CN104203626A - Helical-toothed gear unit, electrical machine - Google Patents
Helical-toothed gear unit, electrical machine Download PDFInfo
- Publication number
- CN104203626A CN104203626A CN201380019437.3A CN201380019437A CN104203626A CN 104203626 A CN104203626 A CN 104203626A CN 201380019437 A CN201380019437 A CN 201380019437A CN 104203626 A CN104203626 A CN 104203626A
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- driving device
- shaft
- helical teeth
- driven shaft
- worm gear
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- 230000008878 coupling Effects 0.000 claims description 65
- 238000010168 coupling process Methods 0.000 claims description 65
- 238000005859 coupling reaction Methods 0.000 claims description 65
- 210000000078 claw Anatomy 0.000 claims description 14
- 230000000295 complement effect Effects 0.000 claims description 4
- 230000007306 turnover Effects 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 description 8
- 238000005096 rolling process Methods 0.000 description 8
- 230000001141 propulsive effect Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000002349 favourable effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000002301 combined effect Effects 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003475 lamination Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000002910 structure generation Methods 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
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
- F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
-
- 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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/18—Freewheels or freewheel clutches with non-hinged detent
- F16D41/185—Freewheels or freewheel clutches with non-hinged detent the engaging movement having an axial component
-
- 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
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
- F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
- F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
- F16D43/2024—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
- F16D7/042—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement
- F16D7/044—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
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- 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
- H02K7/081—Structural association with bearings specially adapted for worm gear drives
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- 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
- H02K7/108—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches
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- 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
- H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
- H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
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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
- F16H31/00—Other gearings with freewheeling members or other intermittently driving members
-
- 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
- H02K7/118—Structural association with clutches, brakes, gears, pulleys or mechanical starters with starting devices
- H02K7/1185—Structural association with clutches, brakes, gears, pulleys or mechanical starters with starting devices with a mechanical one-way direction control, i.e. with means for reversing the direction of rotation of the rotor
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Gear Transmission (AREA)
Abstract
The invention relates to a helical-toothed gear unit (9), particularly for an electrical machine (1), comprising a drive shaft (12) on which a helical-toothed drive pinion (5), particularly a worm (11), is non-rotatably mounted, and comprising an output pinion (15), particularly a worm wheel (13), that is arranged on an output shaft (14) and is engaged with the drive pinion (5). According to the invention, the output pinion (5) is connected by means of a freewheel device (17) to the output shaft (14), the freewheel device (17) being designed to be at least substantially controlled by a rotational direction. The invention further relates to an electrical machine.
Description
Technical field
The driving device that the present invention relates to a kind of engagement of the helical teeth especially for motor, described driving device has: axle drive shaft can not relatively turn the Drive pinion, the particularly worm screw that are furnished with over the ground helical teeth engagement on described axle drive shaft; With driven miniature gears, particularly worm gear, it is arranged on driven shaft and with described Drive pinion and meshes.
The invention still further relates to a kind of motor, especially for the electrical motor of self-propelled vehicle, there is the driving device of helical teeth engagement, described driving device has: axle drive shaft can not relatively turn the Drive pinion, the particularly worm screw that are furnished with over the ground helical teeth engagement on described axle drive shaft; With driven miniature gears, particularly worm gear, it is arranged on driven shaft and with described Drive pinion and meshes, and wherein, axle drive shaft is formed by the rotor shaft of motor.
