JP2002520995A - Two-pole synchronous machine with horizontal rotor and method of adjusting amplitude of double frequency resonant vibration in this synchronous machine - Google Patents

Abstract

(57) [Summary] In a two-pole synchronous machine with a horizontal rotor, the amplitude of the double rotation frequency resonance vibration can move horizontally, for example, in order to minimize the amplitude of the double rotation frequency resonance vibration. By raising and lowering the bearing legs (43) of the rotor bearing (4) with the wedges (45, 46), adjustment is made in relation to the vertically eccentric position setting of the rotor axis (21) in the stator bore (6). You.

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to the field of rotating electric machines, and more particularly to the suppression of resonance vibration of a horizontal rotor of a two-pole synchronous machine having a frequency corresponding to a double rotation frequency of a rotor.

A two-pole synchronous machine in which a rotor supported by a bearing device is arranged in a hole of a stator and a rotor axis is set in the hole of the stator (literature, AEG / Mitting (
Report)), 1956, pp. 93/94), the transverse anisotropy of the rotor, together with gravity, excites vibrations in the transverse direction, in particular in the vertical direction, and the frequency of the vibrations depends on the respective rotation of the rotor. Frequency equivalent to twice the frequency (German Patent Publication No. 126
2686, column 1). The excitation oscillation has one or more resonance ranges. In particular, in the case of a machine with variable rotational speed, its resonance frequency is usually located within the operating rotational speed range.

Conventionally, the amplitude of the resonance vibration at twice the rotation frequency of the rotor is determined by forming a slit extending perpendicularly to the axis of the rotor when the rotor is manufactured, and using the slit to provide the bending stiffness of the rotor at the pole face. Is usually controlled by reducing However, in this method, various influence factors on the amplitude and frequency of the resonance vibration, such as the structure of the rotor shaft, the shape of the pole pieces and the pole windings, and the material properties, are calculated by the complexity of their interaction. Since it is not precisely sought, only partial success is obtained. Furthermore, it is known that the vibration behavior of a multiply supported shaft system must be controlled by changing the spring constant and / or damping constant of its bearing (DE-A 25 01 2009, no. See pages 1 and 2.)

The object of the present invention is to provide a means, starting from a two-pole synchronous machine according to the preamble of the first claim, for further reducing the amplitude of the double-frequency resonant vibration of the rotor.

This problem is solved according to the invention in that the amplitude of the double-rotation frequency resonant oscillation is adjusted in relation to the setting of the position of the rotor axis in the stator bore that is vertically eccentric. In connection with this adjustment, starting from the average adjustment of the vertically eccentric position setting of the rotor in the stator bore, first the resonance of the rotor at twice the rotational frequency in various operating conditions (no load, full load). The amplitude of the vibration is measured,
Thereafter, in relation to the most disadvantageous measurement value (maximum vibration amplitude) in each case, the vertically eccentric position setting of the rotor is changed by a relative movement of the rotor axis with respect to the stator axis, followed by a "double rotation frequency resonance". It is advantageous if the "measurement of vibration amplitude" and "movement of the rotor axis" processes are repeated until the best adjustment is obtained, and that best adjustment is retained.

The means according to the invention for setting the eccentric position of the rotor axis in the vertical direction is such that in synchronous machines of this kind, in addition to the transverse cross-sectional anisotropy of the rotor, for radial forces of double rotation frequency, We start with the idea that a second excitation source exists. The second excitation source is one of the harmonic component of the rotor field generated by the rotor windings and one of the two eccentric fundamental fields, i.e., the additional harmonic component of the air gap field resulting from the eccentric arrangement of the rotor in the stator bore. It is caused by cooperation with This alternating force, acting on the rotor at twice the rotational frequency, acts in the opposite direction to the narrowest point in the air gap between the rotor and the stator, and always when the extremes of the magnetic field pass through the narrowest point. Reaches its maximum value. The amplitude of this alternating force is proportional to the air gap eccentricity. What is important for the measures according to the invention is that, when the rotor axis is normally located in the stator bore, the narrowest part of the air gap occurs below the rotor in a vertical plane (especially during no-load operation) and therefore The magnetic excitation has the same phase position as the gravitational excitation, so that both excitations are added. However, if the rotor is positioned such that the narrowest point of the air gap occurs above the rotor in a vertical plane, the two excitations interact and thereby at least partially cancel. Thus, the amplitude of the double frequency resonant vibration is adjusted by the vertical translation of the rotor axis and can be adjusted during operation of the machine. If the rotor is designed to be anisotropic in the longitudinal direction, the amplitude of the double-rotation frequency resonant oscillation can also be controlled, if necessary, by additionally tilting the rotor axis.

