DE4343277A1 - Rotary piece with roller bearing - Google Patents

Abstract

The axis of one of the two adjacent rollers (20) intersects the axis of the other roller at right angles. Each roller is cylindrical and has a total length equal to the external diameter.Several spacers (21) are positioned in a peripheral direction along the neutral axis of the inner space. Each spacer is positioned between two adjacent rollers. The axis of the two adjacent rollers slopes at 45 degrees to a plane at right angles to the rings' centre axis (11,12), in order to adjust the contact angles of the roller to the annular surface of the V-shaped groove (13,14) at under 45 degrees.

Description

The invention relates to a rotating device that rolls uses bearings with rolling contact, and in particular a construction for a roller bearing, which ge suitable is used for a rotating device for a rotating seat from Vehicles, for example a car, bus, truck, plane or electric vehicles or the like.

Various swivel seats for vehicles have recently been featured propose and have been developed in which the orientation the seat is adjustable in every direction, depending on the type requirements of the vehicle user sitting on it. Like all is commonly known, the rotary seat uses a rotating device attached to its bottom, so the orientation suitable to adjust the seat by changing the angle position of the seat on a horizontal plane. Such a Seat has been disclosed in Japanese Utility Model First published (Jikkai Showa) 63-83058. The filming Direction for a swivel seat according to the prior art a pair of links coaxially and rotatably coupled together pelt, which is an upper rotatable member, the is attached to the bottom of the seat, and the other one un teres stationary member is attached to a base plate is brought. In the aforementioned Japanese utility model is a substantially annular inner chamfered Ab cut the upper rotating member slidably and rotatably  a substantially annular inner groove of the lower one stationary member with frictional contact between the annular Contact surfaces put on. The rotating device according to the state the technique includes an additional fitting plate, which on the in first annular flanged section of the lower glie which is arranged to rub the mated pair in the to keep in contact and to prevent the upper link breaks away from the lower limb due to an excessive large upward breakaway force on the seat works. The conventional rotating device usually comprises a locking mechanism which is arranged for Ver prevent relative rotation of one of the two passports link to the other to get the seat in a desired win to keep the position. In the swivel seat with the turning device device according to the prior art is the locking device direction first in its unlocked state in order the rotation of the upper link to the lower link Frictional contact while setting to a desired win allow the seat to be in the lower position. Then the Verrie gelungseinrichtung back in its locked state to lock the upper and lower limbs when the Seat has been rotated to its desired angular position. This way the desired orientation of the seat receive.

In the described rotating device for a rotating seat the upper as well as the lower link with a bead or flange provided to increase the stiffness of each link. Since that lower stationary link, the upper rotatable link and the Fit plate in its vertical direction in this order are stacked on top of each other, there is also a tendency that the total size of the rotating device, in particular the verti kale size of the device is increased. In Anbe it is the cost of placing the seat on the base plate desirable to miniature the vertical size of the device lubricate. Furthermore, the conventional rotating device requires a relatively high machining accuracy of the upper one as well  of the lower limb so that both limbs are slidable on to be put one on the other without chafing. The efficiency of the Mon days of the turning device is reduced due to the additional fitting plate. Usually the upper as well as the lower one Link made by pressing sheet metal. A relatively thick one Metal plate must be used to make a mechanical Fe Ensure stability that is sufficient for the seat in any reliable circumferential positions of the rotating device support. All links, namely the lower stationary Link, the upper rotating link and the fitting plate must be larger be dimensioned to be sufficiently secure against an excessive upward breakaway force, wel on the seat during rapid braking of the vehicle acts to break it off the bottom plate. Hence be there is a tendency that the manufacturing cost of the rotating device according to the state of the art due to the larger size Parts are increased. Since the upper link is sliding on the un Tere link with frictional contact is also placed the durability of the two sliding contacting links necessarily diminished. Assume that the angular position tion of the seat is adjusted in a state in which a Excessively heavy eccentric load applied to the seat there is a risk that a locally increased voltage focus on any point of contact between the above ren and lower contacting link is caused. So has the rotating device according to the prior art, the applies two links with frictional contact, the disadvantage of that the reliability of the angular position setting operation tends to be ring.

The swivel seat often uses a seat slide as well the above-mentioned rotating device, so as to be slidable to front and rear from the initially set position of the seat to be adjustable. Because of this, it would be him wishes a small sized thin turning device for one To create a swivel seat.

An object of the invention is therefore in view of the above Disadvantages of creating a simplified, for a shoot suitable rotating device, which is a roller bearing relatively small weight and small size, which is superior machinability, high assembly efficiency enz of the unit and has a high durability.

