US20110220769A1 - Support plate for bearings - Google Patents
Support plate for bearings Download PDFInfo
- Publication number
- US20110220769A1 US20110220769A1 US13/121,705 US200913121705A US2011220769A1 US 20110220769 A1 US20110220769 A1 US 20110220769A1 US 200913121705 A US200913121705 A US 200913121705A US 2011220769 A1 US2011220769 A1 US 2011220769A1
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- US
- United States
- Prior art keywords
- support device
- clock position
- support plate
- predetermined break
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/067—Fixing them in a housing
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
- H02K5/1732—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at both ends of the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/50—Positive connections
- F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49826—Assembling or joining
- Y10T29/49947—Assembling or joining by applying separate fastener
Definitions
- FIG. 8 shows a vertical section through the support plate
- cracks 70 which run from the notch bottom of the first and/or the second outer notch 66 and/or 68 inward toward the internal diameter 80 are produced during operation of the generator and during mechanical loading of the support plate 60 .
- Said cracks 70 represent a macroscopic change in the geometry of the support plate 60 and convert the mechanical loadings into precisely the cracks 70 , with the result that loading peaks can be absorbed not by the components of the electric machine 10 in accordance with the illustration in FIG. 1 , but rather substantially by the support plate 60 .
- the plastic deformation 88 (shown in FIG. 7 a ) of those ends of the webs 86 which lie opposite one another represents a macroscopic change in the geometry of the support device 60 which is configured to be plate-shaped, by way of which change the stresses can be dissipated which are produced in the support device 60 which is configured to be plate-shaped in the case of mechanical loading of the latter, and accordingly a complete fracture or a partial fracture is accepted of the support device 60 which is configured to be, in particular, plate-shaped, in order as a result to protect the components of the electric machine 10 in accordance with the sectional illustration in FIG. 1 against excessive mechanical loadings in the frequency range mentioned.
- the crack 70 extends from the notch bottom of the planar-side notch 92 to the planar side 96 .
- the planar-side notch 92 can also be formed on the opposite second planar side 96 of the support device 60 which is proposed according to the invention and is configured to be, in particular, plate-shaped.
Abstract
The invention relates to a support device (60) for fixing a bearing (28) on a bearing shield (13.1, 13.2) of a housing (13) of an electric machine (10). Rotatably mounted in the support device is a rotor (20) with a shaft (27). The support device (60) is substantially flat and comprises a plurality of fastening openings (62) that are grouped about a central opening (64). The support device (60) comprises at least one design break point (66, 68; 72, 74; 76, 78; 92) that acts to provide a local limit to the excess stresses in the material of the support device (60).
Description
- As a rule, air-cooled generators for applications in the automotive sector are mounted by means of a locating bearing in a first bearing plate (A bearing plate) and a floating bearing in a second bearing plate (B bearing plate). A ball bearing which is used as a bearing is fixed axially here between a bearing plate and a support plate. As a result of the generally present bearing play, oscillations of the rotor occur as overall body in the axial direction. This phenomenon which is also called rotor bouncing occurs as a rule between 100 Hz and 500 Hz and is generally associated with very high mechanical loadings in the generator on various components.
- DE 44 03 957 A1 relates to a flange bearing. Said flange bearing serves to receive a prong shaft of the winch or the pick-up drum of a harvester or of another correspondingly equipped agricultural machine. The flange bearing comprises a bearing body which is divided on one side and the outer casing of which has a cylindrical center section. The latter is adjoined by sections which are beveled conically on both sides. The bearing body is provided with a web which permits positionally accurate insertion of the bearings into the receptacle of a winch star and at the same time serves as antirotation safeguard. The bearing halves are connected elastically to one another by an integral hinge, a cutout being provided in an adjacent manner to the integral hinge, which cutout facilitates the widening of the bearing body, which is produced from a robust plastic, during mounting and dismantling. This solution concerns a hinge which can be bent more easily on account of the lower rigidity at a notched point.
