JP2002233102A - Support structure of rotor for high-speed rotating electric machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further suppress the vibration of a rotor, when it is rotated at a high speed, and prevent the corrosion of a resin flange part of a stator by lubricating oil shaken off from an oil thrower. SOLUTION: The lubricating oil is fed, in relation to between a rear side bearing 123R and a rear side retainer 122R, between a rear side preload member 128 and the rear side retainer 122R, between a front side bearing 123F and a front side retainer 122F, and between a front side preload member 21 and the front side retainer 122F. The rotor 108 is pressed to an inner side in its thrust direction by a coil spring 129 and a superposed plate spring 22. In addition, the lubricating oil, shaken off by the front side oil thrower 125 to directly intrude into a front side lubricating oil jet nozzle 127F, is made so as to surely collide against its sidewall of a lubricating oil jet nozzle 127F, the diameter of the front side oil thrower 125F, the radius of curvature of its internal wall of a front-side flange 121F, and the diameter and length or the like of the front side lubricating oil jet nozzle 127F are determined. At this point, even a rear side lubricating oil jet nozzle 127R is similarly determined.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotor support structure for a high-speed rotating electric machine in which a rotor rotates at a high speed in a gas turbine engine or the like.

[0002]

2. Description of the Related Art Conventionally, as a high-speed rotating electric machine for rotating a rotor in a gas turbine engine, for example, there is a high-speed generator 101 shown in a sectional view of FIG. Therefore, here, the high-speed generator 101 of FIG. 4 will be described. As shown in FIG. 4, in the high-speed generator 101, the casing 102
Is mounted in a state where a cylindrical stator 107 is housed therein.
The rotor 108 is inserted.

[0003] In this regard, the stator 107 has a structure in which the conductive wire of the coil 105 is wound between the teeth of the laminated silicon steel sheets 103 which are superposed, and is fixed in a vacuum state by an epoxy compound resin. In particular, in the stator 107, the bent portion 211 of the coil 105 that protrudes from both edge portions 110 of the housing 109 is also hardened in a vacuum state by a resin containing epoxy, thereby forming a resin flange portion 212. ing.

On the other hand, the rotor 108 is formed by fixing a permanent magnet provided on the peripheral surface of a shaft by covering it with a metal tube, and includes a front bearing 123F (corresponding to a "second bearing") and a rear bearing 123R. (Corresponding to the “first bearing”). That is, as shown in FIG. 4, the front retainer 122F (corresponding to the "second retainer") holding the front bearing 123F is fixed to the front flange 121F (corresponding to the "second flange"). The front flange 121F is bolted to the front end surface of the casing 102, so that the front end of the rotor 108 (corresponding to "the other end of the rotor") is rotatably supported.

A rear retainer 122R (corresponding to a "first retainer") holding a rear bearing 123R is fixed to a rear flange 121R (corresponding to a "first flange"). Rear flange 1
The rear end of the rotor 108 (corresponding to “one end of the rotor”) is rotatably supported by the 21R being bolted to the rear end surface of the casing 102.

In particular, the rear bearing 123R is bolted to the rear preloading member 128 (corresponding to the "first preloading member") abutting the rear bearing 123R and the rear flange 121R. Between the lid 130
Coil spring 129 (corresponding to "first spring member")
, An external force of about 250 N is applied to the inner side in advance in the thrust direction of the rotor 108. This mainly suppresses the vibration of the rotor 108 in the thrust direction.

Further, between the front retainer 122F and the front bearing 123F, the front retainer 122F
The lubricating oil is supplied through the oil hole of (1), and an oil film having a thickness of about 0.02 mm is formed, thereby providing a film damper that exerts a vibration damping effect by a squeeze action. Also,
Similarly, the rear retainer 122R and the rear bearing 1
23R, and also between the rear retainer 122R and the rear preload member 128, lubricating oil is supplied through the oil hole of the rear retainer 122R to form an oil film having a thickness of about 0.02 mm. As a result, a film damper that exerts a vibration damping effect by a squeeze action is provided. Thus, radial vibration of the rotor 108 is mainly suppressed.

Accordingly, in the high-speed generator 101 shown in FIG. 4, by connecting the front end of the rotor 108 to the output shaft of the gas turbine engine, high-speed rotation of the rotor 108 can be performed with low vibration.

However, at this time, the wind pressure generated by the high-speed rotation of the rotor 108 may make it impossible to effectively feed the lubricating oil to the bearings of the front bearing 123F and the rear bearing 123R. At 124F, the lubricating oil is injected into the bearing portion of the front bearing 123F and the rear jet nozzle 1
Forcible lubrication is performed by injecting lubricating oil into the bearing portion of the rear bearing 123R at 24R.