Another object of the invention is to create a for a small-sized rotating device suitable for a rotating seat, which uses a thinned roller bearing unit with a mechanical strength that is sufficient to counteract locally increased stress concentration on a tread due to heavy eccentric load placed on the seat to be sure.

Another object of the invention is to create a for a rotating seat suitable rotating device, which is a small dimensioned roller bearing with a concentric pair of rin gene applies that over several roles with rolling contact are coupled, which camp despite a relatively small a satisfactory mechanical strength speed shows both against an axial load in the axial direction of the bearing acts like a breakaway force that so that it acts one of the two rings from the other ring breaks away.

To achieve the aforementioned and other objects of the invention Chen, a rotating device with a roller bearing includes one Inner ring and an outer ring which are coaxially attached to each other are arranged, a pair in the circumferential direction and ra dial opposite V-shaped grooves that are continuous Lich on the outer circumferential surface of the inner ring or continuous only on the inner circumferential surface of the outer ring forms, with each V-shaped groove a pair in um includes circumferential annular surfaces, wel cut each other at right angles and the same Have dimensions, as well as a plurality of roles that  radially in an inner space running in the circumferential direction are arranged by the opposite V-shaped Grooves is defined so that the inner ring and the outer Outer ring can be rotatably coupled. The axis one of the two adjacent roles intersects the axis of the other role at right angles, and besides, each one is Roll substantially cylindrical and has an overall length equal to the outside diameter. In addition, a plurality of Spacers in the circumferential direction along the neutral axis of the inner space. Each spacer is between rule the two adjacent roles so that the two adjacent rollers a predetermined distance apart have other. The one roller axis is preferably the two neighboring rollers inclined at 45 ° to one plane, which is perpendicular to the central axis of the rings by a con contact angle of the roller on the matching annular surface the V-shaped groove to 45 °. The role can an essentially cylindrical roller with both flat ones End faces and have a cylindrical surface. In this The case is the cylindrical roller in the inner space arranged that the two flat ends on one of the two ge abut opposite pairs of annular surfaces, which define the V-shaped grooves and the cylin surface of the cylindrical roller with the other against overlying pair fits.

Alternatively, the roll can comprise a barrel-shaped roll with spherical surfaces at both ends and one barrel outer circumferential surface. In such a case, the opposite V-shaped grooves defined by four circumferential spherical surfaces, and zu In addition, the curvature of each spherical end must be the tone NEN-SHAPED ROLL, the curvature of the barrel-shaped outer Circumferential surface of the roll and the respective curvatures of the four spherical surfaces, which the opposite V-för define grooves, be identical to each other in order  a self-alignment function between the axes of the two To form rings.

One of the circumferential annular surfaces Chen who cuts the other has the same shape and dimensions on like the other annular surface. Before preferably the spacer has the same shape and Ab measurements like the roll on.

In view of the superior assembly efficiency of the turning device direction on two turned parts such as one Seat body and a base plate, it is advantageous that the V- formed on the outer circumferential surface of the inner ring shaped groove against the neutral axis of the inner ring in An axial direction of the rings is offset and which on the in neren peripheral surface of the outer ring formed V-shaped Groove against the neutral axis of the outer ring in the whose axial direction of the rings is offset, so that a be tenwand of the inner ring protrudes through a plane through a side wall of the outer ring is defined, and the the side wall of the inner ring is withdrawn under one Level that defi through the other side wall of the outer ring is renated.

There is also a cut-out section on one of the rings designed in such a way that the interior is exposed, around the rollers and spacers through the cutout to insert in the inner space, and in addition an Ab to cover a section of the circumferential annular surfaces to bil the one that defines the V-shaped raceway. The out cut section includes a beveled neckline with trapezoidal shape, and the cover is trapezoidal to fit in to fit the neckline. Preferably, the cover we at least contain a stop pin, and the cut out tete portion may include a stop pin hole that in the stop pin is fitted so as to prevent  the cover moves in the radial direction of the rings. The thickness of the beveled cover and the height of the bege slanted section can be set half as thick such as the thickness of the ring that has the cutout, and in addition, the width of the section can be limited to a minimum dimension, which is required Roll or insert a spacer in the interior Zen.

The invention is based on one in the drawing shown embodiment described in more detail. In the Show drawing:

Figure 1 is a schematic lateral sectional view of an embodiment of a ball bearing with a concentric pair of rings which are coupled together by a plurality of rollers with rolling contact, which bearing is used in a rotating device according to the invention.

