JPH0835544A - Transmission - Google Patents

Abstract

PURPOSE:To provide a transmission which has simple structure and facilitates handling and manufacture, and provides high efficiency in a wide-ranging speed change region. CONSTITUTION:A transmission is equipped with a rotatable input shaft 1, an output shaft 2 which is rotatable coaxially with the input shaft 1, a sun bevel gear 3 which integrally revolves with the input shaft 1, a sun external spur gear 4 which revolves integrally with the sun bevel gear 3, intermediate planetary bevel gear 5 which is rotatable around the axis center C and revolves around the inner rotary axis center A and is meshed with the sun bevel gear 3, the planetary internal spur gear 6 meshed with the sun external spur gear 4, the output planetary bevel gear 7 which revolves integrally with the planetary internal spur gear 6 and meshed with the intermediate planetary bevel gear 5, and a transmission means 8 for varying the revolution speed of the intermediate planetary bevel gear 5. On the output shaft 2, the planetary internal spur gear 6 and the output planetary bevel gear 7 are installed freely rotatable around the axis center B and freely revolvable around the input rotary axis center A.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION The present invention relates to a transmission.

[0002]

2. Description of the Related Art As a transmission used for a machine tool, an industrial machine, a construction machine, an agricultural machine, a vehicle machine or the like, a transmission which is electrically controlled by an inverter or a servomotor has been known.

[0003]

However, in the above-mentioned transmission, there is a problem that the efficiency is poor because of low torque and insufficient output in the low speed range. Further, a transmission used for an automobile or the like that does not use electric power has a problem that control is difficult and the structure is complicated.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a transmission which has a simple structure, is easy to handle and manufacture, and has a high efficiency in a wide speed range.

[0005]

In order to achieve the above object, the present invention provides a rotatable input shaft, an output shaft rotatable coaxially with the input rotation axis of the input shaft, and the input shaft. A sun bevel gear that rotates integrally on the same axis, a sun outer spur gear that rotates integrally on the same axis as the sun bevel gear, and the input rotation is rotatable about an axis intersecting the input rotation axis at a predetermined angle. An intermediate planetary bevel gear that is revolvable around an axis and meshes with the sun bevel gear, a planetary internal spur gear that meshes with the sun outer spur gear, and the planetary inner spur gear that rotates integrally with the inner planetary spur gear coaxially. An output planetary bevel gear that meshes with the intermediate planetary bevel gear;
A speed change means for changing the revolution speed of the intermediate planetary bevel gear, and the output shaft, the internal planetary spur gear and the output planetary bevel gear are rotatable about an axis parallel to the input rotation axis and. It is provided so as to freely revolve around the input rotation axis.

Further, the transmission means surrounds the first external gear that rotates integrally with the input shaft coaxially, the second external gear that meshes with the first external gear, the first external gear and the second external gear. A casing having a storage chamber, an oil suction passage and an oil discharge passage that communicate with the storage chamber, and a flow rate control mechanism that controls the flow rate of the oil. The first external gear and the second external gear are provided. The second external gear is rotatably provided in the storage chamber so that oil is sent from the suction passage to the discharge passage by the tooth groove of, and the intermediate planetary bevel gear is rotatably provided in the casing. The casing is rotatably provided on the input shaft so that the intermediate planetary bevel gear can revolve around the input rotation shaft center.

Further, a rotatable input shaft, an output shaft rotatable coaxially with the input rotation axis of the input shaft, a sun bevel gear that rotates integrally with the input shaft coaxially, and the sun bevel gear. A sun outer spur gear that rotates integrally on the same axis, is rotatable about an axis intersecting with the input rotation axis at a predetermined angle and revolves around the input rotation axis, and meshes with the sun bevel gear. A crown gear, a planetary spur gear that meshes with the sun outer spur gear, a planetary bevel gear that rotates integrally with the planetary inner spur gear and meshes with the crown gear, and the revolution speed of the crown gear is changed. And a speed change means for causing the output shaft to:
The internal planetary spur gear and the planetary bevel gear are provided so as to be rotatable about an axis parallel to the input rotation axis and revolvable around the input rotation axis.

