PIVOTABLE ELEMENTS

The subject invention concerns a device for setting the relative positions of pivotable elements, such as setting the position of inclination of the back rest of a seat, preferably a vehicle seat, comprising pivot components disposed in pairs for mutual rotational movement and arranged to be associated for instance with the back rest and with the seat cushion part, respectively of the seat, each component of said pair being formed with at least one of concentric side by side gear rims and with a number of planet wheels spaced about the associated gear rim circumference with each such planet wheel simulta¬ neously engaging the two gear rims, said planet wheels and said gear rims being mutually adapted to cause the gear rims and the associated rotational components to perform a relative angular movement upon rolling of the planet wheels in mesh with the gear rims.

In devices of the kind defined above it is often of very great importance that the components of the joint be kept together in a very stable manner, without play.

The main purpose of the invention is to provide a device of this kind, in which the pivot components of the joint are efficiently kept together in such a manner that no play occurs.

This purpose is achieved by means of a device in accordance with the invention, in which the planet wheels are supported so as to be able to move radially and in which means are provided to urge the planet wheels radially into contact with the gear rims.

Preferably, the planet wheels are spring biased in the direction towards the gear rims. In addition, the planet wheels preferably are interconnected by means of planet carriers of a resilient material. In accordance with one preferred embodiment of

2 the invention the planet carriers are shaped as annular members formed with planet wheel bearing means spaced around the periphery of the annular member.

In addition, the planet wheel shaft bearing means 5 preferably are formed by the cooperation between peri¬ pheral grooves formed in the planet wheel shafts and edge portions of the planet carriers in engagement with said grooves.

Preferably, the planet carriers planet carriers are

10 formed by an essentially circular ring-shaped spring member the periphery of which is biased into nesting engagement with said grooves formed in the end portions of the planet wheel shafts, thus forming a race cooperating with the bottom faces of the shaft grooves.

15 In addition, means preferably are provided to at least partially counteract, i.e. annul the contact pressure exerted on the planet wheels during setting, i.e. during the pivotal movement of the pivot components.

Furthermore, the means arranged to counteract the

20 contact pressure preferably could be operatively connected with the actuating means designed to set the positions of the pivot components for the purpose of diverting the contact pressure in a direction acting oppositely to the contact pressure.

25 The pivot components or components of the articulated or pivotable joint preferably are disc-shaped fittings arranged in abutting relationship, each one having two concentric apertures the periphery of which forms the associated gear rim, the two disc-shaped fittings being

30 retained one against the other by means of end plates arranged in abutment against its associated one of external flat faces and kept together by means of spacer members positioned between the planet wheels and bridging the thickness of the fittings.

35 Preferably, the spacer members are formed with external faces in abutment against the gear rim tooth apices and forming sliding tracks on which slide said

apices for the purpose of maintaining the concentric relationship of the gear tracks.

Some embodiments of the invention will be described in the following with reference to the accompanying drawings, wherein

Fig. 1 is a partly cut lateral view through the articulated fitting in accordance with a first embodiment of the invention,

Fig. 2 illustrates the same fitting as seen from the right-hand side with respect to Fig. 1, the lower part being shown in a lateral view and the upper part in cross- section,

Fig. 3 is a view as seen from the same direction as Fig. 1 but showing a pivot fitting in accordance with a second embodiment, the lower part being shown in a lateral view and the upper one part being partly cut,

Fig. 4 is a partly cut view, corresponding to Fig. 2, of the fitting of Fig. 3,

Fig. 5 is a partly cut view, corresponding to Figs. 2 and 4, of a pivot fitting in accordance with a somewhat different embodiment,

Figs. 6 and 7 are partly cut views, corresponding to Figs. 2, 4 and 5, of a pivot fitting in accordance with still another embodiment, Fig. 8 is a schematical representation showing the principles of yet another pivot fitting as seen from the same direction as that in Figs. 1 and 3 but shown in a more schematic way,

Fig. 9 is an exploded view of a fitting in accordance with the embodiment of Fig. 8,

Fig. 10 is a lateral view of the fitting in Figs. 8 and 9,

Fig. 11 is a partly cut view as seen from the right- hand side in Fig 10, of the same fitting, Fig. 12 is a view corresponding to Fig. 10, of a pivot fitting in accordance with yet another embodiment, and

Fig. 13 illustrates a component incorporated in the fitting of Fig. 12.

