder portion.

The body 38 has an oil passage 40 which is connected to the cylinder part, and the four oil passages are connected to the oil passage 35 and the oil passage 34. When the oil is supplied, the piston 39 slides in the connecting direction, and when the pressure oil is released, the piston 39 slides in the cutting direction by a spring (not shown) or the like.
A pressure receiving ring 42 is provided on the boss portion 38A of the cylinder body 38 via a receiver 41, and a driven clutch disc 43 is provided between the pressure receiving ring 42 and the piston 39. Internal gear 2 between 43
6A is provided with a drive clutch disk 44 that is engaged with a locking engagement portion 26C.

Furthermore, in FIG. 2, reference numeral 45 denotes a one-way clutch on the input side, which is interposed between the planetary carrier 28 and the sleeve 27, and is, for example, a sprag type clutch, similar to the one-way clutch 37 on the output side illustrated in FIG. Although it engages in the rotational direction of the input shaft 5A, that is, in the clockwise direction in FIG. 3, it is configured to rotate freely in the opposite direction.

That is, the one-way clutch 45 on the input side and the one-way clutch 37 on the output side act in opposite directions.

According to the specific example of the present invention configured as described above, the input shaft 5
When engine power is transmitted to A, the inner ring transmission body 26, which is shown as an internal gear in the embodiment, moves in the same direction as the input shaft 5A, that is,
It rotates in the direction of arrow A shown in FIG. 3 at a rotational speed of NI, for example.

Therefore, in the embodiment, pressure oil is sent to the piston 39 of the cylinder body 36, which is represented by a fluid clutch, to each disk 43, 4.
4, the inner ring transmission body 26 and the sun transmission body 31 come into engagement, and the sun transmission body 31' is rotated in the same direction as the inner ring transmission body 26. In this case, the one-way clutch 37 on the output side does not restrict the rotation direction of the sun power transmission body 31 in the counterclockwise direction.

Therefore, the planetary carrier 28 is not a planetary deceleration, but the N
The required torque is transmitted to the output shaft 5B at the same rotational speed as I, that is, at a high speed. Moreover, if the pressure oil to the piston 39 of the cylinder body 38 is released, that is, if the engagement relationship between the inner ring transmission body 26 and the sun transmission body 31 is released, the planetary transmission body 30 is connected to the inner ring transmission body 26. In the example, since the solar power transmission body 31 is engaged with the planetary power transmission body 30, the solar power transmission body 31 tries to rotate in the opposite direction to the inner ring transmission body 26.

At this time, in the embodiment, the rotation of the solar power transmission body 31 in the reverse direction is restrained via the one-way clutch 37 formed by the sprag type clutch body 37A.

That is, by holding the solar power transmission body 31 solid when the hydraulic clutch piston 39 is in the cutting direction,
The required torque is transmitted to the output shaft 68 via the planetary carrier 28 under the N.XZ reduction ratio.
Note that ZI is the number of teeth of the internal gear 26, and Z2 is the number of teeth of the planetary gear 3.
The number of teeth of 0 and Z3 are the number of teeth of the solar power transmission body 31, and in the example, an example is illustrated in which the speed is reduced by 28%. Thus, the hydraulic clutch is disengaged to perform a two-speed gear shift, and thereafter the driving wheels roll through the differential gear 21 via the main transmission device A and the like.

Next, in the chapters and embodiments, when the tractor travels downhill, etc., the planetary transmission system in which the fluid pressure clutch and the one-way clutch 37 are assembled between the input shaft 5A and the output shaft 5B as described above is used. If E is provided, the engine brake will not substantially act, but in such a case, since the one-way clutch 45 is provided between the sleeve 27 provided on the input shaft 5A and the planetary carrier 28, Since this one-way clutch 45 is engaged in the forward rotation direction of the input shaft 5A, engine braking is possible here.

In addition, if the engine starting system of the tractor is malfunctioning and it is virtually difficult to start the engine, push or pull the tractor.
Even at this time, the rolling rotation of the rear wheels is transmitted to the input shaft 5A via the one-way clutch 45 on the input side, and by assisting the running clutch 3, the engine speed is reduced. It becomes possible to drive or operate.

The present invention provides a transmission device in which an input shaft 5A driven by an engine and an output shaft 5B coaxial with the input shaft 5A are provided with a planetary transmission E, and an inner ring transmission body 26 on the input side and an output shaft 5B on the output side. A clutch for disengaging the solar power transmission body 31 is provided, and the solar power transmission body 31 is connected to the fixed part village 33 by the clutch 3.
7, so by disengaging the inner ring transmission body 26 and the sun transmission body 31, it is possible to select between high-speed rotation that does not go through the planetary transmission E and low-speed rotation that goes through the planetary transmission E. It can be implemented freely, and even if such a configuration is adopted, even if the engine brake becomes incapacitated or malfunctions, or the engine stops working due to the inability or malfunction of the engine starting system. By providing a one-way clutch 45 that engages the input shaft 5A and the planetary carrier 28 in the forward rotation direction of the input shaft 5A, but does not engage in the reverse rotation direction, these problems can be dealt with. It has great practical benefits as it effectively achieved the intended purpose.

[Brief explanation of the drawing]

Fig. 1 is an overall sectional view of a tractor transmission as an example to which the present invention is applied, Fig. 2 is a sectional view of an embodiment of the present invention, Fig. 3 is a sectional view taken along line 3-3 in Fig. 2, and Fig. 4 is a sectional view taken along line 4-4 in FIG. 5A...Input shaft, 5B...Output shaft, 26...
... Inner ring transmission body, 28 ... Planet carrier, 30 ...
・Planetary transmission body, 31... Solar transmission body, 39, 43,
44...Clutch component for restraining solar power transmission body, 37...
...Output side clutch, 45...Input side one-way clutch. Figure 1 Figure 3 Figure 2 Figure 4

Claims (1)

[Claims] 1. An inner ring transmission body is provided on the input shaft that receives rotational power of the engine, a planetary carrier and a solar transmission body are provided on the output shaft coaxial with the input shaft, and the planetary carrier is interlocked with the inner ring transmission body and the solar transmission body, respectively. In a planetary transmission device comprising a planetary transmission body, a clutch is provided for engaging and disengaging the sun transmission body and the inner ring transmission body, and a clutch is provided between the sun transmission body and the fixed member only in the reverse rotation direction of the output shaft. A transmission device characterized in that the planetary carrier is provided with a clutch that engages with the input shaft, and the planetary carrier is provided with a clutch that engages with the input shaft only in the normal rotation direction thereof.