JPH072127B2 - Continuously adjustable hinge - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION This application is a US patent application filed April 2, 1984.
No. 595591 "Continuously Variabl
e Adjustable Hinge) ".

BACKGROUND OF THE INVENTION In the field of automatic seat recliners, a continuously variable adjustment is achieved by a "taumel" type geared by the rotation of a cam by a handle knob, when manually operated. The handknob produces one tooth for relative forward movement between the outside and inside of the Tomel mechanism for each rotation of the handknob. The self-locking friction of the elements results in a fully locked state for any position of continuous adjustment; however, the overall adjustment between end positions does not result in ratchet and pawl type recliner hinges. In comparison, the ratchet and claw pipe hinges are those commonly used in the United States, such as those disclosed in U.S. Pat. In order to adjust the quick positioning,
A handle actuated cam disengages the pawl from engagement with the toothed sector such that disengagement of the handle lever allows cam locking of the pawl in tooth engagement with the sector. In such hinges, the adjustment position is incrementally limited to a single tooth difference in relative sector and pawl position.

In addition to sufficiently urgent manufacturing requirements, various approaches have been attempted to meet the need for better adjustment than is possible in the general sector and nail tooth pitch. And in U.S. Pat. Nos. 4,223,946 and 4,355,846, an additional "translation" linkage mechanism amplifies the angular motion of the toothed sector in relation to the angular motion of the seat back, and the pawl and sector. Cooperating to correspondingly reduce the angular displacement of the seat back for the adjustment of one tooth in its engagement. In other cases, U.S. Pat.
As shown in No. 2, the exceptionally small tooth pitch is adjusted by using a specific gripping action in the cam actuation mechanism to better ensure that the teeth do not engage due to the bias of the interengaging components. To prevent.

Although some improvements in goodness of adjustment have been achieved with such devices, the concept of true continuous variable adjustment combined with the immediate and global adjustment to the desired seat back position was formerly known. Was not fully achieved.
Various attempts at frictional fixation cannot withstand the life test under applied load, the safety criterion (load) being a range of the seat hinge design's range of locational and cost constraints included in the parameters. Is required within.

SUMMARY OF THE INVENTION A complete solution to the long-standing quest for immediate overall and continuous targeted adjustment is finally achieved,
In it, the fixing strength of the conventional toothed sector and of the pivoted pawl that self-fixes the cam actuation holds for a continuous adjustment, which is a distinction of the normal toothed sector. Provided by allowing the pawl to move within the pitch of a single tooth in a fully engaged position for precise adjustment, followed by actuation of two cams at the angularly related surfaces of the pawl. To lock the pawl in such an adjusted holding position and to adjust the operating position of one tooth of the pawl to reach its initial fully engaged position. It involves providing a variable transition of. A self-locking angle that is not greater than 6 ° and is effective over the entire range of cam transitions.
With e), the pawl engages the sector with an initial sufficient tooth engagement (t
The shape of the pawl and cam is used with sufficient length of the cam surface to accommodate preliminary variation of a single tooth of the pawl in achieving ooth engagement.

In addition to two pivoted cam elements that are actuated simultaneously to a retracted position by a single handle, a link for positively disengaging the pawl teeth from the sector is provided for preliminary tooth engagement. Is adapted to be held in a centered relative position and the preliminary tooth engagement is completed by spring bias before cam engagement of the pawl occurs. The extension arm of each cam is biased by the connecting tension spring towards the engagement of the pawls allowed by the release of the hand lever. Each cam engagement may occur sequentially or simultaneously depending on the particular initial engagement position of the pawl. In either case, full installation of the two cams in a fixed condition with all gaps closed is accomplished without displacing the pawl from its initial fully engaged position.

