CN108368933A - Transmission and drive unit with transmission - Google Patents
Transmission and drive unit with transmission Download PDFInfo
- Publication number
- CN108368933A CN108368933A CN201680073011.XA CN201680073011A CN108368933A CN 108368933 A CN108368933 A CN 108368933A CN 201680073011 A CN201680073011 A CN 201680073011A CN 108368933 A CN108368933 A CN 108368933A
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- China
- Prior art keywords
- ball bearing
- central axis
- ball
- transmission device
- sun gear
- Prior art date
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 51
- 238000005096 rolling process Methods 0.000 claims description 49
- 230000033001 locomotion Effects 0.000 claims description 5
- 238000012512 characterization method Methods 0.000 claims description 2
- 238000010276 construction Methods 0.000 claims 1
- 238000003475 lamination Methods 0.000 description 9
- 240000002853 Nelumbo nucifera Species 0.000 description 3
- 235000006508 Nelumbo nucifera Nutrition 0.000 description 3
- 235000006510 Nelumbo pentapetala Nutrition 0.000 description 3
- 230000000295 complement effect Effects 0.000 description 3
- 210000001331 nose Anatomy 0.000 description 3
- 206010068051 Chimerism Diseases 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 241000276457 Gadidae Species 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
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
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2845—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the sun gear
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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
- F16C19/545—Systems comprising at least one rolling bearing for radial load in combination with at least one rolling bearing for axial load
-
- 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
-
- 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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
-
- 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
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
-
- 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
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
- F16C19/166—Four-point-contact ball bearings
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- General Details Of Gearings (AREA)
Abstract
The invention relates to a transmission (2) having at least one housing (7) and a planetary transmission (8), wherein the planetary transmission (8) is formed at least by a planet carrier (10) which is rotatably mounted in the housing (7) about a central axis (3) of the transmission (2) and by a sun gear (6) which is rotatable about an axially oriented central axis (3) and which is in toothed engagement with the planet gears (9), and wherein the sun gear (6) is axially supported on a component (34) of the transmission (2) by means of an axial bearing (11) in the same direction as the central axis (3).
Description
Technical field
Transmission device has at least one shell and planetary driving device, wherein planetary driving device is at least by around biography
The central axis of dynamic device be rotatably supported in planet carrier in shell and by it is rotatable around axial central axis,
The sun gear that tooth chimerism is in planetary gear is constituted, and wherein, and sun gear is in the same direction using cod and central axis
Ground is axially supported on the component of transmission device.The invention further relates to a kind of drivings with electric drive and this transmission device
Unit, in the transmission device, sun gear is connected with the armature spindle of electric drive.
Background technology
This transmission device discloses in JP2011208758A2.Transmission device belongs to hybrid drive train, and there are one its tools
Internal combustion engine and two motor.The motor can be chosen for use as driver or generator.One of driver turns
Sub- axis is supported on using ball bearing in the shell of driving unit as common as in electro-motor, and is passed through
It is effectively connect with planetary driving device by the slip-clutch of multidisc clutch type.Planetary driving device have planet carrier,
Planetary set, gear ring and sun gear.Multidisc clutch is made of external lamination holder and internal lamination holder.External is folded
The hub of plate rack is furnished with spline, and the spline of the spline and armature spindle is in the sealed connection of shape.In external lamination holder
On, the external laminations that can be elapsed in the axial direction are placed as seeing as usual in inside, these external laminations and multiple-piece clutch
The internal laminations of device replace.For internal lamination from external internally placed lamination holder, its hub is planetary driving device
Sun gear.The mullion of sun gear and internal lamination carrier are fixedly connected to each other.Sun gear is borrowed in a supporting portion
It helps sliding bearing to be radially supported on armature spindle, and is axially supported on by cod in another supporting portion
On planet carrier.Planet carrier is radially supported on via needle bearing on axis, and this axis is radially supported via ball bearing
On the shell of driving unit.
Sun gear allow on planetary gear freely in the clear radially itself relative to planetary driving device
Central axis centering so that power is delivered evenly to and all is on the planetary gear of tooth chimerism with sun gear.
Sun gear equipped with helical teeth portion is axially supported on via cod on planet carrier herein.
The shortcomings that this arrangement, is that the connection and centre that the shape of the structural detail of rotation or its bearing is sealed are wrong
Position can interfere self-centering.Thus undesirable power of enforcement is generated in teeth portion and bearing, it may cause driving unit to lose in advance
Effect.Therefore each component and its cooperation must be highly precisely made with expending accordingly with high cost.In order to overcome this
Point often also produces connection that have the shortcomings that significantly greater gap, that shape is sealed to compensate these.However this is larger
Gap again exactly cause in there are the connection of undesirable dislocation connection in relative motion.These relative motions may be led
It causes noise and undesirable abrasion may also be caused.
