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WO2019001634A1 - Moteur électrique à palier et chaîne cinématique - Google Patents

Moteur électrique à palier et chaîne cinématique Download PDF

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Publication number
WO2019001634A1
WO2019001634A1 PCT/DE2018/100585 DE2018100585W WO2019001634A1 WO 2019001634 A1 WO2019001634 A1 WO 2019001634A1 DE 2018100585 W DE2018100585 W DE 2018100585W WO 2019001634 A1 WO2019001634 A1 WO 2019001634A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
housing
drive shaft
rotor
shaft
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.)
Ceased
Application number
PCT/DE2018/100585
Other languages
German (de)
English (en)
Inventor
Maximilian Bossecker
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2019001634A1 publication Critical patent/WO2019001634A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
    • 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
    • H02K7/08—Structural association with bearings
    • H02K7/086—Structural association with bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
    • 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
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the invention relates to an electric motor for a drive train of a motor vehicle, comprising a housing, a housing fixedly mounted stator, a rotor receiving and via a (bearing with training) bearing rotatably mounted relative to the housing drive shaft and a non-rotatably connected to the drive shaft in an axial direction of the drive shaft offset from the rotor arranged external toothing region. Furthermore, the invention relates to a drive train for a motor vehicle, with this electric motor.
  • a further embodiment is the so-called "standard bearing", wherein the rotor and the external toothing region are arranged between the two axially spaced bearings as seen in the axial direction, however, this bearing again has the disadvantage that the axial space requirement between the bearings is increased, thereby making it more useful Space between the camps is lost. It is therefore an object of the present invention to remedy the known from the prior art disadvantages and in particular to provide an electric motor, in which on the one hand, the mechanical load on the moving components is kept low during operation and the axial space is used even more intense.
  • the bearing is arranged radially within the outer toothing region such that the bearing is at least partially covered / superimposed in the axial direction of the outer toothed region. Consequently, a nested arrangement in the radial direction of the outer toothing region is implemented relative to the bearing.
  • the bearing is located directly under the outer teeth section.
  • the bearing is designed as a roller bearing, preferably as a roller bearing or as a needle bearing
  • a first rolling bearing track is formed on a shaft region of the housing (preferably on a radial outer side of the shaft region) and a second rolling bearing track on the drive shaft (preferably on a radial shaft) Inside the drive shaft) is formed, the bearing is designed to save space.
  • the bearing is designed as a first bearing and also a further second bearing is provided, wherein the second bearing on a first bearing axially facing away from the rotor, the drive shaft relative to the housing, preferably relative to the shaft region of the housing, supports / rotatably supports. If the first rolling bearing track and / or the second rolling bearing track overlap / overlap the outer toothed area in the axial direction, a particularly clever radial nesting of the (first) bearing and the outer toothed area is implemented.
  • the rotor is designed as an external rotor or an internal rotor.
  • the electric motor is particularly variable used.
  • the housing can be produced in a particularly cost-effective manner.
  • the bearing shaft is positively and / or non-positively, preferably via at least one press fit, more preferably two press fits, each of which a press fit is provided at an end portion of the bearing shaft is fixed in the housing.
  • the assembly of the electric motor is further facilitated.
  • the drive shaft has two drive shaft sections connected to one another in a rotationally fixed manner, wherein the rotor is rotatably received on a first drive shaft section and the outer gear section is formed on a second drive shaft section, and wherein the drive shaft sections are rotationally coupled to one another via an overload protection coupling.
  • the overload protection coupling is used in particular to open when exceeding a limit to be transmitted between the rotor and the drive shaft limit torque and to be closed below this limit torque. As a result, overload protection for the electric motor is used in a particularly space-saving manner.
  • an overload protection coupling which is exceeded when a between the rotor and the drive shaft to be transmitted limit torque opens and is closed below this limit torque is arranged.
  • the overload protection coupling can be formed in different ways and placed in different ways.
  • Lubricant receiving space of the housing is arranged, which is sealed against a rotor-receiving rotor receiving space of the housing.
  • the shaft region and / or the housing is formed so that in operation a lubricating lubricant bearing the lubricant channel is formed, which opens into the bearing or passes through this in the axial direction, also by means of the lubricant, the bearing is sufficiently lubricated, so that the Life of the electric motor is further extended.