The triangular relationship of the two camshafts with the engagement of the pawl teeth and the effective angle of cam surface engagement is self-sustaining from any compression pressure generated from the tooth pressure in either direction. Allows you to set a fixed angle. Thus, while providing the strength and retention characteristics of the cammed toothed pawl and sector structures are well retained, providing a single tooth pawl variation and then two cams Fastening achieves a fully continuous variable adjustment combined with immediate global positioning of the seat back, which has long been a fantastic goal of recliner hinge designers. It was

The varying pawls in any relative angular adjustment relationship of the seat bracket and back rest bracket fixed against angular displacement by the action of the two cams are sufficient to engage the teeth of the sector. And each cam has a variable self-fixing angular displacement, the displacement being sufficient to adjust at least the entire range of change of a single tooth in the adjustment, thereby providing a continuously variable bracket adjustment. Multiple modifications can be made using the principle that However, Applicants have discovered through experimental testing a particularly preferred embodiment, which has shown better durability under harsh life testing without any adverse effects. A detailed description of such preferred embodiments is a continuation-in-part dis
1) is added to the embodiment of the parent application of FIGS. 1 and 2.

In a preferred embodiment developed since the parent application was filed, the low tooth profile results in a reduced tooth angle and corresponding separation force between the nail and the sector, eg It is used to allow reducing the stresses that occur with the radial component of tooth pressure. The rotation of the two cams is reversed, so that the force profile on the pawl caused by the load on the seat back biases the loaded cams towards a higher position and thereby creeps from cyclical loads. A stronger resistance to The pawl acts as a tooth slide without a shaft and is simplified to act to remove the shaft arm. A new system of disengagement and pawl control adjusts the flattened end of the shallow angle low tooth and the reaction end of the torque spring to bias each cam towards the engaged position towards the sector. Used to bias the pawl and move it into full tooth engagement prior to installing the cam to lock the pawl in place. The shape of the cam to resist the loading of the pawl teeth is centered on the resultant force of the seat load torque on the sector and the couple of teeth trying to remove the pawl on the axis of the loaded cam shaft. It is ideal for optimizing things and providing a grooved cam profile to minimize bias over the entire range of cam and pawl engagement.

Description of the First Preferred Embodiment With reference to FIG. 1, said hinge bracket 10 and lower hinge bracket 11 are pivotally connected at 12, said hinge brackets being respectively on the seat back or seat of a motor vehicle. Can be connected. The circular arcsector 13 of the upper bracket 10 is provided with teeth 14,
The teeth 14 are engaged by mating teeth 15 on a pawl 16 which is attached to the bracket 11 via an elongated slot 18.
Loosely attached by upper pin 17 and thus the slot
18 provides sufficient movement of the pawl teeth 15 so that the pawl teeth 15 are fully engaged with adjacent teeth of sector 13 in any relative angular position of brackets 10 and 11.
n) can be carried out, in which case the pawl 16 is approximately centered with respect to the mounting pin 17 and the slot 18 upon initial engagement of the pawl tooth 15 with the sector tooth 14.

Cams 19 and 20, which are pivotally mounted on bracket 11 by pins 21 and 22, respectively, are provided with eccentric cam surfaces 23 and 24, which cam surfaces have angularly corresponding flats on pawl 16. Engageable with 25 and 26. Cam surface 23
And 24 have a sufficient actuation arc, for example 45 ° actuable, and due to the relative position of the bracket 10, any fully engaged position of the pawl within the pitch of one tooth provided by the elongated slot 18. even There will be set, for example, 5 _^1/2 °
The locking angles bring the cam surfaces 23 and 24 into engagement with the pawl flats 25 and 26.

The relative angular relationship of the cam surfaces 23 and 24 as they reach the position where they engage the flats 25 and 26 is within the range of a single tooth pitch provided by the elongated slot 18 and the pawl 16. It will be appreciated that the displacement of the pawl 16 on either side of its central position (FIG. 1) will vary.

Prior to engaging each cam and pawl, the pawl 16
At any intermediate position possible in achieving sufficient engagement with 13, the pawl is displaced in either direction under pressure of the teeth of the interengaging sectors by virtue of the locking angle provided by the engagement of the cam. Effectively holds the pawl 16 in place, and thus effectively locks the bracket 10 against the bracket 11 in any continuous adjustment position.