For this reason, the lubricating oil sprayed from the front jet nozzle 124F and the rear jet nozzle 124R forms a mist and fills the inside of the casing 102. However, the lubricating oil condensed and liquefied above the inner wall of the front flange 121F,
After being collected in the groove 126F provided on the inner wall of the casing 102, it flows down to the bottom of the casing 102 and is discharged from the lubricating oil discharge port 131 provided on the bottom of the casing 102.
Similarly, the lubricating oil condensed and liquefied above the inner wall of the rear flange 121R is also collected in the groove 126R provided on the inner wall of the rear flange 121R, and then flows down to the bottom of the casing 102. Is discharged from a lubricating oil discharge port 131 provided on the bottom surface of the casing 102. Therefore, the lubricating oil liquefied from the mist does not adhere to the rotor 108 rotating at high speed.

Further, the liquid lubricating oil jetted from the front jet nozzle 124F and passed through the bearing portion of the front bearing 123F is shaken off by the centrifugal force of the front oil thrower 125F attached to the rotor 108, and is applied to the front flange 121F. After being ejected from the provided front lubricating oil outlet 127F, it flows down to the bottom of the casing 102 and is discharged from the lubricating oil outlet 131 provided on the bottom of the casing 102. Also, the rear jet nozzle 1
The same applies to the liquid lubricating oil injected from the 24R and passed through the bearing portion of the rear bearing 123R.
After being shaken off by the centrifugal force of the rear oil thrower 125R attached to the rear side and ejecting from the rear lubricating oil outlet 127R provided on the rear flange 121R, the casing 1
02 flows down to the bottom surface of the casing 102 and is discharged from a lubricating oil discharge port 131 provided on the bottom surface of the casing 102. Therefore, the liquid lubricating oil does not adhere to the rotor 108 rotating at high speed.

Therefore, in the high-speed generator 101 shown in FIG. 4, between the rotor 108 and the stator 107, the liquid lubricating oil does not become a resistance to the high-speed rotation of the rotor 108, and the liquid lubricating oil is Since there is no possibility of carburizing and sticking due to the frictional heat of the high-speed rotation of 108, torque fluctuations and output fluctuations do not occur.

The front bearing 123F and the rear bearing 123R are angular bearings. Also,
Casing 102, front flange 121F, rear flange 121R, front retainer 122F, rear retainer 1
The material of 22R is a casting (FCD500).

[0014]

However, in the high-speed generator 101 shown in FIG. 4, vibration noise often occurs during operation. For example, when the rotation speed of the rotor 108 is 800
When a durability test was performed at 00 rpm, the operation time was 100
0 to 2000 hours of vibration of the rotor 108 in the radial direction of 3 kHz or less (only primary and secondary vibration components)
The results shown in FIG. 5 were obtained by measuring. Further, for example, when the rotation speed of the rotor 108 is
When the thrust direction vibration of the rotor 108 was measured by an electric method when the operation was performed for m, the results shown in FIG. 6 were obtained. In FIG. 6, the rotor 1 has six cycles of the wave curve.
08, one rotation, and each maximum value (or each minimum value) of the wave curve represents the position of the end face of the rotor 108. At this time, the rotor 108 About 365Hz with amplitude of about 0.16mm
That is, the vibration was performed.

The present invention has been made in order to solve the above-described problems, and it is a first object of the present invention to provide a rotor support structure for a high-speed rotating electric machine in which vibration of the rotor during high-speed rotation is further suppressed. Make it an issue.

In the high-speed generator 101 shown in FIG. 4, the lubricating oil that has been shaken off by the centrifugal force of the front oil thrower 125F gushes out from the front lubricating oil outlet 127F of the front flange 121F. In some cases, the resin flange 212 may be dug out by hitting the resin flange 212. Similarly, the lubricating oil that has been shaken off by the centrifugal force of the rear oil thrower 125R spouts vigorously from the rear lubricating oil outlet 127R of the rear flange 121R. The collision may cause the resin flange portion 212 to be dug out.

Accordingly, the present invention has been made to solve the above-mentioned problem, and has prevented the resin flange portion of the stator from being eroded by the lubricating oil shaken off by the centrifugal force of the oil thrower. A second object is to provide a rotor support structure for a high-speed rotating electric machine.

[0018]

Means for Solving the Problems According to a first aspect of the present invention, there is provided a rotor provided in a casing, and a first bearing rotatably supporting one end of the rotor. A second bearing rotatably supporting the other end of the rotor, a first retainer supporting the first bearing, a second retainer supporting the second bearing, and the first retainer being fixedly mounted. A first flange attached to the casing, a second flange fixed to the second retainer, and a second flange attached to the casing.
A flange, a first preload member that presses the first bearing inward in the thrust direction of the rotor, and a first preload member that urges the first preload member inward in the thrust direction of the rotor.
A spring member, between the first retainer and the first bearing, between the first retainer and the first preload member, and between the second retainer and the second bearing. In a rotor support structure of a high-speed rotating electric machine that feeds lubricating oil, a second preload member that presses the second bearing inward in a thrust direction of the rotor, and presses the second preload member inward in a thrust direction of the rotor. And a second spring member, wherein lubricating oil is fed between the second retainer and the second preload member.
According to a second aspect of the present invention, there is provided the rotor support structure of the high-speed rotating electric machine according to the first aspect, wherein the second preload member is a leaf spring.

