WO2013075619A1 - 一种座椅调角器及其座椅 - Google Patents

一种座椅调角器及其座椅 Download PDF

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Publication number
WO2013075619A1
WO2013075619A1 PCT/CN2012/084932 CN2012084932W WO2013075619A1 WO 2013075619 A1 WO2013075619 A1 WO 2013075619A1 CN 2012084932 W CN2012084932 W CN 2012084932W WO 2013075619 A1 WO2013075619 A1 WO 2013075619A1
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WO
WIPO (PCT)
Prior art keywords
driving
plate
cam
eccentric wheel
drive
Prior art date
Application number
PCT/CN2012/084932
Other languages
English (en)
French (fr)
Inventor
江冲
黄兴
黄正坤
杜渐
Original Assignee
湖北中航精机科技股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 湖北中航精机科技股份有限公司 filed Critical 湖北中航精机科技股份有限公司
Priority to US14/348,145 priority Critical patent/US9376035B2/en
Publication of WO2013075619A1 publication Critical patent/WO2013075619A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
    • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
    • B60N2/2252—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms in which the central axis of the gearing lies inside the periphery of an orbital gear, e.g. one gear without sun gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
    • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
    • B60N2/2254—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms provided with braking systems

Definitions

  • the utility model relates to a Chinese patent application submitted by the Chinese Patent Office on November 25, 2011, with the application number of 201110381621.5, and the invention name is "a seat recliner and its seat”. Priority is hereby incorporated by reference in its entirety.
  • the present invention relates to a seat adjustment technique, and more particularly to a seat recliner and a seat including the seat recliner. Background technique
  • the seat recliner is used to connect the seat and back of the car seat to enhance the comfort of the seat. Passengers can adjust the angle of the seat back to the best position through the seat recliner for the most comfortable and habitual ride angle. For the driver, the best view is achieved by adjusting the angle of the seat back, and it is easy to manipulate the steering wheel, pedal and shift lever.
  • the planetary gear transmission principle is generally adopted for the electric seat recliner. Due to the inevitable manufacturing error of the parts, there is a certain gap inside the recliner. When used, the gap will cause the seat back. The swing is relatively large in the front-rear direction of the seat and is accompanied by noise, which in turn affects the comfort of the seat. Therefore, a clearance eliminating mechanism is usually provided inside the recliner.
  • Chinese patent document CN201468560U discloses a seat recliner and a seat having the same: an inner tooth plate having an internal spur, an outer tooth plate having an external spur, an eccentric wheel, a wedge block and a drive cam
  • the inner tooth plate is fixedly connected to the seat back, and the inner tooth plate is provided with a shoulder in a middle portion thereof;
  • the outer tooth plate is fixedly connected to the seat, and the middle portion of the outer tooth plate is provided with an axial center a hole;
  • the external gingival meshes with the internal gingival and the shape of the shoulder and the axial hole a radial eccentric region;
  • the eccentric is disposed in the radial eccentric region, the eccentric, the inner tooth plate and the outer tooth plate constitute a planetary gear transmission mechanism with less tooth difference;
  • the wedge block is placed in the diameter And the eccentric wheel and the wedge block cancel the gap between the eccentric wheel and the axial hole of the inner tooth plate and the meshing tooth under the circumferential force applied by the elastic member;
  • the wedge block in order to accommodate the purpose that the wedge is wedged in the circumferential direction to eliminate the internal clearance of the recliner and the assembly manufacturing error, the wedge block must have sufficient circumferential seating space to ensure that it can always be in the wedge. In a tight state, therefore, there must be a certain operational idle travel between the drive cam and the wedge block, as shown in Figure 1, the space described by the angles a, b, during the adjustment of the recliner, especially the backrest reversal During the adjustment process, the driving cam is driven by the driving eccentric to drive the wedge block, and must pass the reserved operation idle stroke, that is, the sum of the angles a and b, and then drive the wedge block to rotate, to realize the backrest angle reversing adjustment, due to the driving cam It is necessary to go through a certain operation of the idle stroke. Therefore, during the reversing adjustment of the seat back, the user can feel that the backrest adjustment action has a relatively obvious lag, and there is a certain waiting time, which affects the comfort of the seat
  • the driving cam is driven by the motor, and the driving cam first rotates through the operation of the idle stroke and then contacts the driving wedge/eccentric wheel to realize the angle adjustment.
  • the driving cam is Higher speeds impinge on the stationary wedge/eccentric wheel, so that during the reversing of the backrest, more pronounced noise is produced, which also affects the comfort of the seat.
  • an adjustment assembly for a backrest adjustable seat and in particular a car seat is disclosed in the Chinese patent document CN1149157C, in which a new one is provided for raising the seat.
  • the comfort solution uses a synchronizing ring to drive two wedges that are wedged to the sides under the action of the elastic element to eliminate the gap. As shown in Figure 2, this solution can reduce the operational idle stroke and weaken the commutation noise. After inventor's trial and error, it discovered its new technical problem: Because during the backrest adjustment process, one of the wedges is in the synchronous ring.
  • the backrest response time lag during the backrest commutation process and the noise of the recliner commutation are eliminated, and the operating torque of the recliner can be effectively controlled to operate the recliner.
  • the torque did not increase.
  • the embodiment of the present invention provides a seat adjustment angle. And its seat.
  • the technical solution is as follows:
  • a seat recliner that includes:
  • a gear transmission mechanism comprising an inner tooth plate with a toothed shank, an outer tooth plate with an external tooth shank, and an eccentric wheel with a wedge block, the inner tooth of the inner tooth plate being identical to the outer tooth plate
  • the outer dents are engaged, a middle portion of the inner tooth plate is formed with a hollow shoulder, and the eccentric wheel is rotatably sleeved on the outer circumferential surface of the shoulder;
  • the driving component comprises a driving cam and a hollow rotating shaft, wherein one end of the rotating shaft is fixedly connected with a middle portion of the driving cam, and the other end thereof sequentially penetrates the eccentric wheel and the shoulder and passes the shaft through a limiting connector Fixed to the inner tooth plate, the rotating shaft is matched with the shoulder gap, and the opposite surface between the driving cam and the eccentric wheel is provided with a resistance torque structure for transmitting torque, the driving station When the driving cam is driven, the driving torque acting on the driving cam transmits the driving torque to the eccentric wheel through the resistance torque structure, and the eccentric wheel is driven to rotate synchronously, thereby realizing the torque to the gear transmission mechanism. transfer.
  • the resistance torque structure includes a spring for increasing a frictional moment between the eccentric and the driving cam, the spring being realized by increasing a frictional moment between the eccentric and the driving cam coupling surface
  • a driving plate is disposed between the eccentric wheel and the driving cam, and is disposed on a rotating shaft between the eccentric wheel and the driving cam, and a running circle is formed on a surface of the driving plate a curved hole, a driving arm disposed on the driving cam is rotatably connected to the eccentric through a circular arc-shaped hole on the driving plate; a friction torque generated between the wheels is transmitted to the driving plate .
  • the driving cam and the driving plate adopt a split structure, one side of the plate produced by the spring is in close contact with the surface of the driving cam, and the driving plate is provided on the eccentric wheel a positioning hole corresponding to the protrusion, a positioning hole on the driving plate is coupled with a protrusion formed on the eccentric wheel to realize synchronous rotation of the driving plate, and the driving plate is axially in the rotating shaft There is a certain gap to adapt to its axial error.
  • the spring is a compression spring
  • a compression sleeve is disposed on a rotating shaft between the driving plate and the inner tooth plate, one end of which acts on an end surface of the driving plate, and the other end acts on the rotating
  • the spring end of the shaft end portion is gap-fitted with the shoulder of the inner tooth plate;
  • the pre-tightening force generated by the spring causes the driving plate to be in close contact with the driving cam, and the eccentric wheel is driven to rotate by a frictional resistance torque formed by the driving plate and the driving cam joint surface.
  • a friction material for increasing the friction coefficient of the driving plate and the driving cam is disposed on the driving plate and/or the driving cam.
  • a movable synchronous pressure plate is disposed between the driving plate and the eccentric wheel, and the synchronous pressure plate is sleeved between the eccentric wheel and the driving cam.
  • the positioning hole on the synchronous platen is matched with the two driving arms on the driving cam, and the synchronous platen can be circumferentially synchronized with the driving cam Rotating, and the synchronous platen is axially slidable along the driving arm, the partial Plug in
  • the pre-tightening force generated by the spring acts on the joint surface between the driving plate and the driving cam and the synchronous pressing plate, so that the two sides of the driving plate are closely matched with the driving cam and the synchronous pressing plate, respectively. .
  • the spring is a compression spring
  • a compression sleeve is disposed on a rotating shaft between the driving plate and the inner tooth plate, one end of which acts on an end surface of the synchronous pressure plate, and the other end acts on the rotation
  • the spring end of the shaft end portion is gap-fitted with the shoulder of the inner tooth plate;
  • the synchronous pressure plate Under the action of the spring force, the synchronous pressure plate is in close contact with an end surface of the driving plate, and the other end surface of the driving plate is pressed against the driving cam, and the driving plate and the driving are performed.
  • the frictional resistance torque formed by the cam joint surface, the frictional resistance torque formed by the synchronous pressure plate and the driving plate joint surface, applies torque to the driving plate to drive the eccentric wheel.
  • the spring is a compression spring of rectangular cross section.
  • a friction material for increasing the friction coefficient is disposed on the joint surface between the driving plate and the driving cam, and the synchronous pressing plate and the driving plate coupling surface, and the friction material is fixed to the driving plate and/or Drive cam and / or synchronous platen.
  • the periphery of the driving plate is bent to form an everted buckle, and the outer periphery of the driving cam is wrapped in the buckle, and the buckle is covered with the buckle
  • a circumferential annulus is formed between the outer periphery of the driving cam in the buckle, and the circumferential annulus is provided with an elastic member for increasing frictional damping at the joint faces.
  • a seat including a hinged seat and a seat back, and the seat recliner disposed between the seat and the back, the outer and inner teeth respectively
  • Seats and chairs are provided for the rotating shaft.
  • the resistance torque structure includes a spring for increasing the resistance torque between the driving plate and the driving cam, and the pressure provided by the spring acts on the driving plate.
  • the force provided is enclosed between the driving cam and the driving plate, and is not transmitted to the gear transmission mechanism.
  • the spring always axially fits the driving plate and the driving cam, and is pressed, when the driving cam drives the driving plate to rotate circumferentially. The friction between the driving plate and the driving cam will prevent its movement. In this way, the circumferential rotation of the driving cam and the eccentric wheel is eliminated.