The pivot fitting illustrated in Figs. 1 and 2 consists of two pivot components, which are arranged for mutual rotational movement relatively to one another in the plane of the drawing figure 1. Pivot component 1 consists of two mutually spaced apart plates la and lb sandwiching between them the second pivot component 2, the latter also being of plate configuration in accordance with the embodiment shown. All plates la, lb and 2 are formed with openings arranged in co-axial relationship, the opening formed in component 2 appearing from Fig. 1 wherein it is designated by reference 3. Along the periphery of the opening, component la is formed with a gear rim 4 and pivot component lb with a gear rim 5 where¬ as also opening 3 is formed along its periphery with a gear rim 6. Corresponding gear rims formed on a number of planet wheels 7, in the example shown three such wheels, mesh with the gear rims 6. In accordance with the example shown the gear rim 6 is of larger diameter size than gear rims 4 and 5, and consequently the centre gear rim of the planet wheels also has a larger diameter size than the two outer gear rims. This difference in diameter sizes causes the pivot components 1 and 2 to rotate relatively to one another as the planet wheels are driven along the gear rims of the two pivot components. A gear ratio of this kind could, of course, be obtained in a variety of different ways known per se by a suitable choice of the number of teeth, diameter size and cog tooth module of the individual gear rims. Numeral reference 8 designates a number of spacer elements, three in accordance with the shown example, the thickness of which approximately corresponds to the total thickness of the two pivot components 1 and 2, the spacer elements thus bridging the space, from side to side, between two end discs 9 and 10 placed externally of the pivot components. The end discs preferably are kept together by means of rivets 11 or

5 other suitable interconnecting members extending through the spacer elements 8 and the end discs 9, 10. In accordance with the embodiment shown, the shafts of the planet wheels extend through apertures 12, 13 in the end discs 9 and 10, respectively so as to project beyond the latter. The extension of the apertures 12, 13 radially exceeds the shaft diameter size of the planet wheels, thus imparting a limited freedom of movement in the radial sense. In accordance with the embodiment shown in Fig. 2, the two pivot component plates la and lb are joined together by means of bending in the areas thereof positioned externally of the pivot component plate 2. In accordance with the embodiment shown, the pivot component plates are formed at their extremities with fastening apertures 14 and 15, respectively, allowing the fitting to be secured to the elements that are to be pivotally interconnected, such as for instance the cushion part and the back rest part of a vehicle seat. Numeral reference 16 designates a centre shaft which is formed at the left-hand side according to Fig. 2 with an enlarged portion or boss 16a which in the area of its transition to the narrower part of the centre shaft forms a shoulder 16b. Onto the right-hand part of the centre shaft as seen in Fig. 2, which shaft part is formed with threads, is screwed a nut 17 centrally supporting a manually operated hand wheel 18 formed with a hub portion 18a extending along the shaft 16 and arranged to be fitted onto the latter. The left end of the hub, as seen in Fig. 2, forms another shoulder 18b. A sun cog wheel 19 is non-rotationally secured to the shaft 16 and drivingly meshes with the planet wheels 7 disposed around the sun wheel circumference. Numeral reference 19 preferably designates two planet carriers positioned one on either side of the planet wheels internally of the end discs 9, 10. The planet carriers 19 preferably consist of a resilient material and centrally they are formed with through-holes through which extends the centre shaft 16,

and they are also formed with through-holes for passage through of the shafts 20 of the planet wheels. In accord¬ ance with the example shown the planet wheel shafts are formed integrally with the planet wheels but obviously the shafts could equally well consists of separate pins pene¬ trating through the planet wheels. In accordance with Fig. 2 the planet carriers 19 of resilient material could be shaped as a three-pointed cross and with such a con¬ figuration that their mutual spacing is larger in the area closest to the centre shaft 16 than in the area of the planet wheels. Because the planet carriers centrally are squeezed between the shoulder 16b of the centre shaft and the shoulder 18b formed on the hand wheel hub the planet wheels are positively retained in the correct position with respect to the gear rims of the two pivot components while at the same time the planet carriers tend to move the planet wheels outwards, radially, and thus to urge them into contact with the the gear rims. Owing to the thus created outwardly directed pressure exerted on the planet wheels any play between the cogs of the two pivot components 1 and 2 thus is efficiently eliminated, resulting in extremely precise setting conditions and an almost negligible risk of movement of the pivot components with respect to one another when exposed to load. If the pivot fitting is to be installed on a vehicle seat the enlarged portion 16a of the centre shaft preferably could be formed with an internal polygonal, preferably hexagonal recess in which may engage one end of an interconnecting rod extending to a pivot fitting positioned on the opposite side of the seat.

