JP2002303359A - Reduction gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reduction gear capable of achieving predetermined speed reduction efficiency and low noise efficiency. SOLUTION: The speed is reduced from approximately 78,000 rpm to approximately 13,000 rpm by a helical parallel gear 5 at a first stage. The frequency of 13,000 rpm is higher than an audible range, and is not heard by a human. The speed is reduced from approximately 13,000 rpm to approximately 3,600 rpm by a planetary traction 6 at a second stage. The frequency of 3,600 rpm is in the audible range, and is not a noise by a characteristic of the planetary traction 6 at the second stage. Therefore, the low noise efficiency can be achieved. Large speed reduction efficiency is not achieved by the planetary traction 6 at the second stage but can be achieved by the helical parallel gear 5 at the first stage. The predetermined speed reduction efficiency can be totally achieved by the combination (hybrid) of the helical parallel gear 5 at the first stage and the planetary traction 6 at the second stage.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION
High speed rotation of about 130,000 rpm is performed for about 3000 to about 50
The present invention relates to a speed reducer that decelerates to 00 rpm, and more particularly to a speed reducer that can achieve a predetermined speed reduction efficiency and a low noise effect.

[0002]

2. Description of the Related Art In general, a speed reducer reduces a high-speed rotation of a drive unit to a low-speed rotation and transmits the reduced rotation to a load unit.

[0003] As the driving device, for example, there is a micro gas turbine of a turbine system. This micro gas turbine can provide high speed rotation of about 60,000 to about 130,000 rpm.

[0004] Examples of the load device include a high-speed generator, an axial flow pump, a marine propulsion screw, and an underwater propulsion screw such as a torpedo. These load sides operate at low speeds of about 3000 to about 5000 rpm.

[0005] From the above, as the reduction gear, about 600
High speed rotation of 00 to about 130,000 rpm
It is necessary to decelerate to about 5000 rpm. The reduction ratio is about 1/12 to about 1/65, and is mainly about 1/2.
It becomes 0.

[0006] For this reason, the speed reducer is a two-stage speed reducer, especially when miniaturization is considered. That is,
In the first stage, the speed is reduced from about 60,000 to about 130,000 rpm to about 10,000 to about 20,000 rpm, and in the second stage,
The speed is reduced from about 10,000 to about 20,000 rpm to about 3000 to about 5000 rpm.

For example, as a conventional speed reducer, as shown in the prior art column of Table 1 below, a combination of a single-stage helical parallel gear and a two-stage helical parallel gear is used, and one stage is a single-stage helical gear. Combination of parallel gear and two-stage planetary gear, one-stage planetary gear and two
The stage includes a combination with a helical parallel gear, a combination of a single-stage planetary gear and a two-stage planetary gear, a combination of a single-stage planetary traction and a two-stage planetary traction, and the like.

[0008]

[Table 1]

On the other hand, it is desired that the speed reducer has a predetermined deceleration efficiency and a low noise effect. In particular, when the load device is used in a city or near a house, low noise efficiency is regarded as important.

[0010]

However, in the conventional speed reducer, it is difficult to achieve both the deceleration efficiency and the low noise effect as shown in the column of the prior art in Table 1 above.

That is, the helical parallel gear has a large deceleration efficiency but a small noise reduction effect. Further, the planetary gear and the planetary traction have a high low noise efficiency but a low deceleration efficiency.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a speed reducer which can obtain a predetermined deceleration efficiency and a low noise effect.

[0013]

To achieve the above object, the invention according to claim 1 is characterized by comprising a single-stage helical parallel gear and a double-stage planetary traction. .

As a result, according to the first aspect of the present invention, a single-stage helical parallel gear can provide about 60,000 to about 13,000.
The speed is reduced from 0 rpm to about 10,000 to about 20,000 rpm. Since the frequency of about 10,000 to about 20,000 rpm is higher than the audible range, it is inaudible to humans.

According to the first aspect of the present invention, the two-stage planetary traction provides about 10,000 to about 2,000
The speed is reduced from 0 rpm to about 3000 to about 5000 rpm. The frequency of about 3000 to about 5000 rpm is in the audible range, but does not become noise due to the characteristics of the planetary traction.

Therefore, according to the first aspect of the invention, excellent low noise efficiency can be obtained.