  • the invention relates to a drive train, which is preferably designed as a hybrid powertrain / hybrid powertrain, for a motor vehicle, with the electric motor according to the invention according to at least one of the embodiments described above.
  • the drive train preferably further comprises a transmission which is rotationally coupled to the outer toothed region via at least one gear / toothing stage.
  • a transmission which is rotationally coupled to the outer toothed region via at least one gear / toothing stage.
  • Lubricant channel opens and through which the lubricant is returned.
  • the supply of lubricant to the respective outer toothed region is made particularly clever.
  • a rotor bearing (comprising at least one (first) bearing) implemented for an axially compact electric motor.
  • the invention proposes to arrange the (first) bearing (roller bearings or needle roller bearings) directly under a pinion tooth system.
  • An additional fixed shaft (housing-fixed shaft area), which is not rotatable, is preferably accommodated in the housing.
  • a rotor and the bearing rotate around this additional stationary shaft.
  • the additional shaft is configured as a hollow shaft to create a lubricant flow for lubricating the bearing.
  • the rotor may be formed as an internal rotor, i. be arranged radially inside the stator, or be formed as an external rotor, i. be arranged radially outside of the stator.
  • FIG. 1 is a longitudinal sectional view of an electric motor according to the invention according to a first embodiment, wherein the electric motor is already used in a drive train and is rotationally coupled with its outer toothed portion with a transmission shaft,
  • FIG. 2 shows a longitudinal sectional illustration of the electric motor according to the invention according to the first exemplary embodiment, similar to FIG. 1, illustrating a lubricant flow in operation for lubricating the outer toothing region and a bearing supporting it, FIG.
  • Fig. 3 is a longitudinal sectional view of an electric motor according to the invention according to a second embodiment, wherein a lubricant conducting Lubricant channel opens into a port introduced in the housing,
  • Fig. 4 is a longitudinal sectional view of an electric motor according to the invention according to a third embodiment, wherein a one-piece drive shaft is now mounted on a (second) bearing directly in a housing, and
  • Fig. 5 is a longitudinal sectional view of an electric motor according to the invention according to a fourth embodiment, wherein a bearing shaft of the drive shaft gerwelle is supported in an end axially on the housing and radially via another bearing on the drive shaft.
  • an inventive electric motor 1 (also referred to as E-motor / electric machine / electric motor) in a first embodiment illustrated.
  • the electric motor 1 has a multipart (preferably three-part) housing 2.
  • a stator 3 is received stationary.
  • a rotor 4 is rotatably supported relative to the stator 3.
  • the rotor 4 is rotatably supported via a drive shaft 6 relative to the housing 2.
  • the drive shaft 6 has, among other things, an external gear section 7, which is coupled via a gear stage 17 to a transmission shaft 18 of a transmission 19.
  • the housing 2 of the electric motor 1 passes directly into a housing of the transmission 19 via or forms this directly from. Accordingly, in the housing 2 and the transmission shaft 18 is rotatably mounted.
  • Electric motor 1 and transmission 19 are part of a hybrid drive train 20 of a motor vehicle.
  • the external gear portion 7 meshes in particular with an intermediate gear 44 of the gear stage 17.
  • the intermediate gear 44 in turn meshes with a gear 46 of the gear shaft 18.
  • the intermediate gear 44 is on a standing shaft 45, which is anchored / fixed in the housing 2, stored.
  • the standing shaft 45 is fixed in receiving holes / bearing eyes of the housing 2.
  • the rotor 4 is designed as an internal rotor.
  • the rotor 4 is thus arranged radially inside the stator 3 (with respect to a rotation axis 38 of the rotor 4 / the drive shaft 6).
  • embodiments of the rotor 4 are also implemented as external rotors, according to which the stator 3 is arranged radially inside the rotor 4.
  • the rotor 4 has a permanently magnetic or magnetizable component 21, which is received in a rotationally fixed manner on the drive shaft 6.
  • the component 21 is in particular constructed from a magnetizable coil winding which is magnetized during operation and forms a magnet.
  • the drive shaft 6 is rotatably supported in this embodiment by means of two bearings 5 and 25 relative to the housing 2 and a housing-fixed component in the form of a shaft region 10.
  • the shaft region 10 is formed by a separate stationary bearing shaft, which is accommodated in the housing 2 fixed to the housing.
  • a first end region 22 of the shaft region 10 is fastened in a first receiving region 26 of the housing 2.
  • a second end region 23 of the shaft region 10 lying opposite this first end region 22 is fastened in a second receiving region 27 of the housing 2.
  • the first end region 22 is pressed into the first receiving region 26.
  • the first receiving region 26 forms a receiving hole, into which the shaft region 10 projects with its first end region 22 and is held in a press fit.
  • the second end region 23 is in turn pressed into the second receiving region 27.
  • the second receiving area 27 likewise forms a receiving hole, into which the shaft area 10 projects with its second end area 23 and is held in a press fit.