Effective continuous variable adjustment requires either cam surface 23 or
Tooth of nail 16 prior to engagement of 24 with its associated nail surface
Not only is it necessary that the teeth 15 of the sector and the teeth 14 of the sector be in full engagement, but also that the teeth of the pawl 16 are oriented approximately in the center described above when engaging the teeth of the sector 13. It will be understood that Proper centering of the pawls for proper sequence of positioning the pawls prior to cam engagement and engagement of the teeth at the beginning of the pawls is provided by a link 27 actuated by a pin 28 which is Extension of release handle 30 pivotally mounted to bracket 11 at
It projects from 29. Upon actuation of the handle 30 in the clockwise direction, through the engagement of the surface 31 of the extension 29 with the pins 32 and 33 projecting from the cams 19 and 20, such a handle is provided with an arm extension of the cams 19 and 20. It operates so as to release the cam engagement with the pawl 16 against the engagement bias (force) of the tension spring 34 connecting the 35 and 36. Slot from the side of nail 16
The linear displacement of the link 27 by the handle 30 which brings the pin 38 projecting into the 37 to the limit position of the slot 37 achieves a positive disengagement of the pawl and sector against the bias of the tension spring 39. , The tension spring 39 is attached to the bracket 11
It is fixed to a shaft projection 40 on the back side of the and the other end of the spring is connected to an extension of a pin 38 of a pawl 16 projecting through a triangular slot 41 in the bracket 11. The disengagement by the end of the slot 37 and the pin 38 occurs after the opening operation of the cam surfaces 25 and 26 at the engagement limit position of one of the cam surfaces 25 and 26, and the pin The engagement of 38 with the arcuate end 42 of the matching slot 41 centers the pawl with respect to slot 18. The two extreme positions of camming are indicated by arcs in the range of 15 ° and 30 respectively on either side of the neutral line 43 corresponding to the center position of the pawl as shown for the cam arm 19.

Counter-clockwise handle 30 return tra
vel), under the tension of spring 39 on pin 38, the same linkage moves to the center position prior to returning cam surfaces 23 and 24 for engagement with pawl flats 25 and 26. Engage the resulting pawl 16 with the tooth 15 of the sector 13. This is done without any movement of the pawl from the previous full tooth engagement, no matter what the exact continuous adjustment position of the seat bracket 10 at the time of initial pawl engagement. That is, the pawl 16 is placed at the center position or the neutral position by the link 27 cooperating with the tension spring 39, and the handle shown in FIG.
Link 27 is a pin protruding from the pawl 16 when 30 is raised.
Operates against 38 and spring 39. Nail 16 is a sector
As soon as it is released from 13 teeth 14, pin 38 is in the center position,
That is, it is located on the line between the pivot pin 12 and the pin 28. Nail 16
Can then be moved within the range of movement provided by the slot 18, i.e. within the range of 3 degrees providing sector adjustment of tooth spacing of 21/2 degrees, thus engaging the pawls 14 of the teeth of the sector 13.
16 moves to a position where it fully engages the teeth of the sector and locks the upper hinge bracket or seatback bracket 10 no matter what position it is in.

A suitable tooth profile is illustrated in FIG. 1 and the tooth profile is conventional broaching operation (br) on both the pawl and sector.
oaching operation) and a tooth profile sharply pointed manufactured with 2 _^1/2 ° pitch by, for any position of the sector with respect to its possible the relative nail and sector tooth tip engaging (point Engagement) It ensures that the pawls are in full engagement with the teeth.

The selective manufacturing method of "fine blanking" requires a small point radius in the fine blanking die, so that the sectors and the teeth of the nail are Not suitable for such sharp teeth. Such a radius increases the likelihood of relative tip engagement of the pawl and sector teeth, such as interfering with full tooth engagement.