On the other hand, according to the first aspect of the present invention, great deceleration efficiency cannot be obtained by two-stage planetary traction.
Large deceleration efficiency can be obtained by a single-stage helical parallel gear. By the combination (hybrid) of the one-stage helical parallel gear and the two-stage planetary traction, the invention according to claim 1 can obtain a predetermined deceleration efficiency in total.

The invention according to claim 2 is characterized in that a projection is provided at a portion of the ring roller that comes into contact with a plurality of planetary rollers.

As a result, according to the present invention, the surface pressure of the ring roller on the concave side and the plurality of planetary rollers on the convex side is small. And the contact pressure increases. As a result, the surface pressure of the plurality of planetary rollers on the convex side as well as the surface pressure of the sun roller on the convex side having a large surface pressure, and the surface pressure of the ring roller and the plurality of planetary rollers are maintained in balance. . Therefore, a predetermined deceleration efficiency can be obtained, and a low noise effect can be obtained.

According to a third aspect of the present invention, the bearing of the input shaft of the one-stage speed reduction mechanism is constituted by an angular ball bearing, and the angular ball bearing is provided with a spring acting in the axial direction. , Characterized in that.

As a result, according to the third aspect of the present invention, with the above configuration, in a no-load state, the angular operation of the angular ball bearing does not run idle due to the spring action of the spring, thereby extending the life of the angular ball bearing. Can be kept.
On the other hand, in the load state, even when thermal expansion occurs in the angular ball bearing when the input shaft of the one-stage reduction mechanism rotates at high speed, the thermal expansion can be absorbed by the spring action of the spring. Therefore, seizure of the angular contact ball bearing is prevented.

Further, the invention according to claim 4 provides a jet nozzle for jetting lubricating oil to the spline side,
The lubricating oil that is jet-sprayed from the jet nozzle is temporarily reflected and accumulated on the spline side. And a supply path to be supplied to the portion.

As a result, the invention according to claim 4 uses the centrifugal force of the high-speed rotating shaft to form a meshing engagement portion between the spline and the coupling, which also rotates at high speed, and requires lubricating oil. Lubricating oil can be reliably supplied to the part.

[0024]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a speed reducer according to the present invention will be described below with reference to the accompanying drawings. The speed reducer is not limited by this embodiment.

(Explanation of Configuration of Embodiment) In FIG. 1, reference numeral 1 denotes a speed reducer according to an embodiment of the present invention. For example, as shown in FIG. 8, the speed reducer 1 reduces the high-speed rotation of the micro gas turbine 2 as a driving device to a low-speed rotation and transmits the reduced speed to a high-speed generator 3 as a load device.

In this example, the micro gas turbine 2 can rotate at a high speed of about 78,000 rpm. Also,
The high-speed generator 3 operates at a low speed of about 3600 rpm in this example. As a result, the speed reducer 1
It requires a / 20 deceleration.

As shown in FIG. 1, the reduction gear 1 has a casing 4 in which a two-stage reduction mechanism is hermetically sealed. The two-stage speed reduction mechanism includes a one-stage helical parallel gear 5 and a two-stage planetary traction 6.

The single-stage helical parallel gear 5 has an input shaft 9 rotatably mounted at both ends to the casing 4 by means of combined angular ball bearings 7 and 8, and is fixed at an intermediate position between the input shaft 9 and the input shaft 9. The output of a small gear input gear 10, an output shaft 13 whose both ends are rotatably mounted on the casing 4 by a cylindrical roller bearing 11 and a combined angular ball bearing 12, and a large gear fixed in the middle of the output shaft 13. And a gear 14.

The two-stage planetary traction 6 has a shell composed of an input-side sun roller 15, a plurality of, in this example, three, planetary rollers 16, and an output-side ring roller 17.

One end of the sun roller 15 is fixed to one end of the output shaft 13 of the helical parallel gear 5. The middle of the sun roller 15 is rotatably mounted on the casing 4 by a combination angular ball bearing 18.

One end of each of the three planetary rollers 16 is attached to the casing 4 so as to be rotatable and rotatable at equal intervals. The three planetary rollers 16 are pressed against the sun roller 15. As a result, the three planetary rollers 16 move in the direction of the arrow (counterclockwise) in FIG. 2 along with the rotation of the sun roller 15 (for example, the rotation in the direction of the arrow (clockwise) in FIG. 2). Each spins.