In addition, the axial clamping force in this arrangement may lead to have axial power to act on supporting portion, it
Ball bearing is not to bear big axial force designed for being not suitable for use in.It is negative in axial direction in order to cope in this case
Lotus is " transferred " on axial needle roller or roller bearing, they accordingly must greatly design and therefore need very for high load capacity
More structure spaces.
Invention content
Therefore the task of the present invention is to create a kind of transmission device and especially a kind of driving unit with electric drive
Electric drive transmission device, wherein avoid the clamping force between structural detail, sun gear can be fixed wherein in the clear
The heart and need few structure space.
The task theme according to claim 1 is addressed.
Present invention provide that the cod for the sun gear in transmission device is ball bearing.Another right
It is required that defining a kind of driving unit with this transmission device.
Sun gear is axially supported in a manner of being supported on component by ball bearing.Component for example can be transmission
Axis, adjacent planet carrier or shell.It is that component is the planet carrier of transmission device as defined in a kind of structural scheme of the present invention.
Ball bearing is journal bearing and is at least furnished with anti-the the first rolling raceway for being associated with sun gear with the relative rotation in type
And at least one second constructed on outer ring rolls raceway and equipped with the ball being radially disposed between rolling raceway.Outside
The second rolling raceway on circle is concentrically surrounding the first rolling raceway at sun gear in side.As alternative or preferably,
Interior rolling raceway is leaned against in placement/peace to be constituted on the inner ring on sun gear.It is the particular approach of the present invention to which ball bearing is outer
Circle is movably freely arranged radially relative to component, so that ball bearing is with its, initial determination is opposite is used only as axial direction
Bearing.The central axis of transmission device is axially orientated.Therefore, radial transverse to central axis.
The outer ring of ball bearing is preferably axially locked in both sides on component, to which sun gear is advantageously in two axis
It is axially supported on direction.Relative to bearing that is common, being carried out using axial needle bearing, this has the advantages that multiple.Often
Axial direction seeing, working in opposite axial directions is supported in transmission mechanism and is arranged in the component for needing to support by two
Left and right side axial needle bearing or roller bearing composition.Correspondingly, for manufacture and installation two is generated
Cost in a bearing to transmission mechanism.It is necessary for two bearing preset structure spaces.In transmission device according to the present invention,
The structure space for a bearing is only needed on the contrary.Cost for manufacturing and assembling transmission device is because be used only one
Bearing and greatly reduce.The interior friction of ball bearing is less than the interior friction of cod.For lubrication in transmission device and cold
But consuming can be reduced by using ball bearing.
Ball bearing advantageously can be the catalogue part provided as bulk article.They are extremely suitable for use in high rotating speed
Under.Because outer ring is freely arranged, ball bearing cannot bear radial load, but axial force is uniformly allocated to institute
Some balls.Sun gear still can freely feel relieved although having used journal bearing, this is because outer ring is relative to the structure
Part is (freigestellt) being freely arranged.The rated speed of the permission of ball bearing is apparently higher than the volume of axial needle bearing
Determine rotating speed.
The cod for being normally used for axially supporting belongs to the type of axial needle bearing, it is by two axial disks and one
A needle roller hat is constituted.It is the guided needle roller in axial cage known in the rolling element of needle roller hat.It is in rolling contact corresponding
Ground is configured to line contact.Therefore these bearings have relatively high axial carrying capacity.The interior friction of cod is correspondingly high.
In addition, because speed discrepancy between the radially inner side of axial raceway and the radial outside of axial raceway and to axial needle bearing or
The rotating speed of roller bearing is provided with limitation.In the driving unit of electric motor, turn along with the high driving of electro-motor
The power of speed is lowered to smaller rotating speed and higher torque by epicyclic transmission mechanism.Epicyclic transmission mechanism joins with armature spindle
The input shaft connect this 1:1 ground is subjected to the driving rotating speed of electro-motor.Because input shaft is sun gear in this case,
Correspondingly must axial needle bearing be set for high rotating speed according to the prior art.This is non-sometimes for the above reasons
It is often difficult.Thus cod becomes very fragile, because its load limit itself is exhausted since rotating speed limits.By
The axial load obtained from tooth forces (its based on due to dislocation caused by axial force or stress further become higher), meeting
Lead to this class bearing premature failure of axial needle bearing with can not avoiding.