Referring to FIG. 2, ensure that the pawl is laterally secured from the position of relative point inter-engagement so that the need for a sharp tooth tip morphology is less critical. For movement, optional modifications can be integrated and make good stamping by the selective manufacturing method with hinge attachment of the present invention. A small pin 50 protruding from the surface of the pawl is in the path of the end tip 51 of the arm extension 52 for lateral movement of the pawl when the mutual engagement of the tips interferes with sufficient engagement. The extension reaches a relatively close position at the instant of initial tip engagement of the pawl and sector teeth during the return travel of the pawl and actuation handle.

If the pawl teeth are sufficiently recessed on either side of the sector teeth to create sufficient engagement, the arm extension 51 will not engage the pin during cam return to the seated position.
50 will pass below; however, extension end 51 will engage pin 50 if the engagement of the in-line tooth tips prevents sufficient pawl engagement. 50 is a cam
Move laterally to the left to the extent that sufficient tooth engagement is achieved prior to installing the 19 and 20 retention engagements.

Since the pawl and handle extension always reach the same relationship upon initial tooth engagement, the pin 50 is always in an effective position relative to the point 51 to perform its function if necessary. .

Supplementary Description of the Preferred Embodiment Referring to FIG. 4, the adjustable positioning element of the test unit comprises two lower bracket plates 56 sandwiched (one removed for clarity). ) Quadrant with a toothed sector 54 centered on an axis 55 extending between
53, a toothed slide pawl 57, and two cams 58, each locked at 59 between lower brackets 56. In FIG. 4, the cam 58 and the claw 57
Is illustrated in solid line in the center position, and claw 57
Is illustrated in dashed lines when it is moved to its one end position; while in FIG. 5 the pawl 57 and cam 58 show the central position in solid lines while the pawl moved to the other end position is shown in broken lines. Is indicated by. Entire range of operation of the pawl 57 is on the order of 3 °, perform infinite adjustment of quadrant 53 with a spacing of teeth of the ₂ ^1/2 °. The claw 57 is provided with an arc, and the arc has a curvature (cu
rvature) and the contact area occurs over a very limited band throughout the entire range of regulation.

The approximately 120 ° slope of the illustrated cam is based on an effective coefficient of friction not less than 0.07, and of substantially constant locking angle with respect to the line extending from the camshaft to the point of contact with the pawl. Use a spline curve (sp
line curve) is shown. The cam rise is arranged to provide the smallest dimension with respect to the axial center at the lower end and the largest dimension at the upper end,
As a result, the propensity of the pawl 57 to be lifted out of engagement with the teeth of the sector as in the case of the opposite cam gradient used in the embodiment of FIGS. 1 and 2 is higher than the lower engagement point. It will be noted that trying to rotate either cam until. It has been found in experimental tests that the cam slopes of FIGS. 4 and 5 are most effective in countering the tendency of cam surface creep during repeated high load cycling of the seat back.

As will be explained below with reference to FIG. 10, the relatively convex curvature of the cams and pawls in the contact area minimizes the deviation of the force vector from its optimum shape.

The test components illustrated in Figures 4-9 were developed to meet the requirements for an endless seat back adjuster.
As a specific example of a component that has undergone repeated torque loading tests, the components of FIGS. 6-9 are dimensioned in millimeters, which sets the critical geometrical relationship well. Optional bracket 56 is constructed from AISI 1018 steel and is 4.
5 Yes in millimeters; heat treatment KN086240 the decorated with thickness 4 ¹ / _2mm SAE1020 steel quadrant, and Rockwell (Rockwell) C38-48 of the quenched and tempered a thickness 4 mm thick up It consists of an AISI 4130 steel pawl; and a 4 mm thick AISI 4130 steel cam that is quenched and tempered to Rockwell C38-45.