  • By adjusting the force of the spring a constant setting between the eccentric and the driving cam can be achieved. Resistance torque.
  • the operating torque of the recliner described in Chinese Patent Document CN201468560U can be determined.
  • gear driving torque it is referred to as gear driving torque
  • the operating torque applied to the recliner must be greater than or equal to the gear driving torque.
  • the backrest angle can be adjusted.
  • the spring sleeve is disposed on the driving cam rotating shaft and is disposed in the central hole of the inner tooth plate shoulder.
  • the spring is specifically in the form of a rectangular cross-section compression spring, and one end thereof always faces the driving plate synchronized with the eccentric wheel.
  • the torque value generated by the frictional force and the resistance torque of the center of the driving cam can be designed.
  • the pressure provided by the spring acts on the drive plate and the force it provides is enclosed between the drive cam and the drive plate, not transmitted to the gearing mechanism, and thus will not increase the gearing torque of the recliner. According to the requirements of the seat, it is necessary to adjust the ratio between the resistance torque and the gear drive torque.
  • the eccentric wheel with the clearance eliminating structure can be directly driven by the resistance torque directly, instead of the driving arm on the driving cam first passing through the wedge block to eliminate the gap.
  • the set idle travel re-drives the eccentric wheel to complete the change of the motion transmission path, thereby eliminating the hysteresis of the backrest adjustment response caused by the idle stroke of the drive cam and the eccentric wheel, and eliminating the direct impact of the drive arm on the drive cam on the eccentric wheel. The noise generated.
  • the driving plate When the driving direction is from the side of the gap eliminating structure wedge block, the driving plate will first drive the eccentric wheel under the resistance torque, and at the same time, the wedge block is in the non-driven state, so the operating torque required for the entire recliner will be Increase, when the actual required operating torque of the recliner is always less than the preset resistance torque, the eccentric movement will be directly driven to realize the rotation of the recliner.
  • the wedge shape 6 In this state, the wedge shape 6 is in a passive drag state, driving Drive arm 51 ' on cam 5 cannot When the small end of the wedge block 6 is touched, collision noise will not occur.
  • the drive cam When the required operating torque exceeds the resistive torque, the drive cam will rotate relative to the drive plate until the drive arm on the drive cam hits the small end of the wedge block. During this process, the operating torque of the angle adjuster will not continue. Increasing, when the driving arm is in contact with the wedge block, the small end of the wedge block is directly driven by the driving arm on the driving cam, and then the big end of the wedge block drives the eccentric wheel to rotate. In this process, since the eccentric wheel is moving slowly During the process, the backrest is always in the adjusted state. Therefore, the response of the backrest will have no obvious stagnation time. At this stage, there will be no relative movement between the drive cam and the drive plate. Therefore, the drive plate will disappear, so the entire recliner The required operating torque will still be equal to the gear drive torque, which will remain in this phase until it is adjusted to the proper angle.
  • the motors that drive the driving cams are always under the same load conditions. It can be understood that the rotational speed of the driving cams moving synchronously with the motor is always in a stable state, and there is no patent document CN201468560U.
  • the driving cam first undergoes an idle stroke and then drives the gap to eliminate the structure wedge or eccentric wheel.
  • the load of the motor is from small to large, and the rotation speed is high to a process of passively decreasing rapidly due to an increase in load.
  • the operating torque of the recliner of the present invention is compared with the angle adjuster without increasing the resistance torque driving system: the overall operating torque is not significantly changed, and the problem faced by the patent document CN1149157C is successfully solved; The delay of the backrest adjustment response caused by the operation of the gap elimination mechanism and the assembly manufacturing error is also solved; The noise during the adjustment of the commutation process is controlled to a relatively low state.
  • the seat recliner provided by the invention is suitable for mass production, has the characteristics of good manufacturing process and low manufacturing cost. Suitable for all kinds of seats that need to adjust the angle of the seat back, especially for car seats.
  • FIG. 1 is a cross-sectional view of a technical solution of the Chinese patent document CN201468560U; and FIG. 2 is a schematic view showing the assembly of a wedge and a synchronizing ring structure of the technical solution of the Chinese patent document CN1149157C;
  • FIG. 3 is an exploded view of the assembly of the seat recliner according to Embodiment 1 of the present invention
  • FIG. 4 is an exploded view of the assembly of the seat recliner according to Embodiment 2 of the present invention
  • Figure 4 is an exploded view of the seat recliner provided by another angle
  • Figure 6 is a schematic diagram of a small-tooth difference, single-stage planetary gear transmission
  • Figure 7 is an exploded view of the assembly between the drag torque structure, the eccentric wheel, the wedge block, the wedge torsion spring and the gear transmission system of the present invention
  • Figure 8 is a cross-sectional view of the seat recliner of the present invention.
  • Figure 9 is a schematic view showing the assembly structure between the resistive moment structure and the driving cam of the present invention
  • Figure 10a is a schematic view showing the setting of the friction material on the driving plate of the present invention
  • Figure 10b is the indicating setting of the driving plate according to the present invention
  • Figure 11 is an exploded view of the assembly of the seat recliner according to Embodiment 3 of the present invention
  • Figure 12 is an exploded view of the seat recliner provided by the present invention at another angle to Figure 11
  • Figure 14 is a schematic view showing the assembly of the seat recliner provided in Figure 11 of the present invention
  • Figure 15 is a schematic view showing the assembly of the resistive moment structure, the driving plate, the cam, the wedge torsion spring, the damper, and the like in the seat recliner provided in Figure 11 of the present invention;
  • Figure 16 is a schematic view showing another structural arrangement of the torque resistance torque according to the present invention.
  • Figure 17 is an external view of the seat according to the present invention.
  • the medial and lateral orientation words described herein are defined on the basis of the axis of the seat recliner, that is, the inner side close to the axis line is the inner side, and the side away from the axial line side is the outer side. It is to be understood that the use of the foregoing orientation words should not be limited by the scope of the claimed application.
  • the forward eccentric direction herein refers to the direction in which the radial space size is the largest in the eccentric region, and the region in the forward eccentric direction is referred to as the forward eccentric region.
  • Example 1 See Figure 3 for an exploded view of the assembly of a seat recliner.
  • the seat recliner provided by the invention mainly comprises a gear transmission mechanism, a driving component and a drag torque structure.
  • the inner tooth plate 2 having the inner spurs 21 is for fixed connection with the seat back
  • the outer tooth plate 3 having the outer spurs 31 is for fixed connection with the seat.
  • the outer tooth plate 3 and the inner tooth plate are both placed in the sheath 1, and the cuffs of the sheath 1 are fixedly coupled with the outer tooth plate 3, and after assembly, the outer teeth 31 of the outer tooth plate 3 and the inner tooth plate 2 are assembled.
  • the gingivals 21 are engaged, and the shoulder 22 in the middle of the inner toothed plate 2 is inserted into the axial hole 32 in the middle of the outer toothed plate 3, and the shoulder 22 is eccentrically disposed with respect to the axial hole 32 and forms a radial eccentric region therebetween.
  • the eccentric wheel 4 as an eccentric structure is placed in the radial eccentric region, which constitutes a small tooth difference planetary gear transmission mechanism with the internal spurs 21 and the external spurs 31, and the transmission principle diagram of the transmission mechanism is as shown in Fig. 5.
  • the inner sprocket 21 is rotated by the eccentric wheel 4 and the external spur 31, so that the outer toothed plate 3 is rotated relative to the inner toothed plate 2, thereby achieving the purpose of adjusting the angle of the seat back.
  • the elastic deformation generated by the preloading of the wedge torsion spring 7 can act on the gap eliminating structure wedge block 6 and the eccentric wheel 4, and respectively rotate the two sides to the small diameter section of the eccentric region. Until the wedged state, the meshing clearance of the inner and outer tooth plates is eliminated.
  • the driving component comprises a driving cam and a hollow rotating shaft, wherein one end of the rotating shaft is fixedly connected with a middle portion of the driving cam, and the other end thereof sequentially penetrates the eccentric wheel and the shoulder and passes the shaft through a limiting connector
  • the rotating shaft is fixedly coupled to the outer end surface of the inner tooth plate, and the rotating shaft is coupled to the shoulder.
  • the driving component is provided with a resistive torque structure for transmitting torque, and the driving convex torque is transmitted to the eccentric wheel to drive the eccentric to rotate synchronously, thereby realizing torque transmission to the gear transmission mechanism.
  • the driving cam 5, the rotating shaft 52 and the two driving arms 51, 51' are formed.
  • the above three features are integrated.
  • the rotating shaft 52 of the driving cam 5 is sequentially passed through the inner hole of the torsion spring 7 and the center of the inner tooth plate 2. After the hole 23 and the sheath 1 are worn out, the elastic dam 10 is stuck on the rotating shaft 52. In the end of the card slot 53, the side surface of the dam is attached to the end surface 24 of the center hole 23 of the inner tooth plate 2, and the drive cam is prevented from falling off in the axial direction to form an integral body.
  • the driving cam 5 axially protrudes from the first driving arm 51 and the second driving arm 51'.
  • the eccentric 4 has a first receiving area 44 and a second receiving area 44', and the circumferential second receiving area 44' The upper portion overlaps the small end of the wedge block 6, as shown in the exploded view of Fig. 3; the first drive arm 51 is placed in the first receiving area 44 of the eccentric 4; the second drive arm 51' is placed in the small wedge 6 The second receiving area 44' of the end.
  • the driving component is provided with a resistance torque structure for transmitting torque
  • the resistance torque structure is a compression spring
  • one end of the spring acts on the eccentric wheel
  • the other end acts on the limit connecting piece disposed on the rotating shaft Actuating on the damper in the rotating shaft slot
  • the pre-tightening force generated by the spring acts on the joint surface of the eccentric and the driving cam
  • the driving transmits the driving torque to the
  • the eccentric wheel drives the eccentric to rotate synchronously, thereby achieving torque transmission to the gear transmission mechanism.
  • the resistance torque structure is disposed between the driving cam and the eccentric wheel, and includes a spring for applying a resistance torque between the eccentric wheel and the driving cam, the spring directly applying an axis on the eccentric wheel To the pressure, the transmission of the two moments is achieved by the frictional force of the eccentric wheel and the driving cam joint surface.
  • a frictional material for increasing the coefficient of friction of the eccentric and the drive cam is provided, and the friction material is fixed to the eccentric and/or the drive cam.
