CN202827204U - Adjusting device of automobile seat electric angle adjustor - Google Patents
Adjusting device of automobile seat electric angle adjustor Download PDFInfo
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- CN202827204U CN202827204U CN 201220447826 CN201220447826U CN202827204U CN 202827204 U CN202827204 U CN 202827204U CN 201220447826 CN201220447826 CN 201220447826 CN 201220447826 U CN201220447826 U CN 201220447826U CN 202827204 U CN202827204 U CN 202827204U
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Abstract
The utility model discloses an adjusting device of an automobile seat electric angle adjustor. The adjusting device of the automobile seat electric angle adjustor comprises a reduction box shell, an engine, a worm, a duplicated gear, a planet gear transmission frame component, a plurality of planet gears and a reduction box cover. A ring gear is arranged on the reduction box shell. The duplicated gear comprises a helical gear and a center gear. The plurality of planet gears are evenly distributed on the planet gear transmission frame component and are meshed with the center gear and the ring gear. An output shaft penetrates through the reduction box cover, the planet gear transmission frame component, the duplicated gear and the reduction box shell and is meshed with the planet gear transmission frame component. The duplicated gear is coaxially located on the reduction box shell and the planet gear transmission frame component along the radial direction. According to the adjusting device of the automobile seat electric angle adjustor, an outer diameter of a locating ring of one end of the duplicated gear is matched with an inner diameter of a locating sleeve of the reduction box shell, an outer diameter of a locating ring of the other end of the duplicated gear is matched with an inner diameter of a locating sleeve of the planet gear transmission frame component, radial location of the duplicated gear can be achieved equally, and therefore the effect that a spline shaft of a synchronizing rod of the angle adjustor penetrates through the center of a planet gear mechanism is possible.
Description
Technical field
The utility model belongs to the automotive seat technical field, relates in particular to a kind of electric angle-adjuster control apparatus of automotive seat, and this device can drive electric angle-adjuster the back of seat angle is regulated.
Background technology
The employed recliner control apparatus of automobile chair is divided into electronic and manual two kinds of forms according to user's configuration needs unusual.Electric adjusting device in the market mainly adopts motor driving drop-gear box system to make chaufeur or passenger reach comfortable seating position.Almost all to face volume large for all actuating devices on the market, Heavy Weight, and installation property is poor, and transmitting ratio is low, and output torque is little, and the drive motor volume is large, the high in cost of production problem.
Referring to Fig. 1, US2012/0119554A1 discloses a kind of electric angle-adjuster control apparatus, the control apparatus of all electric angle-adjuster control apparatuss and this patent adopts same principle in the market, the first order of this control apparatus is slowed down and is worm screw-Helical gear Transmission, slow down and be Spur Gear Driving in the second stage, the part of its running part comprises worm screw 53, dual gear 57 and output gear 58.
The electric angle-adjuster control apparatus subject matter of this structure comprises:
1, volume is large, and installation property is poor:
Distance between being distributed on two axis of dual gear 57 and output gear 58, two axles generally about 30mm, causes the drop-gear box part long along the length on the motor shaft direction, generally about 90-100mm.Therefore the length of whole control apparatus on the motor shaft direction is long, and is very unfavorable for control apparatus arranging on seat back-rest framework; Simultaneously because its volume reduces the actual effective thickness of the relative human body of back of seat foaming piece than senior general, passenger's comfort level is had a negative impact.
2. transmitting ratio is low:
Because the restriction of volume requirement, the number of teeth of dual gear 57 and output gear 58 each several parts can not be too large, the transmitting ratio that the general first order is slowed down is about 1:40-50, the transmitting ratio that slows down in the second stage about 1:3.5-4, so the transmitting ratio of drop-gear box integral body generally at 1:150 between the 1:200.Require the motor output torque large, cost is high.Because the restriction of transmitting ratio, reach in the situation of identical output torque, the output torque of motor needs larger.If make regulating mechanism limit output torque reach 25Nm, general motor rotation blockage moment of torsion need reach about 0.3Nm.
The utility model content
Technical problem to be solved in the utility model is to provide for the existing deficiency of above-mentioned prior art a kind of electric angle-adjuster control apparatus of automotive seat, the technical matterss such as electric angle-adjuster control apparatus volume is large to overcome in the market, Heavy Weight, transmitting ratio is low, the output torque is limited.