Ball bearing used in transmission device according to the present invention preferably arranges with one or can also be with more
It is listed in the adjacent ball in side.The ball central point of one row ball is with the rotation axis diameter having the same relative to ball bearing
It is in central point sagittal plane to the mode of spacing, the central point sagittal plane is by the rotation axis of ball bearing and transmission
Pass through to the central axis upright of axis.
The rolling raceway of ball bearing is the groove extended around rotation axis, they axially two circlewise around
It is constituted between the edge that rotation axis extends.Groove is in arbitrary profilograph lengthwise along the rotation axis of ball bearing
It is configured to curve.Curve axis side at interior rolling raceway from the departure place of ball center towards the direction of rotation axis/axis
Be bent to spill, or shell side at outer rolling raceway from the departure place of ball center towards the direction spill of shell
Bending.Curve is described by radius respectively in the simplest case.This radius is more than ball bearing radius.Radius and ball half
Ratio between diameter is referred to as spending closely.Groove observed in this vertical section but can not only by unique radius, but
Can be described using arbitrary curved course, for example, by multiple interconnections, curve section with different radii come
Description.These curves are respectively provided with vertex.Vertex is understood to be in the point on curve along load direction under rated condition,
Described, curve is changed direction in terms of its trend.
The type of ball bearing can according to set orientation under rated load and according to operation in its contact
Quantity and therefore obtained load direction describe.Here, to when ball bearing is zero load rated condition in ball axis
Load condition when carrying lotus is distinguish.
Ball bearing is characterized by ball with the point contact for rolling raceway.Here, being in rated condition in ball bearing
It rolls when lower, including the convexly curved surface of ball and is propped up respectively in the correspondingly concave groove of raceway and outer rolling raceway
Support is at least one contact.Here, the contacts of two rolling raceways with ball central point be with reference to mutually opposed, and can be with
It is connected using imaginary pressure line.Pressure line extends through ball central point herein.In the case where ball bearing is in rated condition
When the angle that is constituted between corresponding pressure line and central point sagittal plane be referred to as nominal pressure angle.Central point sagittal plane it
Between, relative to 90 ° of angles complementary angle be correspondingly between pressure line and central axis press from both sides angle.
In ball bearing load, observe due to the radial and axial obtained bearing load of component (power), it
Extend along pressure line under load condition.Here, one of component may be zero.
Under load condition, point contact becomes in order to which face contacts, and is ideally described as pressure ellipse.Pressure is elliptical
Extend additionally related with the size of load, the size of ball and the rolling geometric properties of raceway.Corresponding pressure line is negative
The face center of gravity of two elliptical ellipsoids of pressure is extended through under lotus state and passes through ball central point.Pressure line is herein with fortune
Row pressure angle is tilted relative to central point sagittal plane, and the operating pressure angle can be different from nominal pressure angle.Operating pressure
Angle and nominal pressure angle difference are much on earth, following standard are depended on, as the action direction of resultant, the running clearance of bearing, bullet
Property deformation, the direction transformation of load and ball bearing type.
In transmission device, at least two classes of the generic of radial ball bearing are selectively provided with according to the present invention
Type, however they are used for axial bearing of the sun gear on planet carrier.
Present invention provide that using at least one radial ball bearing, it can be the ball axis with two-point contact
It holds and it is widely also referred to as radial deep groove ball bearing or radial ball bearing.In the radial direction rolling in two-point contact
In pearl bearing, pressure line under rated condition first radially towards rotation axis be orientated, and on common point with rotation
Axis intersects.Interior rolling raceway and outer rolling raceway are disposed concentrically upon to each other as follows, that is, the spill of two rolling raceways
The vertex of curve mutual opposed in central point sagittal plane radially, ball center under the rated condition of ball bearing
It also is located in the central point sagittal plane.Contact is located in sagittal plane on the vertex for the curve for rolling raceway.Rated pressure
Angle is 0 °.
In support loading only radially, the resultant of radial ball bearing middle (center) bearing load is vertical using two-point contact
In rotation axis it is directed toward.Bearing load be partially distributed in radial ball bearing ball bearing it is only several side that
On this adjacent ball, and others almost keep non-loaded.Bear pressure line in the ball of load herein also radially
It perpendicular to rotation axis is orientated, and is all in a sagittal plane and extends.In corresponding pressure line and sagittal plane
Between the corresponding operating pressure angle that constitutes corresponding to nominal pressure angle and be equal to 0 °.