- U.S. Pat. No. 3,431,032 discloses a cylindrical bearing housing which has a milled slot as viewed in the axial direction. As a result, internal stresses which are produced are dissipated, such as residual stresses which are produced during casting. Deformation of the bearing housing is possible as a result of the slot.
- DE 10 2004 053 078 A1 relates to a bearing arrangement. The latter comprises a bearing carrier which is connected to a bearing which is preferably configured as an antifriction bearing. In one of its bearing rings, the bearing has a groove which extends in the circumferential direction. At least one projection which is arranged on the bearing carrier and extends in the radial direction engages into said groove. At a circumferential point, the bearing carrier has a slot which extends substantially in the radial direction.
- Finally, WO 03/081750 A1 discloses a generator for a vehicle, the generator comprising a support plate which has a slot which extends in the radial direction. Said slot which extends in the radial direction serves as tolerance compensation means. According to this solution, any stresses which possibly occur during the screwing connection of the support plate are dissipated, since a deformation of the material of the support plate is possible as a result of the slot and accordingly a dissipation of the stresses can take place.
- The present invention is based on the object of protecting the components of the generator from excessive mechanical loadings, in particular excessively high oscillating accelerations, acting on the components of the generator for too long.
- Following the solution which is proposed according to the invention, in an electric machine, for instance a generator which is used in the automotive sector, the support plate is configured in the region of the mounting in such a way that its macroscopic geometry changes during the operation of the generator. In particular, the change in the macroscopic geometry of the support plate is manifested by visible plastic deformations up to and including fractures of the support plate. The change in the geometry of the support plate achieves a situation where mechanical component loadings in the frequency range, for example, between 100 Hz and 500 Hz act for only a short time period on the components of the electric machine, for instance of a generator and for the most part are absorbed by the material of the support plate. To this extent, the material of the support plate acts as an absorber or damper, in particular for high mechanical oscillating accelerations.
- The change in the macroscopic geometry of the support plate is achieved by the induced enforcement of fractures in the case of excessive loads as a result of defined predetermined break points. To this end, notches can be made at defined points of the support plate, which notches lead to high but locally delimited excessive loadings of the material of the support plate. If said delimited excessive loadings exceed a limiting value, this necessarily leads to the occurrence of a plastic deformation and, as a final consequence, to the formation of fractures. As a result of the support plates being partially or completely fractured at one or more points, the transmission of high mechanical component loadings to the components of the generator is avoided and damped or absorbed by the partially/completely fractured support plate.
- In addition to the formation of notches at defined points of the support plate, plastic deformations can be forced in the support plate in the case of overloads, for instance also as a result of local rigidities, such as tapering regions of the support plate. This results in a reduction in the loading of the functionally important components of the support plate.
- The support plate which is proposed according to the invention is designed, in particular, in such a way that at least one crack, that is to say a partial fracture or a complete fracture of the support plate, is produced in the case of more than 150,000 load changes with accelerations over 400 m/s2. Accelerations of this type do not occur during the normal vehicle operation. In contrast, no fractures or cracks may be produced in the case of accelerations below 300 m/s2. After the occurrence of at least one fracture in the support plate which is proposed according to the invention, the response characteristic of the generator changes, as a result of which the maximum load is reduced on account of damping effects which are produced.
- Should the fracture faces not rub against one another after the fracture of the support plate, this is associated with a loss of friction energy. However, a completely fractured or partially fractured support plate will have a lower rigidity in comparison with an intact, that is to say unfractured, support plate. A reduced rigidity of the support plate leads to greater deformations of the latter and, as a result, additionally to damping potential which results in addition to the damping potential which exists at the fracture face. It is a further positive effect that the transmission characteristic of the generator can be influenced positively by the lower rigidity of the support plate. This effect is substantially independent of whether the fracture faces of the support plate rub against one another or whether this is not the case.
- With regard to the pitch circle of the support plate screws, it is to be aimed for that it corresponds to the pitch circle of the holes which are formed in the support plate, that is to say the two pitch circles have identical dimensions.
- In that design variant of the support plate proposed according to the invention which is provided with notches at defined points, it is to be aimed for that the geometry of the notch is designed in such a way that said notch has a stress concentration factor of Kt>2.0.