One end of the ring roller 17 is rotatably mounted on the casing 4 by a bearing (not shown). The ring roller 17 is pressed against the three planetary rollers 16. As a result, the ring roller 17 rotates in the direction indicated by the arrow in FIG. 2 (counterclockwise) with the rotation of the three planetary rollers 16.

One end of the input shaft 9 is connected to one end of an output shaft 19 of the micro gas turbine 2 via a spline coupling mechanism 20 described later. One end of the ring roller 17 is connected to an input shaft 24 (see FIG. 6) of the high-speed generator 3. As a result, the micro gas turbine 2 and the high-speed generator 3 are connected via the speed reducer 1.

The casing 4 of the speed reducer 1 is divided into a space 22 for hermetically storing the helical parallel gear 5 and a space 23 for hermetically storing the two-stage planetary traction 6 by an oil seal 21 or the like. Have been. Gear oil (not shown) is in the one-stage helical parallel gear storage space 22, while traction oil (not shown) is in the two-stage planetary traction storage space 23. Each is filled. The oil seal 21
May be provided closer to the sun roller 15 than the combined angular ball bearing 18.

(Explanation of Operation of the Embodiment) The speed reducer 1 in this embodiment has the above-described configuration.
Hereinafter, the operation will be described.

First, the micro gas turbine 2 is driven to start. Then, the output shaft 19 of the micro gas turbine 2 rotates at a high speed of about 78000 rpm. About 78
The high-speed rotation of 000 rpm is transmitted to the input shaft 9 of the single-stage helical parallel gear 5 via the spline coupling mechanism 20.

The input gear 1 of the single-stage helical parallel gear 5
Approximately 78000 rp due to the reduction ratio between 0 and the output gear 14
m is reduced to about 13000 rpm. This frequency of about 13000 rpm is higher than the audible range and is inaudible to humans.

With the single-stage helical parallel gear 5, approximately 7
The medium-speed rotation reduced from the high-speed rotation of 8000 rpm to about 13000 rpm is transmitted to the sun roller 15 of the two-stage planetary traction 6 via the output shaft 13 of the one-stage helical parallel gear 5.

The sun roller 15 of the two-stage planetary traction 6, three planetary rollers 16, and a ring roller 17
Medium speed rotation of about 13000 rpm,
The speed is reduced to about 3600 rpm. About 3600 rpm
Is in the audible range, but does not become noise due to the characteristics of the two-stage planetary traction 6.

That is, as shown in Table 1, according to the noise inspection data at a place 1 m away from the device (reduction gear 1), a value of 87 dBA was obtained. This noise value is a noise value that humans can endure. Therefore, the reduction gear 1 in this embodiment can achieve low noise efficiency.

On the other hand, the speed reducer 1 in this embodiment
Although a large reduction efficiency cannot be obtained by the two-stage planetary traction 6, a large reduction efficiency can be obtained by the single-stage helical parallel gear 5. Combination of this one-stage helical parallel gear 5 and two-stage planetary traction 6 (hybrid)
Thus, the reduction gear 1 in this embodiment can obtain a predetermined reduction efficiency in total.

That is, as shown in Table 1 above, a value of 92% was obtained in the deceleration efficiency.

As described above, in the speed reducer 1 according to this embodiment, a predetermined speed reduction efficiency (92%) is obtained.
In addition, a low noise effect (87 dBA) can be obtained. Then, the low-speed rotation reduced to about 3600 rpm is transmitted to the input shaft 24 of the high-speed generator 3 via the ring rollers 17 of the two-stage planetary traction 6.

(Explanation of Modification of Ring Roller) In the two-stage planetary traction 6, two ring-shaped projections 25 are formed on the inner peripheral surface of the ring roller 17 that presses against three planetary rollers 16. Are provided integrally.

Although the surface pressure between the inner peripheral surface of the ring roller 17 on the concave side and the outer peripheral surfaces of the three planetary rollers 16 on the convex side is small, the projection 2 provided on the inner peripheral surface of the ring roller 17 is small.
5, the surface pressure between the ring roller 17 and the three planetary rollers 16 is increased. Thereby, the surface pressure between the outer peripheral surface of the sun roller 15 on the convex side where the surface pressure is large and the outer peripheral surface of the three planetary rollers 16 also on the convex side,
The surface pressure with the individual planetary rollers 16 is kept in balance. Therefore, a predetermined deceleration efficiency can be obtained, and a low noise effect can be obtained.