In the rotor supporting structure for a high-speed rotating electric machine according to the present invention having such features, the first preload for pressing the first bearing is provided between the first bearing and the first retainer which rotatably supports one end of the rotor. Lubricating oil is fed between the member and the first retainer, and lubricating oil is fed between the second bearing and the second retainer which rotatably supports the other end of the rotor. The lubricating oil is also supplied between the second preload member that presses the second bearing and the second retainer.

That is, in the rotor support structure of the high-speed rotating electric machine according to the present invention, the lubricating oil is also supplied between the second preload member for pressing the second bearing that supports the other end of the rotor and the second retainer. Since a film damper that exerts a vibration damping effect by squeezing action is newly provided at the other end of the rotor, new damping is added to the radial vibration system of the rotor. That is, at both ends of the rotor, the film dampers exhibiting the vibration damping effect by the squeezing action are provided substantially uniformly, so that the unbalance of the vibration system of the rotor in the radial direction is reduced, and Accordingly, radial vibration of the rotor during high-speed rotation can be further suppressed.

In the rotor supporting structure for a high-speed rotating electric machine according to the present invention, the first spring member presses the first bearing inward in the thrust direction of the rotor via the first preload member, and the second preload member is connected to the first preload member. Through the second spring member
The bearing is pressed inward in the thrust direction of the rotor. In other words, the first spring member and the second spring member face inward and press the rotor in the thrust direction, so that the vibration system of the rotor in the thrust direction is formed. Since the spring constant is reduced, the vibration of the rotor in the thrust direction during high-speed rotation can be further suppressed.The natural frequency of the vibration system of the rotor in the thrust direction also decreases, and the resonance of the rotor in the thrust direction is reduced. Since the transition is made to the rotation range, the resonance phenomenon in the thrust direction of the rotor during high-speed rotation (during rated operation) can be avoided.

Further, the fact that the first spring member and the second spring member face inwardly and press the rotor in the thrust direction can stabilize the position of the rotor in the thrust direction and reduce the impact due to the vibration of the rotor in the thrust direction. Is further reduced, so that the life of the first bearing, the second bearing, and the like is improved.

Further, since the leaf spring has a damper function, in the rotor supporting structure of the high-speed rotating electric machine according to the present invention, if the second preload member is a leaf spring, a new vibration system for the rotor in the thrust direction is provided. Since damping can be added, vibration in the thrust direction of the rotor during high-speed rotation can be further suppressed.

According to a third aspect of the present invention, there is provided the rotor support structure for a high-speed rotating electric machine according to the first or second aspect, wherein the first retainer is press-fitted into the first flange and fixed. In addition, the second retainer is press-fitted into the second flange and fixed.

That is, in the rotor support structure of the high-speed rotary electric machine according to the present invention, if the first retainer is press-fitted into the first flange and fixed, and the second retainer is press-fitted into the second flange, the second retainer is fixed. The relative friction between the first retainer and the first flange acts as a Lanchester damper against the vibration of the first flange, and the relative friction between the second retainer and the second flange acts as a Lanchester damper against the vibration of the second flange. In addition, the vibration of the second flange can be suppressed, and the vibration of the rotor during high-speed rotation can be further suppressed.

According to a fourth aspect of the present invention, there is provided a stator provided with a resin flange protruding from an edge of a housing, and a stator inserted into a hollow portion of the stator. Rotor, a bearing supporting the rotor, a flange supporting the bearing via a retainer, an oil thrower fixed to the rotor inside the bearing and included in the flange, and A rotor support structure for a high-speed rotating electrical machine having a perforated lubricating oil outlet, and for supplying lubricating oil by jet injection to the bearing, in which the oil thrower scatters in a circumferential direction through the bearing. After the lubricating oil collides with the inner wall of the flange or the side wall of the lubricating oil outlet, flows out from the lubricating oil outlet. There.

In the rotor support structure for a high-speed rotating electric machine according to the present invention having such features, the inside of the flange is
The bearing is supported by a retainer, and lubricating oil is sent to the bearing by jet injection. The lubricating oil that has been jet-jetted and passed through the bearing flows along the rotor supported by the bearing, and is scattered in the circumferential direction of the oil thrower by being shaken off by the centrifugal force of the oil thrower. I do. At this time, the lubricating oil scattered in the circumferential direction of the oil thrower once collides with the inner wall of the flange, and then flows along the inner wall of the flange and the side wall of the lubricating oil outlet of the flange. Or after colliding with the side wall of the lubricating oil outlet of the flange, flows along the side wall of the lubricating oil outlet and flows out of the lubricating oil outlet.