- In the following text, the invention will be described in more detail using the drawing, in which:
-
FIG. 1 shows a longitudinal section through a generator, -
FIG. 2 shows the plan view of a conventionally configured support plate, -
FIG. 3 shows a first design variant of the support plate which is proposed according to the invention, -
FIG. 3 a shows the changing macroscopic geometry of the support plate in accordance with the first embodiment according toFIG. 3 , -
FIG. 4 shows a further, second possible embodiment of the support plate which is proposed according to the invention, -
FIG. 4 a shows the change which is produced in the macroscopic geometry of the support plate in accordance with the second embodiment according toFIG. 4 , -
FIG. 5 shows a further, third possible embodiment of the support plate which is proposed according to the invention, -
FIG. 5 a shows the changing macroscopic geometry of the third embodiment (shown inFIG. 5 ) of the support plate which is proposed according to the invention, -
FIG. 6 shows a horizontal sectional profile through the support plate, -
FIG. 7 shows a sectional profile in accordance with the sectional profile A-A which is shown inFIG. 6 , -
FIG. 7 a shows the plastic deformation which is produced in the sectional plane in accordance with the illustration inFIG. 7 , -
FIG. 8 shows a vertical section through the support plate, -
FIGS. 9 and 9 a show the illustration of fracture faces which are produced during the complete or partial fracture of the support plate which is proposed according to the invention, and -
FIGS. 10 and 10 a show macroscopic geometry changes which are produced in the support plate which is proposed according to the invention, in the sectional plane of the section B-B in accordance withFIG. 6 . - The illustration according to
FIG. 1 shows a section through anelectric machine 10, configured here as a generator or three-phase generator for motor vehicles. Saidelectric machine 10 has, inter alia, a two-part housing 13 which consists of a first bearing plate 13.1 and a second bearing plate 13.2. The first bearing plate 13.1 and the second bearing plate 13.2 receive astator 16 between them, which stator 16 firstly consists of a substantially circularlyannular stator iron 17 and in the radially inwardly directed, axially extending grooves of which a stator winding 18 is inserted. Saidannular stator 16 surrounds arotor 20 with its radially inwardly directed grooved surface, whichrotor 20 can be configured as a claw pole rotor. Therotor 20 consists, inter alia, of twoclaw pole plates claw pole fingers claw pole plates rotor 20 in such a way that theirclaw pole fingers rotor 20. This results in magnetically required intermediate spaces between the oppositely magnetizedclaw pole fingers rotor 20 is mounted rotatably in the first and second bearing plates 13.1 and 13.2 by means of ashaft 27 and in each case oneantifriction bearing 28 which is situated on in each case one rotor side. - The
rotor 20 has a total of two axial side faces, to which in each case oneventilator 30 is fixed. Saidventilator 30 consists substantially of a plate-shaped or disc-shaped section, from which ventilator vanes emanate in a known manner. Theventilator 30 serves to make an exchange of air possible viaopenings 40 in the bearing plates 13.1 and 13.2 between the outer side of theelectric machine 10 and the interior of theelectric machine 10. To this end, theopenings 40 are provided substantially at the axial ends of the bearing plates 13.1 and 13.2, via whichopenings 40 cooling air is sucked into the interior of theelectric machine 10 by means of theventilator 30. Said cooling air is accelerated radially to the outside by the rotation of theventilator 30, with the result that said cooling air can pass through the windingprojection 45 which is permeable to cooling air. The windingprojection 45 is cooled by this effect. After passing through the windingprojection 45 or after flowing around said windingprojection 45, the cooling air follows a path radially to the outside, through an opening which is not shown inFIG. 1 . - Furthermore, it is apparent from the illustration in accordance with
FIG. 1 that aprotective cap 47 which protects various components against environmental influences is situated on the right hand side. Thus, for example, thisprotective cap 47 covers aslip ring assembly 49 which serves to supply an exciter winding 51 with exciter current. A coolingbody 53 which acts here as a positive cooling body is arranged around saidslip ring assembly 49. The second bearing plate 13.2 acts as what is known as a negative cooling body. A connectingplate 56 is arranged between the second bearing plate 13.2 and the coolingbody 53, which connectingplate 56 serves to connectnegative diodes 58 which are arranged in the bearing plate 13.2 and positive diodes (not shown here in this illustration) in the coolingbody 53 to one another and therefore to realize a bridge circuit which is known per se. A support plate of theelectric machine 10 is denoted by designation 59 inFIG. 1 . - A support plate in accordance with the prior art which is used on an electric machine can be gathered from the illustration in accordance with