(Explanation of High Speed Rotating Shaft Bearing) The input shaft 9 of the single-stage helical parallel gear 5 (single-stage reduction mechanism) is approximately 7
It rotates at a high speed of 8000 rpm. The bearing of the input shaft 9 of the high-speed rotating shaft is provided by the combination angular contact ball bearings 7 and 8.
It is composed of The outer ring of the combined angular contact ball bearing 8 on the back side (the side opposite to the side connected to the output shaft 19 of the micro gas turbine 2) is provided with a spring 26 acting in the axial direction.

With the above configuration, the bearing of the input shaft 9 of the high-speed rotating shaft is free from the idling of the combined angular ball bearings 7 and 8 due to the spring action of the spring 26 in the no-load state. The life of the angular ball bearings 7 and 8 can be kept long.

On the other hand, when the input shaft 9 of the single-stage helical parallel gear 5 rotates at a high speed of about 78000 rpm in a load state, thermal expansion occurs in the inner rings of the combined angular ball bearings 7 and 8. Since the thermal expansion can be absorbed by the spring action of the spring 26, seizure of the combined angular ball bearings 7 and 8 is prevented.

Here, as shown in FIG.
The spring preload (arrow a) is set to 50 kgf, and the input gear 10
Thrust load on the input shaft 9 (arrow c) when the radial load (arrow b) on the input shaft is 80 kgf
Is 20 kgf.

In the bearing of the high-speed rotating shaft, an oil damper 27 can be provided between the outer ring of the combined angular ball bearing 7 connected to the output shaft 19 of the micro gas turbine 2 and the casing 4. .

With the above configuration, the combined angular ball bearings 7 and 8 can be slightly moved in the thrust direction, so that the life of the combined angular ball bearings 7 and 8 can be maintained long, and the combined angular ball bearing 7 And 8 can be prevented from burning.

(Explanation of Lubricating Oil Supply Mechanism at Connection of High Speed Rotating Shaft) Output Shaft 1 of Micro Gas Turbine 2
9 and the input shaft 9 of the one-stage helical parallel gear 5 rotate at a high speed of about 78,000 rpm. The output shaft 19 and the input shaft 9 of the high-speed rotation shaft are connected by the spline coupling mechanism 20.

The spline coupling mechanism 20 includes:
As shown in FIG. 1, splines 28 and 29 are fixed to one end of the output shaft 19 and one end of the input shaft 9, respectively, and a coupling 30 is engaged with the splines 28 and 29. ing. The spline coupling mechanism 20 is provided with a lubricating oil supply mechanism 31.

As shown in FIG. 5, the lubricating oil supply mechanism 31 includes a lubricating oil 32 (in the figure, a dotted portion is shown).
Nozzle 33 for jetting the lubricating oil to the spline 28 side, a lubricating oil reservoir 34 in which the lubricating oil 32 jetted from the jet nozzle 33 is reflected once on the spline 28 side, and a lubricating oil in the lubricating oil reservoir 34 32
And a supply path 36 that is supplied to the engagement portion 35 between the splines 28 and 29 and the coupling 30 by the centrifugal force of high-speed rotation of the output shaft 19 and the input shaft 9.

Since the lubricating oil supply mechanism 31 is constructed as described above, by utilizing the centrifugal force of the output shaft 19 and the input shaft 9 which rotate at high speed, the splines 28 and 29 which also rotate at high speed and the coupling 30 are used. The lubricating oil 32 can be reliably supplied to the portion where the lubricating oil 32 is required through the supply path 36 (see the arrow in FIG. 5).

The jet nozzle 33 is provided on the side of the output shaft 19 of the micro gas turbine 2.
May be provided on the input shaft 9 side, or may be provided on both sides.

(Description of Micro Gas Turbine and High Speed Generator) Next, the micro gas turbine 2 and the high speed generator 3 connected via the speed reducer of the present invention will be described with reference to FIGS. The micro gas turbine 2 has a compressor 38 and a turbine 39 on the same output shaft 19 rotatably supported by a high-speed bearing 37.
Are provided. Further, the micro gas turbine 2 is provided with a combustor 40 and a regenerative heat exchanger 41.