  • the drive shaft 6 completely penetrates the rotor 4 / the component 21 in the axial direction and thus projects out of this from two opposite axial sides of the rotor 4.
  • a first bearing 5 serves to support the drive shaft 6 (in the radial direction) relative to the first axial side of the rotor 4 Shaft region 10.
  • a second bearing 25 serves on a, the first axial side facing away, the second axial side of the rotor 4 for supporting the drive shaft 6 (in the radial and axial directions) relative to the shaft portion 10.
  • the first bearing 5 is formed as a rolling bearing
  • the second bearing 25 is also designed as a roller bearing.
  • the first bearing 5 is designed as a needle bearing, but may in principle be configured in other ways.
  • the first bearing 5 is formed in other embodiments as a roller bearing.
  • the second bearing 25 is formed as a ball bearing.
  • the drive shaft 6 has an outer toothed region 7 which is integral with it / directly formed.
  • the external toothing region 7 is arranged directly radially outside the first bearing 5.
  • two rolling bearing tracks 8, 9 of the first bearing 5 overlap in the axial direction with teeth 24 of the external toothing region 7 at least in sections.
  • a first rolling bearing track 8 is provided directly on the shaft portion 10 (on a radial outside of the shaft portion 10); a second rolling bearing track 9 is provided directly on the drive shaft 6 (on a radial inner side of the drive shaft 6).
  • a plurality of rolling bodies 28 distributed in the circumferential direction are arranged.
  • the drive shaft 6 is divided into two parts.
  • the drive shaft 6 has a first drive shaft section 11 (designed as a first tube) and a second drive shaft section 12 (designed as a second tube).
  • the first drive shaft section 1 1 directly takes the rotor 4 against rotation.
  • the second drive shaft section 12 directly forms the outer gear section 7 on a longitudinal region protruding axially from the first drive shaft section 11.
  • the two drive shaft sections 1 1, 12 are rotatably coupled together.
  • an overload protection clutch 13 is integrated in the drive shaft 6.
  • the overload protection clutch 13 is in the form of a slip clutch and designed so that it is closed below a predetermined limit torque, so that the two drive shaft sections 1 1, 12th rotatably connected to each other, and above this limit torque opens so that the two drive shaft sections 1 1, 12 are freely rotatable to each other. As a result, an impact protection for the electric motor 1 is ensured.
  • the overload protection clutch 13 is thus used in such a way that it rotatably connects the rotor 4 with the second drive shaft section 12 / the external gear section 7 below the limit torque and opens when the limit torque is exceeded and a free rotation of the rotor 4 relative to the second drive shaft section 12 / the external gear section. 7 allows.
  • the overload protection clutch 13 is used in this first embodiment in the radial direction between the two drive shaft sections 1 1, 12.
  • the overload protection coupling 13 is designed as a shaft-hub connection 40 which connects the two drive shaft sections 11, 12 in a materially and non-positively connected manner.
  • a shaft of the shaft-hub connection 40 is formed by the second drive shaft section 12 and a hub of the shaft-hub connection 40 is formed by the first drive shaft section 11.
  • the overload protection coupling 13 / the shaft-hub connection 40 is divided into two axially spaced-apart overload protection coupling regions 39a, 39b.
  • the overload protection coupling 13 forming a connection area between the drive shaft sections 1 1, 12 is divided into two overload protection coupling areas 39 a, 39 b spaced apart in the axial direction.
  • Each overload protection coupling portion 39a and 39b forms a press-press soldering connection.
  • the second drive shaft section 12 is frictionally held in the respective overload protection coupling region 39a, 39b via a press fit in the first drive shaft section 11.
  • a cohesive connecting layer 41 in the form of a soft metal layer is introduced radially between the drive shaft sections 11, 12 per overload protection coupling area 39a, 39b.
  • the shaft-hub connection 9 is implemented as the press-press-soldering connection.
  • this press-press soldering connection reference is made to DE 10 2015 208 146 A1, the implementations of which for the press-press soldering connection being considered to be integrated here. In Fig.
  • a lubricant supply for the external gear portion 7 of Fig. 1 is illustrated.
  • the external toothing region 7 is arranged in a lubricant accommodating space 14, which is at least partially filled with lubricant during operation.
  • This lubricant accommodating space 14 is sealed against a rotor accommodating space 15 of the housing 2 accommodating the rotor 4.
  • a sealing ring 29 is inserted between the housing 2 and a radial outer side of the drive shaft 6.
  • the lubricant receiving space 14 is adjoined by a lubricant channel 16 which dissipates the lubricant during operation.
  • the lubricant runs down on an inner side / side wall formed by a cover 33 of the housing 2 and penetrates into the lubricant channel 16.
  • a collecting channel is attached / formed on the inner side / side wall of the housing 2 / of the cover 33 in further embodiments.