Technical problem to be solved in the utility model can be achieved through the following technical solutions:
A kind of electric angle-adjuster control apparatus of automotive seat comprises:
One reduction box casing, described reduction box casing have the first container cavity and second container cavity of mutual perforation, and the wall periphery is provided with internally toothed annulus in the chamber of described the second container cavity;
One is installed in the motor on the described reduction box casing, and the motor shaft of described motor extends in described the first container cavity;
One is installed in the worm screw on the described motor shaft, and a described worm screw part extends to the second container cavity by described the first container cavity;
One is housed inside the dual gear in described the second container cavity, and described dual gear has one of coaxial setting and consists of the center gear of planet circular system with the helical wheel and of described worm mesh;
One consists of the planet gear transmission frame component of described planet circular system;
Circumferentially be distributed on the several rows star-wheel on the described planet gear transmission frame component, this several rows star-wheel and described center gear and the engagement of described internally toothed annulus;
One is installed in the gear box cover on the described reduction box casing, and described gear box cover is limited in described dual gear, planet gear transmission frame component, several rows star-wheel in the space that described gear box cover and reduction box casing limit;
One passes the output shaft of described gear box cover, planet gear transmission frame component, dual gear and reduction box casing successively, and described output shaft is meshed with described planet gear transmission frame component, it is characterized in that,
Described dual gear is coaxial to be radially positioned on described reduction box casing and the described planet gear transmission frame component.
In a preferred embodiment of the present utility model, described dual gear is respectively arranged with the first steady ring and the second steady ring along the two ends of central axis, the center is provided with one first locating bush at the bottom of the chamber of the second container cavity of described reduction box casing, be provided with one second locating bush at described planet gear transmission frame component with respect to the first surface center of described dual gear, wherein the first steady ring of dual gear is inserted in the first locating bush of described reduction box casing and carries out radial location, and the second steady ring of dual gear is inserted in the second locating bush on the described planet gear transmission frame component and carries out radial location.
In a preferred embodiment of the present utility model, the end face of the first locating bush on the described reduction box casing is the first flange face, and described the first flange face and described dual gear cooperatively interact with respect to that side end face of described reduction box casing described dual gear is carried out axial location.
In a preferred embodiment of the present utility model, be provided with one the 3rd steady ring at described planet gear transmission frame component with respect to second center of described gear box cover, offer a center positioning hole at the center of described gear box cover, the second steady ring on the described planet gear transmission frame component is inserted in the center positioning hole on the described gear box cover and carries out radial location.
In a preferred embodiment of the present utility model, as the center of circle circumferentially be evenly equipped with described satellite gear quantity identical planet wheel spindle take the center of described the second locating bush at described planet gear transmission frame component on respect to the first surface of described dual gear, cover has a satellite gear on each planet wheel spindle.
In a preferred embodiment of the present utility model, the center offers respectively the first centre hole, the second centre hole and the 3rd centre hole at the bottom of the chamber of the second container cavity of the center of the center of described planet gear transmission frame component, dual gear and reduction box casing, wherein said the first centre hole runs through the first steady ring and the second locating bush on the described planet gear transmission frame component, the second centre hole runs through the first steady ring and second steady ring of described dual gear, and the 3rd centre hole runs through at the bottom of the chamber of the first locating bush on the reduction box casing and the second container cavity; Described output shaft passes the first centre hole, the second centre hole and the 3rd centre hole successively.
In a preferred embodiment of the present utility model, be provided with one section female splines in the first centre hole on described planet gear transmission frame component, described output shaft has at least one section splined shaft section, and the female splines in the first centre hole on the splined shaft section on the described output shaft and the described planet gear transmission frame component is intermeshing.
In a preferred embodiment of the present utility model, described motor is DC machine.
In a preferred embodiment of the present utility model, described worm screw is hollow worm screw, and this hollow worm set is contained on the motor shaft of described motor.
In a preferred embodiment of the present utility model, described reduction box casing has orthogonal the first attachment face and the second attachment face, wherein the first attachment face perpendicular to the axis of described the first container cavity in order to the location with described motor is installed, the second attachment face perpendicular to the axis of described the second container cavity in order to the location with described gear box cover is installed.
In a preferred embodiment of the present utility model, described internally toothed annulus and described reduction box casing are made into integration.
In a preferred embodiment of the present utility model, described internally toothed annulus and described reduction box casing are independently made respectively, and described internally toothed annulus is embedded on the chamber wall periphery of described the second container cavity.
In a preferred embodiment of the present utility model, helical wheel and center gear in the described dual gear are made into integration.
In a preferred embodiment of the present utility model, helical wheel and center gear in the described dual gear are independently made respectively, and wherein said helical wheel has an interior perforation, an end of described center gear be inserted in the described interior perforation and with its engagement.
In a preferred embodiment of the present utility model, described planet gear transmission frame component is by planet gear transmission support body, center sleeve and some straight pins that consists of planet wheel spindle; Described planet gear transmission support body is disk structure, the planet gear transmission support body both ends of the surface of disk structure form respectively the second flange face and three-flange face, the first surface of the described planet gear transmission frame component of the second flange face formation relative to described dual gear, three-flange face second of consisting of described planet gear transmission frame component relative to gear box cover; Planet gear transmission support body center at described disk structure offers a center pore, described center sleeve passes described center pore and captives joint with the planet gear transmission support body, and the two ends that center sleeve exposes the planet gear transmission support body consist of respectively the second locating bush and the 3rd steady ring in the described planet gear transmission frame component; The endoporus of described center sleeve consists of the first centre hole of described planet gear transmission frame component; Center take described center sleeve on the second flange face of described planet gear transmission support body circumferentially is evenly equipped with some cylinder pin holes as the center of circle, each cylinder pin hole periphery is provided with a little flange face, in each cylinder pin hole, be fixed with a straight pin, cover has a satellite gear on each straight pin, each satellite gear contacts with described little flange face towards the planet gear transmission support body side, to limit the axial location of satellite gear.