The pivot fitting described in the aforegoing functions in the following manner. When the hand wheel 18 is turned, the engagement of the sun wheel 19 with the planet wheels 7 forces the planet wheels to roll along the gear tracks of the pivot components 1 and 2, and owing to the mutual differences in the nature of the gear tracks of the pivot components the latter will move with respect to

one another for the purpose of setting the desired angular position. As already mentioned, the resilient planet carriers 19 tend to maintain the planet wheels pressed against their respective gear track of the associated pivot component. It is possible to adjust this pressure by suitable adaptation of the spacing between the two shoulders 18a and 18b. This adaptation could likewise be effected by tightening the nut 17 to a larger or smaller extent or by inserting suitable washers between the nut and its face of abutment on the hand wheel.

In Figs. 3 and 4 details that essentially correspond to those referred to in the previous drawing figures are given identical numeral references with the addition of 100. For example, one of the pivot components are referred to generally by numeral 101, its two pivot component plates by 1001a and 101b, respectively, and the second pivot component by 102. In addition, the aperture or opening formed in pivot component 102 has been given numeral reference 103, the two gear rims of the pivot component 101 references 104 and 105 and the gear rim of component 2 reference 106. The planet wheels are designated by 107. Spacer means are provided just like in the previous embodiment but are not shown here. On the other hand, the rivets 111 interconnecting them with the respective end discs 109 and 110 are shown. The apertures in which are mounted the planet wheel shafts 120 in the end plates are designated by 112 and 113, respectively. In addition, the mounting holes of the pivot components are designated by 114 and 115, respectively. In this case, the centre shaft is designated by 116, an enlarged portion on one it its ends by 116a and the shoulder formed in the transition area between said enlarged portion and the narrower part of the shaft is designated by 116b. The hand wheel is designated by 118. Reference numeral 121 designates a sun wheel which is non-rotationally mounted on the shaft 116 but so as to be allowed displacement in the axial direction. In this embodiment like in the

previous one the planet wheel shafts 120 are radially movable in spacious apertures 112, 113 formed in the end plates. On the other hand the resilient planet carrier of the previous embodiment has been eliminated in this case. In contrast to the previous example, the end plate 110 is formed with a centrally located, housing-shaped hub 125. Inside the hub 125 is accommodated a compression spring

122 which is held between the inner face of the hub portion 125 and the sun wheel 121. In addition, a nut 123 cooperates with threads formed on the shaft 116 and abuts against the outer face of the hub portion 125. In the subject example, the hand wheel hub is designated by 118a. Further, the hand wheel is attached to the shaft by means of a locking pin 124. The cogged periphery of the sun wheel 121 is slightly conical, as indicated by in Fig. 4. This means that the operative circumference of the sun wheel against the planet wheels increases as the sun wheel is displaced to the right relatively to the planet wheels, The spring 122 tends to urge the sun wheel to the left, i.e. into abutment against the shoulder 116b. As the nut

123 is tightened against the housing 125 the shoulder 116b is displaced to the right while the compression spring 122 is being compressed. The displacement thus obtained increases the active diameter of the sun wheel and in consequence thereof the planet wheels are pressed out¬ wards, against the races formed by the gear rims in the pivot components 101 and 102. By means of the nut 123 it thus becomes possible to regulate the force of abutment or pressure of the planet wheels in contact with the associated gear rims.

The function otherwise agrees with that described with respect to the previous embodiment.

In Fig. 5 the details that are equivalent to those described with reference to the embodiment of Figs. 1 and 2 have been given the same numeral reference with the exception of the addition of 200. For instance, the two pivot components are designated by 210 and 202,

respectively. The two-part plates of the pivot component 201 thus are designated 2011a adn 201b, respectively. The gear rims formed in the pivot components are designated by 204, 205 and 206. In addition, the planet wheels are designated by 207. The spacer means that are suitable for maintaining the spacing between the end plates 209 and 210 are not shown in this embodiment. Preferably, the end plates are kept together by rivets 211 passing through the spacer means. The centre shaft is designated by 216. Like in the previous case, the centre shaft is formed with an enlarged portion 216a having a shoulder 216b thereon. In addition, the hand wheel is designated by 218 and the wheel hub by 218a. Reference 218b designates a spacer means arranged for the purpose of maintaining the mutual spacing between the plates 201a and 201b so as to ensure that they may extend in parallel over their entire longi¬ tudinal extension. The subject embodiment is distinguished from the previous ones essentially in that the planet wheels 207 have no centre shaft. Instead, the end plates 209 and 210 are provided with inwardly extending projections 209a and 210a, respectively, penetrating into corresponding central depressions formed in the planet wheels. The projections then have a somewhat smaller radial extension than have the recesses in the planet wheels, allowing the latter to perform a limited radial movement. Reference numeral 221 designates a sun wheel formed with a sleeve 221a which passes through the end plate 210 and which projects into the hub 218a of the hand wheel. Reference 222 designates a transverse pin passing through the wheel hub 218a and interconnecting the hand wheel and the centre shaft 216. In addition, a depression 223 is formed in the sleeve 221a, preferably on each one of the oppositely positioned sides thereof, the width of said depressions tapering towards the depression bottom, which means that the depression forms an oblique plane on which the pin 222 may slide upon turning movement of the hand wheel. The shoulder 216b rests against the