Fig. 2 is a perspective view of the rotating device of the embodiment, partly in section;

Fig. 3 is a partially enlarged portion of the Kugella gers, which uses several cylindrical rollers;

FIGS. 4A and 4B are views for explaining the track which receives by acting below the external pressure exerted on the outer ring of the bearing;

Fig. 5A and 5B are views for explaining the track which receives by acting below the external pressure exerted on the inner ring of the bearing;

Fig. 6A is a plan view showing the upper side of the ball bearing of the device shown in Fig. 1;

Fig. 6B is a side view illustrating the ball bearing partly in section;

6C is an enlarged radial sectional view of a spacer which is interposed between the applied in the ball bearing rollers.

Figures 7A, 7B and 7C are top, side and elevation views, respectively, illustrating a tapered cover through which the rollers and spacers are inserted into the concentric pair of rings of the bearing;

Fig. 8 is a partially enlarged perspective view showing the insertion section for the rollers and the standoff;

Fig. 9 is an explanatory view showing the relative positional relationship between the rollers used and from standoffs;

FIG. 10A and 10B are views for explaining a method of inserting two rollers which are spaced apart by a spacer;

Fig. 11 is a partial plan view showing the state of assembly of the beveled cover from the ge formed on the outer ring cutout;

Fig. 12 is an enlarged view showing a conversion from the rotary device according to the invention, partly in section;

Fig. 13 is a schematic view of a swivel seat assembly using the rotating device according to the invention;

Fig. 14A is an elevation showing the rotary seat assembly loaded by two different vertical loads X and W, which are offset from each other in the lateral direction of the seat;

Fig. 14B is a side view showing the rotary seat arrangement, which are loaded by two different vertical loads Y and V, which are offset in the longitudinal direction of the seat against each other; and

Fig. 15 is a partially enlarged portion for presen- tation of the ball bearing, which uses several barrel-shaped rollers.

In the drawing, in particular in FIGS. 1 to 14B, the rotating device of the invention is shown using the example of a rotatable bench seat for electric vehicles attached to the vehicle. As can be seen in FIGS. 13, 14A and 14B, the rotating seat 1 mounted on the rotating device of the first embodiment comprises a seat cushion 2 and backrests 3 . Although not clearly shown, the respective backrest 3 generally uses an adjustment mechanism (not shown) in order to suitably adjust the inclination of the backrest. In FIGS. 13, 14, 14A and 14B, reference numeral 4 denotes a base part of the seat 1. The foot part 4 of the seat 1 is cantilevered on a base plate 5 such that it is attached at one end to the base plate and at its other end to the bottom of the bench seat 1 is BEFE Stigt. In particular, the other end of the foot part 4 comprises a horizontally extending support 4 a, on which the rotary device 10 is mounted according to the invention for changing the angular position of the seat on the horizontal support 4 a and for adjusting the orientation of the seat.