In a preferred embodiment of the present utility model, be provided with some hooks at described reduction box casing, be provided with some buckles at described gear box cover, when gear box cover was installed on the reduction box casing, described buckle was buckled on the described hook.
In a preferred embodiment of the present utility model, be provided with a bolt mounting holes on the described reduction box casing, so that the electric angle-adjuster control apparatus of described automotive seat is fixed on the side board support frame of seat back-rest framework.
In a preferred embodiment of the present utility model, described output shaft is backrest recliner synchronizing bar.
The principle of work of the electric angle-adjuster control apparatus of automotive seat of the present utility model is as follows: (according to preferred embodiment)
The electric angle-adjuster control apparatus of automotive seat of the present utility model by DC machine as propulsion source, Motor torque is delivered to worm screw by motor shaft, be delivered to the helical wheel part of dual gear by worm screw, the helical wheel of worm screw and plastics dual gear partly consists of the first order deceleration of speed reduction gearing again.Wherein, number of threads is 1, and the helical wheel part number of teeth is 54, and the transmitting ratio that therefore can obtain first order deceleration is 1:54.
After finishing first order deceleration, power partly is delivered to the center gear part by the helical wheel of dual gear, is outputed power by the planet gear transmission frame component by the several rows star-wheel in the planet circular system again.Slow down in the second stage that the internally toothed annulus part of the center gear of dual gear, several rows star-wheel, reduction box casing and pinion carrier transmission component consist of speed reduction gearing.Wherein, the internally toothed annulus part links to each other with drop-gear box shell frame, forms NGW planetary wheeling mechanism (center gear input, pinion carrier output).The center gear number of teeth is 15, and the satellite gear number of teeth is 18, and the internally toothed annulus number of teeth is 51, and the transmitting ratio that therefore can obtain slowing down the second stage is 1:4.4(1+51/15).
The overall gear ratio of double reduction is that the independent transmitting ratio of two-stage is long-pending, i.e. 1:237.6.Like this, if the limit output torque of control apparatus is 25Nm, the motor torsional torque only need reach 0.21Nm.The electric angle-adjuster control apparatus of automotive seat of the present utility model can foreshorten to 68.6mm along the extreme length on the motor shaft direction.
The electric angle-adjuster control apparatus of automotive seat of the present utility model compared with prior art has following characteristics:
1. in the reduction box casing and gear box cover of the electric angle-adjuster control apparatus of the utility model automotive seat, dual gear (comprising the center gear that slows down in helical wheel that the first order is slowed down and the second stage) has been abandoned traditional internal diameter with gear matches to reach the radial location of gear with the external diameter of optical axis mode, but adopt the external diameter of the first steady ring of the end (helical wheel end) of dual gear is matched with the first locating bush internal diameter on the reduction box casing, the second steady ring external diameter of the other end (center gear end) matches with the internal diameter of the second locating bush of planet gear transmission frame component, to reach equally the radial location of dual gear.This structure locate mode does not need an optical axis to the location of planetary wheeling mechanism center gear, and having created from the planetary wheeling mechanism through for non-optical axis (such as the castellated shaft of recliner synchronizing bar) may.
2. pass through the topology layout mode of the electric angle-adjuster control apparatus of adjusting the utility model automotive seat, can make the miscellaneous part that drives as mouth with planet circular system be distributed in simultaneously the both sides of control apparatus, and not need extra coupler can ensure the synchronism in both sides of two driven parts.This with exported at an end of planet circular system in the past, drive one of them driven parts, and then by the mode that coupler or multi-connecting-rod mechanism drive another driven parts very large optimization arranged, saved part, improved the resistance to overturning of system.
Description of drawings
Fig. 1 is the schematic perspective view of the described device of US2012/0119554A1.
Fig. 2 is the schematic appearance of the electric angle-adjuster control apparatus of the utility model automotive seat.
Fig. 3 is the exploded perspective view of whole parts of seeing from a direction of the electric angle-adjuster control apparatus of the utility model automotive seat.
Fig. 4 is the exploded perspective view of whole parts of seeing from another direction of the electric angle-adjuster control apparatus of the utility model automotive seat.
Fig. 5 is the assembling schematic diagram between motor in the electric angle-adjuster control apparatus of the utility model automotive seat, reduction box casing, the worm screw.
Fig. 6 is the reduction box casing structural representation in the electric angle-adjuster control apparatus of the utility model automotive seat.
Fig. 7 is the structural representation of the dual gear in the electric angle-adjuster control apparatus of the utility model automotive seat.
Fig. 8 is the assembling schematic diagram between dual gear in the electric angle-adjuster control apparatus of the utility model automotive seat and satellite gear, the planet gear transmission frame component.