Further, the speed change means encloses the first external gear that rotates integrally with the input shaft coaxially, the second external gear that meshes with the first external gear, the first external gear and the second external gear. A casing having a storage chamber, an oil suction passage and an oil discharge passage that communicate with the storage chamber, and a flow rate control mechanism that controls the flow rate of the oil. The first external gear and the second external gear are provided. The second external gear is rotatably provided in the accommodating chamber so that oil is sent from the suction passage to the discharge passage by the tooth groove of, and the crown gear is rotatably provided in the casing and the crown gear is provided. The casing is provided so as to be rotatable relative to the input shaft so that the shaft can be revolved around the input rotary shaft.

[0009]

In the transmission provided with the intermediate planetary bevel gear, while the input shaft is being rotated by the prime mover or the like, the speed change means changes the revolution direction and revolution speed of the intermediate planetary bevel gear to the rotational direction of the input shaft and If it is the same as the rotation speed, all the gears that transmit the rotation torque from the input shaft to the output shaft are locked, and the output shaft has the same rotation speed as the input shaft. When the revolution speed of the intermediate planetary bevel gear is made slower than the rotation speed of the input shaft, the speed difference between the two causes the internal planetary spur gear and the output planetary bevel gear to start rotating, and the above rotation speed difference becomes large. Therefore, the rotation of the output shaft becomes slow. Further, when the revolution direction of the intermediate planetary bevel gear is made opposite to the rotation direction of the input shaft, the output shaft rotates in the opposite direction to the input shaft.

Further, in a transmission equipped with a crown gear, when the input shaft is rotated by a prime mover or the like, the transmission means
If the revolution direction and revolution speed of the crown gear are the same as the rotation direction and revolution speed of the input shaft, all the gears that transmit rotational torque from the input shaft to the output shaft will be in a locked state, and the output shaft will It has the same rotation speed. Then, when the revolution speed of the crown gear is delayed from the rotation speed of the input shaft, the speed difference between the two causes the planetary internal spur gear and the output planetary bevel gear to start rotating, and as the rotation speed difference increases, The output shaft rotates slowly. Furthermore, when the revolution direction of the crown gear is opposite to the rotation direction of the input shaft, the output shaft rotates in the direction opposite to the input shaft.

Further, in the case where the speed change means is provided with the first and second external gears and the casing, only the flow rate of the oil flowing by the rotation of the first and second external gears is controlled to rotate the second external gear. The rotation speed of the casing (that is, the revolution speed of the intermediate planetary bevel gear or the crown gear) can be easily changed by changing the speed and the revolution speed.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings showing embodiments.

FIG. 1 shows an embodiment of a transmission according to the present invention. This transmission has a rotatable input shaft 1 and an input shaft 1.
Output shaft 2 which is rotatable coaxially with the input rotation axis A, a sun bevel gear 3 which rotates integrally with the input shaft 1 on the same axis A, and a sun outer spur gear which rotates integrally with the sun bevel gear 3 on the same axis A. 4, an intermediate planetary bevel gear 5 that is rotatable about an axis C that intersects the input rotation axis A at a predetermined angle α, is revolvable around the input rotation axis A, and meshes with the sun bevel gear 3. The planetary internal spur gear 6 that meshes with the sun outer spur gear 4, the output planetary bevel gear 7 that integrally rotates with the planetary inner spur gear 6 and that meshes with the intermediate planetary bevel gear 5, and the revolution of the intermediate planetary bevel gear 5 A speed change means 8 for changing the speed, and a planetary internal spur gear 6 and an output planetary bevel gear 7 are attached to the output shaft 2 so as to be rotatable about an axis B parallel to the input axis A and the input axis. It is revolving around the heart A.