That is, in the rotor support structure of the high-speed rotating electric machine according to the present invention, the lubricating oil scattered in the circumferential direction of the oil thrower once collides with the inner wall of the flange, and thereafter the lubricating oil outlet of the inner wall of the flange and the flange. Flow along the side wall of the lubricating oil outlet and
After once colliding with the side wall of the lubricating oil jet port of the flange, it flows along the side wall of the lubricating oil jet port and flows out of the lubricating oil jet port. The momentum is weakened, and even if it hits the resin flange of the stator, such resin flange is not dug out, so the lubricating oil shaken off by the centrifugal force of the oil thrower erodes the resin flange of the stator. Can be prevented.

According to a fifth aspect of the present invention, there is provided a rotor supporting structure for a high-speed rotating electric machine according to any one of the first to fourth aspects, wherein the rotor is rotated at a high speed by a gas turbine engine. It is characterized.

In particular, if the rotor is rotated at a high speed in a gas turbine engine, the problem of erosion of the rotor and erosion of the resin flange of the stator due to the high-speed rotation of the rotor tends to be extremely large. In the rotor support structure of the high-speed rotating electric machine according to the present invention, the above-described effects can be significantly exerted as long as the rotor is rotated at a high speed by the gas turbine engine.

The high-speed rotating electric machine having the rotor support structure of the high-speed rotating electric machine according to the present invention includes a high-speed generator and a high-speed electric motor.

[0032]

Embodiments of the present invention will be described below with reference to the drawings. The rotor support structure of the high-speed rotating electric machine according to the present embodiment mainly includes the periphery of the front bearing 123F and the front lubrication of the front flange 121F in the rotor support structure of the high-speed generator 101 shown in FIG. The oil outlet 127F and the rear lubricating oil outlet 127R of the rear flange 121R are modified. Therefore,
The outline of the high-speed generator including the rotor support structure of the high-speed rotating electric machine according to the present embodiment is the same as that of the high-speed generator 101 of FIG. 4 described in the section of the related art, and thus the detailed description thereof will be omitted. The reference numerals in FIG. 4 used in the column of the related art are also used in the description of this column.

As shown in FIG. 1, in the high-speed generator 1 having the rotor support structure of the high-speed rotating electric machine according to the present embodiment,
The front retainer 122F is press-fitted into the front flange 121F by shrink fitting or the like and fixed.
The rear retainer 122R is press-fitted and fixed to the rear flange 121R by shrink fitting or the like.

The front preload member 21 (corresponding to the "second preload member") is brought into contact with the outside of the front bearing 123F, and the leaf spring 22 (the "second
Spring material)),
An external force of about 250 N is applied to the inside in advance in the thrust direction of the rotor 108.

Further, lubricating oil is supplied between the front retainer 122F and the front preload member 21 through an oil hole of the front retainer 122F to form an oil film having a thickness of about 0.02 mm, thereby providing a squeezing effect. A new film damper has been added to provide a vibration damping effect.

On the other hand, as shown in FIG.
Even if the lubricating oil L which is shaken off by the centrifugal force of the front oil thrower 125F and scattered in the tangential direction of the front oil thrower 125F directly enters the front lubricating oil outlet 127F, the front lubricating oil jet is It is designed to always hit the side wall of the outlet 127F, and from this viewpoint,
Diameter of front oil thrower 125F, front flange 12
The radius of curvature of the inner wall of 1F, the diameter and length of the front lubricating oil jet 127F, and the like are determined.

In the same manner, the rear flange 121R
Even if the lubricating oil L that is shaken off by the centrifugal force of the rear oil thrower 125R and scatters in the tangential direction of the rear oil thrower 125R directly enters the rear lubricating oil jet 127R, It is designed so that it always hits the side wall of the lubricating oil outlet 127R. From this viewpoint, the diameter of the rear oil thrower 125R, the radius of curvature of the inner wall of the rear flange 121R, and the diameter of the rear lubricating oil outlet 127R And length are determined.

FIG. 3 shows the front oil thrower 125.
Front oil thrower 125F shaken off by centrifugal force of F
Of the lubricating oil scattered in the tangential direction, the one that does not directly enter the front lubricating oil outlet 127F is not described, but the lubricating oil collides with the inner wall of the front flange 121F and the inner wall of the front flange 121F. After flowing along the front lubricating oil jet 127F.

Similarly, FIG. 3 shows that among the lubricating oil that is shaken off by the centrifugal force of the rear oil thrower 125R and scatters in the tangential direction of the rear oil thrower 125R, the lubricating oil is discharged to the rear lubricating oil outlet 127R. Although not described, the lubricating oil collides with the inner wall of the rear flange 121R, flows along the inner wall of the rear flange 121R, and then enters the rear lubricating oil outlet 127F. .