Fig. 9 is the structural representation of the planetary transmission frame component in the electric angle-adjuster control apparatus of the utility model automotive seat.
Figure 10 is the gear box cover structural representation in the electric angle-adjuster control apparatus of the utility model automotive seat.
Figure 11 is the electric angle-adjuster control apparatus drive connection schematic diagram of the utility model automotive seat.
Figure 12 is the schematic perspective view that the electric angle-adjuster control apparatus of the utility model automotive seat is connected with backrest frames.
The specific embodiment
Describe the utility model in detail below in conjunction with the drawings and specific embodiments.
The structure of the conventional adjustment means that contrast Fig. 1 provides, Fig. 2 to Figure 12 provides preferred embodiment of the present invention, and is described in detail, and enables to understand better function of the present invention, characteristics.
Referring to Fig. 2 to Fig. 4, the electric angle-adjuster control apparatus of the automotive seat that provide among the figure comprises that reduction box casing 100, DC machine 200, worm screw 300, dual gear 400, planet gear transmission frame component 500, gear box cover 600, backrest recliner synchronizing bar 700 and three satellite gear 800(can certainly be four even more).
In conjunction with referring to Fig. 6, reduction box casing 100 plays in electric angle-adjuster control apparatus of the present utility model and connects and positioning action.This reduction box casing 100 has the container cavity 110,120 and orthogonal attachment face 130,140 of mutual perforation, wherein attachment face 130 perpendicular to the axis of container cavity 120 in order to the location with DC machine 200 is installed, attachment face 140 perpendicular to the axis of container cavity 110 in order to the location with gear box cover 600 is installed.On reduction box casing 100, also be provided with a bolt mounting holes 180 in addition, so that electric angle-adjuster control apparatus of the present utility model is fixed on the side board support frame of seat back-rest framework.
On reduction box casing 100, also be provided with three hooks 170, be convenient to be connected with gear box cover 600.
The wall periphery is provided with internally toothed annulus 190 in the chamber of container cavity 110; Internally toothed annulus 190 can adopt metallic material or integrally moulded forming with reduction box casing 100, also can adopt metallic material or plastics independently to make respectively, if internally toothed annulus 190 is independently made with reduction box casing 100, internally toothed annulus 190 is embedded on the chamber wall periphery of container cavity 110.
The center is provided with a locating bush 150 and offers a centre hole 160 at the bottom of the chamber of container cavity 110, and centre hole 160 runs through at the bottom of the chamber of locating bush 150 and container cavity 110, and locating bush 150 can carry out radial location to dual gear 400 like this.The end face of locating bush 150 is flange face 151, and this flange face 151 can carry out axial location to dual gear 400.
In conjunction with referring to Fig. 5, DC machine 200 is installed on the attachment face 130 of reduction box casing 100 by bolt 210, the motor shaft 220(of DC machine 200 is referring to Fig. 3 and Fig. 4) extend in the container cavity 120, be set with hollow worm screw 300 at motor shaft, hollow worm screw 300 parts are extended in the container cavity 110 by container cavity 120, so as with dual gear 400 in helical wheel 410 engagement.
In conjunction with referring to Fig. 7, dual gear 400 has helical wheel 410 and the center gear 420 of coaxial setting, and the moment of torsion that is passed over by hollow worm screw 300 is passed to planet circular system through helical wheel 410 and center gear 420.Helical wheel 410 in the dual gear 400 and center gear 420 can adopt metallic material or plastics to be made into integration.Also can adopt metallic material or plastics independently to make respectively, if independently make respectively, then offer an interior perforation (not shown) at helical wheel 410 centers, an end of center gear 420 be inserted in the interior perforation and with its engagement.
The scheme that helical wheel 410 in the preferred dual gear 400 of this specific embodiment and center gear 420 adopt plastics to be made into integration.Be respectively arranged with steady ring 430,440 at dual gear 400 along the two ends of central axis like this, offer simultaneously one at the center of dual gear 400 and run through steady ring 430,440 centre hole 450.Steady ring 430 can be inserted into that the locating bush 150 of reduction box casing 100 is interior to carry out radial location to dual gear 400.Dual gear 400 cooperatively interacts with respect to the flange face 151 of those side end faces 460 of reduction box casing 100 and locating bush 150 dual gear 400 is carried out axial location.
In conjunction with referring to Fig. 9 and Fig. 3, the planet gear transmission frame component 500 that consists of planet circular system can certainly be four even more by planet gear transmission support body 510, center sleeve 520 and three straight pin 530(that consist of planet wheel spindle).
Planet gear transmission support body 510 is disk structure, planet gear transmission support body 510 both ends of the surface of disk structure are flange face 511,512, flange face 511 and the dual gear 400 relative first surfaces that consist of planet gear transmission frame components 500, flange face 512 and gear box cover 600 relative second of consisting of planet gear transmission frame components 500.