In Figs. 1 to 3 10 includes the rotary device which he a number sten embodiment of an inner ring or inner race 11 and an outer ring or outer race 12, a plurality of rollers 20 between the inner ring 11 and the outer ring are included 12, and of spacers 21 , which are each arranged between two adjacent rollers 20 . As can be seen in FIGS. 2 and 3, the two rings 11 and 12 are aligned coaxially with one another, so that the outer circumferential surface 11 a of the inner ring 11 and the inner circumferential surface 12 a of the outer ring 12 are radially opposite one another. Along the radially opposite two To circular surfaces 11 a and 12 a are two circumferentially duri fende V-shaped grooves 13 and 14 defined in such a way that the continuously formed on the outer peripheral surface 11 a ge V-shaped groove 13 and the continuously the inner peripheral surface 12 a formed V-shaped raceway 14 are radially opposite one another. In the rotating device 10 of the preferred embodiment, each roller 20 has a cylindrical shape. Although not clearly shown in the figures, the total length of the roll is substantially equal to the outside diameter of the roll. Preferably, the spacer 21 has substantially the same shape as the roller 20 in view of the assembly efficiency. In the embodiment, the spacer is cylindrical and has the same dimensions as the roller 20 . As shown in Fig. 1, the respective cylindrical spacers in the circumferential direction of the opposite V-shaped grooves are arranged such that the two neigh disclosed rollers 20 are spaced from each other via one of the spacers 21 . As best seen in Fig. 3, the opposed pair of V-shaped grooves 13 and 14 engage a pair of opposed rectangular grooves to define a generally annular space 15 which is generally square in cross-section and which includes rollers 20 and the spacers 21 operationally takes on. The plurality of rollers 20 are arranged radially with respect to the central axis of the rings 11 and 12 . In addition to this, the respective axial directions of the two adjacent cylindrical rollers 20 are different from one another, so that the axis of the roller shown in FIG. 3 by the solid line is inclined at an angle of 135 ° to the horizontal plane and the axis of the roller in FIG. 3 by the dashed line roller is inclined at an angle of 45 ° with respect to the horizontal plane. In other words, a plurality of rollers 20 are arranged radially in the annular space 15 , which is defined in the pair of opposed V-shaped grooves 13 and 14 , such that the rollers 20 are at equal distances from one another by means of the spacer 21 and one of the two adjacent ones Rollers 20 is inclined at an angle of substantially 90 ° to the other. The two adjacent rollers 20 , which are spaced apart from one another by a spacer 21 , are arranged in the square space 15 such that one roller axis and the other roller axis intersect one another at right angles. As can be seen in Fig. 3, more specifically, the rectangular inner race 13 is defined by an upper groove surface 13 a with an inclined angle of 135 ° and a lower groove surface 13 b with an inclined angle of 45 °, whereas the rectangular outer race 14 is defined by an upper groove surface 14 a with a ge inclined angle of 45 ° and a lower groove surface 14 b with an inclined angle of 135 °. That is, the inner right-angled groove 13 is obtained by the groove surface 13 a with the 135 ° angle and the groove surface 13 b with the 45 ° angle intersect at a right angle, whereas the outer right-angled groove 14 is obtained by Cut the groove surface 14 a with the 45 ° angle and the groove surface 14 b with the 135 ° angle at a right angle. The upper groove surface 13 a with the 135 ° angle has the same shape and dimensions as the lower groove surface 13 b with the 45 ° angle, whereas the upper groove surface 14 a with the 45 ° angle has the same shape and dimensions as the lower groove surface 14 b with the 135 ° angle. As can be seen from the figures, the two face each other to work the groove surfaces 13 a and 14 b together, to act as bearing surfaces or tracks for the 135 ° roles, while the two mutually facing groove surfaces 13b and 14a together menarbeiten to as bearing surfaces or tracks to work for the 45 ° rollers. In Fig. 3 abut the upper and lower flat ends of the roller 20 , which are each represented by the solid line, to the 45 ° groove surface 14 a of the outer ring 12 with surface contact and to the 45 ° groove surface 13 b of the Inner ring 11 with surface contact. The upper and lower flat ends of the rollers 20 , which are each represented by the dashed line, abut the 135 ° groove surface 13 a of the inner ring 11 with surface contact and to the 135 ° groove surface 13 b of the outer ring 12 with surface contact . On the other hand, the cylindrical surface of the roller 20 shown by the solid line fits to the 135 ° groove surface 13 a of the inner ring 11 with line contact and to the 135 ° groove surface 14 b of the outer ring 12 with Linienkon, whereas the cylindrical line shown by the broken line Surface of the roller 20 , the 45 ° groove surface 13 b of the inner ring 11 with line contact and the 45 ° groove surface 14 a of the outer ring with line contact adjusts. In other words, the roller 20 shown by the solid line has a contact angle of 45 ° with respect to the groove surface 13 a of the inner ring 11 and the groove surface 14 b of the outer ring 12 , while the roller 20 shown by the broken line has a contact angle of 45 ° be with respect to the groove surface 13 b of the inner ring 11 and the groove surface 14 a of the outer ring 12 .

With the arrangement described, the inner ring 11 and the outer ring 12 are rotatably coupled to each other by means of the rollers 20 which are operatively arranged in the opposite pair of rectangular grooves. As can be understood from the above, the seat body can be rotatably connected to the bottom plate 5 , assuming that the outer ring 12 and the inner ring 11 are attached to two respective links, such as the bottom of the seat 1 and the foot part 4 , respectively. which is firmly attached to the base plate 5 . In Fig. 2 be the reference numeral 11 b denotes a hole through which the inner ring 11 is screwed to the bottom plate 5 , while the reference numeral 12 b denotes a hole through which the bottom of the seat 1 is screwed to the outer ring 12 . The annular space 15 is preferably filled with lubricant, such as grease, in order in this way to ensure a satisfactory rolling action of each roller 20 . As can be seen in FIG. 1, the annular space 15 of the rotating device 12 actually accommodates nine roller spacer sequences, each sequence having a first roller, a first spacer, a second roller with an axial direction different from the first roller, and one second spacer in this order.