The micro gas turbine 2 is started by a starting motor or a starting motor (not shown) built in the high-speed generator 3. Then, the output shaft 19,
The compressor 38 and the turbine 39 rotate. Along with the rotation, air in the atmosphere (indicated by a dashed line arrow in FIG. 6) is taken in by the compressor 38 and compressed. The compressed air (indicated by solid arrows in FIG. 6) is mixed with fuel (for example, city gas, etc.) and
Burned at zero. The combustion gas (indicated by a dotted arrow in FIG. 6) rotates the turbine 39 and exchanges heat with the compressed gas in the regenerative heat exchanger 41 to be exhausted to the atmosphere.

When the turbine 39 rotates at a high speed, the output shaft 19 rotates at a high speed. The high speed rotation of the output shaft 19 is reduced through the speed reducer 1 and transmitted to the high speed generator 3.

The high-speed generator 3 is, as shown in FIG.
A permanent magnet rotor 42 fixed to the input shaft 24,
And a stator 43. When the high-speed rotation of the gas turbine 2 is reduced through the speed reducer 1 and transmitted to the input shaft 24, the permanent magnet rotor 42 rotates to generate electric power.

(Another Use Example of Load Device) FIGS. 9 and 1
0 is an explanatory diagram showing another example of use of the load device. FIG. 9 shows an axial flow pump 44 as a load device. FIG.
0 is a marine propulsion screw 45 as a load device. In addition, as the load device, for example, there is an underwater propulsion screw such as an underwater vehicle.

[0062]

As is apparent from the above description, according to the speed reducer according to the present invention (claim 1), the speed is reduced from about 60,000 to about 130,000 rpm to about 10,000 to about 20,000 rpm by the single-stage helical parallel gear. Is done. Since the frequency of about 10,000 to about 20,000 rpm is higher than the audible range, it is inaudible to humans. In addition, with two-stage planetary traction, about 10,000 to about 20,000r
pm to about 3000-5000 rpm.
The frequency of about 3000 to about 5000 rpm is in the audible range, but does not become noise due to the characteristics of the planetary traction. Therefore, low noise efficiency is obtained.

On the other hand, according to the speed reducer according to the present invention (claim 1), a large speed reduction efficiency cannot be obtained by the two-stage planetary traction.
Great deceleration efficiency can be obtained. By the combination (hybrid) of the one-stage helical parallel gear and the two-stage planetary traction, a predetermined deceleration efficiency can be obtained in total.

Further, according to the speed reducer according to the present invention (claim 2), since the projection is provided at a portion of the ring roller that comes into contact with the plurality of planetary rollers, the ring roller on the concave side and the convex surface are provided. Although the surface pressure between the plurality of planetary rollers on the side is small, the surface pressure between the ring roller and the plurality of planetary rollers is increased by the protrusion. As a result, the surface pressure of the plurality of planetary rollers on the convex side as well as the surface pressure of the sun roller on the convex side having a large surface pressure, and the surface pressure of the ring roller and the plurality of planetary rollers are maintained in balance. . For this,
A predetermined deceleration efficiency can be obtained, and a low noise effect can be obtained.

According to the speed reducer according to the present invention (claim 3), the bearing of the input shaft of the one-stage speed reduction mechanism is constituted by an angular ball bearing, and a spring action is applied to the angular ball bearing in the axial direction. In the no-load state, the angular action ball bearing does not run idle due to the spring action of the spring. As a result, the life of the angular contact ball bearing can be maintained long. On the other hand, in the load state, even when thermal expansion occurs in the angular ball bearing when the input shaft of the one-stage reduction mechanism rotates at high speed, the thermal expansion can be absorbed by the spring action of the spring. .
As a result, seizure of the angular ball bearing is prevented.

Further, according to the speed reducer according to the present invention (claim 4), the jet nozzle for jetting the lubricating oil to the spline side, and the lubricating oil jet jetted from the jet nozzle is reflected once on the spline side. And a supply path through which lubricating oil in the lubricating oil reservoir is supplied to the meshing engagement portion between the spline and the coupling due to the centrifugal force of the high-speed rotation of the shaft. By utilizing the centrifugal force of the high-speed rotating shaft, it is possible to reliably supply the lubricating oil to a portion where the spline and the coupling also rotate at a high speed and which require lubricating oil.

[Brief description of the drawings]

FIG. 1 is a partial longitudinal sectional view showing an example of an embodiment of a speed reducer of the present invention.

FIG. 2 is a view taken along line II-II in FIG.

FIG. 3 is a partial longitudinal sectional view showing a modification of the ring roller of the two-stage planetary traction.