Planet gear transmission support body 510 centers at disk structure offer a center pore 513, and center sleeve 520 passes center pore 513 and captives joint with planet gear transmission support body 510.The two ends that center sleeve 520 exposes planet gear transmission support body 510 consist of respectively locating bush 521 and the steady ring 522 in the planet gear transmission frame component 500; The endoporus of center sleeve 520 consists of the centre hole 523 of planet gear transmission frame component 500.Steady ring 440 in the dual gear 400 is inserted in the locating bush 521 in the planet gear transmission frame component 500 just can carries out axial location and support its rotation dual gear 400.
In the endoporus of center sleeve 520, be provided with one section female splines 524, rotate so that center sleeve 520 cooperates to drive recliner with the recliner synchronizing bar 700 of cushion frame.
Circumferentially being evenly equipped with three cylinder pin hole 514(as the center of circle take the center of center sleeve 520 on the flange face 511 of planet gear transmission support body 510 can certainly be four even more), each cylinder pin hole 514 periphery is provided with a little flange face 515, in each cylinder pin hole 514, be fixed with a straight pin 530, cover has a satellite gear 800(referring to Fig. 8 on each straight pin 530), each satellite gear 800 contacts with little flange face 515 towards planet gear transmission support body 510 sides, to limit the axial location of satellite gear 800, can improve the contact relation of planet gear transmission support body 510 and satellite gear 800 by little flange face 515 ways of contact, reduce noise.
Above line planet gearing support body 510 center sleeves 520 and three straight pins 530 that consist of planet wheel spindle can adopt metallic material or plastics to be integrated into, and also can adopt metallic material or plastics independently to make.
Three satellite gears 800 measure-alike can adopt metallic material or plastics to make.Referring to Fig. 8, three satellite gears 800 are enclosed within respectively on the straight pin 530 that on the planet gear transmission support body 510 of planet gear transmission frame component 500 three consist of planet wheel spindles, center gear 420 and 190 engagements of the internally toothed annulus in the reduction box casing 100 in three satellite gears 800 and the dual gear 400.
In conjunction with referring to Figure 10, gear box cover 600 can adopt metallic material or plastic support, it is made of end cap part 610 and three buckles 620 that are arranged on end cap part 610 outer rims, the center of end cap part 610 offers a center positioning hole 611, carries out radial location in being inserted into the steady ring 522 in the planet gear transmission frame component 500 in the center positioning hole 611 on the end cap part 610.Three buckles 620 on end cap part 610 outer rims are connected with three hooks 170 on the reduction box casing 100, make gear box cover 600 relative reduction box casing 100 side seals and circumferential the location.Prevent from getting loose in the assorted operation process of electric angle-adjuster control apparatus of the present utility model or producing extra relative motion.Certainly buckle quantity and the hook number on the reduction box casing 100 on end cap part 610 outer rims is not limited to three, can be decided according to the actual requirements.
The assembling mode of the electric angle-adjuster control apparatus of this specific embodiment is as follows:
Referring to Fig. 3 and Fig. 4, at first with hollow worm screw 300 shell-likes on the motor shaft 220 of DC machine 200, on the attachment face 130 of the reduction box casing 100 of then two bolts of DC machine 200 employings 210 being installed, the motor shaft 220 of DC machine 200 and hollow worm screw 300 are inserted in the container cavity 120, and hollow worm screw 300 parts are extended in the container cavity 110 by container cavity 120, so as with dual gear 400 in helical wheel 410 engagement (as shown in Figure 5).
Then three satellite gears 800 are enclosed within respectively on the straight pin 530 that on the planet gear transmission support body 510 of planet gear transmission frame component 500 three consist of planet wheel spindles, then the steady ring 440 in the dual gear 400 is inserted in the locating bush 521 on the planet gear transmission support body 510 of planet gear transmission frame component 500, and makes center gear 420 and three satellite gears 800 engagements (as shown in Figure 8) in the dual gear 400.
Three satellite gears 800, planet gear transmission frame component 500 and the dual gear 400 that will assemble again packed in the container cavity 110 of reduction box casing 100 together, and steady ring 430 on the dual gear 400 is inserted in the locating bush 150 at center at the bottom of the chamber of container cavity 110 can carry out radial location.Make simultaneously helical wheel 410 and hollow worm screw 300 engagements in the dual gear 400, three satellite gears 800 mesh with internally toothed annulus 190.
At last gear box cover 600 is installed on the attachment face 140 of reduction box casing 100, and the steady ring 522 in the planet gear transmission frame component 500 is inserted in the center positioning hole 611, again three buckles 620 on the gear box cover 600 are buckled on three hooks 170 on the reduction box casing 100 and can assemble complete (referring to Fig. 2).