When radial deep groove ball bearing is also loaded with axial force component, that is to say, that also with the power in the same direction with rotation axis
When being acted on, rolling raceway may mutually elapse and/or overturn relative to each other in the axial direction.The ball of each ball
Central point may be elapsed from common sagittal plane towards sagittal plane different, adjacent to each other.Obtained bearing load
It can fall in a pressure line, this pressure line is angularly radially put down towards side with the operating pressure more than 0 ° according to load direction
Face tilts, and in the other directions with 0 and less than 90 ° between, corresponding complementary angle tilts to rotation axis.Axial component
Partly it is distributed on the ball of ball bearing.Radial component according to axial component size be distributed only over it is several peripheral side that
On this adjacent ball, or sufficiently large axial component more or less part passed through based on the axial prestress of ball bearing
Ground is distributed on all balls.The vertex of the curve of the spill of raceway is rolled according to bearing clearance, closely degree and elastic deflection
Mutually it is directed towards passage as follows in the axial direction, that is, so that compared to the corresponding vertex of outer rollaway nest, the interior vertex for rolling raceway
In the sagittal plane that another is vertically passed through by rotation axis.Pressure is oval and its center of gravity is correspondingly from common
Sagittal plane and vertex are released, and at the same time coming the corresponding edge for rolling raceway upwards.When ball connects with raceway is rolled
It touches herein moved as far into the edge at edge, then pressure ellipse just can not be formed to complete holohedral form.And at edge
On seamed edge " broken to lack ".It is distributed to the Stress non-homogeneity generated herein, and the seamed edge beyond edge.It thus may be on the side at edge
It generates the edge stress that does not allow along upper and generates undesirable peak stress in ball.Therefore, with two-point contact
Ball bearing can only bear limited axial support loading.Because deep groove ball bearing can only be axial in use according to the present invention
Ground loads, so these loads are advantageously distributed to first on all balls rather than in a part.Deep groove ball bearing can be with
It uses at high speed, and small interior friction is only had based on two-point contact.However, deep groove ball bearing also can only be expected
It is used in the case that axial force is smaller.
Therefore the another kind of the present invention and preferred structural scheme define the use of 4 ball bearings.In 4 balls
In bearing, internal rolling raceway and outer rolling raceway are in arbitrary vertical section along the rotation axis quilt across ball bearing
It separates, and is described respectively by the curve of two spills or two vertex.This can be in undivided bearing race respectively
Groove on or by two of bearing race enclose it is constituting, on " separating " groove.Thus corresponding ball is obtained at least in volume
Determine the contact on four contacts under state.Outer rolling raceway has two of which contact, and two contact designs are rolled inside
On dynamic raceway.
Groove is following concentrically with each other radially to be arranged, that is, is passing through the arbitrary of ball bearing along rotation axis
In vertical section, correspondingly, a vertex of outer rolling raceway is not only opposite in the axial direction with another vertex of outer rolling raceway
Set, but also with it is interior rolling raceway on a vertex be radially staggered in the axial direction in a plane or slightly it is opposite
It sets.Here, it is interior roll raceway vertex under rated condition and under load condition have relative to rotation axis it is identical
Radial spacing, but be in different sagittal planes with being separated from each other in the axial direction.Sagittal plane in the axial direction with center
Point sagittal plane is adjacent.This equally sets up outer rolling raceway.Under normal circumstances, correspondingly, interior roll raceway one
Vertex and a vertex of outer rolling raceway are in common sagittal plane, this common sagittal plane is vertically by ball
The rotation axis of bearing passes through.Under rated condition, vertex is contact.
Contact geometry feature is constituted as follows, that is, has a pressure line respectively on each ball of 4 ball bearings
It is placed through in the first sagittal plane and outer rolling raceway contact and across in the second sagittal plane and interior rolling
Extend to the contact of dynamic raceway, and an also pressure line be placed through it is in the second sagittal plane, with outer rolling raceway
Contact and be placed through it is in the first sagittal plane, with it is interior roll raceway contact extend.Corresponding pressure line is according to limit
Surely the corresponding ball central point being perforated through in central point sagittal plane.From the pressure line of wherein side in common intersection point
The upper central axis with the rotation axis of 4 ball bearings or transmission device intersects.There are two pressure lines altogether respectively as a result,
It is located on one of the ball central point in central point sagittal plane ball center intersection.On rotation axis
Intersection point is spaced from each other in the axial direction, and is axially spaced in left and right side and sagittal plane, and ball center exists
In the sagittal plane.Thus it obtains, pressure line is respectively with the nominal pressure angle more than 0 ° and with less than 90 °, corresponding
Complementary angle is obliquely oriented relative to sagittal plane.