FIG. 2 . - The
support plate 60 which can be of rectangular, round or, as shown inFIG. 2 , square configuration comprises a throughopening 64 and a number offastening openings 62. Thefastening openings 62 can be produced as punched holes, as drilled holes with or without threads, or the like. Theantifriction bearings 28 which are shown in section in accordance withFIG. 1 are fixed in the housing of theelectric machine 10 by way of thesupport plate 60 in accordance with the illustration inFIG. 2 . It is apparent from the illustration in accordance withFIG. 2 that thesupport plate 60 which is shown there is of planar configuration in relation to its outer and its inner borders. -
FIG. 3 shows a support plate which is proposed according to the invention and is illustrated in a first design variant. - It is apparent from the illustration in accordance with
FIG. 3 that theopening 64 has aninternal diameter 80 and contains a number offastening openings 62. A firstouter notch 66 and a secondouter notch 68 which lies opposite the former are situated in each case in a 6 o'clock arrangement and 12 o'clock arrangement on the outer edge of thesupport plate 60 in accordance with the illustration inFIG. 3 . The firstouter notch 66 and the secondouter notch 68 could also be configured to be turned by 90°, that is to say could be configured in the 3 o'clock and the 9 o'clock arrangement. Twoouter notches - As is apparent from the illustration in accordance with
FIG. 3 a, cracks 70 which run from the notch bottom of the first and/or the secondouter notch 66 and/or 68 inward toward theinternal diameter 80 are produced during operation of the generator and during mechanical loading of thesupport plate 60. Said cracks 70 represent a macroscopic change in the geometry of thesupport plate 60 and convert the mechanical loadings into precisely thecracks 70, with the result that loading peaks can be absorbed not by the components of theelectric machine 10 in accordance with the illustration inFIG. 1 , but rather substantially by thesupport plate 60. - The
support device 60 is preferably configured to be plate-shaped, that is to say as a support plate. - It is to be noted in relation to the
cracks 70 which extend from the notch bottom of theouter notches internal diameter 80 of thecentral opening 64 that the faces which delimit thecrack 70 are relatively rough and brittle and accordingly do further damping work in the context of the present invention by rubbing on one another and accordingly absorbing oscillating accelerations with the acceptance of a slight temperature increase. - A further, second design variant of the support device which is proposed according to the invention and is configured to be, in particular, plate-shaped can be gathered from the illustration in accordance with
FIG. 4 . -
FIG. 4 shows that, in addition to the firstouter notch 66 and the secondouter notch 68 on the external circumference of the plate-shapedsupport device 60, notches which lie opposite one another, that is to say a first inner notch 72 and a secondinner notch 74, are also configured on theinternal diameter 80 of thecentral opening 64. In an analogous manner to the firstouter notch 66 in the 12 o'clock position, the first inner notch 72 is likewise situated in the 12 o'clock position on theinternal diameter 80 of thecentral opening 64. The same applies to the secondinner notch 74 which, analogously to the secondouter notch 68, is situated in the 6 o'clock position on theinternal diameter 80 of thecentral opening 64. It goes without saying that both theinner notches 72, 74 and theouter notches 66 can be arranged in each case turned by 90° with respect to one another. -
FIG. 4 a shows the crack pattern which is produced of thecracks 70 in the case of mechanical loading of thesupport device 60 which is proposed according to the invention and is preferably configured to be plate-shaped. On account of the small remaining material web between the notch bottoms which face one another of the firstouter notch 66 and the first inner notch 72 and the secondouter notch 68 and the secondouter notch 74, relativelyshort cracks 70 extend, as indicated inFIG. 4 a, between the notch bottoms which in each case point toward one another. - The faces which are produced and delimit the