Since the magnitude of the magnetic force at the double rotation frequency depends on the magnitude of the excitation of the machine in addition to the air gap eccentricity, the amplitude of the resonance vibration at the double rotation frequency additionally changes the excitation of the rotor. Can also be adjusted. However, this method can only be used for fine tuning to minimize the amplitude of the resonance vibration.

The adjustment according to the invention of the vertically eccentric position setting of the rotor axis in the stator bore is performed by various structural means. Generally, this method requires a relative movement between the rotor bearing and the stator. When the rotor bearing and the stator are mounted independently of each other on a foundation frame or separate foundation boards, their relative movement is effected by vertical movement of the rotor bearing or the stator. For example, the movement of the rotor axis is performed by raising and lowering the bearing legs of the rotor bearing by a horizontally movable wedge. Another approach consists in utilizing two rotatable eccentrics, the outer eccentric of which is arranged on the bearing bracket or base frame of each rotor bearing, and the inner eccentric receives the bearing housing. Such moving means can also displace the rotor axis horizontally.

Another structural measure consists in mounting the bearing legs of the rotor bearing on the base frame or the floor plate, in such a way that the bearing legs can be lifted by push-up bolts, between the bearing legs and the floor plate. The final size of the lifting is fixed by the insertion of the shim plate,
Subsequently, the lifting bolt is loosened. The stator can be moved up and down in the same manner. In this case, mounting bolts are used to fix the bearing legs or stator legs on the base plate or foundation frame, which are formed as highly elastic extension bolts or equipped with a spring element below the bolt head. Is done.

The measures according to the invention described above also apply to rolling bearings, journal bearings and magnetic bearings. In a synchronous machine having a magnetic bearing, the rotor axis can be moved by controlling the magnetic force of the magnetic bearing.

In the following, the invention will be described in detail with reference to an embodiment shown in the drawings.

FIG. 1 schematically shows the basic structure of a two-pole synchronous machine. The synchronous machine comprises a stator 1 and a rotor 2 arranged on a base frame 3, the rotor 2 being arranged with its axis 21 horizontal and extending through a hole 6 in the stator 1. Both ends of the rotor shaft 8 are supported by bearing devices 4 and 5, respectively. These bearing devices 4
, 5 are similarly arranged on the base frame 3. The rotor 2 is placed in the hole 6 of the stator 1
It is arranged so that a gap 7 exists between the rotor 2 and the stator 1.

In order to minimize the amplitude of the double frequency resonant vibration in such a synchronous machine, the electrical and mechanical structure data must first be determined by calculation, on the one hand, in particular winding and slot wedges From the quantities that determine the anisotropy of the rotor 2, such as the cross-sectional area and the stiffness effect of the machine, and from the static air gap eccentricity and the excitation on the other hand,
The effect of the double rotation frequency on the occurrence of lateral rotor vibrations is calculated, and the ideal position of the rotor in the stator bore is determined to compensate for both excitation sources. This ideal positioning, including mainly the vertical eccentric arrangement of the rotor in the stator bore, is such that when the rotor is fitted into the stator, the bearing axes of the rotor bearings on both sides are correspondingly aligned with the axis of the stator bore. This is achieved by aligning. During a test run in various operating states of the synchronous machine, the gap size is determined, for example, by means of corresponding calipers, and the rotor is driven in a non-contact manner on the rotor shaft, e.g. A double rotation frequency oscillation is determined and adjusted in one or several passes to optimize the air gap eccentricity. For this purpose, it is necessary to move the rotor axis parallel in the vertical direction and possibly additionally tilt. This is done by raising and lowering the bearing legs of the rotor bearing or alternatively by raising and lowering the stator with respect to the rotor. A first embodiment for this is shown in FIGS.