Specifically, the input shaft 1 and the output shaft 2 are rotatably supported by a casing or the like via bearings 9 ... The base end side of the input shaft 1 is connected to a prime mover (not shown) to be rotationally driven, and the tip end side of the output shaft 2 is connected to a machine that is driven at variable speeds. In the figure, the left side is the tip side and the right side is the base side.

The sun bevel gear 3 and the sun outer spur gear 4 are integrally formed on a part of the input shaft 1 (the tip portion in the illustrated example) so as to be aligned in the axial direction, and the output shaft 2 is provided on the tip portion of the input shaft 1. A base end portion of the is pivotally supported so as to be relatively rotatable.

The internal planetary spur gear 6 and the output planetary bevel gear 7 are integrally formed on a cylindrical rotary member 10 with a collar. This rotating body 10
The internal planetary spur gear 6 and the output planetary bevel gear 7 are connected to each other via an eccentric shaft portion 11 formed on a part of the output shaft 2 (a base end portion in the example).
It is pivotally attached to the eccentric shaft 11 so as to be rotatable about the axis B of the eccentric shaft 11 and revolve around the input rotation axis A. Reference numeral 12 is a weight body (weight) for improving dynamic balance of the entire transmission and suppressing vibration during rotation.

Next, the speed changing means 8 includes a first external gear 13 that rotates integrally with the input shaft 1 coaxially with the input shaft 1, a pair of second external gears 14 and 14 that mesh with the first external gear 13, and a first external gear 13. A casing 16 having a storage chamber 15 that surrounds the external gear 13 and the second external gears 14, 14, an oil suction passage 17 and an oil discharge passage 18 that are connected in communication with the storage chamber 15, and a diagram for controlling the flow rate of the oil. A flow rate control mechanism including a flow rate control valve, etc., omitted;
The second external gears 14, 14 are rotatably provided in the storage chamber 15 so that oil is sent from the suction passage 17 to the discharge passage 18 by the tooth grooves of the 13 and second external gears 14, 14.

The casing 16 is provided with the intermediate planetary bevel gear 5 rotatably, and the casing 16 is relatively rotatable with respect to the input shaft 1 so that the intermediate planetary bevel gear 5 can revolve around the input rotation axis A. To be installed.

In the illustrated example, a central hole is formed through the casing 16 so that the casing 16 is rotatably fitted on the input shaft 1 and the casing 16 is
Has a pivot 22 formed on the tip cylindrical portion thereof, and the intermediate planetary bevel gear 5 is rotatably attached to the pivot 22 so as to form 90 ° with the input rotation axis A.
The shaft C is rotatable about an axis C intersecting at the angle α and is revolvable around the input rotation shaft A. Reference numeral 19 is a weight body (weight) for improving the dynamic balance of the entire transmission and suppressing vibration during rotation.

The first external gear 13 is connected to the input shaft 1 by a key or the like and rotates integrally. The second external gear 14 is a support shaft 20 that is fixed to the casing 16 and is parallel to the input rotation axis A.
The second external gear 14 is rotatably and pivotally mounted, and is rotatable about the axis of the support shaft 20 and revolves around the input rotation axis A.

The first external gear 13 and the second external gear 14 start to mesh with each other, and the part where the meshing separates from each other becomes a void, and the first external gear 13 and one of the second external gears.
14 the space where the meshing starts and the first external gear 13
The inner surface 15a of the storage chamber 15 to the tooth tips of the first external gear 13 and the second external gears 14 and 14 so that the voids in the areas where the meshing of the second external gear 14 and the other external gear 14 separates from each other. They are brought into close proximity or in sliding contact with each other.

Further, the first external gear 13 and the second external gear 14 on one side are connected to the gap portion where the meshing is separated from the suction passage 17, and the first external gear 13 and the second external gear 14 on the other side are connected. The discharge passage 18 is communicatively connected to the void portion where the meshing of the gear starts, and the discharge passage 18 is configured to function as a gear pump.