  • the lubricant channel 16 is formed by the housing 2 and the shaft region 10 such that the lubricant in operation in the lubricant accommodating space 14 is supplied to the shaft region 10 from the first end region 22 forming the (first) end face 30 of the shaft region 10. On the part of a second end region 23 with forming (second) end face 31, the lubricant is removed.
  • the shaft portion 10 / the bearing shaft is designed as a hollow shaft.
  • part of the lubricant channel 16 is formed directly by a through-hole 43 penetrating the shaft region 10.
  • the lubricant channel 16 is formed by further holes 32 introduced directly into the housing 2.
  • the bores 32 connect the through-hole 43 extending through the shaft region 10 to the lubricant accommodating space 14.
  • the lubricant passage 16 extends from the second end face 31 of the shaft region 10, again radially outward, over a connecting bore 42 extending transversely to the shaft region 10 in the housing 2 merges into a radial gap 36 / gap between the drive shaft 6 and the shaft portion 10. There, the two bearings 5, 25 are arranged.
  • the lubricant channel 16 is designed in such a way that a portion of the lubricant previously conveyed outward in the radial direction from the outer toothed region 7 from the lubricant accommodating space 14 by means of the lubricant channel 16, the second bearing 25 and in turn thereafter the first bearing 5 in the axial direction flows through.
  • the bearing shaft From the first bearing 5 from the gap 36 is in a passage 30, which is connected to a transmission shaft 18 receiving the gear housing 34 of the transmission 19.
  • a second exemplary embodiment according to FIG. 3 for which only the differences from the first exemplary embodiment are listed below for the sake of brevity, it can be seen that in principle it is also possible to form the bearing shaft somewhat differently in the form of the wave region 10.
  • the shaft portion 10 is hollow only in a limited longitudinal region.
  • a subsequent second longitudinal region of the shaft portion 10 is designed as a solid shaft.
  • the lubricant channel 16 thus has, instead of the through-hole 43, a blind hole 35 introduced in the shaft region 10. In operation, the lubricant flows through the blind hole 35 and in the radial direction outside the shaft portion 10, in the gap 36 it is supplied in two partial streams in two axially opposite directions to the first bearing 5 and the second bearing 25.
  • connection 37 is provided in the housing 2, through which the lubricant previously flowed through the second bearing 25 can be returned to the lubricant system.
  • the second bearing 25 can also be positioned in other ways.
  • the second bearing 25 is used on the second axial side of the rotor 4 for supporting the drive shaft 6 (in the radial and axial directions) relative to the housing 2 directly.
  • the second bearing 25 is radially outside the drive shaft 6 between see the housing 2 and the drive shaft 6 used.
  • the drive shaft is integrally formed in this embodiment.
  • the shaft region 10 may also be fixed in other manner in a positive and / or non-positive and / or material fit in the housing 2.
  • the shaft region / the rotor shaft 10 lies with its second end region 23 / its second end face 31 only axially in the second receiving region 27 on the housing 2.
  • the second receiving area 27 thus serves only as an axial stop area.
  • a further third bearing 47 (designed as a roller bearing, namely a needle / roller bearing) is inserted radially between the drive shaft 6 and the shaft region 10 (in the second end region 23).
  • the third bearing 47 is nested radially, namely arranged radially inside the second bearing 25 (in turn executed as a ball bearing).
  • the second bearing 25 is in turn directly (in contrast to the indirect arrangement of the first embodiment on the shaft portion 10) in the housing 2, between the housing 2 and the drive shaft 6, arranged / set.
  • the shaft portion 10 is fixed on one side only (in the first end portion 22) rotatably in the housing 2 (via the press fit).
  • the housing 2 serves merely as an axial stop.
  • a bearing 5 (roller / needle bearing) is placed immediately below the pinion toothing (/ of the external toothing region 7).
  • an additional, standing wave (wave range 10) is provided which is mounted against rotation in the housing 2 is.
  • Rotor 4 and bearing 5 rotate about this shaft 10.
  • the standing shaft 10 is hollow drilled so that lubricant through it in the form of oil for lubrication of the opposite (second) bearing 25 can be promoted.
  • the transmission concept 19 likewise has an intermediate gear 44, which serves for transmitting the e-machine power from the drive pinion (the outer toothing region 7) to the transmission input shaft (transmission shaft 15). Again, the concept of a standing wave 45 is provided.
  • the lubrication of the e-motor bearings takes place in particular such that the spray oil from the pinion 7 on the housing wall (inside of the housing 2) of the gear cover 33 runs down and through a channel (holes 32) to the hollow drilled, standing wave (Wave range 10) is passed.
  • a collecting channel may be attached / formed on the housing wall 2. In the hollow bore (through hole 43), the oil reaches the rear ball bearing
  • the lubrication of the electric motor bearings 5 and 25 is carried out in particular such that the spray oil from the pinion 7 on the housing wall of the gear cover 33 runs down and is through the channel 32 to the central bore (blind hole 35) standing wave 10 is passed.
  • the channel 32 can in principle also be realized by an additionally attached cap.
  • the heat of the rotor 4 is also removed via the oil. LIST OF REFERENCE NUMBERS