cracks 70 have a relatively high roughness, which is favorable with regard to additional damping work, via which oscillating accelerations can be dissipated. - A further, third design variant of the
support device 60 which is proposed according to the invention and is configured to be, in particular, plate-shaped can be gathered from the illustration in accordance withFIG. 5 . In contrast to the first design variant in accordance withFIG. 3 and the second design variant in accordance withFIG. 4 , thesupport device 60 which is proposed according to the invention and is configured to be plate-shaped has, in accordance withFIG. 5 , shell-shapedopenings support device 60. This results in material webs which extend in each case from the ends of theopenings support device 60 which is configured to be plate-shaped and also to theinternal diameter 80 which delimits thecentral opening 64. Excessive loadings are produced in said remaining, relatively short material sections in the case of mechanical loading of thesupport device 60 which is proposed according to the invention, on account of oscillating accelerations which occur, which excessive loadings lead to thecrack courses 70 which are shown inFIG. 5 a, firstly in the direction of the external circumference and thesupport device 60 and secondly in the direction of theinternal diameter 80 of thecentral opening 64. - Fastening
openings 62 are a common feature of all the design variants in accordance withFIGS. 3 to 5 of the support device which is proposed according to the invention and is configured to be, in particular, plate-shaped. Saidfastening openings 62 can be simply punched holes, or they can be drilled holes which are configured with or without internal threads. The pitch circle diameters both of the pitch circle of thefastening openings 62 and also that of the screws which penetrate thefastening openings 62 are preferably identical. - An illustration of the
support device 60, in which a horizontal sectional profile A-A is represented, can be gathered from the illustration in accordance withFIG. 6 . -
FIGS. 7 and 7 a show thesupport device 60 in the sectional plane A-A, which supportdevice 60 is shown inFIG. 6 with the sectional profile A-A, is proposed according to the invention and is configured to be, in particular, plate-shaped. It is apparent from the sectional illustration in accordance withFIG. 7 that, in the region of thecentral opening 64, thesupport device 60 has a reducedthickness 84 in relation to itsthickness 82, that is to say atapered section 84. The taperedregion 84 which adjoins thecentral opening 64 of thesupport device 60 which is configured to be, in particular, plate-shaped results inwebs 86 which lie opposite one another and experience aplastic deformation 88 in the case of a mechanical loading of thesupport device 60 which is configured to be, in particular, plate-shaped, as is shown inFIG. 7 a. - The plastic deformation 88 (shown in
FIG. 7 a) of those ends of thewebs 86 which lie opposite one another represents a macroscopic change in the geometry of thesupport device 60 which is configured to be plate-shaped, by way of which change the stresses can be dissipated which are produced in thesupport device 60 which is configured to be plate-shaped in the case of mechanical loading of the latter, and accordingly a complete fracture or a partial fracture is accepted of thesupport device 60 which is configured to be, in particular, plate-shaped, in order as a result to protect the components of theelectric machine 10 in accordance with the sectional illustration inFIG. 1 against excessive mechanical loadings in the frequency range mentioned. -
FIG. 8 shows a sectional profile A-A, B-B.FIG. 9 shows the profile through thesupport device 60 before the fracture, whereasFIG. 9 a represents the sectional profile after the occurrence of a fracture in thesupport device 60 which is proposed according to the invention. - A sectional profile B-B in accordance with the sectional illustration in
FIG. 8 can be gathered fromFIGS. 10 and 10 a. According to the sectional profile B-B as shown inFIG. 10 , a planar-side notch 92 is made on one of theplanar sides support device 60 which is configured to be, in particular, plate-shaped. As a result, a reduced thickness is produced between the notch bottom of the planar-side notch 92 and theplanar side 94 which lies opposite it. Acrack 70, as indicated in the illustration in accordance withFIG. 10 a, extends precisely in this reduced thickness in the case of mechanical overloading of thesupport device 60 which is proposed according to the invention and is preferably configured to be plate-shaped. Thecrack 70 extends from the notch bottom of the planar-side notch 92 to theplanar side 96. As an alternative to the position (shown inFIGS. 10 and 10 a) of the planar-side notch 92 on the firstplanar side 94, it goes without saying that the planar-side notch 92 can also be formed on the opposite secondplanar side 96 of thesupport device 60 which is proposed according to the invention and is configured to be, in particular, plate-shaped. - It is to be noted with respect to
