JPH0366531B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a method of providing two parallel rails, which are spaced apart in the axial direction of the rail and substantially perpendicular to the axis, guided movably along the rail in the axial direction of the rail. a bearing body having an end surface and at least one set of rolling element circuits, each rolling element circuit of the set of rolling element circuits engaging with a loaded rolling surface parallel to the axis of the bearing body; It has one row of rolling elements that transmits a linear load, one row of rolling elements that is returned, and two rows of circular arc rolling elements, and the row of rolling elements that are returned are approximately parallel to the axis of the bearing. The end plate is provided with a deflection surface for the row of arcuate rolling elements, and the end plate is provided with a deflection surface for the row of circular arc rolling elements, which are aligned with each other and at the end. A type of linear motion roller comprising a merging axis-parallel retaining web that keeps the load-transmitting rolling element row engaged with the load-receiving rolling surface of the bearing body. Regarding a bearing device.

BACKGROUND OF THE INVENTION Rolling bearings of the above type with plastic cages (end plates + half-webs) are known. DE 32 27 902 and DE 3 148 331 disclose a linear guide device in which a plastic holder is divided into two parts perpendicular to the axial plane. The device consists of end plates each provided with a ball return notch and having five injection molded retaining webs. Disadvantages of this configuration include the use of multiple retaining webs for guiding the four loaded ball rows, the need for complex and uneconomical injection molding tooling, and the large amount of material required. be. Furthermore, due to the deflection of the balls at the outlet or inlet relative to the adjacent ball track, the bearing body must be heavily rounded or beveled, which results in considerable machining. If this were not done, the load on the supporting ball would be removed or applied rapidly, resulting in extreme edge loads at the end plate transitions, which would impede progress and reduce service life. The maturity period is significantly reduced. Despite the rounding, the arrangement disclosed in German Patent Application No. 32 27 902 does not go far enough. This is because the inner and outer deflection radii do not form concentric semicircles, so the deflected ball is not stable and causes various plays.

In DE 31 48 331 A1, this drawback is largely eliminated. However, the problem here is that the outer curvature continues at the transition of the return hole in the bearing body. This can only be carried out with great difficulty, if not impossibility in terms of manufacturing technology. To enable lubrication of linear bearings, one
Cutting is required to provide one lubrication hole and a plurality of connecting passages (German Patent Application No. 3227902). This requires additional cost and time to manufacture the bearing member. Since no sealing elements are provided, the lubricant is very susceptible to leakage and dirt can penetrate into the bearing element, resulting in a shortened service life.

In DE 32 24 282 A1, in addition to four injection-molded cage retaining webs for the two ball rows, three additional strips are used which are screwed onto the bearing body. ing. This makes the bearing devices even more complex. Other points are West German patent application no.
This corresponds to what has been described in specification No. 3227902.

DE 33 03 831 A1 discloses a ball bearing with two plastic cage halves. In this case too, post-processing on the bearing body and complex injection molding tools are necessary for deflection, and post-lubrication and sealing are not possible. Moreover, the durability of this bearing member is limited. This is because the shaft cannot be consistently supported. Furthermore, this construction is not based on a bearing block that can be screwed directly via a flat support surface, but on a sleeve-like element that is received in the housing bore.

In French Patent No. 2,523,669 a cage is shown for an open rail guide with two rows of balls. This cage is made of metal or plastic and has the characteristics of the cages described above. The ball guides for both the end plates and the rolling surfaces of both cage halves are integral as shown in FIGS. 4 and 5. Ball deflection takes place at the end plate. Post-processing is necessary to achieve a good transition, low wear and quiet operation at the ball inlet or ball outlet. In this case, the West German patent application publication no.
As already mentioned in No. 3,227,902 and No. 3,148,331, nevertheless, sufficient progress is not achieved or the manufacturing of the end region of the outer deflection curvature is extremely difficult in connection with the return hole. Post-lubrication and sealing are also not possible in this case.

However, longitudinal guide bearing members are also known, in which good ball transfer and quiet ball rolling are achieved without the need for extensive post-processing of the rolling surfaces that receive the load of the bearing body. West German Patent Application Publication No.
No. 3005579, No. 1425966, No. 3313129, No. 3304895, and No. 3313575 use a semi-cylindrical deflector whose radius corresponds to 1/2 of the ball diameter. The deflector is arranged in a recess between the end plate and the end face of the bearing body and guides the ball from the inside. The outer ball guide is a known U on the side plate.
This is done by cutting out the glyph. These solutions have structural similarities. That is, the end plate with the ball deflection part and the retaining web are manufactured separately and assembled. This results in a large number of parts, which in turn increases manufacturing and assembly costs, and increases the number of butt points and sources of error.