  • the embodiment is different from the first embodiment in that a driving plate is disposed between the eccentric and the driving cam, and is disposed between the eccentric and the driving cam.
  • a circular arc-shaped hole is formed on the shaft surface of the driving plate, and a driving arm disposed on the driving cam passes through the circular arc hole on the driving plate and is rotatably coupled to the eccentric wheel The resistance torque generated between the cams is transmitted to the drive plate.
  • the increase of the drive plate makes the eccentric The structure becomes a single.
  • the rotating shaft 52 of the driving cam 5 is sequentially inserted through the inner hole of the torsion spring 7 , the inner hole 84 of the driving plate 8 , the center hole 23 of the inner tooth plate 2 , and the sheath 1 , and the elastic dam 10 is locked in rotation.
  • the side of the dam is protruded from the end surface 24 of the center hole 23 of the inner tooth plate 2, and the driving cam is prevented from falling off axially to form an integral body;
  • the first driving arm 51 passes through the driving plate 8.
  • the arcuate hole 85 is inserted out and placed in the first receiving area 44 of the eccentric wheel 4;
  • the second driving arm 51' is passed through the arcuate hole 85' on the driving plate 8 and placed at the small end of the wedge block 6
  • the second receiving area 44 is,.
  • the drive cam is integrally formed with the drive plate by welding or riveting.
  • the driving cam and the driving plate adopt a split structure, and the two sides of the driving plate are respectively matched with the surface of the driving cam and the surface of the eccentric wheel, and the positioning holes and the molding holes thereon are formed
  • the convex engagement connection on the eccentric wheel realizes synchronous rotation of the two, and the driving plate has a certain degree of freedom in the axial direction of the rotating shaft to adapt to its axial error, as shown in FIG.
  • the drag torque structure includes a spring for increasing a resistive torque between the drive plate and the drive cam, the spring achieving transmission of torque by increasing a resistance torque of the drive plate and the drive cam joint surface.
  • a frictional material for increasing the friction coefficient of the driving plate and the driving cam is provided on the driving plate and/or the driving cam.
  • the spring is a compression spring, and a compression sleeve is disposed on a rotating shaft between the driving plate and the inner tooth plate, one end of which acts on an end surface of the driving plate, and the other end acts on an end of the rotating shaft
  • the spring is coupled to the shoulder of the inner tooth plate by a clearance fit.
  • the resistance torque structure comprises a spring 9 and a friction material disposed on the joint surface of the driving plate 8 and the driving cam, and cooperates with the driving cam 5 to work together.
  • Two protrusions 42 and 43 are disposed on the upper surface of the eccentric wheel 4, and the driving plate 8 is provided.
  • Two holes 82, 83 are arranged on the shaft, and the holes 42 and 43 of the eccentric wheel are slidably arranged, and the driving plate 8 is further provided with an arc groove 81, and the two axial legs 71 of the torsion spring 7 are wedged, ⁇ ' Inserted into the arcuate groove 81, the surface of the drive plate is attached to the upper surface of the eccentric, the drive plate and The eccentric is capable of synchronous circumferential rotation and a certain active clearance in the axial direction.
  • the spring 9 is preferably a compression spring of a rectangular cross section. After being pressed, the clearance fits over the rotating shaft 52 of the driving cam 5, and is placed in the center hole 23 of the inner tooth plate 2, the outer diameter and the inner tooth of the spring.
  • the central hole 23 of the plate 2 is gap-fitted; one end acts on the driving plate, specifically on the bottom surface 86 of the convex cover where the central hole 84 of the driving plate is located, and the convex hull where the central hole 84 is located is placed in the inner diameter of the torsion torsion spring 7, the spring
  • the other end is mounted on the dam 10 in the card slot 53 of the extended end of the rotating shaft 52, as shown in FIG.
  • the force provided by the spring 9 acts on the drive plate 8, and the force it provides is enclosed between the end of the rotating shaft 52 of the drive cam 5 and the drive plate 8, not transmitted to the gear train, and the spring 9 will always drive.
  • the surface of the plate 8 is axially fitted to the cam lower surface 54 of the drive cam 5, and is pressed as shown in Fig. 9 of the structural cylinder.
  • a constant resistance torque can be set between the drive plate 8 and the lower surface 54 of the drive cam 5 by adjusting the force of the spring 9.
  • the torque value generated by the frictional force and relative to the resistance torque at the center of the rotation shaft 52 of the driving cam 5 can be designed. According to the use requirements of the seat, the ratio between the resistance torque and the gear driving torque needs to be adjusted.
  • the pressure provided by the spring 9 acts on the drive plate 8 and the force it provides is enclosed between the drive cam 5 and the drive plate 8 and is not transmitted to the gear drive mechanism and therefore will not increase the gearing torque of the angle adjuster.
  • the driving plate 8 When the driving direction is from the direction of the gap eliminating structure wedge block 6, the driving plate 8 will first drive the eccentric wheel 4 under the action of the driving plate, and at the same time, the wedge block 6 is in a non-driving state, so the whole The operating torque required by the recliner will increase slightly.
  • the eccentric When the actual required operating torque of the recliner is always less than the value of the preset resistance torque, the eccentric will be directly driven to realize the rotation of the recliner.
  • the wedge shape 6 is in a passive drag state, and the driving arm 51' on the driving cam 5 cannot touch the small end of the wedge block 6, so that the collision noise will not occur or the operation of the idle stroke is delayed, and the backrest adjustment response delay occurs. .
  • the drive cam 5 When the required operating torque exceeds the drive plate, the drive cam 5 will rotate relative to the drive plate 8 until the drive arm 51' on the drive cam 5 hits the small end of the wedge block 6, in the process, The operating torque of the recliner will not continue to increase.
  • the driving arm 51' When the driving arm 51' is in contact with the small end of the wedge block 6, the wedge block 6 will be directly driven by the driving arm 51' on the driving cam 5, and then the big end of the wedge block
  • the eccentric wheel 4 is driven to rotate.
  • the backrest since the eccentric wheel 4 is in the process of slow movement, the backrest is always in the adjusted state, therefore, the response of the backrest will have no obvious stagnation time, and at this stage, the driving cam 5 and the driving are driven. There will be no relative movement in the circumferential direction between the plates 8, so the drive plate will disappear, so the operating torque required for the entire recliner will still be equal to the gear drive torque, which will remain in this state until the appropriate angle is adjusted.
  • the driving plate When the driving cam 5 is operated, when the driving direction is the side of the driving eccentric 4, the driving plate will directly drive the eccentric 4 with the clearance eliminating structure synchronized with the driving plate 8, instead of being driven by the driving arm 51 on the driving cam 5 After the idle travel provided for the wedge block 6 to eliminate the gap and then drive the drive plate 8 to rotate, there will be no backlash response delay, and the drive arm 51 on the drive cam 5 will not directly contact the first receiving area 44 of the eccentric 4 The end faces are in contact, so there is no collision sound, and the drive arm 51 only serves to protect against abnormal operation.
  • the eccentric wheel 4 synchronized with the driving plate 8 is also in a slow motion process, and the motor that drives the driving cam 5 to rotate is always in the same resistance and is equivalent to the rotation operation of the recliner.
  • the rotational speed of the driving cam 5 moving synchronously with the motor is always in a stable state, so that when the driving arm 51' on the driving cam comes into contact with the wedge-shaped block 6 of the gap eliminating structure, the relative moving speed of the two is lowered.
  • the noise generated by the collision is controlled at a low level.
  • a friction-increasing friction material 8' may be disposed between the upper surface of the driving plate 8 and the cam lower surface 54 of the driving cam 5, and may be fixed to the driving plate in the form of a whole surface or a plurality of blocks.
  • the friction material can likewise be attached to the cam surface 54 of the drive cam 5, or both.
  • the present embodiment is different from the second embodiment in that a movable synchronous pressure plate is disposed between the lower surface of the driving plate 8b and the upper surface of the eccentric wheel between the eccentric wheel and the driving cam. 8a, the synchronous pressure plate 8a and the driving plate 8b are also sleeved on the eccentric and the Driving on the axis of rotation between the cams;
  • the driving plate 8b is formed with a circular arc-shaped hole 8b3, 8b6 formed therein, and positioning holes 8a5', 8a5 are provided on the synchronous pressing plate 8a, and the two driving arms disposed on the driving cam 5 are respectively passed through
  • the large circular arc-shaped holes 8b3, 8b6 on the driving plate 8b continue to fit through the positioning holes 8a5', 8a5 on the synchronous pressing plate 8a, and reach the receiving area 44 of the eccentric wheel and the second receiving area 44 of the small end of the wedge block 6. ' Inside;
  • the driving cam 5 and the synchronous pressing plate 8a can rotate in the circumferential direction synchronously and the synchronous pressing plate can slide along the axial direction of the driving arm, under the action of the spring 9,
  • the synchronous platen 8a can be pressed against the surface 8b7 of the driving plate 8b;
  • the positioning holes 8b1, 8b4 of the driving plate 8b and the two protrusions 42, 43 of the upper surface of the eccentric wheel 4 are respectively assembled, so that the driving plate 8b and the eccentric wheel 4 can be synchronously rotated in the circumferential direction and can be slid in the axial direction, driving
  • the large circular arc-shaped holes 8b3, 8b6 of the arms on the driving plate 8b have sufficient circumferential movable space to accommodate the action of the wedge-shaped block 6 and the eccentric wheel 4 being wedged to the sides by the action of the wedge-twisting spring.
  • the two axial legs 71 of the wedge torsion spring 7 pass through the arcuate groove 8b2 of the driving plate 8b, pass through the arcuate groove 8a1 of the synchronous pressure plate 8a, respectively act on the eccentric wheel 4 and the wedge block 6, and wedge toward the sides Close the gap.
  • the rotating shaft 52 of the driving cam 5 is sequentially passed through the inner hole of the torsion spring 7 and the inner hole 8b5 of the driving plate 8b, the inner hole 8a4 of the synchronous pressing plate 8a, the center hole 23 of the inner tooth plate 2, and the sheath 1 are pierced.
  • the elastic dam 10 is fitted in the slot 5 3 of the extended end of the rotating shaft 52, and the side of the dam is attached to the end surface 24 of the center hole 23 of the inner tooth plate 2 to prevent the driving cam from falling off in the axial direction and forming an integral body.
  • the spring 9 is preferably a compression spring of a rectangular cross section in the present embodiment. After being pressed, the clearance fit fits over the rotating shaft 52 of the driving cam 5 and is placed in the center hole 23 of the inner tooth plate 2, The outer diameter of the spring is matched with the center hole 23 of the inner tooth plate 2; one end acts on the synchronous pressure plate 8a, specifically, the convex bottom surface 8a6 of the inner hole 8a4 of the synchronous pressure plate 8a.