Under the load condition there is only radial load, the power in 4 ball bearings is distributed to only several sides phase each other
On adjacent ball, so that these balls are supported on four contacts in ball bearing.With radial direction and axial
Load load condition under, these contacts are relatively firmly maintained at apex, or only slightly therefrom remove, that is,
Say that nominal pressure angle is identical or almost the same with operating pressure angle.This deviation can be by axis in the frame of running clearance
Overturning and closely degree preset.It rolls raceway and then bearing race is all relatively firmly maintained on their position.Therefore,
It need not advantageously consider variation of the contact relative to the orientation at corresponding edge.Big axial load can be born, is especially handed over
For load.
The interior friction of 4 ball bearings in general, namely under radial load or combination radial direction-axis
To load when, based on being four point contacts so relatively large.However, in only axial load, the base in 4 ball bearings
The two-point contact according to angular contact ball bearing type is but formed in running clearance, to which this disadvantage can be by according to the present invention
Ground is excluded using 4 ball bearings.This allows for that the interior of two-point contact of high rated speed, deep groove ball bearing is allowed to rub
Smaller these advantages with the high intensity of 4 journal bearings are wiped to unite.
Description of the drawings
Below the present invention is more fully illustrated by a kind of embodiment of the driving unit 1 with transmission device 2.
Driving unit 1 is shown with the profilograph of the central axis 3 along transmission device 2 to Fig. 1 simplified schematics.
Fig. 2 enlargedly shows the details Z from transmission device 2 shown in FIG. 1 with not meeting actual proportions.
Specific implementation mode
Fig. 1：There is driving unit 1 electric motor driver 4, the sun gear 6 of its armature spindle 5 and transmission device 2 to pass through
It is effectively connected by the sealed connection of shape.The sealed connection of shape is, for example, to be set up by spline, to which sun gear 6 is opposite
It limitedly can axially be elapsed in armature spindle 5.It thus ensures, the supporting part 28 of armature spindle 5 can not apply with the axis of sun gear 6
Xiang Li.Transmission device 2 is incompletely shown.It can be seen that a part for shell 7 and planetary driving device 8.Planetary driving device 8
At least it is made of planet carrier 10, sun gear 6 and one group of planetary gear 9.There are two loading plate 10a and 10b for the tool of planet carrier 10, on it
Carry planet pin 9a.Planetary gear 9 is placed on planet pin 9a.During sun gear 6 and planet carrier 10 rotation axis is respectively
Mandrel line 3.Sun gear 6 by cod 11 by with central axis 3 it is in the same direction in the way of axially support or be supported on transmission device 2
Component 34 on.On shaft end that cod 11 is placed in sun gear 6, axially deviating from armature spindle 5 and it is placed in structure
In part 34.Component 34 is planet carrier 10 in the present embodiment.
Fig. 2：Planet carrier 10 has housing bore 18 in loading plate 9b, it be drill out, punching press or arbitrarily with its other party
Formula is introduced into the material of planet carrier 10.It is in the face 18a that internal structure goes out inner cylinder in housing bore 18.
Cod 11 is ball bearing 12.Ball bearing 12 has the interior rolling raceway 13 on inner ring 14.Inner ring 14 is
It is separated and be fixedly mounted on the spindle nose 6a of sun gear 6.Separated interior rolling raceway 13 is configured on inner ring 14.Make
For alternative it is contemplated that interior rolling raceway is introduced directly into the surface of spindle nose 6a.In addition, ball bearing 12 is furnished with outer ring 15,
It is configured with outer rolling raceway 16 thereon.Outer ring 15 surrounds inner ring 14 in side around 3 ground of central axis.Raceway 13 is rolled as a result,
With 16 each other part be disposed concentrically upon.Radially, between outer ring 15 and inner ring 14, ball 17 in a manner of row side around
Central axis 3, which is arranged in, to be rolled on raceway 13 and 16.The rotation axis and central axis 3 of ball bearing 12 overlap.Outer ring
15 it is diametrically opposed be movably freely arranged in component 34, and here, can be diametrically opposed in radial clearance S
It is moved in the face 18a of inner cylinder, and is axially fixed to 19 He of relieving ring towards the both direction of central axis 3 in the axial direction
Between housing shoulder 18b.Axial gap S is made of according to shown in Fig. 2 the gap size S1 and S2 of annulus 20, therein every
One size is the half of radial clearance S in the ideal case.In the ideal case, sun gear 6 is fixed as follows on planetary gear 9
The heart, that is, its rotation axis is accurately concentrically consistent with central axis 3.Sun gear 6 is supported on the only one of transmission device 2
In supporting portion, which there is ball bearing 12 to be used as unique bearing.The advantage is that therefore sun gear 6 can lead to
It crosses and overturns and/or move in parallel relative to central axis 3 in the frame in gap and feel relieved in the clear.