In FIG. 2, a bearing device 4 mainly including a bearing stand 41, a bearing metal 42, and a bearing leg 43 is disposed on the base plate 3 by a support structure 44. Its support structure 44
Consists of two adjusting wedges 45, 46 which can be moved relative to one another by a turnbuckle 47, indicated by an axis. The lower surface of the bearing leg 43 is formed in a wedge shape, so that the wedge surface of the bearing leg 43 and the wedge surfaces of the adjusting wedges 45 and 46 come into contact with each other. The bearing 4 is lifted by tightening and pulling both adjusting wedges 45, 46.

In FIG. 3, two adjustment wedges 48, 49 are additionally provided on both adjustment wedges 45, 46. These adjustment wedges 48 and 49 are displaced and adjusted by the turnbuckle 50 at right angles to the tightening direction of the turnbuckle 47. These adjusting wedges 48, 49 cooperate with the wedge surfaces at the inner ends of the two adjusting wedges 45, 46 such that the two adjusting wedges 45, 46 are pushed away from each other, so that the bearing device 4 is lowered.

The adjusting wedges 45, 46 are also provided with a lateral guide 52 and a fixing element 51. When the bearing leg 43 is finally adjusted, the bearing leg 43 is fixed by a mounting bolt 53 extending through the elongated hole of the bearing leg 43 and the elongated holes of the adjustment wedges 45 and 46.

The support structure 44 is, in principle, an adjusting wedge 45 with a turnbuckle 47,
It can also be provided that the 46 is arranged longitudinally rather than at right angles to the rotor axis.

FIGS. 4 and 5 schematically show that the adjustment wedges 45, 46 have a flat wedge surface 54. 6 and 7, the adjustment wedges 55 and 56 have a keyway-shaped wedge surface 58.

In FIG. 8, the translation of the rotor axis in the vertical direction is performed by lifting and lowering the bearing device at both ends of the rotor by bolts 60 and 61 extending through the bearing legs 59. One bolt 60 is a push-up bolt for lifting the bearing feet, and the other bolt 61 is a retaining bolt formed as an extension bolt (similar to DE 1237387). When the bearing leg is lifted, the shim plate 62 is inserted and arranged between the bearing leg and the floor plate 3.

In the right part of FIG. 8, there is shown a retaining bolt 63 equipped with a spring element in the form of a disc spring 64 below the bolt head.

In FIG. 9, the movement of the rotor axis is performed by two rotatable eccentric wheels 65 and 66. The outer eccentric 66 is arranged on a bearing bracket 67 or a base frame, and the inner eccentric 65 receives a bearing 68. With the corresponding rotation of the two eccentrics 65, 66, the bearing 68 is not only raised and lowered but also moved laterally.

[Brief description of the drawings]

FIG. 1 is a schematic cross-sectional view of a two-pole synchronous machine of a rotor horizontal arrangement type.

FIG. 2 is a side view of a rotor bearing that can be moved vertically by a wedge-shaped element.

FIG. 3 is a plan view of an adjustment wedge of the rotor bearing in FIG. 2;

FIG. 4 is a side view of a different embodiment of the adjustment wedge.

FIG. 5 is a sectional view taken along the line VV in FIG. 4;

FIG. 6 is a side view of a further different embodiment of the adjustment wedge.

FIG. 7 is a sectional view taken along the line VII-VII in FIG. 6;

FIG. 8 is a side view of a different embodiment of the rotor bearing.