  • the convex hull in which the inner hole 8a4 is located is placed in the inner diameter of the wedge torsion spring 7, and is placed in the inner hole 8b5 of the driving plate 8b, and the other end of the spring is placed on the card slot which is fitted at the protruding end of the rotating shaft 52. 5 3 set the dam, in order to effectively provide the limit and avoid the adverse effects of the circumferential movement of the spring 9, between the end of the spring 9 and the dam 10, a spacer, as shown in Figure 15.
  • the force provided by the spring 9 acts on the synchronous pressure plate 8a, and the synchronous pressure plate 8a, the drive plate
  • the cams of the drive cams 5 are pressed together, and two friction pairs are formed on both sides of the drive plate 8b.
  • the drive torque is applied to the drive cam 5, the cam lower surface 54 of the drive cam 5 and the side surface 8b8 of the drive plate 8b
  • the frictional resistance torque at the center of the opposite rotating shaft 52 formed by the frictional force will drive the driving plate 8b to rotate, and at the same time, between the upper surface 8a3 of the synchronous pressing plate 8a and the side surface 8b7 of the driving plate 8b which rotate in synchronization with the driving cam 5
  • the frictional force also forms a frictional resistance moment with respect to the center of the rotating shaft 52.
  • This torque also drives the driving plate 8b to rotate.
  • the driving plate 8b transmits the motion to the eccentric wheel 4 under the driving of the two frictional resistance moments to realize the angle adjustment. Angle adjustment of the device.
  • a friction material for increasing the coefficient of friction may be provided on the joint surface between the synchronous platen 8a and the drive plate 8b, the drive plate 8b and the cam of the drive cam 5, as needed, and the friction material is fixed to the synchronous platen 8a and/or Or the drive plate 8b and/or the cam, or the drive plate 8b, is fabricated directly from a friction material.
  • the driving cam 5 is operated.
  • the driving plate 8b will also first rotate the eccentric wheel 4 under the action of the two frictional resistance moments, and at the same time, the wedge shape Block 6 is in a non-driven state, so the operating torque required for the entire recliner will increase slightly.
  • the eccentric motion will be directly driven.
  • the recliner is rotated. In this state, the wedge shape 6 is in a passive drag state, and the drive arm 51' on the drive cam 5 cannot touch the small end of the wedge block 6, so that collision noise will not occur.
  • the drive cam 5 When the operating torque exceeds the value of the preset resistance torque due to the backrest load, the drive cam 5 will rotate at a significantly reduced speed relative to the drive plate 8b until the drive on the drive cam 5 The arm 5 1 ' touches the small end of the wedge block 6 , during which the operating torque input to the recliner will no longer continue to increase.
  • the driving arm 51 ′ When the driving arm 51 ′ is in contact with the small end of the wedge block 6 , The driving arm 51' on the driving cam 5 directly drives the wedge block 6, and then the big end of the wedge block drives the eccentric wheel 4 to rotate. In the process, the eccentric wheel 4 is in the process of slow movement, and the backrest is always in the adjusted state. Therefore, the response of the backrest will have no obvious stagnation time and collision sound.
  • the resisting torque directly drives the eccentric 4 having the clearance eliminating structure in synchronization with the driving plate 8b, instead of passing by the driving arm 51 on the driving cam 5
  • the idle stroke provided for the wedge block 6 to eliminate the gap re-drives the drive plate 8b, and there will be no delay in the backrest response, and the drive arm 51 on the drive cam 5 will not directly end with the end face of the first receiving region 44 of the eccentric 4
  • the drive arm 51 only acts as a protection in the case of abnormal operation.
  • the operating torque of the recliner of the present invention is compared with the angle adjuster without increasing the resistance torque driving system: the overall operating torque is not significantly changed, and the problem faced by the patent document CN1 149157C is successfully solved; The delay of the backrest adjustment response caused by the operation of the idle travel required to eliminate the mechanism and assembly manufacturing errors is also solved; the noise during the backrest adjustment commutation is controlled to a relatively low state.