FIG. 4 is a partial longitudinal sectional view showing a structure of a bearing of an input shaft of a single-stage helical parallel gear.

FIG. 5 is an enlarged sectional view of a portion V in FIG. 1 showing a lubricating oil supply mechanism of the spline coupling mechanism.

FIG. 6 is an explanatory diagram showing operations of a micro gas turbine and a high-speed generator.

FIG. 7 is a block diagram showing operations of the micro gas turbine and the high-speed generator.

FIG. 8 is an explanatory diagram showing a case where the load device is a high-speed generator.

FIG. 9 is an explanatory diagram showing a case where the load device is an axial flow pump.

FIG. 10 is an explanatory diagram showing a case where the load device is a marine propulsion screw.

[Explanation of symbols]

 Reference Signs List 1 speed reducer 2 micro gas turbine (drive unit) 3 high-speed generator (load unit) 4 casing 5 one-stage helical parallel gear 6 two-stage planetary traction 7, 8, 12, 18 combined angular ball bearing 9 input shaft DESCRIPTION OF SYMBOLS 10 Input gear 11 Cylindrical roller bearing 13 Output shaft 14 Output gear 15 Sun roller 16 Planetary roller 17 Ring roller 19 Output shaft 20 Spline coupling mechanism 21 Oil seal 22 One stage helical parallel gear storage space 23 Two stage planet Traction storage space 24 Input shaft 25 Projection 26 Spring 27 Oil damper 28, 29 Spline 30 Coupling 31 Lubricating oil supply mechanism 32 Lubricating oil 33 Jet nozzle 34 Lubricating oil reservoir 35 Mesh fitting portion 36 Supply path 37 High-speed bearing 38 Compressor 39 Turbine 40 Combustor 41 Regeneration heat exchange Exchanger 42 Permanent magnet type rotor 43 Stator 44 Axial flow pump 45 Propulsion screw for boat

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F16H 57/02 301 F16H 57/02 301D 57/04 E 57/04 J F16D 1/02 E (72) Invention Person: Shiro Yoshida 3000, Tana, Sagamihara-shi, Kanagawa Prefecture, Mitsubishi Heavy Industries, Ltd. ) Inventor Kimiki Kirihara 3000 Tana, Sagamihara-shi, Kanagawa F.M.T.I. AA31 AA42 AA60 AB01 AB16 AC01 BA26 CG95 3J063 AA23 AA40 AB02 AB35 AC01 BA11 CA01 CB13 CB36 CB41 CD02 CD63 XD03 XD14 XD22 XD42 XE15 XF14 X F16

Claims (4)

[Claims] 1. A speed reducer for reducing a high-speed rotation of a drive device to a low-speed rotation via a two-stage reduction mechanism and transmitting the reduced speed to a load device side, comprising: a one-stage helical parallel gear; A speed reducer comprising traction. 2. The planetary traction includes: an input-side sun roller; a plurality of planetary rollers which are in contact with the sun roller and rotate by rotation of the sun roller; An output-side ring roller that is pressed by a roller and rotates with the rotation of the plurality of planetary rollers, and a portion of the ring roller that presses against the plurality of planetary rollers has a surface. The speed reducer according to claim 1, wherein a protrusion for increasing pressure is provided. 3. A reduction gear for reducing the high-speed rotation of a drive device to a low-speed rotation via a plurality of stages of reduction mechanisms and transmitting the reduced rotation to a load device, wherein the bearing of the input shaft of the one-stage reduction mechanism has an angular ball. A speed reducer comprising a bearing, wherein the angular ball bearing is provided with a spring acting in the axial direction. 4. A speed reducer for reducing the high-speed rotation of a drive device to a low-speed rotation via a plurality of stages of speed reduction mechanisms and transmitting the reduced speed to a load device side, wherein the input shaft of the one-stage speed reduction mechanism and the drive device A spline is fixed to each of the output shafts, and a spline coupling is meshed with the spline on the input shaft side and the spline on the output shaft side, respectively. And, in the connected reducer, a jet nozzle for jetting lubricating oil to the spline side, and a lubricating oil reservoir in which the lubricating oil jet jetted from the jet nozzle is temporarily reflected and accumulated on the spline side, A supply path through which lubricating oil in the lubricating oil reservoir is supplied to a meshing engagement portion between the spline and the spline coupling by centrifugal force of high-speed rotation of the shaft; A speed reducer comprising: