EP3394962A1 - Machine de travail électrique - Google Patents

Machine de travail électrique

Info

Publication number
EP3394962A1
EP3394962A1 EP16815538.0A EP16815538A EP3394962A1 EP 3394962 A1 EP3394962 A1 EP 3394962A1 EP 16815538 A EP16815538 A EP 16815538A EP 3394962 A1 EP3394962 A1 EP 3394962A1
Authority
EP
European Patent Office
Prior art keywords
section
hub
shaft
circular cross
connections
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.)
Withdrawn
Application number
EP16815538.0A
Other languages
German (de)
English (en)
Inventor
Guido Kochsiek
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Iprotec Maschinen und Edelstahlprodukte GmbH
Original Assignee
Iprotec Maschinen und Edelstahlprodukte GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Iprotec Maschinen und Edelstahlprodukte GmbH filed Critical Iprotec Maschinen und Edelstahlprodukte GmbH
Publication of EP3394962A1 publication Critical patent/EP3394962A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/003—Couplings; Details of shafts
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F16D1/072—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving plastic deformation
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0852—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft
    • F16D1/0858—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft due to the elasticity of the hub (including shrink fits)
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/102—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via polygon shaped connections

Definitions

  • Electric machines are electric motors, power generators and the like.
  • the shrink joints ensure a high assembly cost with corresponding costs (heating or cooling of the components, unfavorable handling of hot or cold components, high energy costs during assembly, possible distortion of the components when heated, high Be Thusspotenzia! Assembly (loss of run when joining long joints due to snow! Cooling during assembly).
  • a correction-disassembly possibility is no longer possible when the shrink connection has cooled down once. In case of service, non-destructive disassembly is possible.
  • connections have technical disadvantages and use the space usually not optimal. splines For example, they forgive the barrel when they need to be hardened. Keyway connections are among the worst types of connection in the industry (imbalance, notch effect, expensive production, expensive assembly, unfavorable torque behavior, backlash).
  • the present invention is based on the invention to simplify electrical machines with regard to their construction and assembly.
  • the invention proposes an electric working machine with the features of claim 1.
  • further independent inventive solutions are shown.
  • the aim of this invention is to optimize the manufacturing processes, to reduce the manufacturing costs and to optimize the connections so that space or weight can be saved, as well as assembly advantages can be achieved and the service friendliness is increased.
  • the invention proposes to design at least one of the connections for torque transmission in such a way that the elements to be connected-usually shaft / hub arrangements-have a non-circular cross-section.
  • the term "undround connections" is used in general for non-circular elements, ie those which do not have a circular cross-section, and polygon connections, in turn, are special non-circular connections, for example, they can produce contours called cycloids. Epicycloids, shortened and lengthened and the like
  • connection length can be reduced and space can be saved or space for additional functions (such as fits, ...) can be released.
  • connection greatly simplified assembly with significantly lower costs (no heating of the components required), shortening of the connection length by non-round positive locking instead of round frictional connection or by non-round shape and friction, gain of space, reduction of weight (energy efficiency, better efficiency, better performance), high running quality (no imbalance) after the greatly simplified installation.
  • Components can be dismantled and then reassembled (significantly cheaper repair costs of an engine).
  • the output shaft end likewise non-circular. If non-circular connections are used anyway, this connection can be manufactured in one clamping, which has a positive effect on the manufacturing quality and the production costs. The same applies to the machining of round sections of the motor shaft (for example, bearing seats) and non-circular connections in one setting in order to improve the running quality between the individual sections. As a result, higher speeds can be achieved on the finished product.
  • the technical advantages of a non-circular connection also at the output shaft end are: no imbalance, self-centering, more compact design with the same performance, freedom from backlash, etc.
  • extended trochoidal are particularly interesting when it comes to the connection of laminated cores and rotor shaft. This particular because the counterpart is a sheet metal part.
  • the solution according to the invention is characterized by a high level of economy through the use of non-circular turning processes. This allows great precision, so that connections can be created that are no longer subject to play, as is the case, for example, with splines. Also, there are no imbalances such as feather key connections.
  • the non-circular turning process makes it possible to produce torsionally stiff, secure oversize joints.
  • the joining can be implemented without heating or cooling, in particular when using a step design, conical connections or similar compounds are sefbstzentrierend and compared to conventional plug-in tooth connections, these aufrgund better power transmission properties in a smaller space be housed or allow for the same space a higher reliability and / or the transmission of larger forces.