  • the driving board structure is formed with an outwardly turned buckle edge at its periphery, and the driving cam The outer periphery is wrapped in the inner side of the buckle, and a circumferential annular gap is formed between the buckle edge and the outer periphery of the driving cam, and a resistance torque structure for increasing the resistance torque at the joint surface of the joint is provided in the circumferential annular gap, where the resistance torque is
  • the structure is an elastic element, and a specific frictional resistance torque can be set between the drive cam 5 and the drive plate 8 only by the pressure provided by the elastic element.
  • the resistance of the spring between the driving cam and the driving plate is brought to a desired value by using the action of the spring in the other embodiment. This makes the adjustment of the seat more stable and improves the comfort of the seat.

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  • Engineering & Computer Science (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
  • Seats For Vehicles (AREA)

Abstract

一种座椅调角器（100）及座椅，其包括带有内齿圈（21）的内齿板（2）、带有外齿圈（31）的外齿板（3）、楔形块（6）、偏心轮（4）及驱动部件，内齿板（2）和外齿板（3）齿轮啮合，内齿板（2）的中部成型一轴肩（22），偏心轮（4）套置于轴肩（22）的外圆周面上；驱动部件包括驱动凸轮（5）和转动轴（52），转动轴（52）的一端同驱动凸轮（5）的中部固定连接，另一端依次贯穿偏心轮（4）和轴肩（22）并通过限位连接件将其轴向固定于内齿板（2）的外侧端面上；驱动凸轮（5）与所述偏心轮（4）之间的相对面上设有用于传递力矩的阻力矩结构，作用于驱动凸轮（5）上的驱动扭矩通过阻力矩结构传递给偏心轮（4），带动偏心轮（4）同步旋转，进而实现对所述齿轮传动机构的力矩传递；本发明能够消除靠背换向过程中出现的靠背响应时间滞后、调角器换向出现噪音的问题。

Description

一种座 ^角器及其座椅 本申请要求于 2011 年 11 月 25 日提交中国专利局、 申请号为 201110381621.5、 发明名称为 "一种座椅调角器及其座椅" 的中国专利 申请的优先权， 其全部内容通过引用结合在本申请中。
本申请要求于 2011 年 11 月 29 日提交中国专利局、 申请号为 201110387739.9、 发明名称为 "一种座椅调角器及其座椅" 的中国专利 申请的优先权， 其全部内容通过引用结合在本申请中。 技术领域
本发明涉及一种座椅调节技术， 具体地说是一种座椅调角器和包括 该座椅调角器的座椅。 背景技术
座椅调角器用于连接汽车座椅的椅座和椅背，以增强座椅的舒适性。 乘客可以通过座椅调角器调节椅背的角度至最佳位置， 获得最舒适和最 习惯的乘坐角度。 对于驾驶员来说， 可以通过调节椅背的角度获得最好 的视野， 且易于操纵方向盘、 踏板和变速杆等操纵件。
目前， 对于电动座椅调角器一般采用行星齿轮传动原理， 由于零件 不可避免的制造误差， 因此， 在此类调角器的内部具有一定的间隙， 使 用时， 该间隙会造成座椅椅背相对于椅座前后方向的摆动较大且伴有噪 音， 进而影响座椅的舒适性， 因此在调角器的内部通常设置有间隙消除 机构。
中国专利文献 CN201468560U公开了一种座椅调角器及具有该调角 器的座椅： 包括具有内齿圏的内齿板、 具有外齿圏的外齿板、 偏心轮、 楔形块和驱动凸轮， 其中， 所述内齿板用于与椅背固定连接， 该内齿板 的中部设置有轴肩； 所述外齿板用于与椅座固定连接， 该外齿板的中部 设置有轴心孔； 所述外齿圏与内齿圏相啮合且所述轴肩与轴心孔之间形 成径向偏心区域； 所述偏心轮置于所述径向偏心区域内， 所述偏心轮、 内齿板和外齿板构成少齿差行星齿轮传动机构； 所述楔形块置于所述径 向偏心区域内； 且， 偏心轮和楔形块在弹性件施加的周向力作用下消除 所述偏心轮与内齿板的轴心孔之间的及啮合齿之间的间隙； 所述驱动凸 轮驱动偏心轮或者楔形块，以便于实现内齿板相对外齿板产生角度转动； 所述偏心轮呈整体偏心环状， 并填满内齿板的轴肩与外齿板的轴心孔之 间形成的正向偏心区域； 楔形块置于偏'、轮的 部。
在上述方案中， 为了适应楔块被弹性件在周向被楔紧以消除调角器 内部间隙的目的及装配制造误差， 楔形块必须有足够的周向安置空间， 以保证其能够始终处于楔紧的状态， 因此， 在驱动凸轮与楔形块之间必 须有一定的操作空行程， 如附图 1所示， 角度 a、 b所描述的空间， 调角 器调节过程中， 尤其是靠背换向调节过程中， 驱动凸轮由驱动偏心轮换 向驱动楔形块， 必须先经过所预留的操作空行程， 即角度 a、 b之和， 再 驱动楔形块转动， 实现靠背角度换向调节， 由于驱动凸轮必须经过一定 的操作空行程， 因此在座椅靠背换向调节过程中， 使用者能够感觉到靠 背调节动作存在比较明显的滞后， 存在一定的等待时间， 影响座椅的使 用舒适性。
另外， 在靠背换向过程中， 驱动凸轮在电机的驱动下， 驱动凸轮先 转动经过操作空行程再接触驱动楔形块 /偏心轮实现角度调节，在此过程 中由于电机没有负载， 驱动凸轮是以较高的速度撞击在静止的楔形块 / 偏心轮上， 因此， 在靠背换向的过程中会产生比较明显的噪音， 同样影 响座椅的舒适性。
针对以上两种失效模式，在中国专利文献 CN1149157C中公开了一种 用于靠背斜度可调式座椅且尤其是汽车座椅的调节组件， 此文献中提供 了一种新的用来提高座椅舒适度的解决方案， 利用同步环驱动两个在弹 性元件作用下向两侧楔紧以消除间隙的楔状物， 如附图 2所示， 此方案 虽然能够减小操作空行程， 弱化换向噪音， 经发明人反复试验发现其新 的技术问题： 由于在靠背调节过程中， 其中一个楔状物是在同步环的摩 擦力下驱动， 由于此楔状物不能及时、 有效地提供运动所需要的间隙， 调角器的操作扭矩必然增大、 扭矩值波动加剧， 将会增加电机的负担， 使电机出现工作时的噪音增大、 容易过载、 寿命减小等问题， 对调角器 自身将会加速零件的磨损， 调角器使用一段时间后， 靠背间隙增大趋势 明显， 影响靠背调节过程的稳定性及使用舒适性。 发明内容
为了有效消除调角器靠背间隙， 消除靠背换向过程中出现的靠背响 应时间滞后、 调角器换向出现噪音的问题， 同时能够有效的控制调角器 的操作扭矩， 使调角器的操作扭矩没有增加。
为了提高座椅在角度调节时的舒适度， 避免靠背换向过程中由于驱 动凸轮对静止的楔形块 /偏心轮的速度撞击而所产生的噪音，本发明实施 例提供了一种座椅调角器及其座椅。 所述技术方案如下：
一方面， 提供了一种座椅调角器， 其包括：
齿轮传动机构， 包括带有内齿圏的内齿板、 带有外齿圏的外齿板、 及带有楔形块的偏心轮， 所述内齿板的内齿圏同所述外齿板的外齿圏相 啮合， 所述内齿板的中部成型一空心的轴肩， 所述偏心轮可旋转地套置 于所述轴肩的外圓周面上；
驱动部件， 包括驱动凸轮和中空的转动轴， 所述转动轴的一端同所 述驱动凸轮的中部固定连接， 其另一端依次贯穿所述偏心轮和轴肩并通 过一限位连接件将其轴向固定于所述内齿板上， 所述转动轴同所述轴肩 间隙配合连接， 所述驱动凸轮与所述偏心轮之间的相对面上设有用于传 递力矩的阻力矩结构， 驱动所述驱动凸轮时， 作用于所述驱动凸轮上的 驱动扭矩通过所述阻力矩结构将其驱动扭矩传递给所述偏心轮， 带动所 述偏心轮同步旋转， 进而实现对所述齿轮传动机构的力矩传递。
所述阻力矩结构包括用于增加所述偏心轮与所述驱动凸轮之间摩擦 力矩的弹簧， 所述弹簧通过增加所述偏心轮同所述驱动凸轮结合面上的 摩擦力矩实现二者之间力矩的传递。 所述偏心轮与所述驱动凸轮之间还设有一驱动板， 其套置于所述偏 心轮与所述驱动凸轮之间的转动轴上， 所述驱动板的板面上成型有贯穿 的圓弧形孔， 设置于所述驱动凸轮上的驱动臂穿过所述驱动板上的圓弧 形孔同所述偏心轮可旋转地连接； 轮之间所产生的摩擦力矩传递给所述驱动板。
优选地， 所述驱动凸轮与所述驱动板采用分体结构， 所述弹簧所产 板的一侧面与所述驱动凸轮的表面紧贴合， 所述驱动板上设有同所述偏 心轮上的凸起相适配的定位孔， 所述驱动板上的定位孔与成型于所述偏 心轮上的凸起配合连接实现二者的同步转动， 所述驱动板在所述转动轴 的轴向上有一定间隙适应其轴向误差。
优选地， 所述弹簧为压缩弹簧， 其压缩套置于所述驱动板与所述内 齿板间的转动轴上， 其一端作用于所述驱动板的端面上， 另一端作用于 所述转动轴端部的限位连接件上， 所述弹簧同所述内齿板的轴肩间隙配 合连接；
所述弹簧所产生的预紧力使所述驱动板同所述驱动凸轮紧贴合， 通 过所述驱动板与驱动凸轮结合面形成的摩擦阻力矩驱动所述偏心轮转 动。