Background technology
The driving device and the motor that start described type are known by prior art.The supporting structure of the structure of motor and particularly rotor shaft is the technology of main flow now.Conventionally rotor shaft is equipped with bearing, particularly rolling body bearing in the both sides that form the stack of laminations of rotor, and it is fixed in the housing of motor.The free end of rotor shaft is equipped with Drive pinion, by this Drive pinion, continues to transmit the torque being provided by motor.Conventionally in order to continue transmitting torque, be provided with driving device, this driving device affects rotating speed and torque by favourable mode and method.For extra high torque is provided on driven shaft, driving device is usually designed to worm gearing.Helical teeth engagement by helical teeth engagement Drive pinion and that also comprise if desired driven miniature gears or worm and worm wheel has also produced axial power, and this power also acts on rotor shaft.In order to absorb this axial power in housing, conventionally by attaching troops to a unit, in the rolling body of Drive pinion, be pressed on rotor shaft and by outer shroud carrying (beschultert) be axially fixed in housing or by the outer shroud of rolling body and be pressed in housing and by interior rim bearing and carry and be axially fixed on rotor shaft.In some applications, when normal work axial force all the time or mostly along equidirectional to rotor shaft generation effect, thereby the supporting structure of rotor shaft absorbs axial force for (along a direction) substantially.When rotation direction reversing or et out of order, yet the axial force producing can reverse or work in opposite direction.In this case, supporting structure is subject to unfavorable load.A design plan of supporting structure is, this supporting structure can similarly absorb axial force along both direction, but this only could realize the in the situation that of the structural input of height.
Summary of the invention
According to driving device of the present invention, that there is feature described in claim 1, with respect to the advantage of prior art, be when et out of order, to prevent that the axial force working along the opposite way round is to rotor shaft with particularly to its supporting structure generation effect., according to the present invention, propose, described driven miniature gears is connected with described driven shaft by means of idling device for this reason, and wherein, described idling device at least substantially rotation direction controllably designs.Therefore driven miniature gears directly can not relatively not turn over the ground and be connected with driven shaft.Alternatively, between driven shaft and driven miniature gears, be provided with idling device, this idling device is according to rotation direction or drive rotation direction and the power transmission according to be passed and/or counteractive torque energy realization or preventing from driven miniature gears to axle drive shaft if desired.Because driven miniature gears can be continued drive and be rotated further thus based on idle running, and do not have power to be passed on driven shaft, therefore the helical teeth engagement by Drive pinion can not produce the axial force to rotor shaft generation effect.
Preferably, described idling device is designed to claw clutch.Idling device carries out the propulsive effort transmission of form fit along a rotation direction thus, and along the form fit of another rotation direction be stopped and therefore power transmission finish.Claw clutch only needs little structure space and therefore can be integrated in driving device well.
Preferably, described claw clutch has attaches troops to a unit in the first coupling element of described driven miniature gears and attaches troops to a unit in the second coupling element of described driven shaft, wherein, described coupling element has a complementary helical teeth engaging piece distolateral respectively, wherein, at least one coupling element can axially movably be arranged.Complementary helical teeth engaging piece causes above-mentioned principle of work, wherein, along driving rotation direction to have form fit, and stops this form fit along contrary rotation direction.This realizes thus: when the direction along contrary drives, helical teeth engaging piece axially squeezes coupling element to open each other when overstepping the extreme limit torque.Because at least one coupling element is axially movably arranged, so this moves axially and is allowed to, thereby helical teeth engaging piece is thrown off engagement and no longer can be carried out power transmission thus when overstepping the extreme limit torque.
A favourable improvement project according to the present invention proposes, and described the first coupling element is formed by driven miniature gears or described worm gear.The first coupling element is integrally formed with driven miniature gears or worm gear thus.By coupling element is integrated in driven miniature gears like this, provide the special compact design form of driving device.Alternatively can certainly consider, the first coupling element forms discretely with driven miniature gears and when mounted driven miniature gears and the first coupling element at least can not be turned to connected with each other over the ground relatively.
Preferably, described the second coupling element is designed to coupling ring.Annular design plan by the second coupling element can push it on driven shaft by simple mode and method.
Preferably, described coupling ring can not relatively turn over the ground and is connected with described driven shaft.Special design becomes, and coupling ring has radially inwardly outstanding drive protrusion, the corresponding drive recess combined action of itself and driven shaft.A plurality of drive protrusions can certainly be set on coupling ring and driven shaft and drive recess.The power transmission of the form fit under any circumstance all having guaranteed from coupling ring to driven shaft.