Referring to FIG. 10, a diagram of the force (ge
The geometry of rorce) can be understood by the following analysis.
A suitable number of claw teeth, together with a suitable number for claw stability, is determined in relation to the shear stress associated with the maximum torque load, in this case at 14 ° 45 'the pressure angle (pressu
It is determined as much as possible like a re-angle) and ₂ ^1/2 ° 10 Quai teeth of the pawl of which is formed with such low teeth shown (stub tooth) with a spacing of. The center point of the tooth load 60 is determined by the tangential torque load at the tooth load center point and the
A combined line 63 passing near the center of curvature 64 for the arc of the pawl at the point of contact was set, along with the sum of the force vectors 61 and 62, respectively, with the radial component associated with the pressure angle of 45 °.

The optimum center of cam curvature is located near the extension of 63 (Fig. 10) to accommodate any torque applied on the cam, and occurs for the sum of individual tooth loads. An additional 2 ° angle 65 is provided to counteract the tendency of the prone claws to separate, and the 2 ° angle passes through the cam curvature center located at 66. And a line passing through the center of curvature of the nail. In addition to such bias, any tendency to lift the pawls tends to rotate the cam to a higher raised position, which causes the teeth of the sector to come out of good contact with the pawls. It further resists any displacement of the nail.

Based on the nail and convex curvature of the cam in contact points, 2 _^1/2 displacement of a single tooth ° claw ranging from installation position for donating an infinite adjustment, (FIG. 10) 2 A very narrow contact zone, such as between the two points 67, is created on the pawl, which will minimize any deviation from the camshaft geometry over the entire range of adjustment.

Tests have shown that with the dimensions and geometries mentioned above, there is no tendency for pawl displacement or cam creep under repeated maximum torque loading, even when the unloaded cam is released from contact. .

Referring to the assembly of FIG. 3, the modified pawl 57a and cam 58a are designed to accommodate shorter arc trajectories and kicker mechanisms for cam transition and cam release. The pawl 57a and the cam 58a are shown in the central position. Two
Two cam actuation links 67 and kicker actuation links
68 is driven by a pin 69 at the tip of each elongated opening, which pin is located at the end of a manual release lever 70, which is pivotally supported at 71 and manually moved to a dotted position 72. It is possible. Those are cams
58a is released in succession and then kicker 73 is actuated, which kicker 73 is pivotally supported at 59 and engages pawl pin 74 to disengage pawl 57a from the engagement of the teeth with a semi-pierced protrusion (semi-pitch). -Pierce projection) 75 to move the claw 57a to the left within the limit of the concave portion 76 installed facing the semi-pierce projection 75.

The downward actuation of the link 68 engaged with the kicker pin 77 overcomes the torque spring 78, which biases the biasing pin 79 of the link 67 in the direction in which the cam engages,
And, in a reactive manner, it biases the kicker 73 counterclockwise; similarly, it overcomes the torque spring 80, which biases the cam pin 81 in the cam engaging direction and the pawl pin 74.
Is urged in the direction in which the teeth engage. Accordingly, moving the hand lever arm 70 from its released position 72 will cause the pawl pin 74 to be raised into engagement with the teeth of the sector by the engaging ends of the torque spring 80, and the pawl and When each flat tooth end of the sector abuts, the curved surface 82 of the kicker 73 will move the pawl 57a to the right until sufficient tooth engagement occurs, and as a result, the pawl 57a.
Will be fully engaged in the adjusted position before both cams 58a return to their respective engaged positions.

The cam 58 in FIGS. 4, 5 and 9 is illustrated with a 120 ° arc of a cam curve based on a friction coefficient of 0.07 for normal lubricating grease, but with the trademark “Suntrack”.
A special high traction lobrican, such as is manufactured by Monsanto Chemical Company under Santotrac.
t) provides a higher and more efficient coefficient of friction on the order of 0.12, which reduces the cam arc to about 70 ° for producing curves similar to those illustrated in FIGS. 4 and 5. Tolerate. Such a shorter arc is used in the release mechanism of FIG. 3 to move the pin 79 of the link 67 between the travel limit trajectories of the cams shown at 84, and the link pin 81. It is used to move between trajectories 85 that indicate the limit of movement. Further positioning of the pin 67 at the end 86 of the limit track in order to carry out further transitions of the link 67, for example the activation of the kicker 73 by means of the link 68, will result from the bottom position 87 of the slot position 88 at the limit of the release transition 72. Actuating pin 69
It is possible by moving.