As described above, the rotor structure of the high-speed rotating electric machine of the present embodiment provided in the high-speed generator 1 of FIG. 1 (hereinafter, referred to as “the rotor supporting structure of the high-speed generator 1 of the present embodiment”).
In FIG. 1, as shown in FIG. 1, a rear bearing 123R that supports the rear end of the rotor 108 and a rear retainer 12
2R and between the rear preloading member 128 that presses the rear bearing 123R and the rear retainer 122R, and a front bearing 123F and a front retainer that support the front end of the rotor 108. 122F
The lubricating oil is supplied between the front preloading member 21 and the front retainer 122F which press the front bearing 123F.

That is, “the high-speed generator 1 of the present embodiment
Of the rotor supporting structure, the front preload member 2 that presses the front bearing 123F that supports the front end of the rotor 108
The lubricating oil is also fed into between the first retainer 122F and the front retainer 122F, so that at the front end of the rotor 108, a film damper exhibiting a vibration damping effect by a squeeze action is newly provided. That is, new attenuation is added to the vibration system of the rotor 108 in the radial direction.

Further, a new damping is added to the vibration system of the rotor 108 in the radial direction.
08, the thickness formed between the rear bearing 123R and the rear retainer 122R is about 0.0
The thickness formed between the film damper of about 2 mm and the rear preloading member 128 and the rear retainer 122R is about 0.5 mm.
There is a film damper of about 02 mm, and the rotor 10
8 has a thickness of about 0.02 between the front bearing 123F and the front retainer 122F.
mm, and the thickness formed between the front side preload member 21 and the front side retainer 122F is about 0.02 mm.
mm, that is, the film dampers exhibiting the vibration damping effect by the squeezing action are provided almost uniformly at both ends of the rotor 108, so that the vibration of the rotor 108 in the radial direction System imbalance is reduced.

Thus, the rotor 108 at the time of high-speed rotation is
In the radial direction can be further suppressed. Specifically, for example, the number of rotations of the rotor 108 is 80,000.
When an endurance test at rpm was performed, the operation time was 2,000 to 2,000.
When the vibration of the rotor 108 in the radial direction of 3 kHz or less (only the primary and secondary vibration components) is measured for 3500 hours, the result shown in FIG. 2 is obtained. FIG. 2 shows the measurement results (operation time of 1000 to 1000) in the rotor support structure of the high-speed generator 101 of FIG.
Although the measurement point of 2000 hours (the measurement point in FIG. 5) is also shown, when compared with these, the vibration of the rotor 108 in the radial direction of 3 kHz or less (only the primary and secondary vibration components) The size has been reduced by half.

In the “rotor support structure of the high-speed generator 1 according to the present embodiment”, as shown in FIG. 1, the coil spring 129 is connected to the rear bearing 1 via the rear preload member 128.
23R is pressed inward in the thrust direction of the rotor 108, and the leaf spring 22
Presses the front bearing 123F in the thrust direction of the rotor 108 in the thrust direction. That is, the coil spring 129 and the leaf spring 22 face inward to press the rotor 108 in the thrust direction. Since the spring constant of this vibration system is reduced, vibration in the thrust direction of the rotor 108 during high-speed rotation can be further suppressed.

More specifically, for example, when the rotation speed of the rotor 108 is 70,000 rpm,
When the vibration in the thrust direction of FIG. 8 is measured by an electric method, the measurement result in the rotor support structure of the high-speed generator 101 in FIG.
6, the maximum value (or each minimum value) of the wave curve, which means the position of the end face of the rotor 108, undulates so as to meander up and down. “The rotor of the high-speed generator 1 according to the present embodiment is Although not shown in the measurement results of the “support structure”, each maximum value (or each minimum value) of the wave curve indicating the position of the end face of the rotor 108 is substantially horizontal.
At this time, it can be said that the vibration width of the rotor 108 in the thrust direction has become so small that it cannot be measured. In the measurement of the “rotor support structure of the high-speed generator 1 according to the present embodiment”, no vibration sound was heard.

In the "rotor support structure of the high-speed generator 1 according to the present embodiment", as shown in FIG. 1, the coil spring 129 and the leaf spring 22 face inward to move the rotor 108 in its thrust direction. By pressing
The natural frequency of the vibration system of the rotor 108 in the thrust direction decreases, and the resonance in the thrust direction of the rotor 108 shifts to the low-speed rotation range. Therefore, the resonance phenomenon in the thrust direction of the rotor 108 during high-speed rotation (during rated operation) is reduced. Can be avoided.

Further, the coil spring 129 and the leaf spring 2
When the rotor 108 faces the inside and presses the rotor 108 in the thrust direction, the position of the rotor 108 in the thrust direction is stabilized, and the impact due to the vibration of the rotor 108 in the thrust direction is further reduced. And the life of the rear bearing 123R and the like is improved.

In the "rotor support structure of the high-speed generator 1 according to the present embodiment", the leaf spring 22 is used as the "second preload member".
2 has a function of a damper, which can add new damping to the vibration system of the rotor 108 in the thrust direction, so that the vibration of the rotor 108 in the thrust direction during high-speed rotation can be further suppressed.