  • the connecting elements (shaft and hub) can be manufactured according to the same procedure.
  • extended shapes can be used, for example, an extended trochoid, because the counterpart, i.
  • the laminated core can not be produced by machining.
  • the individual elements of a polygonal connection can be formed of different materials, which also results in simplifications and possibilities for improvement.
  • Fig. 1 is a schematic representation of a non-circular shaft-hub connection in the
  • Fig. 2 is a schematic representation of a non-circular shaft-hub connection between
  • FIG. 3 is a schematic representation of the non-circular shaft-hub connection according to the invention in the viewing direction III according to FIG. 2.
  • the hub seat 2 and the hub of the component 5 form a polygon connection, that is, the hub seat 2 has a polygonal cross-sectional outer contour, wherein the component 5 has a trained example as a bore receptacle with a corresponding to the outer contour of the hub seat 2 inner contour.
  • the polygon profile used may be a five-corner. Basically, of course, that the polygonal profile as Unrundprofil over as needed according to many corners may have.
  • the invention is not limited to a five-cornered polygonal profile.
  • the hub seat 2 and the component 5 received therefrom are of equal length in the longitudinal direction 1 1 of the shaft 1 or equally wide with respect to the plane of the sheet according to FIG. 1.
  • the hub seat 2 is delimited on the left as well as on the right by a connecting region 3 or a connecting region 4, which connecting regions 3 and 4 are circular in cross section in contrast to the hub seat 2.
  • the hub seat 2 in the illustrated embodiment has two further radial shoulders 9 and 10, so that a total of a three-stage hub seat 2 with the three stages I, II and III is formed.
  • the hub of the component 5 a laminated core, is formed according to the invention multi-stage of the hub seat 2 accordingly.
  • the individual stages I, II and III of the hub seat are the same width with respect to the plane of the drawing of FIG. 2, that is, the same length with respect to the longitudinal direction 1 of the motor shaft 1.
  • the second stage II of the hub seat 2 forming radial shoulder 9 projects beyond the first stage I of the hub seat 2 in the radial direction depending on the embodiment and application by at least some ⁇ up to several millimeters.
  • the third step III formed by the radial shoulder 10 projects beyond the second step II of the hub seat 2 provided by the radial shoulder 9 in the radial direction.
  • Fig. 3 shows the shaft-hub connection according to the invention in the direction of view III of FIG. 2. From this illustration, the individual radial paragraphs 9 and 10 and the individual Steps I, II and III of the hub seat are clearly visible. It can be seen in particular from this representation that the hub seat 2 forms a polygonal polygonal profile, whereas the connecting areas 3 and 4 adjoining the hub seat 2 with reference to the illustration according to FIG. 2 on the left and right sides have a circular cross-section.
  • FIG. 2 a shows a diagram showing the force or stress distribution 8 in the region of the hub seat 2 of the shaft 1, wherein the force introduced into the shaft 1 on the y-axis 7 extends over the axial extent of the hub seat 2 according to the x-axis 6 is worn away.
  • a force or voltage curve 8 results, which increases with respect to the plane of the drawing according to FIG. 2 per stage I, II and III of the hub seat 2 from left to right. The maximum stress results in each case with reference to the plane of the drawing according to FIG. 2 on the right side of each stage I, II and III of the hub seat 2.
  • FIGS. 1 a and 2 a are merely illustrative and should not be scientifically and technically correct in any way.
  • the force peaks also define an average force, which corresponds approximately to the mean value between 0 and F max .
  • This average force is the measure of the efficiency of the shaft-hub connection and this average value is shown as a dashed line.
  • a shaft-hub connection according to the prior art results in a power or voltage distribution 8, as shown in Fig. 1 a.
  • Fig. 1 a In a comparison of the diagrams of Fig. 1a and Fig. 2a shows that either the total force introduced into the hub seat 2 is equal, but that a force distribution with respect to the maximum force acting on the individual stages I, II and III of the Hub seat 2 is achieved according to the embodiment of the invention. Or the other way around the shaft-hub connection according to the invention is more resilient and can be a larger average power transmitted. This results in the result that in the embodiment of the invention a minimized in comparison to the prior art with the same force introduction maximum load on the shaft 1 acts.
  • the minimization of the maximum load is achieved in that a distribution of the maximum forces and / or stresses on the individual stages I, II and III of the hub seat 2 takes place according to the embodiment of the invention. Due to this stress distribution, an improved, that is reduced, contact corrosion compared to the prior art can be achieved. Or alternatively, the shaft-hub connection according to the invention can be regarded as significantly more efficient, ie, it represents a significant improvement in every respect. By targeted different excesses in the stages, further optimizations can be achieved in terms of the function of the compound.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Manufacture Of Motors, Generators (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)