In FIGS. 4A to 5B, the contact relationship between the roller 20 and the groove surfaces is shown, which groove the running define 13 and 14, is charged in the case in which the outer ring 12 by a vertical load W downward, and in the case in which the inner ring 11 is loaded downward by a vertical load W. If it is assumed in FIGS. 4A and 4B that the downward load W acts on the upper side wall of the outer ring 12, the two rings 11 and 12 are offset relative to each other so that the distance between the two mutually indicative Rillenflä chen 13 b and 14 a is reduced a little and the distance between the two mutually facing groove surfaces 13 a and 14 b is increased a little. So the load W is satisfactorily received by both flat end surfaces of the roller with the roller axis inclined at 135 ° to the horizontal plane with surface contact. Assuming that, in contrast, the downward load W acts on the upper side wall of the inner ring 11 , the two rings 11 and 12 are offset relative to each other so that the distance between the two mutually facing groove surfaces 13 a and 14 b is reduced little and the distance between the two mutually facing groove surfaces 13 b and 14 a is increased a little. So the load W is safely absorbed by line contact between the cylindrical surface of the roller with the 135 ° roller axis and the 135 ° groove surfaces 13 a and 14 b. The line contact and surface contact noted above are necessary to create a bearing unit or rotary device of small size for high loads, since line contact or surface contact is generally superior to point contact in the durability of bearings.

As shown in Figs. 14A and 14B, various loads W, X, Y and V act on the swivel seat. Assuming that the rotating device 10 is arranged in the middle between the two backrests 3 , the rotating device is subjected to a relatively small moment if the two vertical loads W and X are simultaneously applied to the seat. If one of the two vertical loads X and W acts on the seat, the rotating device 10 is subjected to a relatively large moment. As seen in Fig. 14B, the vertical load Y applied to a position that is excessively offset from the center axis of the rotating device 10, as compared to the Vertika len load V. In the case of such an eccentric load Y, the rotating device 10 is a relatively large Submit moment. The large moment acts as a breakaway force or tear force that breaks the inner ring 11 away from the outer ring 12 . As can be understood thereafter, the rotating device according to the invention shows, via the surface contact and the line contact between the track and each roller 20, a mechanical strength which is sufficient to be secure against the large loose power due to such a large moment. In particular, it is advantageous to fix the contact angle of the roller 20 within 45 ° ± 30 °, preferably to 45 °, so as to increase the mechanical strength of the rotating device against heavy breakaway force. The seat is thus rotatably supported by the rotating device 10 with a high reliability factor despite a relatively high breakaway force. In the case where the seat 1 is statically loaded under a condition in which the swivel seat has been set to a desired seating position, the static load is satisfactorily absorbed via surface contacts between the 45 ° groove surface 13 b of the inner ring 11 and the upper one flat end of the roller and between the 45 ° groove surface 14 a of the outer ring 12 and the lower flat end of the roller. Thus, the rotating device 10 shows a high mechanical strength against the static load. The surface contact and line contact noted above ensure high durability without local wear on the track. Since the roller bearing constituting the rotating device 10 includes the inner ring 11 and the outer ring 12 , each ring made of solid material such as steel, aluminum alloy, synthetic resin or the like, the rotating device 10 exhibits a higher durability compared to that Prior art turning device which is produced by pressing sheet metal. In order to increase the durability of the rotating device 10 , the respective rings 11 and 12 are preferably made of aluminum alloy in view of abrasion or wear resistance and weight reduction of the device. Likewise, the rollers 20 and spacers 21 can be made of steel, aluminum alloy, synthetic resin or the like. It is not necessary for the rollers to be made of the same material as the rings 11 and 12 . For example, the rollers and spacers can be made of steel other than aluminum alloy, while the rings 11 and 12 are made of aluminum alloy. In this case, the surface contact and the line contact are highly advantageous against wear on the running surface compared to the point contact in ball bearings.