According to a preferred embodiment proposition of the present invention, on described driven shaft, described coupling ring is axially movably arranged, and driven miniature gears or described worm-wheel shaft are to arranging regularly and rotationally.According to this embodiment, also just propose, coupling ring is axially movable, to can realize especially the disengagement engagement of the helical teeth engaging piece of claw clutch.Driven miniature gears this axial restraint be arranged on driven shaft, yet there is the degree of freedom along hand of rotation, thereby it can reverse on driven shaft.When normal work, therefore propulsive effort is passed on driven miniature gears by Drive pinion, and this driven miniature gears continues propulsive effort to be delivered on driven shaft by the helical teeth engaging piece of claw clutch.If drive rotation direction reversing, the helical teeth engaging piece that coupling ring is passed claw clutch when surpassing corresponding torque moves axially, thereby the helical teeth engaging piece of claw clutch is thrown off engagement and so power is not delivered on driven shaft.Correspondingly, the helical teeth engaging piece by Drive pinion and driven miniature gears does not have axial force and is applied on axle drive shaft, and this axial force can have a negative impact to the supporting structure of axle drive shaft.
An interchangeable embodiment according to the present invention preferably proposes, and on described driven shaft, described worm gear axially movably and is rotationally arranged, and described coupling ring axial restraint ground is arranged.Distinguishing of the embodiment of before describing alternatively also just proposes, and is not that coupling ring but worm gear self are axially movably arranged, can realize the disengagement engagement of the helical teeth engaging piece of claw clutch while driving rotation direction with box lunch transposing.In other side, accord with above-mentioned principle of work.
Preferably, described coupling ring and driven miniature gears or described worm gear are spring loaded and utilize its helical teeth engaging piece mutually to clamp.Spring loaded in tension is used for, and when normal work, claw clutch or idling device are kept to form fit engagement, or (now, coupling element engagement disconnected from each other) has been guaranteed after rotation direction has been changed, and coupling element is again intermeshing.In order to realize spring, loading, be provided with preferably at least one spring element, particularly spring washer, is particularly preferably at least one cup spring or coil spring, and it preferably remains between the axial stop and driven miniature gears or coupling ring on driven shaft in advance tightly.The axial stop of driven shaft is formed by convex shoulder especially at this, and this convex shoulder forms by the enlarged-diameter portion of driven shaft.In order to keep pretension, be preferably provided with another axial stop, driven miniature gears or coupling ring are extruded to this axial stop by means of at least one spring element.The second axial stop for example can form by the set collar being arranged on driven shaft, and this set collar is arranged in the annular groove of driven shaft.
According to advantage of the present invention, that have the motor of feature described in claim 10, be, the supporting structure of rotor shaft can rotation direction be constructed best, and this is because prevented from reliably producing the axial force of detrimental effect---be in reverse to normal action direction.For this reason, motor has driving device, as previously mentioned.Therefore other embodiment and advantage also draw as previously mentioned.
Accompanying drawing explanation
Under describe with reference to the accompanying drawings the present invention in detail.Shown in figure
Fig. 1 illustrates motor with the longitudinal sectional view of simplifying,
Fig. 2 illustrates a favourable embodiment of worm gearing,
Fig. 3 illustrates the exploded drawings of the idling device of worm gearing,
Fig. 4 illustrates another embodiment of favourable worm gearing, and
Fig. 5 illustrates the exploded drawings of second embodiment.
The specific embodiment
Fig. 1 illustrates motor 1 with the longitudinal sectional view of simplifying, and it has one can not turn the rotor 3 being arranged in over the ground on rotor shaft 2 relatively, and wherein, rotor shaft 2 is rotatably supported in housing 4.The Drive pinion 5 of the driving device 9 not being shown specifically be also provided with Fig. 1 on its free end on rotor shaft 2 in, it has helical teeth engaging piece 6.