In the "rotor support structure of the high-speed generator 1 of the present embodiment", the rear retainer 122R is press-fitted into the rear flange 121R by shrink fitting or the like and fixed, and the front retainer 122F is fixed. Front flange 121
It is press-fitted into F with shrink fit and fixed. for that reason,
The relative friction between the rear retainer 122R and the rear flange 121R acts as a Lanchester damper against the vibration of the rear flange 121R, and the front retainer 122F
Friction between the front flange 121F and the front flange 121F
Since it acts as a Lanchester damper against the vibration of 21F, the rear flange 121R and the front flange 121F
Of the rotor 108 during rotation at high speed.
Vibration can be further suppressed.

In the "rotor support structure of the high-speed generator 1 according to the present embodiment", as shown in FIG. 1, a front retainer 122F supports a front bearing 123F inside a front flange 121F and a front bearing 123F. Lubricating oil is sent to the bearing portion of 123F by jet injection of the front jet nozzle 124F. The lubricating oil that has been jetted by the front jet nozzle 124F and passed through the front bearing 123F is
The fluid flows along the rotor 108 pivotally supported by 3F, and is further scattered in the tangential direction of the front oil thrower 125F by being shaken off by the centrifugal force of the front oil thrower 125F as shown in FIG.

At this time, of the lubricating oil scattered in the tangential direction of the front oil thrower 125F, the front flange 121
The lubricating oil L that has directly entered the front lubricating oil outlet 127F of F collides with the side wall of the front lubricating oil outlet 127F, and then flows along the side wall of the front lubricating oil outlet 127F, and the front side It flows out from the lubricating oil outlet 127F toward the bottom surface of the casing 102. Although not shown, the remaining lubricating oil once collides with the inner wall of the front flange 121F, and then the inner wall of the front flange 121F and the front lubricating oil outlet 12 of the front flange 121F.
It flows along the side wall of 7F and flows out from the front lubricating oil outlet 127F toward the bottom surface of the casing 102.

Similarly, as shown in FIG. 1, the rear retainer 12 is provided inside the rear flange 121R.
2R supports the rear bearing 123R, and the rear jet nozzle 1 is mounted on the bearing portion of the rear bearing 123R.
Lubricating oil is fed by 24R jet injection. Then, the lubricating oil jetted by the rear jet nozzle 124R and passing through the rear bearing 123R flows along the rotor 108 supported by the rear bearing 123R, and further, as shown in FIG. Side oil thrower 1
By being shaken off by the centrifugal force of 25R, the oil scatters in the tangential direction of the rear oil thrower 125F.

At this time, of the lubricating oil scattered in the tangential direction of the rear oil thrower 125R, the rear flange 121
The lubricating oil L that has directly entered the rear lubricating oil outlet 127R of R collides with the side wall of the rear lubricating oil outlet 127R, and then flows along the side wall of the rear lubricating oil outlet 127R. Then, the oil flows out from the rear lubricating oil outlet 127 </ b> R toward the bottom surface of the casing 102. Although not shown, the remaining lubricating oil once collides with the inner wall of the rear flange 121R, and then the inner wall of the rear flange 121R and the rear lubricating oil outlet 12 of the rear flange 121R.
It flows along the side wall of 7R and flows out from the rear lubricating oil outlet 127R toward the bottom surface of the casing 102.

That is, “the high-speed generator 1 of the present embodiment
Rotor support structure ", the front oil thrower 125F
Lubricating oil scattered in the tangential direction of the front flange 121F
Once colliding with the inner wall of the front flange 121F
Inner wall and front lubricating oil outlet 1 of front flange 121F
The lubricating oil which flows along the side wall of 27F and flows out from the front lubricating oil outlet 127F toward the bottom surface of the casing 102, or scatters in the tangential direction of the front oil thrower 125F as shown in FIG. The oil L once collides with the side wall of the front lubricating oil outlet 127F of the front flange 121F, and then flows along the side wall of the front lubricating oil outlet 127F, and the front lubricating oil outlet 127F.
It flows out from F toward the bottom surface of the casing 102.
Therefore, the casing 10
The lubricating oil flowing toward the bottom surface of the stator 2 has a weakened momentum, and the resin flange 212
(See FIG. 1), the resin flange 21
2 is not dug down, so that the resin flange portion 212 of the stator 107 can be prevented from being eroded by the lubricating oil shaken off by the centrifugal force of the front oil thrower 125F.