Fig. 1 and 2：Ball bearing 12 is 4 ball bearings, wherein the ball central point 23 of ball, which is located at, to be extended vertically
In central point sagittal plane ME in figure plane.4 ball bearings it is shown and along central axis 3 extend
Vertical section in (especially see Fig. 2) respectively by two it is imaginary, at ball central point 23 intersect and wear respectively herein
Cross contact line 21 and 22 of the ball with interior the first contact 24 for rolling raceway 13 and with the second contact 25 of outer rolling raceway 16
Characterization.There are contact points 24 and 25 in each sagittal plane E1 or E2.During two sagittal planes E1 and E2 are parallel on the left side
Extend to heart point sagittal plane ME.Each contact line is all tilted with the angle of 90 ° of 0 ° of ＞ α ＞ to central axis, preferably with 90 °
The angle of 55 ° of ＞ α ＞ is tilted to central axis.Gap from this contact geometry form and ball bearing 12, the sun
Wheel 6 is supported on inner ring via shaft shoulder 26 by the axial force towards one of axial direction according to load direction and edge
It contact line 22 to be supported in housing bore 18 via outer ring 15 and relieving ring 19, or passes through the axis towards another axial direction
It is supported on inner ring 14 via relieving ring 27 to power and is supported on housing shoulder 18b via outer ring 15 along contact line 21.
Selected angular range ensures, 4 ball bearings of standard, such as catalogue item series can be used as axial axis
Hold, and it is axial on can load-bearing capacity at high speed still in optimum range.
Fig. 1：Planet carrier 10 around central axis 3 is revolvably supported on the first supporting portion 29 and in the axial direction with first
At supporting portion the second supporting portion 30 spaced apart, and it is fixedly fastened in opposite axial directions on shell 7.Often
A supporting portion 29 and 30 all has angular contact ball bearing 31 and 32.Each angular contact ball bearing 31 and 32 is according to Fig. 1
Vertical section in characterized by contact line 33, these contact lines with the angle of 90 ° of 0 ° of ＞ α ＞ relative to central axis 3 tilt.
Here, angular contact ball bearing 31 and 32 is set up as follows relative to each other, that is, contact line 33 is being axially located at two respectively
Intersect with central axis 3 at intersection point 35 between a supporting portion 29 and 30.Ball bearing 12 and one of angular contact ball axis
It holds 32 concentrically to arrange as follows, that is, so that it is surrounded by angular contact ball bearing 32, to required for two ball bearings 12 and 32
Axial structure space be advantageously minimized to the space requirement of only one ball bearing.
Reference numerals list
1 driving unit
2 transmission devices
3 central axis
4 electric motor drivers
5 armature spindles
6 sun gears
6a spindle noses
7 shells
8 planetary driving devices
9 planetary gears
9a planet pins
10 planet carriers
10a loading plates
10b loading plates
11 cods
12 ball bearings
Raceway is rolled in 13
14 inner rings
15 outer rings
16 outer rolling raceways
17 balls
18 housing bores
The surface of 18a inner cylinders
18b housing shoulders
19 relieving rings
20 annulus
21 contact lines
22 contact lines
23 ball central points
24 contacts
25 contacts
26 shaft shoulders
27 relieving rings
The supporting part of 28 armature spindles
29 supporting portions
30 supporting portions
31 angular contact ball bearings
32 angular contact ball bearings
33 contact lines
34 components
35 intersection points
Claims (10)
1. transmission device (2), at least one shell (7) and planetary driving device (8), wherein planetary driving device (8)
At least by the planet carrier (10) that can be rotatably supported at around the central axis of transmission device (2) (3) in shell (7) and around axis
To orientation central axis (3) it is revolvable, be in the chimeric sun gear (6) of tooth with planetary gear (9) and constitute, and wherein, institute
State the component (34) that sun gear (6) is axially supported at transmission device (2) using cod (11) in the same direction with central axis (3)
On, which is characterized in that the cod (11) is ball bearing (12), wherein the sun gear (6) is by ball bearing
(12) it is revolvably supported on the component (34) around central axis (3), and the ball bearing (12) is at least arranged
There are the rolling raceway (13) for resisting the inside for being associated with sun gear (6) with the relative rotation and at least one construction on outer ring (15)
External rolling raceway (16) and it is provided with the ball (17) for being radially disposed at and rolling between raceway (13,16), wherein institute
External rolling raceway (16) is stated concentrically in a manner of side around internal rolling raceway (13), and here, described outer
Circle (15) is freely arranged transverse to central axis (3), relative to the component (34) in which can move radially radially.