For supporting rotor axle 2, be provided with two rolling body bearings 7 and 8.At this rolling body bearing 7, on rotor shaft 2, be arranged between rotor 3 and Drive pinion 6, and rolling body bearing 8 is arranged on the side being oppositely arranged of rotor 3.The helical teeth engaging piece 6 of Drive pinion 5 produces axial force when work, and this responsive to axial force is in rotor shaft 2 and conventionally utilize rolling body bearing 7 to absorb and supporting.For this reason, the interior ring of rolling body bearing 7 is pressed on rotor shaft 2 and outer shroud is carried in housing 4 and axial restraint.Yet the type of supporting structure is unimportant for the present invention.In this important being only, supporting structure type can absorb high axial force along a direction only conventionally.This supporting structure is used in particular for that wherein motor 1 is all the time along the application of identical rotation direction work, and for example, for motor, this motor drives the extrusion piston of hydraulic pressure by driving device 9.Yet if the rotation direction of axle drive shaft 2 changes, for, axial force, based on helical teeth, engagement acts on rotor shaft 2 in opposite direction for this.If supporting structure is correspondingly designed for substantially along a direction only, absorb axial force, it is impaired that this can cause motor.The supporting structure that can load in the same manner axial force along both direction may cause the expensive of structural and manufacturing technology.
Fig. 2 shows an advantageously embodiment of the driving device 9 of design, utilizes this embodiment to prevent, axial force exerts an influence to the supporting structure of rotor shaft 2 along disadvantageous direction.According to the present embodiment, driving device 9 is designed to worm gearing 10, and wherein, Drive pinion 5 is arranged by worm screw 11, and this worm screw can not relatively turn and is arranged in over the ground on the rotor shaft 2 working as axle drive shaft 12.Worm screw 11 and worm gear 13 engagements, this worm gear is arranged on driven shaft 14.Therefore worm gear 13 is and the coefficient driven miniature gears 15 of Drive pinion 5.Worm gear 13 can have helical teeth engaging piece or the straight gear teeth for this reason in its shell side, it and worm screw 11 combineds action.Worm gear is can be on driven shaft 14 rotatable and can axially movably arrange, as shown ground by double-head arrow 16.Be applied to axial force on worm gear 13 by means of idling device 17 relevant with rotation direction being delivered on driven shaft 14 substantially.
Idling device 17 has claw clutch 18, and this claw clutch is formed by two coupling elements 19 and 20.The first coupling element 19 is integrally formed at this and worm gear 13, and the second coupling element 20 is formed by independent coupling ring 21, this coupling ring can not relatively turn be connected with driven shaft 14 over the ground and axial restraint thereon.To this, coupling ring 21 is arranged in a side on the backstop convex shoulder of driven shaft 14 and is fixing by the set collar 22 of annular groove 23 that is positioned at driven shaft 14 at opposite side.
Fig. 3 illustrates the part of slave end of worm gearing 10 to better understand with perspective exploded view.In order relatively to turn connected over the ground with driven shaft 14, coupling ring 21 has radially inwardly outstanding drive protrusion 24 in side within it, this drive protrusion is arranged in the drive recess 25 of driven shaft 14 under mounted state, wherein, in circumferential direction, be formed on and drive protrusion 24 and drive form fit between recess 25 for power transmission.
Coupling ring 21 has helical teeth engaging piece 26 at it on the side of worm gear, and this helical teeth engaging piece is characterised in that, tooth has pitch face 27 in rotation direction, in contrary rotation direction, has the vertical flank of tooth 28.Therefore helical teeth engaging piece 26 draws by the pitch face 27 of tooth.Substantially, helical teeth engaging piece 26 is equivalent to straight line profile gear-tooth (Hirth-Verzahnung), and wherein, tooth has pitch face and on opposite side, has the vertical or steep flank of tooth in a side.
Worm gear 13 has groove 29 on the side towards coupling ring 21, and its external diameter surpasses the external diameter of coupling ring 21, so coupling ring 21 can be contained in groove 29 completely.The bottom of groove 29 is equipped with the helical teeth engaging piece 30 with 26 complementations of helical teeth engaging piece, and it is characterised in that the tooth with the inclined-plane that a skew back flank of tooth is vertical with opposite side equally.Worm gear 13 self utilizes helical teeth engaging piece 30 to form the first coupling element 19, this first coupling element and coupling ring 21 combineds action.