That is, when the gears 13 and 14 mesh and rotate in a predetermined direction, the volume of the above-mentioned void portion which is communicated with the suction passage 17 increases, and the suction action due to the pressure decrease causes the oil to be sucked from the suction passage 17. . This oil is sequentially held in the tooth spaces of the gears 13, 14, 14 that mesh with each other, and is sent to the discharge passage 18 side. And
In the above-mentioned gap portion which is connected to the discharge passage 18, the volume is reduced by the meshing rotation of the gears 13 and 14, and the oil is discharged from the discharge passage 18 by the pushing action due to the increase in pressure.

The revolution speed of the intermediate planetary bevel gear 5 can be changed by controlling the flow rate of the oil with a flow rate control mechanism. That is, when the first external gear 13 (input shaft 1) is rotated and the flow of oil from the suction passage 17 to the discharge passage 18 is stopped to make the flow rate zero, the second external gear 14,
Reference numeral 14 denotes the first external gear 13 without causing meshing rotation (rotation).
Is rotated (revolved) integrally with the casing 16, whereby the intermediate planetary bevel gear 5 revolves in the same direction and speed as the input shaft 1.

From this state, if the oil is allowed to flow from the suction passage 17 to the discharge passage 18, the second external gears 14, 14 will rotate, and as the oil flow rate increases, the second external gear 14, 14
The rotation of the casing becomes faster, and the revolution (the rotation of the casing 16) becomes slower due to the rotation. In this way, the revolution speed of the intermediate planetary bevel gear 5 can be changed.

The suction passage 17 and the discharge passage 18 are casings.
16 holes 28, 29 and a joint that can rotate relative to the casing 16
36 holes 30 and 31, and is connected to a flow control valve (not shown), an oil tank, or the like. This joint 36 does not rotate, and even if the casing 16 rotates due to a peripheral groove (not shown), the hole
The holes 28, 30 and the holes 29, 31 are always connected to each other.

Further, an outer brim-shaped clutch portion 23 is formed on the base end cylindrical portion of the casing 16, and a clutch plate 25 which can be pressed and separated from the clutch portion 23 by manual or power drive is provided on the input shaft 1. The friction clutch mechanism 26 is configured. The clutch plate 25 can rotate integrally with the input shaft 1 by a slide key 24 and can slide in the direction of the axis A. By directly connecting the input shaft 1 and the casing 16 by the friction clutch mechanism 26, it is possible to stop unnecessary rotation of gears and improve efficiency.

Further, a casing 16 corresponding to the storage chamber 15
The outer peripheral surface 16a is formed in a circular shape, and a friction member 21 that can be pressed and separated is provided on the outer peripheral surface 16a by manual or power drive.
A friction brake mechanism 27 is configured. Thereby, the rotation of the casing 16 (the revolution of the intermediate planetary bevel gear 5) can be easily stopped.

Here, to give an example of specific numerical values such as the number of teeth of each gear in the embodiment of FIG. 1, the sun bevel gear 3 and the sun outer spur gear 4 have the same number of teeth, and the inner planetary spur gear 4 has the same number of teeth. The gear 6 and the output planetary bevel gear 7 have the same number of teeth, and the sun bevel gear 3
The ratio of the number of teeth of the (external sun spur gear 4) and the planetary spur gear 6 (output planetary bevel gear 7) is set to 9:11. For example, the sun bevel gear 3
The number of teeth of the sun outer spur gear 4 is 27, and the number of teeth of the planet inner spur gear 6 and the output planetary bevel gear 7 is 33.