external face of the end plate 209. A spring 224 is held between the inner face of the same end plate and the sun wheel 221, said spring acting in the axial direction on the sun wheel, the latter like the wheel in the previous example, having a conical configuration indicated by c in the drawing. A spacer washer 225 is arranged intermediate the hand wheel and the end plate 210. The compression spring 224 tends to urge the sun wheel and consequently the sleeve 221a of the latter to the right as seen in the drawing, which means that the sun wheel presses the planet wheels in the radial direction against their associated one of the gear rims in the pivot components 101 and 102. Upon turning movement of the hand wheel the pin 222 will slide towards the sloping planes in the depression 223, displacing the sun wheel to the left while compressing the spring 224. Owing to this axial movement of the sun wheel the pressure on the planet wheels will lessen with con¬ sequential reduction to a minimum of the frictional forces involved upon angular setting of the two pivot components. On the other hand, when the hand wheel is released the sun wheel returns to its pressure-exerting position and the interconnection, free of play, between the two pivot components is efficiently re-established.

In the same manner as in the previous examples the details of Fig. 6 that are functionally identical with those of Figs. 1 and 2 have received the same numeral reference with the addition of 300. For instance, the upper pivot component is designated by 301, the lower pivot component by 302 and the planet wheels are designated by 307. In addition, the two end plates are designated by 309 and 310, respectively. The gear rim formed in pivot component 301 is designated by 304 and the gear rim of pivot component 302 by 306. The shafts of the planet wheels are designated by 320. Reference 321 designates a sun wheel formed as a single piece integrally with a sleeve 322, the latter projecting externally of the end plates 309 and 310. Numeral references 323 and 324

designate spacer rings chosen to ensure a suitable spacing from the inner face of the associated end plate to the sun wheel. The sun wheel is conical also in accordance with this embodiment, as indicated by α in the drawing. Owing to this configuration the axial displacement of the sun wheel and the consequential pressure of the planet wheels against the associated gear rims is determined by the choice of the axial extension of the spacer rings 323 and 324, respectively. Also in accordance with the embodiment illustrated in Fig. 6 the mutual distance between the end plates 309 and 310 preferably is maintained by means of spacer means which are not visible in this drawing figure but could correspond e.g. to the spacer means 8 of Fig. 1. The various details are also in this case kept together by means of suitable interconnection means, such as the rivet 311 illustrated in the drawing. The relative turning movement of the two pivot components preferably is effected by means of a rod-shaped member inserted into the sleeve 322 and secured to a hand wheel or other actuating means, for instance a motor-operated device, or else the pivot fitting in accordance with Fig. 6 could be arranged on the side of the seat opposite to the one where the hand wheel is mounted. For instance, the pivot fitting could be interconnected with a pivot fitting of the kind illus- trated in Fig. 7, but the second pivot fitting could also be entirely identical to that shown in Fig. 6. Numeral references 312 and 313 refer to the apertures having a radial space in which the planet wheels are mounted, just like in the previous examples. The two attachment apertures of the two pivot components are designated by 314 and 315, respectively, in accordance with this embodiment.