By the complementary design of helical teeth engaging piece 26 and 30, under initial condition, the tooth of coupling ring 21 is between the tooth of coupling element 19.This is supported thus, and coupling ring 21 is axially fixed on driven shaft 14, and worm gear 13 is pressed towards coupling ring 21 by the cup spring 31 on a plurality of convex shoulders 32 that are bearing in driven shaft 14, as shown in Figure 2.
When normal work, worm gear 13 drives like this by worm screw, and the vertical flank of tooth of helical teeth engaging piece 30 is pressed towards the vertical flank of tooth 28 of helical teeth engaging piece 26.Form fit ground drives coupling ring 21 thus, drives the drive protrusion 24 of recess 25 that power is continued to be delivered on driven shaft 14, thereby make its rotation by being arranged in.If change the rotation direction of motor 1, this causes, and the pitch face of helical teeth engaging piece 30 is pressed towards the pitch face 27 of helical teeth engaging piece 26 now.Produced thus axial force, this axial force works like this between coupling ring 21 and worm gear 13, and it is sufficiently pushed when surpassing the breakdown torque that can also transmit.Because coupling ring 21 is axially fixed on driven shaft 14, so worm gear 13 is remotely overcome cup spring 31 by coupling ring 21 power at this moves along the direction of backstop convex shoulder 32 on driven shaft 14.Thus, helical teeth engaging piece 26 and 30 disengagement engagements and propulsive effort are no longer passed on driven shaft 14.Correspondingly, axle drive shaft can axially not be loaded along disadvantageous direction by the helical teeth engagement of worm and worm wheel.Prevented thus the overload of the supporting structure of rotor shaft or axle drive shaft 12.
Figure 4 and 5 show another embodiment of the motor 1 with worm gearing 10, and wherein, known element has identical Reference numeral, therefore can be with reference to above-mentioned explanation.Will only inquire into difference below.
Fig. 4 shows worm gearing 10 with perspective cut-away schematic view.Only be with the difference of embodiment above, worm gear 13 is axially fixed on driven shaft 14, and coupling ring 21 is axially movably arranged on driven shaft 14.In addition this layout changes like this, remains between the worm gear and cup spring 31 of axial restraint to coupling ring 21 compressions now.If motor 1 drives along normal operative orientation, helical teeth engaging piece 26 and 30 utilizes the vertical vertical flank of tooth to be in other words engaged with each other, propulsive effort by form fit be delivered on driven shaft 14.If change the rotation direction of motor 1, the spring force that helical teeth engaging piece 26 and 30 pitch face overcome coupling ring 21 cup spring 31 from worm gear 13 press from, so helical teeth engaging piece 26 and 30 is thrown off engagement and interrupts to the power transmission on driven shaft.Therefore according to this embodiment, also by simple mode and method, by means of idling device 17, prevented from maybe when being not intended to change rotation direction, along disadvantageous direction, rotor shaft 2 being loaded under failure condition.
Drive recess 25 preferably with pod form, to be parallel in this case the rotation axis alignment of driven shaft 14, thereby coupling ring 21 can be utilized and drive protrusion 24 to move on driven shaft 14, and can not make to drive protrusion 24 and drive recess 25 to throw off engagement.
Also can consider in theory, idling device 17 at drive side, that is to say on the axle drive shaft 12 at motor 1 and to arrange.
Above-mentioned motor 1 is particularly suitable for, and is used as actuating device in brake servo unit, and it conventionally needs normal work rotation direction and can or only seldom along contrary rotation direction, with low torque, not drive.By idling device 17, can avoid have high input and supporting Expenses Cost at housing 4 rotor axles 2.Because idling device 17 is almost built in worm gear 13 completely, so it can be in the situation that do not have large supernumerary structure space requirement to arrange.
Driven shaft 14 is for example connected with hydraulic piston to be driven by connecting rod, and wherein, connecting rod is converted to rotatablely moving of driven shaft 14 motion of translation of piston.Described cup spring 31 can certainly be set more or less, for compressing claw clutch 18.