Similarly, the rear oil thrower 1
The lubricating oil scattered in the tangential direction of the 25R
After colliding with the inner wall of 21R, the rear flange 1
It flows along the inner wall of 21R and the side wall of the rear lubricating oil outlet 127R of the rear flange 121R and flows out from the rear lubricating oil outlet 127R toward the bottom surface of the casing 102, or as shown in FIG. As shown, the lubricating oil L scattered in the tangential direction of the rear oil thrower 125R once collides with the side wall of the rear lubricating oil outlet 127R of the rear flange 121R, and then the lubricating oil jet 12
It flows along the side wall of 7R and flows out from the rear lubricating oil outlet 127R toward the bottom surface of the casing 102. Accordingly, the lubricating oil flowing out from the rear lubricating oil outlet 127 </ b> R toward the bottom surface of the casing 102 is weakened, and even when the lubricating oil hits the resin flange 212 of the stator 107 (see FIG. 1), the resin Since the portion 212 is not dug, the resin flange portion 212 of the stator 107 can be prevented from being eroded by the lubricating oil shaken off by the centrifugal force of the rear oil thrower 125R.

When the rotor 108 is rotated at a high speed by the gas turbine engine, the vibration of the rotor 108 and the
However, in the "rotor supporting structure of the high-speed generator 1 according to the present embodiment", the rotor 108 is rotated at a high speed by a gas turbine engine. Therefore, the above-described effects (the effect of further suppressing the vibration of the rotor 108 during high-speed rotation, the resin of the stator 107 due to the lubricating oil L shaken off by the centrifugal force of the front oil thrower 125F and the rear oil thrower 125R) The effect of preventing the flange portion 212 from being eroded can be greatly exhibited.

It should be noted that the present invention is not limited to the above embodiment, and various changes can be made without departing from the gist of the present invention. For example, in the “rotor support structure of the high-speed generator 1 according to the present embodiment”, the rotor 108 is rotated at a high speed by the gas turbine engine. From the viewpoint of preventing the resin flange portion 212 of the stator 107 from being eroded by the lubricating oil L shaken off by the centrifugal force of the front oil thrower 125F and the rear oil thrower 125R, the driving source of the rotor 108 Need not be limited to gas turbine engines.

Further, the rotor supporting structure of the high-speed rotating electric machine of the present embodiment provided in the high-speed generator 1 can be provided not only in the high-speed generator but also in a high-speed motor. Similar effects can be obtained.

[0059]

According to the rotor support structure of the high-speed rotating electric machine of the present invention, the lubricating oil is also supplied between the second preload member for pressing the second bearing which supports the other end of the rotor and the second retainer. Since a film damper that exerts a vibration damping effect by squeezing action is newly provided at the other end of the rotor, new damping is added to the radial vibration system of the rotor. That is, at both ends of the rotor, the film dampers exhibiting the vibration damping effect by the squeezing action are provided substantially uniformly, so that the unbalance of the vibration system of the rotor in the radial direction is reduced, and Accordingly, radial vibration of the rotor during high-speed rotation can be further suppressed.

In the rotor support structure for a high-speed rotating electric machine according to the present invention, the first spring member presses the first bearing inward in the thrust direction of the rotor via the first preload member, and the second preload member is connected to the first preload member. Through the second spring member
The bearing is pressed inward in the thrust direction of the rotor. In other words, the first spring member and the second spring member face inward and press the rotor in the thrust direction, so that the vibration system of the rotor in the thrust direction is formed. Since the spring constant is reduced, the vibration of the rotor in the thrust direction during high-speed rotation can be further suppressed.The natural frequency of the vibration system of the rotor in the thrust direction also decreases, and the resonance of the rotor in the thrust direction is reduced. Since the transition is made to the rotation range, the resonance phenomenon in the thrust direction of the rotor during high-speed rotation (during rated operation) can be avoided.

Furthermore, the fact that the first spring member and the second spring member face inward and press the rotor in the thrust direction can stabilize the position of the rotor in the thrust direction, and reduce the impact due to the vibration of the rotor in the thrust direction. Is further reduced, so that the life of the first bearing, the second bearing, and the like is improved.

Further, since the leaf spring has a damper function, when the second preload member is a leaf spring in the rotor supporting structure of the high-speed rotating electric machine of the present invention, a new vibration system of the rotor in the thrust direction is provided. Since damping can be added, vibration in the thrust direction of the rotor during high-speed rotation can be further suppressed.

In the rotor support structure for a high-speed rotating electric machine according to the present invention, if the first retainer is press-fitted into the first flange and fixed, and the second retainer is press-fitted into the second flange, the second retainer is fixed. The relative friction between the first retainer and the first flange acts as a Lanchester damper against the vibration of the first flange, and the relative friction between the second retainer and the second flange acts as a Lanchester damper against the vibration of the second flange. In addition, the vibration of the second flange can be suppressed, and the vibration of the rotor during high-speed rotation can be further suppressed.

In the rotor support structure of the high-speed rotating electric machine according to the present invention, the lubricating oil scattered in the circumferential direction of the oil thrower once collides with the inner wall of the flange, and then the lubricating oil outlet of the inner wall of the flange and the flange. Flows along the side wall of the lubricating oil outlet, or once collides with the side wall of the lubricating oil outlet of the flange, and then flows along the side wall of the lubricating oil outlet to provide such lubrication. Since the lubricating oil flowing out of the lubricating oil outlet flows out from the oil spout, the momentum of the lubricating oil is weakened, and even if the lubricating oil hits the resin flange portion of the stator, the resin flange portion is not dug and cut off. Erosion of the resin flange portion of the stator by the lubricating oil shaken off by the centrifugal force of the thrower can be prevented.