FIGS. 3 , 4, 5 and 10 that the notches which are shown there, whether they areouter notches inner notches 72, 74 or planar-side notches 92, are all preferably configured with a stress concentration factor of Kt>2.0. The stress concentration factor xKt is defined as the quotient from maximum loading and nominal loading. - In the embodiments shown in
FIGS. 3 , 4, 5, 7 and 9 of thesupport device 60 which is proposed according to the invention and is configured to be, in particular, plate-shaped, it is to be noted that the geometry of said support device is configured in such a way that thesupport device 60 fractures when more than 150 000 load changes at accelerations over 400 m/s2 occur. Thesupport device 60 which is proposed according to the invention and is configured to be, in particular, plate-shaped is preferably dimensioned in such a way that it does not fracture in the case of accelerations below 300 m/s2. After the fracture or partial fracture of thesupport device 60 which is proposed according to the invention as a result of at least onecrack 70 occurring, the response characteristic of theelectric machine 10 changes, as a result of which the maximum load is reduced by way of damping effects. - If the fracture faces 90 which are shown in
FIG. 9 a no longer rub against one another after the fracture, part of the friction energy, in which energy is dissipated, is lost. However, a fractured or partially fracturedsupport device 60 will have a lower rigidity than anintact support device 60. A reduced rigidity of thesupport device 60 in turn leads to somewhat greaterplastic deformations 88, as is shown in an exaggerated manner inFIG. 7 a, and additionally leads, as a result, to damping which is to be considered to be additional damping in relation to the damping which can be achieved by way of the fracture faces 90.
Claims (13)
1. A support device (60) for fixing a bearing (28) on a bearing plate (13.1, 13.2) of a housing (13) of an electric machine (10), in which a rotor (20) is rotatably mounted with a shaft (27), and the support device (60) is of substantially plate-shaped configuration and has a number of fastening openings (62) which are arranged around an opening (64), characterized in that the support device (60) has at least one predetermined break point (66, 68; 72, 74; 76, 78; 92) which brings about locally delimited excessive loadings.
2. The support device (60) as claimed in claim 1 , characterized in that at least one predetermined break point (66, 68; 72, 74) is configured as a notch.
3. The support device (60) as claimed in claim 1 , characterized in that at least one predetermined break point (76, 78) is configured as an aperture in the material of the support device (60).
4. The support device (60) as claimed in claim 2 , characterized in that at least one predetermined break point (92) is configured as a notch on a planar side (94, 96) of the support device (60).
5. The support device (60) as claimed in claim 2 , characterized in that at least one predetermined break point (66, 68; 72, 74) is configured on an external circumference of the support device (60).
6. The support device (60) as claimed in claim 2 , characterized in that a number of predetermined break points (66, 68; 72, 74) are configured on at least one of an external circumference and an internal diameter (80) of the central opening (64).
7. The support device (60) as claimed in claim 2 , characterized in that the support device is configured with a variable thickness (82, 84).
8. The support device (60) as claimed in claim 7 , characterized in that the support device has a tapered section (84), in which plastically deformable webs (86) extend.
9. The support device (60) as claimed in claim 2 , characterized in that at least one predetermined break point (66, 68; 72, 74; 92) which is configured as a notch has a stress concentration factor of Kt>2.0.
10. The support device (60) as claimed in claim 6 , characterized in that at least two predetermined break points (66, 68; 72, 74) are arranged so as to lie opposite one another on at least one of the external circumference and the internal diameter (80) of the central opening (64).