优选地， 所述驱动板同所述驱动凸轮之间的结合面上设置有用于增 加二者摩擦系数的摩擦材料，所述摩擦材料固定于所述驱动板和 /或驱动 凸轮上。
进一步优选地， 为了能提高所设定的阻力矩值， 所述驱动板与偏心 轮之间还设置一活动的同步压板， 所述同步压板套置于所述偏心轮与所 述驱动凸轮之间的转动轴上；
所述同步压板上成型定位孔和弧形槽， 所述同步压板上的定位孔同 所述驱动凸轮上的两驱动臂相适配， 所述同步压板同所述驱动凸轮配合 后可周向同步转动， 且所述同步压板可沿所述驱动臂轴向滑动， 所述偏 插接；
所述弹簧所产生的预紧力作用于所述驱动板与所述驱动凸轮、 同步 压板之间的结合面上， 使所述驱动板的两侧面分别同所述驱动凸轮和同 步压板紧贴合。
优选地， 所述弹簧为压缩弹簧， 其压缩套置于所述驱动板与所述内 齿板间的转动轴上， 其一端作用于所述同步压板的端面上， 另一端作用 于所述转动轴端部的限位连接件上， 所述弹簧同所述内齿板的轴肩间隙 配合连接；
在所述弹簧弹力的作用下 ，所述同步压板同所述驱动板的一端面紧 贴合， 所述驱动板的另一端面与所述驱动凸轮压紧， 通过所述驱动板与 所述驱动凸轮结合面所形成的摩擦阻力矩、 所述同步压板与所述驱动板 结合面形成的摩擦阻力矩一起对所述驱动板施加扭矩， 实现对所述偏心 轮的驱动。
优选地， 所述弹簧为矩形截面的压缩弹簧。
进一步优选地， 所述驱动板同所述驱动凸轮之间的结合面、 同步压 板与驱动板结合面上设置有用于增加摩擦系数的摩擦材料， 所述摩擦材 料固定于所述驱动板和 /或驱动凸轮和 /或同步压板上。
另一优选地， 所述驱动板的周边经折弯后成型一外翻的扣边， 所述 驱动凸轮的外周边被包覆于所述扣边内， 所述扣边与包覆于所述扣边内 的驱动凸轮的外周边之间形成一周向环隙， 所述周向环隙内设有用于增 加二者结合面处摩擦阻尼的弹性元件。
另一方面， 提供了一种座椅， 包括铰接的椅座和椅背以及置于椅座 与椅背之间的上述座椅调角器， 所述的外齿板和内齿板分别同椅座和椅 用于所述转动轴上提供。
本发明提供的最优选的座椅调角器中， 所述阻力矩结构包括用于增 加驱动板与驱动凸轮之间阻力矩的弹簧， 弹簧提供的压力作用在驱动板 上且其提供的力量被封闭在驱动凸轮与驱动板之间， 没有传递到齿轮传 动机构， 弹簧始终将驱动板与驱动凸轮轴向贴合， 压紧， 当驱动凸轮带 动驱动板周向转动时， 驱动板与驱动凸轮的摩擦力将阻止其运动， 通过 这种方式， 消除驱动凸轮与偏心轮的周向转动空行程； 通过调整弹簧的 力量可以实现在偏心轮和驱动凸轮之间设置恒定的阻力矩。
通过理论分析及实际测量可以确定中国专利文献 CN201468560U 中 所述的调角器的操作扭矩， 在此为方便称之为齿轮驱动扭矩， 对调角器 所施加的操作扭矩必须大于或等于齿轮驱动扭矩， 才能驱动少齿差行星 齿轮传动机构转动， 实现靠背角度调节。
弹簧套在驱动凸轮转动轴上且设置在内齿板轴肩的中心孔内， 在挡 圏的限制作用下， 弹簧具体形式为矩形截面的压缩弹簧， 其一端始终对 与偏心轮同步的驱动板施加压力， 驱动板与驱动凸轮之间压力产生的摩 擦力将阻止驱动板与驱动凸轮相对转动， 通过调整弹簧的力量可以设计 由摩擦力产生、 相对驱动凸轮转动中心的阻力矩的力矩值， 由于弹簧提 供的压力作用在驱动板上且其提供的力量被封闭在驱动凸轮与驱动板之 间，没有传递到齿轮传动机构， 因此将不会增加调角器的齿轮传动扭矩。 根据座椅的使用要求， 需要调整阻力矩同齿轮驱动扭矩之间的比值。
当驱动方向是驱动偏心轮侧时， 就可以直接利用阻力矩直接驱动与 驱动板同步、 带有间隙消除结构的偏心轮转动， 而不是由驱动凸轮上的 驱动臂先经过为楔形块消除间隙所设置的空行程再驱动偏心轮转动， 完 成了动作传递路径的更改， 从而消除驱动凸轮与偏心轮的空行程造成的 靠背调节响应滞后现象， 消除驱动凸轮上的驱动臂直接撞击在偏心轮上 而产生的噪音。
当驱动方向是从间隙消除结构楔形块侧时， 在阻力矩作用下， 驱动 板将先带动偏心轮转动， 于此同时， 楔形块处于无驱动状态， 因此整个 调角器所需的操作扭矩将增加， 当调角器实际所需的操作扭矩始终小于 预先设定的阻力矩时， 将直接驱动偏心轮运动， 实现调角器转动， 此状 态下， 楔形快 6处于被动的拖动状态， 驱动凸轮 5上的驱动臂 51 ' 无法 碰上楔形块 6的小端， 故碰撞噪声将不会产生。
当所需的操作扭矩超过阻力矩时， 驱动凸轮将相对驱动板转动直至 驱动凸轮上的驱动臂碰上触上楔形块的小端， 在此过程中， 调角器的操 作扭矩将不再继续增加， 当驱动臂与楔形块接触后， 将由驱动凸轮上的 驱动臂直接驱动楔形块的小端， 再由楔形块的大端驱动偏心轮转动， 此 过程中， 由于偏心轮都是在緩慢运动过程中，靠背始终处于调节的状态， 因此， 靠背的响应将没有明显的停滞时间， 到此阶段， 驱动凸轮与驱动 板之间将没有相对运动， 因此， 驱动板将消失， 故整个调角器所需的操 作力矩将仍等于齿轮驱动扭矩， 随后阶段将保持此状态， 直到调节到合 适的角度。
由于可控的阻力矩的存在， 带动驱动凸轮转动的电机都始终处于基 本相同的负载工况下， 可以理解， 与电机同步运动的驱动凸轮的转速始 终处于平稳状态， 不会出现专利文献 CN201468560U 所述技术方案的情 况： 驱动凸轮先经历一个空行程再驱动间隙消除结构楔形块或偏心轮的 过程， 电机的负载由很小到大， 转动速度由高到由于负载增加而被动快 速降低的过程。
由于可控的阻力矩的存在， 驱动凸轮上的驱动臂将不直接与偏心轮 接触； 由于可控的阻力矩的存在， 驱动臂向楔形块方向转动时， 与驱动 板同步的偏心轮都处于緩慢运动过程中； 由于可控的阻力矩的存在， 带 动驱动凸轮转动的电机都因始终处于基本相同且与调角器转动操作相当 的负载工况下， 电机同步运动的驱动凸轮的转速始终处于平稳状态，故， 当驱动凸轮上的驱动臂与间隙消除结构楔形块接触时， 二者的相对运动 速度被降到一个很低的水平， 故二者碰撞产生的噪音将被控制在一个很 低的水平。
因此， 本发明所述的调角器的操作扭矩与没有增加阻力矩驱动系统 的调角器相比： 整体的操作扭矩没有明显的变化， 成功解决专利文献 CN1149157C技术方案所面临的问题； 为适应间隙消除机构及装配制造误 差所必须的操作空行程带来的靠背调节响应的延迟现象亦被解决； 靠背 调节换向过程中的噪音被控制在一个相当低的状态。
本发明提供的座椅调角器适合批量生产， 具有制造工艺性好， 制造 成本较低的特点。 适用于各种需要调节椅背角度的座椅， 特别适用于汽 车座椅。 附图说明
为了更清楚地说明本发明实施例中的技术方案， 下面将对实施例描 述中所需要使用的附图作筒单地介绍， 显而易见地， 下面描述中的附图 仅仅是本发明的一些实施例， 对于本领域普通技术人员来讲， 在不付出 创造性劳动的前提下， 还可以根据这些附图获得其他的附图。
图 1是中国专利文献 CN201468560U所述技术方案的剖视图； 图 2是中国专利文献 CN1149157C中技术方案的楔块、同步环结构的 装配示意图；
图 3是本发明的实施例 1所提供的座椅调角器的装配爆炸图； 图 4是本发明的实施例 2所提供的座椅调角器的装配爆炸图； 图 5是本发明对图 4采用另一角度提供的座椅调角器装配爆炸图； 图 6 是少齿差、 单级行星齿轮传动原理图；
图 7是本发明中的阻力矩结构、 偏心轮、 楔形块、 楔紧扭簧和齿轮 传动系统之间的装配爆炸图；
图 8 是本发明的座椅调角器剖视图；
图 9是本发明中阻力矩结构与驱动凸轮之间的装配结构示意图； 图 10a 是本发明所述的驱动板上表明设置摩擦材料的示意图； 图 10b 是本发明所述的驱动板上表明设置摩擦材料的另一种结构 示意图；
图 11是本发明的实施例 3所提供的座椅调角器的装配爆炸图； 图 12是本发明对图 11采用另一角度提供的座椅调角器装配爆炸图； 图 1 3是本发明中的阻力矩结构、驱动板、 凸轮、楔紧扭簧和齿轮传 动系统之间的装配爆炸图； 图 14是本发明中图 11所提供的座椅调角器装配示意图；
图 15是本发明中图 11提供的座椅调角器中阻力矩结构、 驱动板、 凸轮、 楔紧扭簧、 挡圏等的装配示意图；
图 16是本发明另一种设置阻力矩扭矩的结构方案示意图； 图 17是本发明所述的座椅的外形图。
图中：
座椅调角器 1 00、 护套 1、 内齿板 2、 内齿圏 21、 轴肩 22、 中心孔 23、 外齿板 3、 外齿圏 31、 轴心孔 32、 偏心轮 4、 凹部 41、 凸起 42、 凸 起 43、 第一容纳区域 44、 第二容纳区域 44'、 驱动凸轮 5、 第一驱动臂 51、 第二驱动臂 51 '、 转动轴 52、 卡槽 53、 下表面 54、 楔形块 6、 楔紧 扭簧 7、 轴向支脚 71、 轴向支脚 71 ' 、 驱动板 8、 摩擦材料 8 ' 、 弧形 槽 81、 定位孔 82、 定位孔 83、 内孔 84、 圓弧形孔 85、 圓弧形孔 85' 、 底面 86、 扣边 87、 同步压板 8a、 弧形槽 8al、 弧形槽 8a2、 上表面 8a 3、 内孔 8a4、 定位孔 8a5、 定位孔 5'、 凸包底面 8a6、 驱动板 8b、 定位 孔 8bl、 弧形槽 8b2、 圓弧形孔 8b 3、 定位孔 8b4、 内孔 8b5、 圓弧形孔 8b6、 侧面 8b7、 侧面 8b8、 弹簧 9、 弹性元件 9' 、 挡圏 10 、 周向环 隙 11。
具体实施方式
为使本发明的目的、 技术方案和优点更加清楚， 下面将结合附图对 本发明实施方式作进一步地详细描述。
本文中所述内侧、 外侧等方位词， 是以座椅调角器的轴心线为基准 定义的， 也就是说， 接近该轴心线侧为内侧， 远离该轴心线侧为外侧， 应当理解， 前述方位词的使用不应当局限本专利申请要求保护的范围。
此外，本文中正向偏心方向指偏心区域内径向空间尺寸最大的方向， 在正向偏心方向上的区域称为正向偏心区域。
实施例 1 参见图 3为一种座椅调角器的装配爆炸图。 本发明提供的座椅调角 器主要包括齿轮传动机构、 驱动部件和阻力矩结构。
齿轮传动机构
其采用少齿差、单级行星齿轮传动。 其中， 具有内齿圏 21的内齿板 2用于与椅背固定连接，具有外齿圏 31的外齿板 3用于与椅座固定连接。 外齿板 3和内齿板均置于护套 1中， 护套 1的收口与外齿板 3固联在一 起， 组装后， 外齿板 3的外齿圏 31与内齿板 2的内齿圏 21啮合， 内齿 板 2中部的轴肩 22插装在外齿板 3中部的轴心孔 32中，轴肩 22相对于 轴心孔 32偏心设置且两者之间构成径向偏心区域。作为偏心结构的偏心 轮 4置于该径向偏心区域内， 其与内齿圏 21和外齿圏 31构成少齿差行 星齿轮传动机构， 该传动机构的传动原理图如图 5所示。 当操作扭矩作 用于驱动凸轮 5时， 通过偏心轮 4、 外齿圏 31带动内齿圏 21转动， 从 而使得外齿板 3相对于内齿板 2转动， 实现调节椅背角度的目的。