In the transmission constructed as described above, the intermediate planetary bevel gear 5 revolves in the same direction and speed as the input shaft 1 with the input shaft 1 rotated at a predetermined speed. Then, all the gears 3, 4, 5, 6, 7 are locked, and the intermediate planetary bevel gear 5, the planetary internal spur gear 6, and the output planetary bevel gear 7 do not rotate and the input rotation axis A It rotates (revolves) integrally around (in the same rotation direction as the input shaft 1).
Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.

From this state, when the revolution of the intermediate planetary bevel gear 5 is delayed by the speed changing means 8 than the rotation of the input shaft 1,
The rotation speed difference causes the intermediate planetary bevel gear 5, the planetary spur gear 6, and the output planetary bevel gear 7 to rotate, so that the revolutions of the gears 6 and 7 (that is, the rotation of the output shaft 2) are slower than the input shaft 1. Finally, the rotation of the output shaft 2 stops (hereinafter referred to as zero rotation).

Further, when the intermediate planetary bevel gear 5 is revolved in the direction opposite to the input shaft 1, the rotation of the intermediate planetary bevel gear 5, the planetary internal spur gear 6, and the output planetary bevel gear 7 is accelerated, and the gears are rotated. 6 and 7 revolve in the opposite direction to the input shaft 1, and thereby the output shaft 2 rotates in the opposite direction to the input shaft 1.

Although not shown, the intermediate planetary bevel gear 5
In order to revolve the engine in the direction opposite to the input shaft 1, a pump that pressurizes the oil in the suction passage 17 and an automatic valve that is arranged upstream of the pump are provided to ensure that the speed is higher than the natural inflow speed. By sending oil to the first external gear 13 and the second external gear 14, the rotation of the second external gear 14 is accelerated, and the second external gear 14 is revolved in the direction opposite to the input shaft 1, thereby Casing 16
The (intermediate planetary bevel gear 5) can be rotated (revolved) in the direction opposite to the input shaft 1.

The above-mentioned gear shift can be performed by servo control or automatic control by a microcomputer or the like. In this way, since the output shaft 2 can be rotated in the forward and reverse directions with respect to the input shaft 1 that rotates in one direction at a predetermined speed, the output shaft 2 is suitable for a transmission of a traveling machine such as an automobile. Moreover,
Since the start is zero and the acceleration is smooth, no black smoke is emitted when the present invention is applied to a diesel vehicle, and pollutants such as nitrogen oxides can be greatly suppressed.

Further, the speed changing means 8 acting as a gear pump
High efficiency can be obtained by using a small capacity. That is,
If the mechanical efficiency of the gear pump is about 80%, if this pump capacity is reduced to 1/10, it can be suppressed to only 2%. Further, although not shown, if a pressure reducing valve is provided in the discharge passage 18, most of the pressurization can be returned to the output shaft 2.

Next, FIG. 2 shows another embodiment, in which the intermediate planetary bevel gear 5 in FIG. 1 is used as a crown gear 32. In this case, the tip end portion of the casing 16 is connected to the input rotation axis. Declination hollow shaft portion 33 having an axis D intersecting with A at a predetermined angle β
The crown gear 32 is rotatably and pivotally attached to the eccentric hollow shaft portion 33 so as to rotate about the shaft center D and to rotate the input rotation shaft A.
It is freely revolving around. The crown gear 32 meshes with the sun bevel gear 3 and the output planetary bevel gear 7.

Reference numeral 34 denotes a retaining nut member screwed to the declination hollow shaft portion 33. Reference numeral 35 is a weight body (weight) for improving dynamic balance of the entire transmission and suppressing vibration during rotation. The other configuration is the same as that of FIG.

Also in this case, the output shaft 2 is changed by changing the revolution direction and revolution speed of the crown gear 32 by the transmission means 8.
It is possible to change the forward and reverse directions freely. Note that the crown gear 32 tries to rotate in the forward direction when a load is applied, but since this is impossible, it is possible to stop the slip and move forward. Therefore, it is possible to reduce the capacity of the transmission means 8 that functions as a gear pump.