The electric angle-adjuster control apparatus that assembles is fixed on the side board support frame 910 of seat back-rest framework 900 by the bolt hole 180 that passes on the reduction box casing 100.At last backrest recliner synchronizing bar 700 is passed successively the center positioning hole 611 of gear box cover 600, the centre hole 523 of planet gear transmission frame component 500, the centre hole 450 of dual gear 400 and the centre hole 160 on the reduction box casing 100.Backrest recliner synchronizing bar 700 in this specific embodiment has one section or whole be castellated shaft, thus its can with the centre hole 523 of planet gear transmission frame component 500 in 524 engagements of one section female splines.
The principle of work of this specific embodiment electric angle-adjuster control apparatus is:
Referring to Figure 11, by DC machine 200 as propulsion source, DC machine 200 moments of torsion are delivered to hollow worm screw 300 by motor shaft 220, be delivered to helical wheel 410 parts of dual gear 400 by hollow worm screw 300, hollow worm screw 300 is slowed down with the first order of the helical wheel 410 parts formation speed reduction gearing of dual gear 400 again.Wherein, 300 numbers of hollow worm screw are 1, and the helical wheel 410 part numbers of teeth are 54, and the transmitting ratio that therefore can obtain first order deceleration is 1:54.
After finishing first order deceleration, power is delivered to center gear 420 parts by helical wheel 410 parts of dual gear 400, outputs power to backrest recliner synchronizing bar 700 by the several rows star-wheel 800 in the planet circular system by planet gear transmission frame component 500 again.Slow down in the center gear 420 of dual gear 400, three satellite gears 800, internally toothed annulus 190 parts of reduction box casing 100 and the second stage that pinion carrier transmission component 500 consists of speed reduction gearing.Wherein, internally toothed annulus 190 parts link to each other with reduction box casing 100, form NGW planetary wheeling mechanism (center gear input, pinion carrier output).Center gear 420 numbers of teeth are 15, and satellite gear 800 numbers of teeth are 18, and internally toothed annulus 190 numbers of teeth are 51, and the transmitting ratio that therefore can obtain slowing down the second stage is 1:4.4(1+51/15).
The overall gear ratio of double reduction is that the independent transmitting ratio of two-stage is long-pending, i.e. 1:237.6.Like this, if the limit output torque of control apparatus is 25Nm, DC machine 200 torsional torque only need reach 0.21Nm.The electric angle-adjuster control apparatus of the automotive seat of this specific embodiment can foreshorten to 68.6mm along the extreme length on the motor shaft direction.
Claims (18)
1. the electric angle-adjuster control apparatus of automotive seat comprises:
One reduction box casing, described reduction box casing have the first container cavity and second container cavity of mutual perforation, and the wall periphery is provided with internally toothed annulus in the chamber of described the second container cavity;
One is installed in the motor on the described reduction box casing, and the motor shaft of described motor extends in described the first container cavity;
One is installed in the worm screw on the described motor shaft, and a described worm screw part extends to the second container cavity by described the first container cavity;
One is housed inside the dual gear in described the second container cavity, and described dual gear has one of coaxial setting and consists of the center gear of planet circular system with the helical wheel and of described worm mesh;
One consists of the planet gear transmission frame component of described planet circular system;
Circumferentially be distributed on the several rows star-wheel on the described planet gear transmission frame component, this several rows star-wheel and described center gear and the engagement of described internally toothed annulus;
One is installed in the gear box cover on the described reduction box casing, and described gear box cover is limited in described dual gear, planet gear transmission frame component, several rows star-wheel in the space that described gear box cover and reduction box casing limit;
One passes the output shaft of described gear box cover, planet gear transmission frame component, dual gear and reduction box casing successively, and described output shaft is meshed with described planet gear transmission frame component, it is characterized in that,
Described dual gear is coaxial to be radially positioned on described reduction box casing and the described planet gear transmission frame component.
2. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 1, it is characterized in that, described dual gear is respectively arranged with the first steady ring and the second steady ring along the two ends of central axis, the center is provided with one first locating bush at the bottom of the chamber of the second container cavity of described reduction box casing, be provided with one second locating bush at described planet gear transmission frame component with respect to the first surface center of described dual gear, wherein the first steady ring of dual gear is inserted in the first locating bush of described reduction box casing and carries out radial location, and the second steady ring of dual gear is inserted in the second locating bush on the described planet gear transmission frame component and carries out radial location.
3. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 2, it is characterized in that, the end face of the first locating bush on the described reduction box casing is the first flange face, and described the first flange face and described dual gear cooperatively interact with respect to that side end face of described reduction box casing described dual gear is carried out axial location.
4. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 3, it is characterized in that, be provided with one the 3rd steady ring at described planet gear transmission frame component with respect to second center of described gear box cover, offer a center positioning hole at the center of described gear box cover, the second steady ring on the described planet gear transmission frame component is inserted in the center positioning hole on the described gear box cover and carries out radial location.
5. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 4, it is characterized in that, as the center of circle circumferentially be evenly equipped with described satellite gear quantity identical planet wheel spindle take the center of described the second locating bush at described planet gear transmission frame component on respect to the first surface of described dual gear, cover has a satellite gear on each planet wheel spindle.
6. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 5, it is characterized in that, center at described planet gear transmission frame component, the center offers respectively the first centre hole at the bottom of the chamber of the second container cavity of the center of dual gear and reduction box casing, the second centre hole and the 3rd centre hole, wherein said the first centre hole runs through the first steady ring and the second locating bush on the described planet gear transmission frame component, the second centre hole runs through the first steady ring and second steady ring of described dual gear, and the 3rd centre hole runs through at the bottom of the chamber of the first locating bush on the reduction box casing and the second container cavity; Described output shaft passes the first centre hole, the second centre hole and the 3rd centre hole successively.
7. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 6, it is characterized in that, be provided with one section female splines in the first centre hole on described planet gear transmission frame component, described output shaft has at least one section splined shaft section, and the female splines in the first centre hole on the splined shaft section on the described output shaft and the described planet gear transmission frame component is intermeshing.
8. the electric angle-adjuster control apparatus of automotive seat as claimed in claim 7 is characterized in that, described planet gear transmission frame component is by planet gear transmission support body, center sleeve and some straight pins that consists of planet wheel spindle; Described planet gear transmission support body is disk structure, the planet gear transmission support body both ends of the surface of disk structure form respectively the second flange face and three-flange face, the first surface of the described planet gear transmission frame component of the second flange face formation relative to described dual gear, three-flange face second of consisting of described planet gear transmission frame component relative to gear box cover; Planet gear transmission support body center at described disk structure offers a center pore, described center sleeve passes described center pore and captives joint with the planet gear transmission support body, and the two ends that center sleeve exposes the planet gear transmission support body consist of respectively the second locating bush and the 3rd steady ring in the described planet gear transmission frame component; The endoporus of described center sleeve consists of the first centre hole of described planet gear transmission frame component; Center take described center sleeve on the second flange face of described planet gear transmission support body circumferentially is evenly equipped with some cylinder pin holes as the center of circle, each cylinder pin hole periphery is provided with a little flange face, in each cylinder pin hole, be fixed with a straight pin, cover has a satellite gear on each straight pin, each satellite gear contacts with described little flange face towards the planet gear transmission support body side, to limit the axial location of satellite gear.
9. such as the electric angle-adjuster control apparatus of the described automotive seat of each claim of claim 1 to 8, it is characterized in that, described motor is DC machine.
10. such as the electric angle-adjuster control apparatus of the described automotive seat of each claim of claim 1 to 8, it is characterized in that, described worm screw is hollow worm screw, and this hollow worm set is contained on the motor shaft of described motor.
11. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8, it is characterized in that, described reduction box casing has orthogonal the first attachment face and the second attachment face, wherein the first attachment face perpendicular to the axis of described the first container cavity in order to the location with described motor is installed, the second attachment face perpendicular to the axis of described the second container cavity in order to the location with described gear box cover is installed.
12. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8 is characterized in that, described internally toothed annulus and described reduction box casing are made into integration.
13. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8, it is characterized in that, described internally toothed annulus and described reduction box casing are independently made respectively, and described internally toothed annulus is embedded on the chamber wall periphery of described the second container cavity.
14. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8 is characterized in that, helical wheel and center gear in the described dual gear are made into integration.
15. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8, it is characterized in that, helical wheel and center gear in the described dual gear are independently made respectively, wherein said helical wheel has an interior perforation, an end of described center gear be inserted in the described interior perforation and with its engagement.
16. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8, it is characterized in that, be provided with some hooks at described reduction box casing, be provided with some buckles at described gear box cover, when gear box cover was installed on the reduction box casing, described buckle was buckled on the described hook.
17. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8, it is characterized in that, be provided with a bolt mounting holes on the described reduction box casing, so that the electric angle-adjuster control apparatus of described automotive seat is fixed on the side board support frame of seat back-rest framework.