Without blocking the engagement of both ends of the claws and teeth of the sector,
Curved surface 83 extends a sufficient distance to allow the first tooth penetration to be completed; however, if such blocking of engagement occurs, the curved surface may be reached before a sufficient engagement relationship is achieved.
The rightward movement of the claw 57a caused by 83 occurs. It is above the bracket plate 56a slots 82 limits the overall movement of the pawl 57a to approximately 3 ° by limiting the lateral movement of the pawl pin 74, the about 3 movement to ° interval 2 _^1/2 tooth It fits well with °.

From the foregoing description of various embodiments, the present invention provides for the continuous variable adjustment of the axially toothed sector.
It will be appreciated that it includes a variety of special devices that effect a positive locking of the geared pawl. Such a structure is especially suitable for seat recline hinges.
seat back for quick release and precise desired position and secure fixation, while being adaptable for r hinge) applications, with the proven strength advantages of toothed claw and sector systems. Adjustments are made, but without the conventional drawbacks of limited and increasing regulators.

[Brief description of drawings]

1 is a side view of a hinge assembly illustrating one preferred embodiment of the present invention; FIG. 2 is a cutaway view of a variation of the hinge mount of FIG. 1; FIG. FIG. 4 is a side view of a seat hinge assembly illustrating a preferred embodiment of the present invention; FIG. 4 is the shape of the sector, pawl and locking cam over the range of displacement of the pawl from the neutral position to one end. Figure 5 is a side view of the test unit; Figure 5 is a view similar to Figure 4 illustrating the displacement of the pawl to the other end in the neutral position; Figure 6 is a toothed sector. Fig. 7 is a detailed view of a cordant according to Fig. 7; Fig. 7 is a detailed view of a lower bracket plate; Fig. 8 is a detailed view of a tooth slide in the form of a nail; Fig. 9 is used in a test unit. Detailed view of the cam; Figure 10 shows the test unit Is an enlarged explanatory view illustrating the state of the power sector and cam toothed (vector). 10 ... Upper hinge bracket, 11 ... Lower hinge bracket, 13, 54 ... Sector, 14, 15 ... Tooth, 16, 57, 57a ...
Claws, 18, 37, 41 ... Slots, 19, 20, 58, 58a ... Cams, 2
7, 67, 68 ... Link, 30 ... Handle, 34, 39, 78, 80 ...
Spring, 43 ... Neutral line, 53 ... Codrant, 56,
56a ... Bracket plate, 64 ... Center of curvature, 70 ... Lever, 73 ... Kicker, 75 ... Semi-pace protrusion, 82,83 ... Curved part surface, 17, 21, 22, 28, 32, 33, 38, 50, 74, 81 …pin

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Karl Rigeense Michigan, USA 49015, Buttle Creek, East Minges Road 559 (56) References JP 57-55108 (JP, A) Actual Kai 56-22050 (JP, U) Actual public 52-16491 (JP, Y2)

Claims (39)