11. The support device (60) as claimed in claim 6 , characterized in that at least two predetermined break points (66, 68; 72, 74) lie on the external circumference of the support device (60), one at the 6 o'clock position and one at the 12 o'clock position, or on the external circumference, one at the 3 o'clock position and one at the 9 o'clock position.
12. The support device (60) as claimed in claim 11 , characterized in that at least two predetermined break points (66, 68; 72, 74) lie on the internal diameter (80) of the central opening (64), one at the 6 o'clock position and one at the 12 o'clock position, or on the internal diameter (80) of the central opening (64), one at the 3 o'clock position and one at the 9 o'clock position.
13. The support device (60) as claimed in claim 6 , characterized in that at least two predetermined break points (66, 68; 72, 74) lie on the internal diameter (80) of the central opening (64), one at the 6 o'clock position and one at the 12 o'clock position, or on the internal diameter (80) of the central opening (64), one at the 3 o'clock position and one at the 9 o'clock position.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008042552.4 | 2008-10-02 | ||
DE200810042552 DE102008042552A1 (en) | 2008-10-02 | 2008-10-02 | Electropneumatic positioner |
PCT/EP2009/062516 WO2010037710A1 (en) | 2008-10-02 | 2009-09-28 | Support plate for bearings |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/062516 A-371-Of-International WO2010037710A1 (en) | 2008-10-02 | 2009-09-28 | Support plate for bearings |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/280,090 Continuation US9115754B2 (en) | 2008-10-02 | 2014-05-16 | Support plate for bearings |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110220769A1 true US20110220769A1 (en) | 2011-09-15 |
Family
ID=41172361
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/121,705 Abandoned US20110220769A1 (en) | 2008-10-02 | 2009-09-28 | Support plate for bearings |
US14/280,090 Active US9115754B2 (en) | 2008-10-02 | 2014-05-16 | Support plate for bearings |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/280,090 Active US9115754B2 (en) | 2008-10-02 | 2014-05-16 | Support plate for bearings |
Country Status (9)
Country | Link |
---|---|
US (2) | US20110220769A1 (en) |
EP (1) | EP2337961B1 (en) |
JP (1) | JP5227458B2 (en) |
CN (1) | CN102171472B (en) |
BR (1) | BRPI0920204B1 (en) |
DE (1) | DE102008042552A1 (en) |
ES (1) | ES2431063T3 (en) |
MX (1) | MX344995B (en) |
WO (1) | WO2010037710A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11365763B2 (en) * | 2018-12-06 | 2022-06-21 | Danfoss Power Solutions Inc. | Cover plate and seal carrier that eliminates bearing endplay |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5317228B2 (en) * | 2011-05-18 | 2013-10-16 | 日本電産サーボ株式会社 | Rotating electric machine |
EP2395638A3 (en) * | 2010-06-11 | 2017-04-12 | Nidec Servo Corporation | Rotary electric machine |
CN102852979A (en) * | 2012-07-31 | 2013-01-02 | 苏州柏德纳科技有限公司 | Mechanical support plate for shaft |
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Cited By (1)
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---|---|---|---|---|
US11365763B2 (en) * | 2018-12-06 | 2022-06-21 | Danfoss Power Solutions Inc. | Cover plate and seal carrier that eliminates bearing endplay |
Also Published As
Publication number | Publication date |
---|---|
EP2337961B1 (en) | 2013-09-18 |
DE102008042552A1 (en) | 2010-04-08 |
BRPI0920204A2 (en) | 2015-12-22 |
WO2010037710A1 (en) | 2010-04-08 |
MX344995B (en) | 2017-01-12 |
MX2011003413A (en) | 2011-04-21 |
ES2431063T3 (en) | 2013-11-25 |
JP5227458B2 (en) | 2013-07-03 |
CN102171472B (en) | 2015-10-07 |
US20140245591A1 (en) | 2014-09-04 |
US9115754B2 (en) | 2015-08-25 |
CN102171472A (en) | 2011-08-31 |
JP2012504929A (en) | 2012-02-23 |
BRPI0920204B1 (en) | 2020-04-28 |
EP2337961A1 (en) | 2011-06-29 |
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Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |
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