18. the electric angle-adjuster control apparatus such as the described automotive seat of each claim of claim 1 to 8 is characterized in that, described output shaft is backrest recliner synchronizing bar.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220447826 CN202827204U (en) | 2012-09-04 | 2012-09-04 | Adjusting device of automobile seat electric angle adjustor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220447826 CN202827204U (en) | 2012-09-04 | 2012-09-04 | Adjusting device of automobile seat electric angle adjustor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202827204U true CN202827204U (en) | 2013-03-27 |
Family
ID=47938976
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220447826 Expired - Fee Related CN202827204U (en) | 2012-09-04 | 2012-09-04 | Adjusting device of automobile seat electric angle adjustor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202827204U (en) |
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| CN103625318A (en) * | 2013-12-17 | 2014-03-12 | 湖北中航精机科技有限公司 | Adjustable chair and angle adjusting device thereof |
| CN105090371A (en) * | 2015-09-21 | 2015-11-25 | 宁波夏厦齿轮有限公司 | Wheelchair planetary reducer |
| CN106917560A (en) * | 2015-12-25 | 2017-07-04 | 德昌电机(深圳)有限公司 | Drive mechanism and the vehicle using the drive mechanism |
| CN107191551A (en) * | 2017-08-01 | 2017-09-22 | 上海昂富新能源设备有限公司 | A kind of planet gear reducing mechanism and drive device |
| CN108237951A (en) * | 2017-12-12 | 2018-07-03 | 北京车和家信息技术有限公司 | Seat adjuster, automotive seat and vehicle |
| CN109398396A (en) * | 2018-12-18 | 2019-03-01 | 湖北火爆机器人科技有限公司 | A kind of high precision speed reducing driving device and its operating method |
| CN109488734A (en) * | 2017-09-13 | 2019-03-19 | 三多乐精密注塑(深圳)有限公司 | A kind of planetary gear transmission mechanism |
| CN110329121A (en) * | 2019-07-19 | 2019-10-15 | 延锋安道拓座椅有限公司 | The angle regulating structure of seat and integrated form angle adjustor thereon |
| CN110594367A (en) * | 2019-09-27 | 2019-12-20 | 延锋安道拓(常熟)座椅机械部件有限公司 | Manual and electric integrated window-shaking motor |
| CN110626232A (en) * | 2018-06-22 | 2019-12-31 | 广东肇庆爱龙威机电有限公司 | Drive for adjusting the lifting of a vehicle seat and vehicle seat with such a drive |
| CN111319528A (en) * | 2020-04-22 | 2020-06-23 | 孙渝辉 | Automobile seat continuous angle adjuster capable of realizing coaxial circular motion output |
| CN112901741A (en) * | 2021-03-29 | 2021-06-04 | 恺博座椅机械部件有限公司 | Electric angle adjuster adjusting mechanism capable of realizing manual adjustment |
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| CN103625318B (en) * | 2013-12-17 | 2015-11-04 | 湖北中航精机科技有限公司 | A kind of barbed chair and angle regulator thereof |
| CN103625318A (en) * | 2013-12-17 | 2014-03-12 | 湖北中航精机科技有限公司 | Adjustable chair and angle adjusting device thereof |
| CN105090371A (en) * | 2015-09-21 | 2015-11-25 | 宁波夏厦齿轮有限公司 | Wheelchair planetary reducer |
| CN106917560A (en) * | 2015-12-25 | 2017-07-04 | 德昌电机(深圳)有限公司 | Drive mechanism and the vehicle using the drive mechanism |
| CN107191551A (en) * | 2017-08-01 | 2017-09-22 | 上海昂富新能源设备有限公司 | A kind of planet gear reducing mechanism and drive device |
| CN109488734A (en) * | 2017-09-13 | 2019-03-19 | 三多乐精密注塑(深圳)有限公司 | A kind of planetary gear transmission mechanism |
| CN108237951B (en) * | 2017-12-12 | 2019-09-27 | 北京车和家信息技术有限公司 | Seat adjuster, automotive seat and vehicle |
| CN108237951A (en) * | 2017-12-12 | 2018-07-03 | 北京车和家信息技术有限公司 | Seat adjuster, automotive seat and vehicle |
| CN110626232A (en) * | 2018-06-22 | 2019-12-31 | 广东肇庆爱龙威机电有限公司 | Drive for adjusting the lifting of a vehicle seat and vehicle seat with such a drive |
| CN109398396A (en) * | 2018-12-18 | 2019-03-01 | 湖北火爆机器人科技有限公司 | A kind of high precision speed reducing driving device and its operating method |
| CN109398396B (en) * | 2018-12-18 | 2024-05-17 | 湖北火爆机器人科技有限公司 | High-accuracy deceleration driving device and operation method thereof |
| CN110329121A (en) * | 2019-07-19 | 2019-10-15 | 延锋安道拓座椅有限公司 | The angle regulating structure of seat and integrated form angle adjustor thereon |
| CN110329121B (en) * | 2019-07-19 | 2020-08-21 | 延锋安道拓座椅有限公司 | Angle modulation structure of seat and integrated angle modulator thereon |
| CN110594367A (en) * | 2019-09-27 | 2019-12-20 | 延锋安道拓(常熟)座椅机械部件有限公司 | Manual and electric integrated window-shaking motor |
| CN111319528A (en) * | 2020-04-22 | 2020-06-23 | 孙渝辉 | Automobile seat continuous angle adjuster capable of realizing coaxial circular motion output |
| CN112901741A (en) * | 2021-03-29 | 2021-06-04 | 恺博座椅机械部件有限公司 | Electric angle adjuster adjusting mechanism capable of realizing manual adjustment |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Kang Road, Pudong New Area Kangqiao Industrial Zone of Shanghai City, No. 669, 201315 Patentee after: Yanfeng Daotuo Ann seat Co. Address before: Kang Road, Pudong New Area Kangqiao Industrial Zone of Shanghai City, No. 669, 201315 Patentee before: Shanghai Yanfeng Johnson Controls Seating Co., Ltd. |
|
| CP01 | Change in the name or title of a patent holder | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130327 Termination date: 20190904 |
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| CF01 | Termination of patent right due to non-payment of annual fee |