[Claims] 1. A seat and seat back bracket (10,11) axially connected, a toothed sector (13) on one of said brackets, and adjusted for the other of said brackets. A toothed pawl (16) holding the toothed sector (13) in relation, and a device for releasably positioning the pawl in fixed and adjusted engagement with the sector (27). And a device (17,18) for mounting the pawl (16) such that the pawl (16) is free to move and lock with respect to the sector by at least one tooth tip. , Displaces the pawl from its position of initial engagement with the two sectors (25, 26) on the pawl and the sector at any non-adjustable relative angle of the bracket. Before to resist doing Separately and pivotally on the other bracket with two individually positionable cam surfaces (23,24) which can be individually engaged with two angularly related surfaces (25,26). In any unlimited adjustable relative position of the mounted pair of cams (19,20) and the bracket, sequentially move the pawl into initial engagement with the sector and then A device for moving the cam to a state of retaining the engagement with the claw (3
9) Adjustable seat back hinge, including and. 2. A hinge according to claim 1, comprising low tooth contours for the sectors and the teeth of the pawl. 3. A hinge according to claim 2 wherein the tooth profile provides a pressure angle on the order of 14 3/4 °. 4. The hinge of claim 3 including teeth spaced about 2 1/2 ° apart. 5. A line in which the contact between the cam and the claw corresponds to the resultant force of the tangential tooth load and the radial load with the tooth pressure angle at the effective center of the accumulated claw tooth load. A hinge as claimed in claim 4 occurring above. 6. A hinge according to claim 5, wherein a convex curvature is provided at the contact surfaces of both the pawl and the cam. 7. A convex cam contact area in the resultant line of force on the pawl caused by a tangential torque load,
7. A hinge as claimed in claim 6, comprising a pawl configured as a single tooth slide with a tooth pressure angle for angular hinge displacement loading in either direction. 8. A pawl control element axially mounted on one pivot of the cam, a pawl control pin protruding from a surface of the pawl, and moving the pawl into an engaged state and an unengaged state. A pin contact surface on the pawl control element, a direction of pawl engagement of the pawl control element with the sector and an elastic device for biasing the individual cams into pawl position engagement, and subsequent to uncoupling the cams. ,
A hinge as claimed in claim 7 and including a manual release device for actuating the control element in a pawl release direction. 9. A resilient device for resetting the manual release device to allow reengagement of the cam and the angularly associated surface subsequent to and from the pawl and the sector. 7. A hinge according to item 8 of the above. 10. The hinge of claim 9 including a common torque spring biasing one of the cams and the control element toward the pawl engagement. 11. A hinge as claimed in claim 10 including the other common torque spring biasing each of the other cam and the pawl in the direction of engagement. 12. A device corresponding to pawl release movement for laterally moving the pawl to one end for reengaging a sector, and a tooth upon initial abutment engagement of the lower tooth end of each pawl and sector. 12. The hinge of claim 11 including a flexure device on the pawl control element for laterally moving the pawl in the other direction to the mating reengagement position. 13. A three-link, one end of each of which is connected to the cam and the pawl control element and the other end of which is connected to a manually actuating element of the manual release device, wherein the link connection is for releasing the pawl and the cam. 12. The hinge of claim 11 including a blunt motion to provide the sequential motion of reengagement. 14. The hinge according to claim 7, wherein the cams are arranged so that the surface of each cam rises with respect to the contact point of the cam surface movement and the claw moving away from the sector. 15. An assembly of pivotally connected elements characterized by a continuously variable adjuster locking the relative angular relationship of the pivotally connected elements, said elements (10,11). ) A toothed device (13) on one (10) and an interengageable toothed device (16) corresponding to said device (13) on the other (11) of said elements; Each of the toothed devices (1
3,16) including a mounting device (17,18) for one of the toothed devices (16) that allows full disengagement of the (10,11) elements. A device (17,8) for allowing full engagement of the well-matched teeth of the respective toothed device (13) for any continuously variable adjustable angular relationship of And for locking the respective toothed device for any relative displacement of the elements (10, 11) in the relative angular relationship, the respective toothed device ( 13,1