在楔紧扭簧 7的作用下， 楔紧扭簧 7的预压产生的弹性变形能作用 在间隙消除结构楔形块 6和偏心轮 4上， 使二者分别向偏心区域的小径 段周向转动直至楔紧状态， 消除内、 外齿板的啮合间隙。
驱动部件， 包括驱动凸轮和中空的转动轴， 所述转动轴的一端同所 述驱动凸轮的中部固定连接， 其另一端依次贯穿所述偏心轮和轴肩并通 过一限位连接件将其轴向固定于所述内齿板的外侧端面上， 所述转动轴 同所述轴肩间隙配合连接。
所述驱动部件上设有用于传递力矩的阻力矩结构， 驱动所述驱动凸 扭矩传递给所述偏心轮， 带动所述偏心轮同步旋转， 进而实现对所述齿 轮传动机构的力矩传递。
具体的结构如下所述：
包括驱动凸轮 5、 转动轴 52及 2个驱动臂 51、 51' , 以上三个特征 构成一个整体， 驱动凸轮 5的转动轴 52依次经楔紧扭簧 7的内孔、 内 齿板 2的中心孔 23、 护套 1穿出后， 弹性挡圏 10卡装在转动轴 52伸出 端的卡槽 53内，挡圏的侧面贴在内齿板 2的中心孔 23的端面 24上， 防 止驱动凸轮轴向脱落， 形成整体。 驱动凸轮 5轴向伸出有第一驱动臂 51 和第二驱动臂 51' , 偏心轮 4上具有第一容纳区域 44和第二容纳区域 44' , 且沿周向第二容纳区域 44' 的上部与楔形块 6的小端部重叠， 如 图 3爆炸图所示； 第一驱动臂 51置于偏心轮 4的第一容纳区域 44内； 第二驱动臂 51' 置于楔形块 6的小端的第二容纳区域 44' 。
所述驱动部件上设有用于传递力矩的阻力矩结构， 此阻力矩结构为 一压缩弹簧， 弹簧的一端作用于偏心轮上， 其另一端作用于设置于所述 转动轴上的限位连接件上， 即作用于转动轴卡槽内的挡圏上， 所述弹簧 所产生的预紧力作用于所述偏心轮与所述驱动凸轮的结合面上， 驱动所 将其驱动扭矩传递给所述偏心轮， 带动所述偏心轮同步旋转， 进而实现 对所述齿轮传动机构的力矩传递。
阻力矩结构
所述阻力矩结构设置于所述驱动凸轮与所述偏心轮之间， 其包括用 于施加所述偏心轮与所述驱动凸轮之间阻力矩的弹簧， 弹簧直接在所述 偏心轮上施加轴向压力， 利用偏心轮同所述驱动凸轮结合面上的摩擦力 实现二者力矩的传递。
优选地， 所述偏心轮同所述驱动凸轮之间的结合面上设有用于增加 二者摩擦系数的摩擦材料，所述摩擦材料固定于所述偏心轮和 /或驱动凸 轮上。
实施例 2
如图 4和图 5所示， 本实施例与实施例 1不同的是， 在偏心轮与驱 动凸轮之间设有一驱动板， 其套置于所述偏心轮与所述驱动凸轮之间的 转动轴上， 所述驱动板的板面上成型有贯穿的圓弧形孔， 设置于所述驱 动凸轮上的驱动臂穿过所述驱动板上的圓弧形孔同所述偏心轮可旋转地 凸轮之间所产生的阻力矩传递给所述驱动板。 驱动板的增加使偏心轮的 结构变的筒单。
驱动凸轮 5的转动轴 52依次经楔紧扭簧 7的内孔、驱动板 8的内孔 84、 内齿板 2的中心孔 23、 护套 1穿出后， 弹性挡圏 10卡装在转动轴 52伸出端的卡槽 53内，挡圏的侧面贴在内齿板 2的中心孔 23的端面 24 上， 防止驱动凸轮轴向脱落， 形成整体； 第一驱动臂 51经驱动板 8上的 圓弧形孔 85穿出后置于偏心轮 4的第一容纳区域 44内；第二驱动臂 51 ' 经驱动板 8上的圓弧形孔 85 ' 穿出后置于楔形块 6的小端的第二容纳区 域 44,。
驱动凸轮与所述驱动板通过焊接或铆接一体成型。
优选地， 所述驱动凸轮与所述驱动板采用分体结构， 所述驱动板的 两侧面分别同所述驱动凸轮的表面和偏心轮的表面相贴合， 其上的定位 孔与成型于所述偏心轮上的凸起配合连接实现二者的同步转动， 所述驱 动板在所述转动轴的轴向上有一定自由度以适应其轴向误差， 如图 8所 示。
阻力矩结构包括用于增加所述驱动板与所述驱动凸轮之间阻力矩的 弹簧， 所述弹簧通过增加所述驱动板同所述驱动凸轮结合面上的阻力矩 实现二者力矩的传递。
优选地， 驱动板同所述驱动凸轮之间的结合面上设置有用于增加二 者摩擦系数的摩擦材料，所述摩擦材料固定于所述驱动板和 /或驱动凸轮 上。
所述弹簧为压缩弹簧， 其压缩套置于所述驱动板与所述内齿板间的 转动轴上， 其一端作用于所述驱动板的端面上， 另一端作用于所述转动 轴端部的限位连接件上， 所述弹簧同所述内齿板的轴肩间隙配合连接。
阻力矩结构包括弹簧 9和设置于驱动板 8与驱动凸轮的结合面上的 摩擦材料， 配合驱动凸轮 5共同起作用， 在偏心轮 4的上表面设置两个 凸起 42、 43 , 驱动板 8上设置两孔 82、 83 , 与偏心轮上的凸起 42、 43 孔轴滑配，驱动板 8上还设有弧形槽 81 ,楔紧扭簧 7的两个轴向支脚 71、 Ί ' 插入弧形槽 81内， 驱动板的表面贴在偏心轮的上表面上， 驱动板与 偏心轮能够同步周向转动且在轴向有一定的活动间隙。
弹簧 9在本方案优选为矩形截面的压缩弹簧， 其受压后， 间隙配合 套在驱动凸轮 5的转动轴 52上， 置于内齿板 2的中心孔 23中， 弹簧的 外径与内齿板 2的中心孔 23间隙配合；一端作用在驱动板上，具体在驱 动板中心孔 84所在的凸包底面 86上，中心孔 84所在的凸包置于楔紧扭 簧 7的内径内， 弹簧的另一端顶在卡装在转动轴 52伸出端的卡槽 5 3内 的挡圏 10上， 如图 7所示。
弹簧 9提供的力量作用在驱动板 8上， 且其提供的力量被封闭在驱 动凸轮 5的转动轴 52的端部与驱动板 8之间，没有传递到齿轮传动机构 中，弹簧 9始终将驱动板 8的表面与驱动凸轮 5的凸轮下表面 54轴向贴 合， 压紧， 如结构筒图图 9所示。
当驱动凸轮 5相对驱动板 8周向转动时， 驱动板 8与驱动凸轮 5的 凸轮下表面 54之间的摩擦力将阻止其运动。通过调整弹簧 9的力量可以 在驱动板 8和驱动凸轮 5的下表面 54之间设置恒定的阻力矩。
通过调整弹簧 9的力量可以设计由摩擦力产生、 相对驱动凸轮 5转 动轴 52中心的阻力矩的力矩值，根据座椅的使用要求，需要调整阻力矩 与齿轮驱动扭矩之间的比值。 弹簧 9提供的压力作用在驱动板 8上且其 提供的力量被封闭在驱动凸轮 5与驱动板 8之间， 没有传递到齿轮传动 机构， 因此将不会增加调角器的齿轮传动扭矩。
操作驱动凸轮 5 , 当驱动方向是从间隙消除结构楔形块 6方向时， 在驱动板作用下， 驱动板 8将先带动偏心轮 4转动， 于此同时， 楔形块 6 处于无驱动状态， 因此整个调角器所需的操作扭矩将略为增加， 当调 角器实际所需的操作扭矩始终小于预先设定的阻力矩的值时， 将直接驱 动偏心轮运动， 实现调角器转动， 此状态下， 楔形快 6处于被动的拖动 状态， 驱动凸轮 5上的驱动臂 51 ' 无法碰上楔形块 6的小端， 故碰撞噪 声将不会产生亦没有操作空行程而产生靠背调节响应延迟的现象。
当所需的操作扭矩超过驱动板时， 驱动凸轮 5将相对驱动板 8转动 直至驱动凸轮 5上的驱动臂 51 '碰上触上楔形块 6的小端，在此过程中， 调角器的操作扭矩将不再继续增加， 当驱动臂 51 ' 与楔形块 6小端部接 触后， 将由驱动凸轮 5上的驱动臂 51 ' 直接驱动楔形块 6 , 再由楔形块 的大端驱动偏心轮 4转动， 此过程中， 由于偏心轮 4都是在緩慢运动过 程中， 靠背始终处于调节的状态， 因此， 靠背的响应将没有明显的停滞 时间， 到此阶段， 驱动凸轮 5与驱动板 8之间周向将没有相对运动， 因 此， 驱动板将消失， 故整个调角器所需的操作力矩将仍等于齿轮驱动扭 矩， 随后阶段将保持此状态， 直到调节到合适的角度。
操作驱动凸轮 5 , 当驱动方向是驱动偏心轮 4侧时， 驱动板将直接 驱动与驱动板 8同步、 带有间隙消除结构的偏心轮 4转动， 而不是由驱 动凸轮 5上的驱动臂 51先经过为楔形块 6消除间隙所设置的空行程再驱 动驱动板 8转动， 将不存在靠背响应延迟的现象， 驱动凸轮 5上的驱动 臂 51将不直接与偏心轮 4的第一容纳区域 44的端面接触， 故没有碰撞 声音 ， 驱动臂 51只是在非正常操作的情况下起保护作用。
驱动臂 51 ' 向楔形块 6方向转动时， 与驱动板 8同步的偏心轮 4也 处于緩慢运动过程中， 带动驱动凸轮 5转动的电机因始终处于基本相同 且与调角器转动操作相当的阻力矩值的负载下， 与电机同步运动的驱动 凸轮 5的转速始终处于平稳状态， 故， 当驱动凸轮上的驱动臂 51 ' 与间 隙消除结构楔形块 6接触时， 二者的相对运动速度被降到一个很低的水 平， 将二者碰撞产生的噪音控制在一个 ί艮低的水平。
为了设置合适的阻力矩驱动力矩， 可以在驱动板 8的上表面和驱动 凸轮 5的凸轮下表面 54之间设置增加摩擦的摩擦材料 8' , 具体可以整 面或数块的形式固定在驱动板 8的表面上， 如附图 10a和图 10b所示， 应当理解，摩擦材料同样可以固定在驱动凸轮 5凸轮表面 54上，或同时 在以上两个零件上设置。
实施例 3
如图 11和图 12所示， 本实施例与实施例 2不同的是， 在偏心轮与 驱动凸轮之间，在驱动板 8b的下表面与偏心轮的上表面之间设置一活动 的同步压板 8a， 同步压板 8a及驱动板 8b同样套置于所述偏心轮与所述 驱动凸轮之间的转动轴上；
所述驱动板 8b的板面上成型有贯穿的圓弧形孔 8b3、 8b6 , 在同步压 板 8a上设置定位孔 8a5' 、 8a5 , 设置于所述驱动凸轮 5上的两驱动臂在 分别穿过驱动板 8b上的大圓弧形孔 8b3、8b6后继续从同步压板 8a上的 定位孔 8a5 '、 8a5间隙配合穿过， 到达偏心轮的容纳区域 44及楔形块 6 的小端的第二容纳区域 44' 内；
通过同步压板 8a上的定位孔 8a5' 、 8a5与两驱动臂的配合，驱动凸 轮 5与同步压板 8a能够周向同步转动且同步压板能够沿着驱动臂轴向滑 动， 在弹簧 9的作用下 ， 同步压板 8a能够压在驱动板 8b的表面 8b7 上；
所述驱动板 8b的定位孔 8bl、 8b4与偏心轮 4的上表面的两个凸起 42、 43分别装配， 使驱动板 8b与偏心轮 4能够同步周向转动且在轴向 能够滑动， 驱动臂在驱动板 8b上的大圓弧形孔 8b3、 8b6具有足够的周 向活动空间， 以适应楔形块 6与偏心轮 4在楔紧扭簧的作用向两侧楔紧 的动作需求。
在同步压板 8a上同样设置大的弧形槽 8a l、 8a2 , 分别让驱动板 8b 上定位孔 8bl、 8b4所在的凸台穿过。