Here, to give an example of concrete numerical values such as the number of teeth of each gear in the embodiment of FIG. 2, the sun bevel gear 3 and the sun outer spur gear 4 have the same number of teeth, and the inner planetary spur gear 4 has the same number of teeth. The gear 6 and the output planetary bevel gear 7 have the same number of teeth, and the sun bevel gear 3
The ratio of the number of teeth of the (sun outer spur gear 4) and the planet inner spur gear 6 (output planetary bevel gear 7) is 40:41. For example, the sun bevel gear 3
And the sun outer spur gear 4 has 40 teeth, the planetary spur gear 6 and the output planetary bevel gear 7 have 41 teeth, and the crown gear 32 has 40 teeth or
41 sheets, pressure angle 20 ° and low teeth.

The present invention is not limited to the above-mentioned embodiments, and design changes can be freely made without departing from the gist of the present invention.
For example, the reference pitch circles, the number of teeth, etc. of the gears 3, 4, 5, 6, 7, 32 can be freely changed. By increasing the number of teeth of the intermediate planetary bevel gear 5 and the crown gear 32, the action of the gear pump can be improved. It is possible to further reduce the capacity of the speed changing means 8 forming Also,
The output planetary bevel gear 7 is preferably large in terms of strength.

Further, the type of tooth profile of the gears 13 and 14, the reference pitch circle, the number of teeth, etc. can be changed and the number of gears 14 can be increased or decreased freely. If the number of teeth of the first external gear 13 is set to an odd number, the pump It is possible to suppress the pulsation as. As the speed change means 8, other than the example shown in the figure, a friction wheel or the like may be freely used, but it is preferable that the speed change means 8 be capable of forward / reverse rotation of the casing 16 for speed change control. In the embodiment of FIG. 2, the friction clutch mechanism 26 may be provided, or the pressure reducing valve, the pump and the automatic valve described in the embodiment of FIG. 1 may be provided.

Further, the sun bevel gear 3, the sun outer spur gear 4, the input shaft 1, the planetary inner spur gear 6, the output planetary bevel gear 7, and the rotating body 10.
Alternatively, separate components may be fixed to each other and integrated without being integrally formed.

[0043]

Since the present invention is configured as described above, the following significant effects can be obtained.

In the transmission according to the first and third aspects, the output shaft 2 can be steplessly and constantly output over a desired range by simply changing the revolution speed of the intermediate planetary bevel gear 5 or the crown gear 32 by the transmission means 8. The speed can be changed to the number of revolutions, sufficient torque can be output even in the low speed range, and efficiency is good. Moreover, the output shaft 2
The zero rotation is obtained regardless of the rotational speed of the prime mover that rotates the input shaft 1, is guaranteed by the rotational force of the prime mover, and is a closed loop. Further, since it is composed of parts having a simple shape and structure such as gears, it is easy to handle and manufacture.

In the transmission according to the second and fourth aspects, since the speed changing means 8 acting as a gear pump can be designed to be significantly small, the efficiency reduction can be suppressed to an extremely small level. Moreover, the speed change means 8 has a simple structure and high reliability, and the rotation speed of the casing 16 (the revolution speed of the intermediate planetary bevel gear 5 or the crown gear 32) can be easily controlled to zero.

In the transmission according to claim 3, the sun bevel gear 3 is provided.
Since the output planetary bevel gear 7 is meshed with the crown gear 32,
It can be quietly rotated without backlash, and has excellent durability and few breakage failures.

[Brief description of drawings]

FIG. 1 is a sectional side view showing an embodiment of the present invention.

FIG. 2 is a sectional side view showing another embodiment.