In FIGS. 6A through 10B, a method is shown for A of the rollers 20 and spacers 21 put in the ringförmi gen space 15 len by the radially opposite Laufril is defined 13 and 14. As best seen in FIGS. 8 and 9, a substantially trapezoidal cut-out cut 30 is formed on either the inner ring 11 or the outer ring 12 for inserting the rollers 20 and the spacers 21 into the annular space 15 . In the preferred embodiment, the chamfered cut 30 is formed on the upper side of the outer ring 12 from such that it is open to the ring-shaped space 15 via the 45 ° groove surface 14 a. To improve the efficiency of inserting the rollers and spacers into the annular space defined in the coaxial rings 11 and 12 , it is advantageous to provide at least two chamfered cutouts 30 at two diametrically opposite positions, as in FIG. 6A see. Only a bevelled cutout 30 needs to be provided on either the inner ring 11 or the outer ring 12 . As shown in FIGS. 9 and 10A and in FIG. 10B, the rollers 20 inclined at 135 °, the spacers 21 , the rollers 20 inclined at 45 ° and the spacers 21 are alternately moved into the square space 15 by the chamfered cutout 30 inserted by inserting the rollers 20 and spacers 21 into the space 15 . As shown in Fig. 8, the chamfered cutout 30 is covered by an inverted trapezoidal cover 31 to form an annular continuous 45 ° groove surface 14 a. The trapezoidal cover 31 has a tapered screw hole 32 a, while the tapered hole has a threaded b of cut portion of the outer ring 12 32nd The threaded hole 32 b is coaxially aligned with the hole 32 a of the cover 31 in a state in which the cover 31 is placed on the chamfered cutout 30 . The cover 31 is fastened to the outer ring 12 by screwing in a fastening machine screw such as, for example, a countersunk head screw (not shown) through the hole 32 a into the threaded hole 32 b. As shown in Fig. 7B, 7C and 8, stop pins 33 and stop may be pin holes 34 are provided at the inclined cover 31 or in the tapered recess 30 of the outer ring 12, a misalignment between the 45 ° surface of from beveled cover To avoid 31 and the 45 ° groove surface of the outer ring 12 and to place the cover 31 at a predetermined location on the beveled cutout 30 of the ring 12 exactly. Due to the engagement between the stop pin 33 and the associated stop pin hole 34 , there is no misalignment in the radial direction shown by the two arrows in FIG. 11. As, 10A and 10B can be seen from FIGS. 8, 9, the thickness of the tapered cover 31, and the height of the tapered section 30 are approximately set to the half of the thickness of the outer ring 12, and additionally is the width of the cutout 30 on minimum dimensions limited, which are required to insert a roller or a spacer in the square space 15 . As a result, the stress concentration on the beveled cutout 30 is negligible. According to the structure of the ball bearing used in the rotating device 10 , the thickness of the rotating device can be reduced to a minimum while maintaining an allowable high mechanical strength sufficient to reliably support the weight of the passengers seated on the rotating seat 1 . Therefore, the rotating device according to the invention can be easily mounted in a limited narrow space between the seat 1 and the Bo denplatte 5 . Since the seat body 1 is screwed to the outer fixed ring 12 and the inner fixed ring 11 is screwed to the base plate 5 , a relatively thin rotating device 10 can also be very rigid connections between the seat 1 and the device 10 and between the base plate 5 and create the device 10 . Are as guide die in the off as shown in FIG. 8 can be seen the outer dimensions of the tapered covers 31 along the inner dimensions of the tapered section 30 profiled, the tapered cap 31 is simply cut on the beveled From placed 30 without any play in its bottom wall and the radial side walls. Therefore, the outer ring unit with the two beveled covers 31 shows a relatively high rigidity. More specifically, the two radially extending side walls of the cover 31 abut the two bevelled surfaces of the cutout 30 , and the bottom wall of the cover 31 abuts the flat bottom surface of the cutout 30 . In addition, the circumferential outer wall of the cover 31 is flush with the outer circumferential surface of the outer ring 12 , and the circumferential inner wall of the cover 31 is flush with the 90 ° groove surface 14 a of the outer ring 12 , whereby a reliable rolling action of the roller bearing is ensured.

In Fig. 12, the vertical positional relationship between the two rings 11 and 12 is shown. As seen from Fig. 12, the bottom point of the groove of the rectangular groove 14 is of Au ßenringes 12 downwardly offset from the neutral axis of the outer ring 12 by a small amount x / 2 = (LL ₁₎ / 2, currency rend the bottom point of the The groove of the right-angled groove 13 is offset upwards against the neutral axis of the inner ring 11 by a small amount x / 2. Consequently, the two rings 11 and 12 are axially offset from one another by an offset x, which is the size (LL ₁ ) equivalent. The two set rings 11 and 12 are advantageous to mount the rings 11 and 12 easily on the two links 1 and 5 relatively rotatably to each other. In the preferred embodiment, since the thickness of the inner ring 11 is set to be equal to the thickness of the outer ring 12 , the upper side wall of the outer ring 12 is positioned to be offset x above the upper side wall of the inner ring 11 rend the lower side wall of the inner ring 11 is positioned so that it is around the offset x below the lower tenwand Be the outer ring 12 . The offset x ensures easy attachment of the outer ring 12 to the bottom of the seat 1 without forming a disturbance between the upper side wall of the inner ring 11 and the bottom of the seat 1 , and easy attachment of the inner ring 11 to the bottom plate 5 without one Disturbance between the lower side wall of the outer ring 12 and the bottom plate. Although in the execution form of the outer ring 12 attached to the seat 1 and the inner ring is mounted on the bottom plate 5 11 In nenring 11 may be attached to the seat. 1 In this case, the rotating device shown in FIG. 12 only needs to be inverted so that the lower side wall of each ring 11 and 12 is inverted with the upper side wall of each ring. If it is desired in the inner ring 11 and outer ring 12 , each containing the slightly offset raceways 13 and 14 , that the side walls of the rings 11 and 12 be flush with each other, only one of the two rings needs to be reversed before the rollers 20 and spacers 21 are used in the room 15 .