楔紧扭簧 7的两个轴向支脚 71、 穿过驱动板 8b的弧形槽 8b2 , 穿过同步压板 8a的弧形槽 8al , 分别作用偏心轮 4和楔形块 6上， 向两 侧楔紧消除间隙。
驱动凸轮 5的转动轴 52依次经楔紧扭簧 7的内孔、驱动板 8b的内孔 8b5， 同步压板 8a的内孔 8a4、 内齿板 2的中心孔 23、 护套 1穿出后， 弹性挡圏 10卡装在转动轴 52伸出端的卡槽 5 3内，挡圏的侧面贴在内齿 板 2的中心孔 23的端面 24上， 防止驱动凸轮轴向脱落， 形成整体。
同实施例 2—样， 弹簧 9在本方案优选为矩形截面的压缩弹簧， 其 受压后， 间隙配合套在驱动凸轮 5的转动轴 52上，置于内齿板 2的中心 孔 23中， 弹簧的外径与内齿板 2的中心孔 23间隙配合； 一端作用在同 步压板 8a上，具体为设置在同步压板 8a的内孔 8a4所在的凸包底面 8a6 上， 内孔 8a4所在的凸包置于楔紧扭簧 7的内径内，置于驱动板 8 b的内 孔 8 b5中， 弹簧的另一端顶在卡装在转动轴 52伸出端的卡槽 5 3所设置 的挡圏上， 为了有效提供限位及避免弹簧 9周向运动带来的不利影响， 在弹簧 9的端部与挡圏 1 0之间， 设置一垫片， 如图 15。
弹簧 9提供的力量作用在同步压板 8 a上， 将同步压板 8a、 驱动板
8b、驱动凸轮 5的凸轮压在一起，在驱动板 8b的两侧面组成两个摩擦副， 当对驱动凸轮 5施加驱动扭矩时，驱动凸轮 5的凸轮下表面 54与驱动板 8 b的侧面 8b8之间的摩擦力形成的相对转动轴 52中心的摩擦阻力矩将 带动驱动板 8b转动，同时，与驱动凸轮 5同步转动的同步压板 8a上表面 8 a 3与驱动板 8b的侧面 8b7之间的摩擦力同样会形成相对转动轴 52中 心的摩擦阻力矩， 此力矩同样会带动驱动板 8b转动， 驱动板 8b在这两 个摩擦阻力矩的驱动下， 将运动传递给偏心轮 4 , 实现调角器的角度调 节。
因此， 在同一个弹簧 9的轴向作用力下， 将产生相对实施例 2两倍 的摩擦阻力矩效果， 驱动效果将更有利。
根据需要， 同步压板 8a与驱动板 8b、 驱动板 8b与驱动凸轮 5的凸 轮之间的结合面上可设置有用于增加摩擦系数的摩擦材料， 所述摩擦材 料固定于所述同步压板 8a和 /或驱动板 8b和 /或凸轮上， 或驱动板 8b 直接就使用摩擦材料制造。
与实施例 2相同， 操作驱动凸轮 5 , 当驱动方向是从间隙消除结构 楔形块 6方向时，在两摩擦阻力矩作用下，驱动板 8b同样将先带动偏心 轮 4转动， 于此同时， 楔形块 6处于无驱动状态， 因此整个调角器所需 的操作扭矩将略为增加， 当调角器实际所需的操作扭矩始终小于预先设 定的阻力矩的值时， 将直接驱动偏心轮运动， 实现调角器转动， 此状态 下， 楔形快 6处于被动的拖动状态， 驱动凸轮 5上的驱动臂 51 ' 无法碰 上楔形块 6的小端， 故碰撞噪声将不会产生。
当操作扭矩因靠背载荷的原因超过预先设定的阻力矩的值时， 驱动 凸轮 5将相对驱动板 8b以明显降低的速度转动直至驱动凸轮 5上的驱动 臂 5 1 ' 碰上触上楔形块 6的小端， 在此过程中， 输入到调角器的操作扭 矩将不再继续增加， 当驱动臂 51 ' 与楔形块 6小端部接触后， 将由驱动 凸轮 5上的驱动臂 51 ' 直接驱动楔形块 6 , 再由楔形块的大端驱动偏心 轮 4转动， 此过程中， 偏心轮 4都是在緩慢运动过程中， 靠背始终处于 调节的状态， 因此， 靠背的响应将没有明显的停滞时间及碰撞声音， 到 此阶段， 驱动凸轮 5与驱动板 8b之间周向将没有相对运动， 因此，摩擦 力所提供的阻力矩将基本不起作用， 故调角器所需的操作力矩将仍等于 齿轮驱动扭矩， 随后阶段将保持此状态， 直到调节到合适的角度。
操作驱动凸轮 5 , 当驱动方向是驱动偏心轮 4侧时， 阻力矩直接驱 动与驱动板 8b同步、带有间隙消除结构的偏心轮 4转动， 而不是由驱动 凸轮 5上的驱动臂 51先经过为楔形块 6消除间隙所设置的空行程再带动 驱动板 8b转动，将不存在靠背响应延迟的现象，驱动凸轮 5上的驱动臂 51将不直接与偏心轮 4的第一容纳区域 44的端面接触， 故没有碰撞声 音 ， 驱动臂 51只是在非正常操作的情况下起保护作用。
本发明所述的调角器的操作扭矩与没有增加阻力矩驱动系统的调角 器相比： 整体的操作扭矩没有明显的变化， 成功解决专利文献 CN1 149157C技术方案所面临的问题； 为适应间隙消除机构及装配制造误 差所必须的操作空行程带来的靠背调节响应的延迟现象亦被解决； 靠背 调节换向过程中的噪音被控制在一个相当低的状态。
实施例 4
同实施例 2、 3的区别在于阻力矩结构的设置形式和驱动板的结构不 同，如图 1 6所示，本实施例中驱动板结构是在其周边形成一外翻的扣边， 驱动凸轮的外周边被包裹在扣边内部， 扣边与驱动凸轮的外周边之间形 成一周向环隙， 在周向环隙内设有用于增加二者结合面处阻力矩的阻力 矩结构， 这里的阻力矩结构为弹性元件， 仅仅利用弹性元件提供的压力 同样可以在驱动凸轮 5及驱动板 8之间设置特定的摩擦阻力矩。
另外， 在上述周向环隙内设置弹性元件的同时， 再利用其它实施例 中的弹簧的作用， 使驱动凸轮和驱动板之间的阻力矩达到所需的数值， 从而使座椅的调节更加稳定， 提高了座椅的舒适度。
以上所述仅是本发明的优选实施方式， 应当指出， 对于本技术领域 的普通技术人员来说， 在不脱离发明原理的前提下， 还可以做出若干改 进和润饰， 实现发明目的。 本发明的保护范围以后附的权利要求为准。

Claims

权 利 要 求
1、 一种座椅调角器， 其包括：
齿轮传动机构， 包括带有内齿圏的内齿板、 带有外齿圏的外齿板、 及带有楔形块的偏心轮， 所述内齿板的内齿圏同所述外齿板的外齿圏相 啮合， 所述内齿板的中部成型一空心的轴肩， 所述偏心轮可旋转地套置 于所述轴肩的外圓周面上；
驱动部件， 包括驱动凸轮和中空的转动轴， 所述转动轴的一端同所 述驱动凸轮的中部固定连接， 其另一端依次贯穿所述偏心轮和轴肩并通 过一限位连接件将其轴向固定于所述内齿板上， 所述转动轴同所述轴肩 间隙配合连接， 其特征在于，
所述驱动凸轮与所述偏心轮之间的相对面上设有用于传递力矩的阻 力矩结构， 驱动所述驱动凸轮时， 作用于所述驱动凸轮上的驱动扭矩通 过所述阻力矩结构将其驱动扭矩传递给所述偏心轮， 带动所述偏心轮同 步旋转， 进而实现对所述齿轮传动机构的力矩传递。
2、 根据权利要求 1所述的座椅调角器， 其特征在于，
所述阻力矩结构包括用于增加所述偏心轮与所述驱动凸轮之间摩擦 力矩的弹簧， 所述弹簧通过增加所述偏心轮同所述驱动凸轮结合面上的 摩擦力矩实现二者之间力矩的传递。
3、 根据权利要求 2所述的座椅调角器， 其特征在于，
所述偏心轮与所述驱动凸轮之间还设有一驱动板， 其套置于所述偏 心轮与所述驱动凸轮之间的转动轴上， 所述驱动板的板面上成型有贯穿 的圓弧形孔， 设置于所述驱动凸轮上的驱动臂穿过所述驱动板上的圓弧 形孔同所述偏心轮可旋转地连接； 轮之间所产生的摩擦力矩传递给所述驱动板。
4、 根据权利要求 3所述的座椅调角器， 其特征在于, 所述驱动凸轮与所述驱动板采用分体结构， 所述弹簧所产生的预紧 面与所述驱动凸轮的表面紧贴合；
所述驱动板上设有同所述偏心轮上的凸起相适配的定位孔， 所述驱 动板上的定位孔与成型于所述偏心轮上的凸起配合连接实现二者的同步 转动， 所述驱动板在所述转动轴的轴向上有一定间隙适应其轴向误差。
5、 根据权利要求 4所述的座椅调角器， 其特征在于，
所述弹簧为压缩弹簧， 其压缩套置于所述驱动板与所述内齿板间的 转动轴上， 其一端作用于所述驱动板的端面上， 另一端作用于所述转动 轴端部的限位连接件上， 所述弹簧同所述内齿板的轴肩间隙配合连接； 所述弹簧所产生的预紧力使所述驱动板同所述驱动凸轮紧贴合， 通 过所述驱动板与驱动凸轮结合面形成的摩擦阻力矩驱动所述偏心轮转 动。
6、 根据权利要求 3或 4或 5所述的座椅调角器， 其特征在于， 所述驱动板同所述驱动凸轮之间的结合面上设置有用于增加二者摩 擦系数的摩擦材料， 所述摩擦材料固定于所述驱动板和 /或驱动凸轮上。
7、 根据权利要求 4所述的座椅调角器， 其特征在于，
所述驱动板与偏心轮之间还设置一活动的同步压板， 所述同步压板 套置于所述偏心轮与所述驱动凸轮之间的转动轴上；
所述同步压板上成型定位孔和弧形槽， 所述同步压板上的定位孔同 所述驱动凸轮上的两驱动臂相适配， 所述同步压板同所述驱动凸轮配合 后可周向同步转动， 且所述同步压板可沿所述驱动臂轴向滑动， 所述偏 插接；
所述弹簧所产生的预紧力作用于所述驱动板与所述驱动凸轮、 同步 压板之间的结合面上， 使所述驱动板的两侧面分别同所述驱动凸轮和同 步压板紧贴合。
8、 根据权利要求 7所述的座椅调角器， 其特征在于，
所述弹簧为压缩弹簧， 其压缩套置于所述驱动板与所述内齿板间的 转动轴上， 其一端作用于所述同步压板的端面上， 另一端作用于所述转 动轴端部的限位连接件上，所述弹簧同所述内齿板的轴肩间隙配合连接； 在所述弹簧弹力作用下 ，所述同步压板同所述驱动板的一端面紧贴 合， 所述驱动板的另一端面与所述驱动凸轮压紧， 通过所述驱动板与所 述驱动凸轮结合面所形成的摩擦阻力矩、 所述同步压板与所述驱动板结 合面形成的摩擦阻力矩一起对所述驱动板施加扭矩， 实现对所述偏心轮 的驱动。
9、 根据权利要求 5或 8所述的座椅调角器， 其特征在于
所述弹簧为矩形截面的压缩弹簧。
10、 根据权利要求 7或 8所述的座椅调角器， 其特征在于， 所述驱动板同所述驱动凸轮之间的结合面、 同步压板与驱动板结合 面上设置有用于增加摩擦系数的摩擦材料， 所述摩擦材料固定于所述驱 动板和 /或驱动凸轮和 /或同步压板上。
11、 根据权利要求 4-10任一所述的座椅调角器， 其特征在于， 所述驱动板的周边经折弯后成型一外翻的扣边， 所述驱动凸轮的外 周边被包覆于所述扣边内， 所述扣边与包覆于所述扣边内的驱动凸轮的 外周边之间形成一周向环隙， 所述周向环隙内设有用于增加二者结合面 处摩擦阻尼的弹性元件。
12、 一种座椅， 包括铰接的椅座和椅背以及置于椅座与椅背之间的 座椅调角器，其特征在于，所述座椅调角器采用如权利要求 1至 11中任 一项所述的调角器， 所述的外齿板和内齿板分别同椅座和椅背中的其一
动轴上提供。
PCT/CN2012/084932 2011-11-25 2012-11-21 一种座椅调角器及其座椅 WO2013075619A1 (zh)

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