2. transmission device according to claim 1, which is characterized in that the component (34) is planet carrier (10), and institute
State outer ring (15) be axially fixed in the opposite direction planet carrier (10) inner cylinder and it is concentric with central axis (3)
Housing bore (18) in, wherein be configured with housing bore (18) central diameter between the housing bore (18) and outer ring (15) of inner cylinder
To, the movement clearance that is transversely to the axial direction.
3. transmission device according to claim 2, which is characterized in that radial movement clearance is by around central axis (3)
Circular annulus (20) is constituted.
4. transmission device according to claim 1, which is characterized in that the ball bearing (12) is 4 ball bearings,
Wherein, 4 ball bearings are arbitrary, imaginary and along central axis (3) extend through the ball bearing
(12) by corresponding imaginary, intersecting at ball central point (23) and be each passed through ball (17) herein in vertical section
With the first contact (24) of internal rolling raceway (13) and with the contact of the second contact (25) of external rolling raceway (16)
Line (21,22) characterizes, and wherein, each contact line (21,22) is all with the angle of 90 ° of 0 ° of ＞ α ＞ relative to central axis
(3) it tilts.
5. transmission device according to claim 1, which is characterized in that the angle is 90 ° of 55 ° of ＞ α ＞.
6. transmission device according to claim 1,2 or 4, which is characterized in that the sun gear (6) is in only one supporting part
It is supported in transmission device (2) on position, wherein there is supporting portion the ball bearing (12) to be used as unique bearing.
7. with electric motor driver (4) and with the driving unit of transmission device according to claim 1 (2)
(1), wherein sun gear (6) is effectively connect with the armature spindle (5) of electric motor driver (4), which is characterized in that ball axis
On shaft end holding the sun gear (6) that (12) are placed in planet carrier (10), deviating from the axial direction with armature spindle (5), and
Outer ring (15) is axially fixed on the inner cylinder of planet carrier (10) and concentric with central axis (3) in the opposite direction
In housing bore (18), wherein be configured between planet carrier (10) and outer ring (15) radial, namely horizontal in housing bore (18)
To the movement clearance being directed toward in axial direction.
8. driving unit according to claim 7, which is characterized in that the planet carrier (10) is with around central axis (3) energy
The second supporting portion that the mode of rotation is supported on the first supporting portion (29) and is spaced apart in the axial direction with the first supporting portion
(30) on, and it is fixedly fastened on shell (7) along opposite axial direction, and wherein each supporting portion (29,30)
All have angular contact ball bearing (31,32), wherein each angular contact ball bearing (31,32) it is arbitrary, imaginary and along
Central axis (3) extend through in the longitudinal sectional drawings of the ball bearing (12) by it is imaginary, pass through ball central point
(23) and the inside that is each passed through the angular contact ball bearing (31,32) herein rolling raceway and the angular contact ball bearing
Contact line (33) characterization of the rolling raceway of the outside of (31,32), and wherein, every contact line (33) is all with 90 ° of 0 ° of ＞ α ＞
Angle relative to central axis (3) tilt.
9. driving unit according to claim 8, which is characterized in that the angular contact ball bearing (31,32) is with such as lower section
Formula is set up relative to each other, that is, the contact line (33) of corresponding angular contact ball bearing (31,32) is at intersection point (35) and central shaft
Line (3) intersects, and the intersection point is axially in central axis between the first supporting portion and the second supporting portion (29,30)
(3) on.