In Fig. 7 details corresponding to those appearing in Figs. 1 and 2 have received the same numeral references with the addition of 400. For instance, the upper pivot component is designated by 401, the lower pivot component by 402 and the planet wheels by 407. In addition, the gear

rim formed in pivot component 401 is designated by 404 and the gear rim of component 402 by 406. Numeral references 409 and 410 designate two end plates spaced mutually apart by means of suitable spacer means through which pass suitable interconnection means such as the rivet 411 just like in the previous examples. Just like end plate 110 in Fig. 4 end plate 410 has a hub portion 425 in the shape of a housing in which is accommodated a compression spring 422. An adjusting nut 423 is pressed against the external face of the hub portion. A central shaft 416 is formed with an enlarged end portion 416a which is formed integrally with a sun wheel 421. Numeral reference 418 designates a hand wheel 418 the hub 418a of which is non- rotationally connected to the shaft 416 by means of a transverse pin 424. Also in accordance with this embodi¬ ment the sun wheel has a conical configuration as indi¬ cated by a in Fig. 7. As a result of this configuration tightening of the nut 423 will cause the sun wheel 421 to move to the right as seen in the drawing figure, just like in accordance with the embodiment of Fig. 4, and con¬ sequently the planet wheels will be pressed against their associated gear rims. Numerals 412 and 413 designate the radially spacous apertures formed in the respective end plate 409, 410 through which extend the planet wheel shafts 420. The attachment apertures in the two pivot components are designated by 414 and 415, respectively. In the same manner as in the previous embodiments, details corresponding to those in Figs. 1 and 2 have received the same numeral references in Figs. 8-12 with the the exception that 500 has been added. Consequently, en upper pivot component is designated by 501 and the lower pivot component by 502. Planet wheel mounting apertures formed in the two pivot components are designated by 503a and 503b, respectively. Numeral reference 504 designates the gear rim formed in pivot component 501 and numeral reference 506 designates the gear rim formed in pivot component 502. Reference 507

designates the planet wheels acting against the gear rims, references 509 and 510 the end plates positioned externally of the pivot components 501 and 502. Rivets 511 or similar means keep the end plates together and extend through spacer means 508. Numeral references 512 and 513 are used to designate radially spacious apertures formed in the two end plates and through which extend the shafts 520 of the planet wheels. Reference 521 designates a sun wheel which is formed integrally with a sleeve 522 extending through central bearing members 509a and 510a, respectively, arranged in the end plates. Attachment apertures in the two pivot components are designated by 514 and 515, respectively. Two planet carriers 519 are positioned one on either external face of the two end plates. In accordance with the embodiment shown the two planet carriers 519 are shaped essentially as an equi¬ lateral triangle the corners of which are apertured at 519a and the sides of which are somewhat curved to allow the apertures to be compressed radially while making use of the resilient nature of the material. Fig. 11 shows how the planet wheel shafts 520 extend through the end plates 509, 510 and the planet wheels 507. Externally of the end plates the planet wheel shafts are formed with grooves 520a. By means of their apertures 519a the resilient planet carriers 519 are fitted into the grooves 520a while radially compressed, as most clearly apparent from Fig. 11. The radial compression of the planet carriers tends to keep the planet wheels pressed outwardly into abutment against their associated gear rim, thus preventing the occurrence of play between the pivot components. The relative position of the various parts also appears from the exploded view of Fig. 9. In the non-round centre aperture preferably could be inserted a shaft which is connected with a hand wheel or other means suitable to effect the sun wheel turning movement and consequently the mutual setting of the pivot components. Fig. 8 shows the way the spacer means 508 follow the circle formed by the

gear rim cog apices, thus forming a sliding face for the centering of the two pivot component relatively to one another.

The pivot fitting illustrated in Figs. 12 and 13 is a modification of the pivot fitting illustrated in Figs. 8-11, the difference being that the triangular planet carrier is replaced by an annular member 619 of a resilient material. In the areas of the planet wheel shafts 620 the annular member is somewhat compressed radially and inserted into the grooves 620a formed in the planet wheel shafts. Just like in the previous example the planet wheel shafts are carried through spacious apertures 613 formed in the end plates. Because the annular member 619, owing to its resiliency, tends to resume its circular shape it exerts pressure on the planet wheel shafts 620 and consequently on the planet wheels, not visible on the drawing figure, moving them outwards against their associated one of the gear rims in the same manner as in the preceding examples. Upon turning movement of the planet wheel shafts 620 the bottom of their grooves 620a will form a race on which the annular member 619 slides, with the result that the wear on the contacting surfaces of the planet carriers 619 and the planet wheel shafts 620 are reduced to a minimum. The annular spring 619 could have any cross-sectional shape, for instance circular or square or rectangular but also other cross-sectional configurations are possible without departure from the inventive idea.

A number of various embodiments have been described in the aforegoing. However, the invention is not limited to these embodiments which could be modified as to their details without departing from the inventive idea. The invention is primarily intended to be used in connection with vehicle seats but a more general application of the invention is equally possible whenever one wishes to interconnect two parts by means of an articulated precision joint.