[Explanation of symbols]

 1 input shaft 2 output shaft 3 sun bevel gear 4 sun outer spur gear 5 intermediate planetary bevel gear 6 planetary inner spur gear 7 output planetary bevel gear 8 speed change mechanism 13 first external gear 14 second external gear 15 storage chamber 16 casing 17 suction Path 18 Discharge path 32 Crown gear A Input rotation axis center B axis center C axis center D axis center α angle β angle

Claims (4)

[Claims] 1. A rotatable input shaft 1, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, and a sun bevel gear 3 which integrally rotates coaxially with the input shaft 1. A sun outer spur gear 4 that rotates integrally with the sun bevel gear 3 coaxially with the sun bevel gear 3, and an axis C that intersects the input rotation axis A at a predetermined angle α and is rotatable about the input rotation axis A. An intermediate planetary bevel gear 5 that can freely revolve around and meshes with the sun bevel gear 3.
And a planetary spur gear 6 that meshes with the sun outer spur gear 4,
An output planetary bevel gear 7 that rotates together with the internal planetary spur gear 6 and that meshes with the intermediate planetary bevel gear 5, and a transmission unit 8 that changes the revolution speed of the intermediate planetary bevel gear 5.
The planetary internal spur gear 6 and the output planetary bevel gear 7 are rotatable on the output shaft 2 about an axis B parallel to the input rotation axis A and revolve around the input rotation axis A. A transmission characterized by being installed freely. 2. The transmission means 8 comprises a first external gear 13 that rotates integrally with the input shaft 1 coaxially with the input shaft 1, a second external gear 14 that meshes with the first external gear 13, and a first external gear 13. And a casing 16 having a storage chamber 15 that surrounds the second external gear 14, and an oil suction passage 17 and a discharge passage 18 that are connected in communication with the storage chamber 15.
A flow rate control mechanism for controlling the flow rate of the oil, so that the oil is sent from the suction passage 17 to the discharge passage 18 by the tooth grooves of the first external gear 13 and the second external gear 14. The external gear 14 is rotatably provided in the storage chamber 15, the intermediate planetary bevel gear 5 is rotatably provided in the casing 16, and the intermediate planetary bevel gear 5 is revolvable around the input rotation axis A. 2. The transmission according to claim 1, wherein the casing 16 is provided on the input shaft 1 so as to be rotatable relative to each other. 3. A rotatable input shaft 1, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, and a sun bevel gear 3 which rotates integrally with the input shaft 1 coaxially. A sun outer spur gear 4 that rotates integrally with the sun bevel gear 3 coaxially with the sun bevel gear 3, and an axis D that intersects the input rotation axis A at a predetermined angle β and is rotatable about the input rotation axis A. A crown gear 32 that is revolvable around and meshes with the sun bevel gear 3, a planetary spur gear 6 that meshes with the sun outer spur gear 4, and a planetary inner spur gear 6 that integrally rotates coaxially with the planetary spur gear 6. An output planetary bevel gear 7 that meshes with the crown gear 32 and a speed changing unit 8 that changes the revolution speed of the crown gear 32 are provided, and the output shaft 2 has the internal planetary spur gear 6 and the output planetary bevel gear 7. Is rotatable about an axis B parallel to the input rotation axis A and revolves around the input rotation axis A. Transmission, characterized in that provided in the. 4. The transmission means 8 comprises a first external gear 13 that rotates integrally with the input shaft 1 coaxially with the input shaft 1, a second external gear 14 that meshes with the first external gear 13, and a first external gear 13. And a casing 16 having a storage chamber 15 that surrounds the second external gear 14, and an oil suction passage 17 and a discharge passage 18 that are connected in communication with the storage chamber 15.
A flow rate control mechanism for controlling the flow rate of the oil, so that the oil is sent from the suction passage 17 to the discharge passage 18 by the tooth grooves of the first external gear 13 and the second external gear 14. The external gear 14 is rotatably provided in the storage chamber 15, the crown gear 32 is rotatably provided on the casing 16, and the crown gear 32 is revolvable around the input rotation axis A. 4. The transmission according to claim 3, wherein the casing 16 is provided on the input shaft 1 so as to be relatively rotatable.