Abstract

L'objet de la présente invention est la mise au point de machines de travail électriques dont la structure et le montage sont simplifiés et dont la puissance est améliorée. A cet effet, une machine de travail électrique selon la présente invention est pourvue d'éléments destinés à transmettre des couples de rotation, au moins une paire d'éléments étant conçue sous forme de liaison non circulaire.
EP16815538.0A 2015-12-21 2016-12-21 Machine de travail électrique Withdrawn EP3394962A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015122380 2015-12-21
PCT/EP2016/082203 WO2017108967A1 (fr) 2015-12-21 2016-12-21 Machine de travail électrique

Publications (1)

Publication Number Publication Date
EP3394962A1 true EP3394962A1 (fr) 2018-10-31

Family

ID=57570888

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16815538.0A Withdrawn EP3394962A1 (fr) 2015-12-21 2016-12-21 Machine de travail électrique

Country Status (7)

Country Link
US (1) US20180358864A1 (fr)
EP (1) EP3394962A1 (fr)
JP (1) JP2019503643A (fr)
CN (1) CN108432101A (fr)
DE (1) DE202016008922U1 (fr)
RU (1) RU2018124639A (fr)
WO (1) WO2017108967A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3263936B1 (fr) * 2016-06-28 2020-01-15 Guido Kochsiek Liaison arbre-moyeu
DE102021115837A1 (de) 2021-06-18 2022-12-22 Vorwerk & Co. Interholding Gesellschaft mit beschränkter Haftung Elektromotor und Verfahren zum Herstellen eines Elektromotors

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4543851A (en) * 1982-06-23 1985-10-01 Acf Industries, Incorporated Torque application assembly for closure valve of a railroad hopper car outlet
JP2672970B2 (ja) * 1988-04-20 1997-11-05 株式会社滝澤鉄工所 非円形断面体ワーク加工用工作機械及びその制御方法
DE50103741D1 (de) * 2001-01-19 2004-10-28 Visteon Global Tech Inc Welle-Nabe-Verbindung
US20020197104A1 (en) * 2001-06-25 2002-12-26 Bauman Brian Jay Polygon connection assembly
KR100381601B1 (ko) * 2001-09-26 2003-04-26 삼성전자주식회사 커플링장치와 현상카트리지 및 이를 채용한 전자사진방식인쇄기
EP1387102A1 (fr) * 2002-07-31 2004-02-04 Robert Bürgler Joint arbre-moyeu à pression
US6812602B2 (en) * 2003-03-13 2004-11-02 Visteon Global Technologies, Inc. Apparatus and method for retaining a cooling fan
US20050191178A1 (en) * 2004-02-26 2005-09-01 A.O. Smith Corporation Assembly including an electric motor and a load
DE102004056642A1 (de) * 2004-11-24 2006-06-01 Ziaei, Masoud, Dr. Einstellbare Profilkonturen mit mehreren Exzentrizitäten für formschlüssige Welle-Nabe-Verbindungen
DE102007007362B4 (de) * 2007-02-14 2009-07-09 Faurecia Autositze Gmbh Verstellmechanismus
PL2103827T3 (pl) * 2008-03-20 2014-01-31 Iprotec Maschinen Und Edelstahlprodukte Gmbh Połączenia wał-piasta
DE102009037789A1 (de) * 2009-08-18 2011-02-24 Behr Gmbh & Co. Kg Nabe-Welle-Baugruppe zur Drehmomentübertragung
DE102011109104B4 (de) * 2011-08-02 2022-11-03 Sew-Eurodrive Gmbh & Co Kg Verzahnungsteil und Verfahren zum Herstellen eines Verzahnungsteils
US8628269B2 (en) * 2011-09-02 2014-01-14 Roy Fan Rotating drive shaft coupling
US9803695B2 (en) * 2014-07-14 2017-10-31 Life Technologies Corporation Drive shaft locking cap and related mixing system and method
DE102015014087B4 (de) * 2015-11-03 2017-11-09 Sew-Eurodrive Gmbh & Co Kg Getriebe

Also Published As

Publication number Publication date
WO2017108967A1 (fr) 2017-06-29
RU2018124639A (ru) 2020-01-09
JP2019503643A (ja) 2019-02-07
DE202016008922U1 (de) 2020-10-08
US20180358864A1 (en) 2018-12-13
CN108432101A (zh) 2018-08-21

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