Although multiple cylindrical solid rollers are used for the roller bearing of the rotating device 10 in the preferred embodiment, the cylindrical solid rollers can be replaced by a plurality of cylindrical hollow rollers, each cylindrical hollow roller having an allowable mechanical strength and wear resistance. In order to self-align the axis of the inner ring 11 with the axis of the outer ring 12 , the roller bearing with the cylindrical rollers 20 can be replaced by a self-aligning roller bearing 100 with a plurality of barrel-shaped rollers 40 , as shown in FIG. 15. In Fig. 15, the total length of the barrel-shaped roller 40 is set to be equal to the outer diameter. The ton-shaped roller 40 has both spherical ends. The self-aligning roller bearing or self-aligning bearing 100 comprises an inner ring 41 and an outer ring 42 which is aligned coaxially on the inner ring 41 . The inner ring 41 is formed with a substantially rectangular annular groove 43 on its outer peripheral surface 41 a, while the outer ring 42 is formed with a substantially rectangular annular groove 44 on its inner peripheral surface 42 a. The two grooves 43 and 44 are radially opposite one another. As can be seen in Fig. 15, the substantially rectangular raceway 43 is defined by an upper spherical surface 43 a with a chord that has an inclination angle of 135 °, and a lower spherical surface 43 b with a chord that has an inclination angle of 45 °, while the substantially rectangular raceway 44 is defined by an upper spherical surface 44 a with a chord that has an inclination angle of 45 °, and a lower spherical surface 44 b with a chord that has an inclination angle of 135 ° has. That is, the substantially rectangular inner groove 43 is obtained by cutting the substantially below 135 ° ste Henden upper spherical surface 43a with the substantially below 45 ° stationary lower spherical surface 43 b at a right angle, while the substantially rectangular externa Outer raceway 44 is obtained by cutting the substantially spherical surface 44 a standing at 45 ° with the lower spherical surface 44 b standing substantially at 135 ° at a right angle. Although not clearly shown in Fig. 15, the two adjacent rollers 40 spaced apart by a spacer are located in the substantially square space defined by the two raceways 43 and 44 so that a roller axis and the other roller axis intersect at a right angle. The substantially below 135 ° upper spherical surface 43 a has the same shape and dimensions as from the substantially below 45 ° lower spherical surface 43 b, while the substantially 45 ° from angled upper spherical surface 44 a the same Shape and dimensions like the angled at 135 ° un tere spherical surface 44 b. As is apparent from Fig. 15, ar up The two mutually facing spherical surfaces 43 a and 44 b together, to act as bearing surfaces or tracks for the inclined at 135 ° barrel-shaped rollers, while the two mutually facing spherical surfaces 43 b and 44 a work together to act as storage areas or raceways for the barrel-shaped rollers inclined at 45 °. In the barrel-shaped roller bearing, the downward load W, which acts on the upper side wall of the outer ring 42, is absorbed by both spherical end faces of the 135 ° roller with line contact. In contrast to the above, the downward load W is acting on the upper side wall of the inner ring 41 acts, through line contact between the substantially spindle-shaped outer peripheral surface of the 135 ° Pulley and the inclined at 135 ° spherical surface 43 a and 44 b added. Since in the ton-shaped roller bearing 100 shown in Fig. 5, the curvature of each spherical end of the roller, the curvature of the barrel-shaped outer circumferential surface of the roller and the respective curvatures of the four spherical surfaces 43 a, 43 b, 44 a and 44 b, which the grooves 43 and 44 define, are identical to each other, the roller bearing 100 can create a desirable self-alignment function.

While the above is a description of what is performed before preferred embodiments of the invention, it is understood that the invention is not described and described here benen particular embodiments is limited, but  that various changes and modifications are made that can without the scope or spirit of the invention to deviate, which is defined by the claims.

Claims (10)