Alternatively also can consider, cup spring 31 is replaced by coil spring.Can freely select number of springs or adjustable spring force in principle, yet by selected spring force, before helical teeth engaging piece 26 and 30 is thrown off engagement, determining can also be along the torque of contrary rotation direction permission transmission, idling device 17.Spring force is larger, and helical teeth engaging piece 26 and 30 is thrown off engagement more lately.According to applicable cases, therefore can adjust by simple mode and method the effect of idling device 17.
Claims (10)
1. the driving device (9) of a helical teeth engagement that is used in particular for motor (1), described driving device has: axle drive shaft (12) can not relatively turn Drive pinion (5), the particularly worm screw (11) that are furnished with over the ground helical teeth engagement on described axle drive shaft; With driven miniature gears (15), particularly worm gear (13), it is arranged in driven shaft (14) above and meshes with described Drive pinion (5), it is characterized in that, described driven miniature gears (5) is connected with described driven shaft (14) by means of idling device (17), wherein, described idling device (17) at least substantially rotation direction controllably design.
2. driving device according to claim 1, is characterized in that, described idling device (17) is designed to claw clutch (18).
3. according to driving device in any one of the preceding claims wherein, it is characterized in that, described claw clutch (18) has attaches troops to a unit in first coupling element (19) of described driven miniature gears (15) and attaches troops to a unit in second coupling element (20) of described driven shaft (14), wherein, described coupling element (19,20) has a complementary helical teeth engaging piece (26,30) distolateral respectively, and wherein, at least one in described coupling element (19,20) can axially movably be arranged.
4. according to driving device in any one of the preceding claims wherein, it is characterized in that, described the first coupling element (19) is formed by described worm gear (13).
5. according to driving device in any one of the preceding claims wherein, it is characterized in that, described the second coupling element (20) is designed to coupling ring (21).
6. according to driving device in any one of the preceding claims wherein, it is characterized in that, described coupling ring (21) can not relatively turn over the ground and is connected with described driven shaft (14).
7. according to driving device in any one of the preceding claims wherein, it is characterized in that, upper at described driven shaft (14), described coupling ring (21) axially can arrange movably, and described worm gear (13) axial restraint ground and arranging rotationally.
8. according to driving device in any one of the preceding claims wherein, it is characterized in that, upper at described driven shaft (14), described worm gear (13) axially can movably and can be arranged rotationally, and described coupling ring (21) axial restraint ground is arranged.
9. according to driving device in any one of the preceding claims wherein, it is characterized in that, described coupling ring (21) and described worm gear (13) are spring loaded and utilize its helical teeth engaging piece (26,30) mutually to clamp.
A motor, especially for the electrical motor of self-propelled vehicle, there is rotor shaft (2) and the driving device (9) that can be bearing in rotationally in housing, described driving device has: axle drive shaft (12) can not relatively turn Drive pinion (5), the particularly worm screw (11) that are furnished with over the ground helical teeth engagement on described axle drive shaft; With driven miniature gears (15), particularly worm gear (13), it is arranged in driven shaft (14) above and meshes with described Drive pinion (5), wherein, described rotor shaft (2) forms the axle drive shaft (12) of described driving device (9), it is characterized in that according to the design plan of any one in aforementioned claim or multinomial described driving device (9).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012205995.4 | 2012-04-12 | ||