In particular, when the rotor is rotated at high speed by the gas turbine engine, the vibration of the rotor and the erosion of the resin flange portion of the stator tend to be significantly increased due to the high speed rotation of the rotor. In the rotor support structure of the high-speed rotating electric machine according to the present invention, the above-described effects can be significantly exerted as long as the rotor is rotated at a high speed by the gas turbine engine.

[Brief description of the drawings]

FIG. 1 is a sectional view of a generator having a rotor support structure for a high-speed rotating electric machine according to the present invention.

FIG. 2 is a diagram showing, in comparison with FIG. 5, a result of measuring radial vibration of a rotor in a generator having a rotor support structure for a high-speed rotating electric machine according to the present invention.

FIG. 3 is a sectional view of a lubricating oil outlet of a flange in a generator including a rotor support structure of a high-speed rotating electric machine according to the present invention.

FIG. 4 is a cross-sectional view of a generator having a rotor support structure of a conventional high-speed rotating electric machine.

FIG. 5 is a view showing a result of measuring radial vibration of a rotor in a generator having a rotor support structure of a conventional high-speed rotating electric machine.

FIG. 6 is a view showing a result of measuring vibration in a thrust direction of a rotor in a generator having a rotor support structure of a conventional high-speed rotating electric machine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 High-speed generator 21 Front-side preload member 22 Laminated leaf spring 102 Casing 107 Stator 108 Rotor 109 Stator housing 110 Stator housing edge 121F Front-side flange 121R Rear-side flange 122F Front-side retainer 122R Rear-side retainer 123F Front-side bearing 123R Rear-side Bearing 128 Rear-side preload member 129 Coil spring 125F Front-side oil thrower 125R Rear-side oil thrower 127F Front-side lubricating oil outlet 127R Rear-side lubricating oil outlet 212 Resin flange portion of stator L Lubricating oil

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) H02K 3/44 H02K 3/44 B 5/173 5/173 AB (72) Inventor Hiroyuki Ogasawara Toyota, Aichi No. 1 Ichimoto-cho Toyota Motor Corporation Motomachi Plant F-term (reference) 3J012 AB07 AB20 BB03 FB10 HB02 3J101 AA03 AA42 AA54 AA62 CA07 CA17 FA01 FA31 GA26 5H604 BB04 BB14 CC01 CC05 DA15 DB01 5H605 AA04 BB03 CC05 CC05 DD05 CC05 DD EB21 EB25 EB39

Claims (5)

[Claims] A first bearing that supports one end of the rotor, a second bearing that supports the other end of the rotor, and a second bearing that supports the first bearing. A first retainer, a second retainer supporting the second bearing, a first flange to which the first retainer is fixed and attached to the casing, and a second flange to which the second retainer is fixed and attached to the casing. An attached second flange, a first preload member for pressing the first bearing inward in the thrust direction of the rotor, and a first spring member for urging the first preload member inward in the thrust direction of the rotor And wherein the first bearing is located between the first retainer and the first bearing.
In a rotor support structure of a high-speed rotating electric machine that feeds lubricating oil between a retainer and the first preload member and between the second retainer and the second bearing, the second bearing is moved in a thrust direction of the rotor. A second preload member that presses inward, and a second spring member that presses the second preload member inward in the thrust direction of the rotor, wherein lubrication is provided between the second retainer and the second preload member. A rotor support structure for a high-speed rotating electric machine, wherein oil is supplied. 2. The rotor support structure for a high-speed rotating electric machine according to claim 1, wherein the second preload member is a leaf spring. 3. The rotor support structure for a high-speed rotating electric machine according to claim 1, wherein the first retainer is press-fitted into the first flange and fixed, and the second retainer is fixed to the first flange. A rotor support structure for a high-speed rotating electric machine, wherein the rotor support structure is fixed by being press-fitted into a second flange. 4. A stator provided with a resin flange protruding from an edge of the housing, a rotor inserted into a hollow portion of the stator, a bearing supporting the rotor, and a bearing connected via a retainer. A supported flange, an oil thrower fixed to the rotor inside the bearing and internal to the flange, and a lubricating oil outlet bored in the flange, and jetted to the bearing by jet injection In the rotor support structure of a high-speed rotating electric machine that feeds lubricating oil, after the lubricating oil that has passed through the bearing and scattered in the circumferential direction of the oil thrower collides with the inner wall of the flange or the side wall of the lubricating oil outlet, And flowing out from the lubricating oil ejection port. 5. The rotor supporting structure for a high-speed rotating electric machine according to claim 1, wherein said rotor is rotated at a high speed by a gas turbine engine. Electric motor rotor support structure.