10. driving unit according to claim 9, which is characterized in that the ball bearing (12) is in circumferential direction
Mode around central axis (3) is surrounded by one of angular contact ball bearing (31,32).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015225630 | 2015-12-17 | ||
| DE102015225630.8 | 2015-12-17 | ||
| PCT/DE2016/200498 WO2017101920A1 (en) | 2015-12-17 | 2016-11-07 | Transmission device and drive unit having a transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108368933A true CN108368933A (en) | 2018-08-03 |
| CN108368933B CN108368933B (en) | 2020-12-18 |
Family
ID=57482114
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680073011.XA Active CN108368933B (en) | 2015-12-17 | 2016-11-07 | Transmission and drive unit with transmission |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN108368933B (en) |
| DE (1) | DE102016221708B4 (en) |
| WO (1) | WO2017101920A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018107084B4 (en) * | 2018-03-26 | 2023-11-09 | Schaeffler Technologies AG & Co. KG | Planetary gear and electromotive drive unit with a planetary gear |
| DE102018009398A1 (en) | 2018-11-29 | 2020-06-04 | Daimler Ag | Drive device for a motor vehicle with a drive unit |
| CN113090725B (en) * | 2019-06-20 | 2022-09-27 | 成都中良川工科技有限公司 | Rotary transmission device and transmission method |
| DE102021100446A1 (en) | 2021-01-13 | 2022-07-14 | Audi Aktiengesellschaft | Bearing arrangement for a transmission shaft |
| DE102021202995A1 (en) | 2021-03-26 | 2022-09-29 | Zf Friedrichshafen Ag | Transmissions, in particular motor vehicle transmissions |
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|---|---|---|---|---|
| CN1262723A (en) * | 1997-07-10 | 2000-08-09 | Skf工程研究中心公司 | Asymmetric angular contact ball bearing |
| DE10143562A1 (en) * | 2000-09-22 | 2002-05-02 | Sew Eurodrive Gmbh & Co | Single or multistage planetary gearbox has input and/or output shaft of at least one planet stage and/or of whole gearbox mounted on ball bearings, with at least one ball bearing as sealed bearing with separate nil loss sealing ring |
| JP2011207386A (en) * | 2010-03-30 | 2011-10-20 | Aisin Aw Co Ltd | Driving device for vehicle |
| JP2011208758A (en) * | 2010-03-30 | 2011-10-20 | Aisin Aw Co Ltd | Torque limiter and hybrid driving device |
| JP2011207387A (en) * | 2010-03-30 | 2011-10-20 | Aisin Aw Co Ltd | Driving device for vehicle |
| CN202612382U (en) * | 2012-04-24 | 2012-12-19 | 北京天马轴承有限公司 | Two-piece outer ring four point contact ball bearing |
| CN204239458U (en) * | 2014-11-30 | 2015-04-01 | 新昌金汇关节轴承有限公司 | A kind of rolling bearing |
| CN104747671A (en) * | 2013-12-27 | 2015-07-01 | 株式会社捷太格特 | Planet roller speed changer |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2841331C3 (en) | 1978-09-21 | 1981-05-27 | Mannesmann AG, 4000 Düsseldorf | Planetary gear with power split |
-
2016
- 2016-11-07 WO PCT/DE2016/200498 patent/WO2017101920A1/en active Application Filing
- 2016-11-07 CN CN201680073011.XA patent/CN108368933B/en active Active
- 2016-11-07 DE DE102016221708.9A patent/DE102016221708B4/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1262723A (en) * | 1997-07-10 | 2000-08-09 | Skf工程研究中心公司 | Asymmetric angular contact ball bearing |
| DE10143562A1 (en) * | 2000-09-22 | 2002-05-02 | Sew Eurodrive Gmbh & Co | Single or multistage planetary gearbox has input and/or output shaft of at least one planet stage and/or of whole gearbox mounted on ball bearings, with at least one ball bearing as sealed bearing with separate nil loss sealing ring |
| JP2011207386A (en) * | 2010-03-30 | 2011-10-20 | Aisin Aw Co Ltd | Driving device for vehicle |
| JP2011208758A (en) * | 2010-03-30 | 2011-10-20 | Aisin Aw Co Ltd | Torque limiter and hybrid driving device |
| JP2011207387A (en) * | 2010-03-30 | 2011-10-20 | Aisin Aw Co Ltd | Driving device for vehicle |
| CN202612382U (en) * | 2012-04-24 | 2012-12-19 | 北京天马轴承有限公司 | Two-piece outer ring four point contact ball bearing |
| CN104747671A (en) * | 2013-12-27 | 2015-07-01 | 株式会社捷太格特 | Planet roller speed changer |
| CN204239458U (en) * | 2014-11-30 | 2015-04-01 | 新昌金汇关节轴承有限公司 | A kind of rolling bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102016221708B4 (en) | 2024-01-04 |
| CN108368933B (en) | 2020-12-18 |
| WO2017101920A1 (en) | 2017-06-22 |
| DE102016221708A1 (en) | 2017-06-22 |
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