| DE102012205995A DE102012205995A1 (en) | 2012-04-12 | 2012-04-12 | Helical gear, electric machine |
| PCT/EP2013/056575 WO2013152955A1 (en) | 2012-04-12 | 2013-03-27 | Helical-toothed gear unit, electrical machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104203626A true CN104203626A (en) | 2014-12-10 |
| CN104203626B CN104203626B (en) | 2017-12-08 |
Family
ID=47998456
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380019437.3A Expired - Fee Related CN104203626B (en) | 2012-04-12 | 2013-03-27 | The transmission device and motor of helical teeth engagement |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2836385A1 (en) |
| CN (1) | CN104203626B (en) |
| DE (1) | DE102012205995A1 (en) |
| WO (1) | WO2013152955A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105305719A (en) * | 2015-11-24 | 2016-02-03 | 王琳 | Worm transmission mechanism |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017206641A1 (en) * | 2017-04-20 | 2018-10-25 | Bayerische Motoren Werke Aktiengesellschaft | Drive unit and motor vehicle with a drive unit |
| EP4117863A4 (en) * | 2020-03-13 | 2024-03-27 | Black & Decker, Inc. | Pipe clamp, pipe clamp driver and anti-backdrive mechanism |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4980591A (en) * | 1988-12-20 | 1990-12-25 | Asmo Co., Ltd. | One-way clutch for a reduction-geared motor |
| JPH04300425A (en) * | 1991-03-27 | 1992-10-23 | Jidosha Denki Kogyo Co Ltd | Miniature motor with friction clutch |
| DE29611395U1 (en) * | 1996-07-01 | 1997-11-06 | Gebr. Bode & Co GmbH, 34123 Kassel | Electromechanical drive device for a rotating column for moving a swing door leaf on a vehicle |
| DE20208246U1 (en) * | 2002-05-27 | 2003-10-09 | Kiekert Ag | Geared motor for sliding doors or tailgates in vehicles, has axially movable coupling part on output shaft for engaging gear wheel with this shaft |
| CN2609267Y (en) * | 2003-03-17 | 2004-03-31 | 刘秋雄 | Composite step-counting control and clutcuh driven D.C. motor apparatus |
| CN1651700A (en) * | 2004-01-22 | 2005-08-10 | 株式会社美姿把 | Automatic opening and closing system for vehicle |
| US20100294612A1 (en) * | 2009-05-20 | 2010-11-25 | Nathan A Mariman | Adjustable seed meter drive coupling |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10356976A1 (en) * | 2003-02-20 | 2004-09-16 | Dr.Ing.H.C. F. Porsche Ag | Motor vehicle door lock has rotary pawl shaft with freely mounted worm wheel engaging connector assembly for pawl lock |
| JP4346638B2 (en) * | 2006-12-01 | 2009-10-21 | 株式会社ツバキエマソン | Reducer with built-in one-way clutch for automobile brake speed test |
-
2012
- 2012-04-12 DE DE102012205995A patent/DE102012205995A1/en not_active Ceased
-
2013
- 2013-03-27 WO PCT/EP2013/056575 patent/WO2013152955A1/en active Application Filing
- 2013-03-27 EP EP13712561.3A patent/EP2836385A1/en not_active Withdrawn
- 2013-03-27 CN CN201380019437.3A patent/CN104203626B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4980591A (en) * | 1988-12-20 | 1990-12-25 | Asmo Co., Ltd. | One-way clutch for a reduction-geared motor |
| JPH04300425A (en) * | 1991-03-27 | 1992-10-23 | Jidosha Denki Kogyo Co Ltd | Miniature motor with friction clutch |
| DE29611395U1 (en) * | 1996-07-01 | 1997-11-06 | Gebr. Bode & Co GmbH, 34123 Kassel | Electromechanical drive device for a rotating column for moving a swing door leaf on a vehicle |
| DE20208246U1 (en) * | 2002-05-27 | 2003-10-09 | Kiekert Ag | Geared motor for sliding doors or tailgates in vehicles, has axially movable coupling part on output shaft for engaging gear wheel with this shaft |
| CN2609267Y (en) * | 2003-03-17 | 2004-03-31 | 刘秋雄 | Composite step-counting control and clutcuh driven D.C. motor apparatus |
| CN1651700A (en) * | 2004-01-22 | 2005-08-10 | 株式会社美姿把 | Automatic opening and closing system for vehicle |
| US20100294612A1 (en) * | 2009-05-20 | 2010-11-25 | Nathan A Mariman | Adjustable seed meter drive coupling |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105305719A (en) * | 2015-11-24 | 2016-02-03 | 王琳 | Worm transmission mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102012205995A1 (en) | 2013-10-17 |
| EP2836385A1 (en) | 2015-02-18 |
| CN104203626B (en) | 2017-12-08 |
| WO2013152955A1 (en) | 2013-10-17 |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20171208 |