6) A set including a cam device (19, 20) engageable with one (16) of the toothed devices (13, 16) after setting a sufficient matching engagement. Three-dimensional. 16. The assembly of claim 15 wherein said pivotally connected elements include hinge bracket members. 17. A device for providing relative lateral tooth displacement when pre-engagement of the tips of each tooth prevents full tooth engagement.
The assembly according to paragraph. 18. Teeth in each angular direction, comprising two individually positionable cam surfaces of said cam device which are individually engageable with one angularly related surface of said toothed device. 16. An assembly according to claim 15, which opposes relative displacement of the element from pressure. 19. The claim of claim 19 wherein each of said two cam surfaces comprises a reactive mount on one of said elements that regulates independent engagement of said angularly related surfaces.
Assembly according to paragraph 18. 20. Each of the two cam surfaces comprises a pivotal mount and frictionally fixing a cam surface engagement angle associated with the pivotal mount through the range of cam engagement. 20. An assembly as claimed in claim 19 comprising. 21. The assembly of claim 18, wherein the angularly related surface comprises an outer surface of a toothed pawl. 22. The assembly of claim 18 wherein the two cam surfaces include the surfaces of each of the individual cam elements pivotally mounted on spaced apart shafts. . 23. The invention of claim 15 wherein said mounting device for adjusting sufficient mating tooth engagement comprises sufficient out-of-motion connection to adjust displacement of a single tooth pitch. Assembly as described in. 24. A toothed device according to claim 23, wherein one of said toothed devices includes a toothed pawl with a sliding attachment.
The assembly according to paragraph. 25. An assembly according to claim 20, comprising a device for centering the pawl in relation to movement from the start of tooth engagement. 26. A device for moving and centering from the mounting comprises a pawl pin projecting into the mounting opening,
26. The assembly according to claim 25, wherein an elastic device within the opening actuates the pin to bias the pawl toward a central engagement position. 27. The assembly of claim 15 wherein said pivotally connected elements include hinged bracket members adapted for use as adjustable seat back hinges. 28. A manually actuated handle device adapted to actuate the cam device to a disengaged position for effective adjustment, and a resilient force to retain the cam device in an engaged position upon manual disengagement of the handle. The assembly of claim 27, comprising a device. 29. An assembly according to claim 28, comprising two individually pivoted cam devices responsive to a single handle actuation. 30. Two cam devices that are individually pivotally supported, and a pawl device that can be engaged by the two cam devices, wherein the elastic device for holding the cam device in the engaged position is the 29. A device according to claim 28, including individual pivotal mounts for each of the two cam devices, with individual torque springs biasing each of the two cam devices in an engaged position. Assembly. 31. The assembly of claim 15 wherein one of said elements comprises a toothed sector having an arcuate center coincident with said pivotal connection. 32. The toothed sector is convex.
32. The assembly of claim 31, wherein the other of the toothed devices includes a claw having a concave arc with matching teeth. 33. One of the toothed devices includes a pawl that has a restricted out-of-motion connection with the other of the elements, the pawl being engageable with the toothed sector, the pawl comprising: 32. An assembly according to claim 31, fixed in a regulated position by the cam device. 34. Handle disengaged to disengage the pawl subsequent to disengagement of the cam device and to fully retain pawl engagement before the cam device reengages. 34. Assembly according to claim 33, comprising an elastic linkage. 35. An apparatus for centering the pawl for reengagement in any adjusted position of the sector within a range of motion of the pawl connection from the pawl connection. Assembly as described in. 36. From a centered position, where in-line relative tooth tip engagement prevents full reengagement of the pawl and sector teeth in the adjusted position. 36. The assembly according to claim 35, comprising a device for laterally displacing the pawl. 37. The device for laterally displacing the pawl includes an extension of the handle when the pawl and sector teeth are prevented from re-engaging in the adjusted position. 37. The assembly of claim 36, including a protrusion on the pawl that is engageable. 38. The device for centering the pawl comprises:
36. A claw pin projecting into an opening having a centrally located corner, and a device for moving the pin into the centrally located corner upon disengagement from the sector. Assembly as described in. 39. A device for effecting lateral movement of the pawl when the preliminary tip engagement of the teeth of the pawl and sector teeth aligned with one another prevents sufficient tooth engagement. The assembly of claim 33, comprising.