FIG. 9 is a diagram showing the basic configuration of a rotor bearing that can be adjusted by an eccentric wheel.

[Description of Signs] 1 Stator 2 Rotor 3 Base frame 4 Rotor bearing 6 Stator hole 21 Rotor axis 60 Push-up bolt 61 Stretch bolt 64 Spring element

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Rauf, Hartmut, Germany Day-12203 Berlin Holbeinstraße 20 F-term (Reference) 5H605 AA04 AA05 BB10 CC03 CC04 CC05 DD03 EA01 EA19 EA29 EA30 EB02 GG04 GG06 5H607 AA04 BB07 BB14 CC01 DD05 DD08 DD15 DD17 GG02 JJ05

Claims (11)

[Claims] 1. A stator comprising: a stator; a rotor horizontally disposed in a hole of the stator; both ends of the rotor are supported by bearing devices; a rotor axis is positioned inside the stator hole; In a two-pole synchronous machine in which the amplitude of the resonance vibration at a frequency corresponding to the frequency has a value as small as possible, the amplitude of the resonance vibration at the double rotation frequency is perpendicular to the rotor axis (2, 21) in the stator hole (6). Bipolar synchronous machine characterized in that it is adjusted in relation to a position setting eccentric in the direction. 2. The two-pole synchronous machine according to claim 1, wherein the amplitude of the resonance vibration at the double rotation frequency is adjusted by vertical translation of the rotor axis. 3. The two-pole synchronous machine according to claim 2, wherein the amplitude of the resonance vibration at the double rotation frequency is adjusted by the inclination of the rotor axis. 4. The method for adjusting the amplitude of resonance vibration at a double rotation frequency in a two-pole synchronous machine according to claim 1, wherein the rotor is vertically eccentric in a stator hole. Starting from an average adjustment of the rotor, the amplitude of the resonant vibration at twice the rotational frequency of the rotor is first measured in various operating conditions (no load, full load), and then the most disadvantageous measured value (maximum vibration amplitude) in each case The adjustment of the vertically eccentric position setting of the rotor is changed by the relative movement of the rotor axis (21) with respect to the stator axis, followed by the "measurement of the amplitude of the resonance oscillation at twice the rotational frequency" and The process of "moving the rotor axis" is repeated until the best adjustment is obtained, and the double rotation frequency is shared in the two-pole synchronous machine characterized in that the best adjustment is maintained. How to adjust the amplitude of vibration. 5. The method according to claim 4, wherein the amplitude of the double rotation frequency resonance oscillation is adjusted by changing the excitation of the rotor. 6. The wedges (45, 46) capable of horizontally moving the rotor axis.
5. The method as claimed in claim 4, wherein the step is carried out by raising and lowering a bearing leg of a rotor bearing by means of a motor. 7. Rotational eccentrics (65, 66) for movement of the rotor axis.
The outer eccentrics (66) of the bearing bracket (6) of each rotor bearing
7) or mounted on the base frame, the inner eccentric (65)
5. The method according to claim 4, wherein the method is receiving 8. The movement of the rotor axis is caused by the lifting of the bearing legs of the rotor bearing by the push-up bolts (60) and the shim plate (3) between the bearing legs (59) and the base frame (3).
The method according to claim 4, wherein the method is performed by the insertion of (62). 9. The movement of the rotor axis is caused by lifting and lowering of the stator with respect to the base frame or the stator base plate by means of push-up bolts arranged on the stator legs, and removal or insertion of a shim plate between the stator leg and the base frame or base plate. 5. The method according to claim 4, wherein the method is performed by: 10. A mounting bolt is used for fixing a bearing leg or a stator leg on a base plate or a base frame, and the mounting bolt is a highly elastic extension bolt (6).
10. The method as claimed in claim 8, wherein the spring element (64) is formed as 1) or is provided below the bolt head. 11. The method according to claim 4, wherein in a synchronous machine having a magnetic bearing, the movement of the rotor axis is performed by controlling the magnetic force of the magnetic bearing.