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

L'invention concerne un moteur électrique (1) pour une chaîne cinématique de moteur à combustion interne, ledit moteur électrique comportant un carter (2), un stator (3) monté solidaire du carter, un arbre moteur (6) logeant un rotor (4) et étant monté de manière à tourner relativement au carter (2) par l'intermédiaire d'un palier (5) ainsi qu'une zone de denture extérieure (7) reliée solidaire en rotation à l'arbre moteur (6) et agencée de manière décalée par rapport au rotor (4) dans une direction axiale de l'arbre moteur (6), ledit palier (5) étant monté radialement à l'intérieur de la zone de denture extérieure (7), de sorte que le palier (5) est recouvert dans la direction axiale, au moins en partie, par la zone de denture extérieure (7). L'invention concerne également une chaîne cinématique (20) présentant ledit moteur électrique (1).
PCT/DE2018/100585 2017-06-27 2018-06-25 Moteur électrique à palier et chaîne cinématique Ceased WO2019001634A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017114211.8A DE102017114211A1 (de) 2017-06-27 2017-06-27 Elektromotor mit Lagerung sowie Antriebsstrang
DE102017114211.8 2017-06-27

Publications (1)

Publication Number Publication Date
WO2019001634A1 true WO2019001634A1 (fr) 2019-01-03

Family

ID=62980974

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2018/100585 Ceased WO2019001634A1 (fr) 2017-06-27 2018-06-25 Moteur électrique à palier et chaîne cinématique

Country Status (2)

Country Link
DE (1) DE102017114211A1 (fr)
WO (1) WO2019001634A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116113773A (zh) * 2020-08-10 2023-05-12 罗伯特·博世有限公司 用于车辆的驱动单元

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102024107393B4 (de) * 2024-03-15 2025-10-16 Schaeffler Technologies AG & Co. KG Elektromotor mit Wickelkopfeinhausung mit einer luftspaltabschirmenden Innenwandung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010095610A1 (fr) * 2009-02-20 2010-08-26 Miyamoto Yutaka Véhicule électrique de type hybride
EP2562914A1 (fr) * 2010-04-23 2013-02-27 IHI Corporation Machine rotative
DE102016124126A1 (de) 2016-12-13 2018-06-14 Schaeffler Technologies AG & Co. KG Zahnradanordnung mit einer Überlastkupplung sowie elektromotorisch antreibbaren Antriebsstrang

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010095610A1 (fr) * 2009-02-20 2010-08-26 Miyamoto Yutaka Véhicule électrique de type hybride
EP2562914A1 (fr) * 2010-04-23 2013-02-27 IHI Corporation Machine rotative
DE102016124126A1 (de) 2016-12-13 2018-06-14 Schaeffler Technologies AG & Co. KG Zahnradanordnung mit einer Überlastkupplung sowie elektromotorisch antreibbaren Antriebsstrang

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116113773A (zh) * 2020-08-10 2023-05-12 罗伯特·博世有限公司 用于车辆的驱动单元

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