1. rotating device with a roller bearing, with an inner ring and an outer ring, which are arranged coaxially to each other,
a pair of circumferentially extending and radially opposite V-shaped grooves which are continuously formed on the outer circumferential surface of the inner ring or continuously on the inner circumferential surface of the outer ring, each V-shaped groove comprising a pair of circumferentially extending annular surfaces, which cut one another at right angles and have the same dimensions,
and a plurality of rollers which are arranged radially in a circumferentially extending inner space, which is defined by the opposite V-shaped grooves, so that the inner ring and the outer ring are rotatably coupled with each other, characterized in that
that the axis of one of the two adjacent rollers ( 20 , 40 ) intersects the axis of the other roller ( 20 , 40 ) at a right angle, each roller ( 20 , 40 ) being essentially cylindrical and having an overall length equal to the outer diameter,
and that a plurality of spacers ( 21 ) in the circumferential direction along the neutral axis of the inner space ( 15 ) is arranged, each spacer ( 21 ) between the two adjacent rollers ( 20 , 40 ) is arranged so that the two adjacent rollers ( 20 , 40 ) have a predetermined distance from one another. 2. Rotating device according to claim 1, characterized in that a roller axis of the two adjacent rollers ( 29 , 40 ) is inclined at 45 ° to a plane which is perpendicular to the central axis of the rings ( 11 , 12 , 41 , 42 ), to adjust the contact angle of the roller ( 20 , 40 ) to the matching annular surface of the V-shaped running groove ( 13 , 14 ) at 45 °. 3. Rotating device according to one of the preceding claims, characterized in that the roller comprises a substantially cylindrical roller ( 20 ) with two flat end faces and a cylindrical surface, and that the cylindrical roller ( 20 ) is arranged in the interior such that the abut two flat ends on one of two opposite pairs ( 14 a, 13 b) of annular surfaces which define the V-shaped grooves ( 13 , 14 ) and the cylindrical surface of the cylindrical roller ( 20 ) with the other opposite pair ( 13 a, 14 b) fits together. 4. Rotating device according to claim 1 or 2, characterized in that the roller comprises a barrel-shaped roller ( 40 ) with spherical surfaces at both ends and a barrel-shaped outer peripheral surface and the opposite V-shaped grooves ( 43 , 44 ) are defined by four in the circumferential direction spherical surfaces ( 43 a, 43 b, 44 a, 44 b), and that the curvature of each spherical end of the ton-shaped roller ( 40 ), the curvature of the barrel-shaped outer peripheral surface of the roller ( 40 ) and the respective Curvatures of the spherical surfaces ( 43 a, 43 b, 44 a, 44 b), which define the opposite V-shaped grooves ( 43 , 44 ), are identical to one another, around the axes of the two rings ( 41 , 42 ) self-aligning close. 5. Rotary device according to claim 3 or 4, characterized in that one of the circumferential ring-shaped surfaces ( 13 a, 13 b, 14 a, 14 b, 43 a, 43 b, 44 a, 44 b), the one cross others, has the same shape and dimensions as the other annular surface ( 13 a, 13 b, 14 a, 14 b, 43 a, 43 b, 44 a, 44 b). 6. Rotating device according to claim 3 or 4, characterized in that the spacer ( 21 ) has the same shape and dimensions as the roller ( 20 , 40 ). 7. Rotating device according to claim 1, characterized in that the V-shaped groove ( 13 ) formed on the outer circumferential surface of the inner ring ( 11 ) is offset against the neutral axis of the inner ring ( 11 ) in an axial direction of the rings ( 11 , 12 ) and the V-shaped groove ( 14 ) formed on the inner circumferential surface of the outer ring ( 12 ) is set against the neutral axis of the outer ring ( 12 ) in the other axial direction of the rings ( 11 , 12 ), so that a side wall of the inner ring ( 11 ) protrudes above a plane defined by one side wall of the outer ring ( 12 ) and the other side wall of the inner ring ( 11 ) is withdrawn below a plane defined by the other side wall of the outer ring ( 12 ). 8. Rotary device according to claim 1, characterized in that a cut-out portion ( 30 ) on one of the rings ( 11 , 12 ) is formed in such a way that the inner space ( 15 ) is exposed to the roles by the cut-out len ( 20 ) and the spacers ( 21 ) in the inner space ( 15 ), and that a cover ( 31 ) is placed on the cut-out portion ( 30 ) to a portion of the circumferential annular surfaces ( 14 a, 14 b ) to form, which define the V-shaped groove ( 14 ). 9. Rotary device according to claim 8, characterized in that the cut-out section ( 30 ) comprises a bevelled cutout ( 30 ) with a trapezoidal shape and the cover ( 31 ) is trapezoidal to fit in the cutout ( 30 ), and in that the cover ( 31 ) comprises at least one stop pin ( 43 ) and the cut-out portion ( 30 ) comprises a stop pin hole ( 44 ) which is fitted in the stop pin ( 43 ) so as to prevent the cover ( 31 ) from moving in the radial direction of the Rings ( 11 , 12 ) adjusted. 10. Rotary device according to claim 9, characterized in that the thickness of the beveled cover ( 31 ) and the height of the beveled cut-out portion ( 30 ) are set half as wide as the thickness of the ring ( 12 ) having the cutout ( 30 ) , And that the width of the section ( 30 ) is limited to a minimum dimension that is required for inserting a roller ( 20 ) or a spacer ( 21 ) into the inner space ( 15 ).