Problems to be Solved by the Invention The present invention provides a rolling bearing device that is easy to manufacture. In this case, demands for easy manufacture are placed particularly on the bearing body and on the retainer consisting of the end plate and the retaining web.

Means for Solving the Problems The object of the present invention is to provide a bearing body that is movably guided along the rail in the axial direction of the rail and has two end faces spaced apart in the axial direction of the rail and substantially perpendicular to the axis. and at least one set of rolling element circuits, each of the rolling element circuits forming one set being provided axially parallel to a load receiving rolling path and a rail, which are provided axially parallel to the bearing body. It has one linear row of rolling elements that transmits the load, one row of rolling elements that is guided back, and two arcuate rows of rolling elements that are guided back and that engage with the rolling path that receives the load. A row of rolling elements is guided in a substantially axis-parallel return guide passage in the bearing body, and end plates are attached to the end faces of the bearing body, and the deflection surfaces for the arcuate rolling element rows are arranged in an arcuate shape on these end plates. It is provided for the row of rolling elements, and both end plates are integrally constructed with axis-parallel retaining webs that are aligned with each other and butt against each other at their ends, the length of the retaining webs being These retaining webs correspond to 1/2 of the length of the bearing body measured between the end faces of the bearing body, and these retaining webs engage the load-transmitting rolling element row with the load-bearing rolling track in the body in use. In rolling bearings for linear motion of the type in which the rolling bearings are maintained in a fixed state, both rows of rolling elements that transmit the loads of both moving body circuits of the pair each belong to one end plate. Each rolling track in the bearing body is kept engaged by a single common retaining web group consisting of two mutually aligned retaining webs arranged between the rows of rolling elements. is supported on the bearing body by a keyway joint extending in the longitudinal direction of the bearing body, and each arcuate rolling element row is provided on the supporting surface of the associated end plate.
It is guided by an outer deflection surface, i.e. a deflection surface further from the bearing body, and an inner deflection surface, i.e. a deflection surface closer to the bearing body, the inner deflection surface being guided by a deflection member receiving part in the support surface of the end plate. The present invention is solved by forming at least one deflection member received in the deflection member.

In an embodiment of the invention, the cage parts, each consisting of an end plate and a holding web for each of the two rolling element circuits, are manufactured in a simple manner, in particular from plastic by casting or injection molding. In this case machining can be completely avoided or reduced to a minimum.

In order to ensure a satisfactory retention of the rolling elements on the bearing body before assembly of the bearing body with the rail, it has been proposed that the retaining web has a retaining surface for the load-transmitting rolling element array.

In order to secure the retaining web uniquely and immovably relative to the bearing body, it has been proposed to support the retaining web on the bearing body with a keyway joint, in particular with a dovetail or similar joint.

In order to connect the retaining webs belonging to mutually opposite end plates to one another at their abutment points and to ensure exact profile alignment of the retaining webs, the mutually opposite ends of the mutually aligned retaining webs are connected to a bayonet joint or to a bayonet joint. It is proposed to combine similar ones with each other.

In order to make it sufficient to provide only a linear rolling surface and a return passage in the bearing body, the end face of the bearing body should be changed from a straight, load-transmitting rolling element row to an arcuate rolling element row. It is proposed to place it in the transition section. Furthermore, it is advantageous to guide the arcuate rolling body row with an outer deflection surface, ie, remote from the bearing body, and an inner deflection surface, ie close to the bearing body, which are recessed in the support surface of the end plate. in this case,
The inner deflection surface is formed in at least one deflection body received in a deflection body receptacle of the support surface of the end plate.
The perfectly quiet operation of the rolling element circuit
It is obtained by making the arcuate rolling element array follow a semicircle. This means that the outer and inner deflection surfaces must have concentric circular courses.

Reliable lubrication of rolling bearings, which likewise requires only a few auxiliary measures during manufacture, is achieved by providing a lubricant supply trough on the supporting surface of at least one end plate, which The lubricant supply is connected to the lubricant supply and leads to the deflection body receptacle, such that one or both rolling element circuits are supplied with lubricant by a lubricant distribution system located in each deflection body receptacle. It's summery. Starting from the fact that the end plate is cast or injection molded from plastic, the lubricant supply trough can be manufactured in the casting or injection process without special machining. In this case, the lubrication distribution system consists of a longitudinal distribution trough and a transverse hole in the deflection body receptacle on the back side remote from the inner deflection surface of the deflection body, which transverse hole connects the longitudinal distribution trough to each row of arcuate rolling bodies. Connected to the inner deflection surface. This allows the lubricant distribution system to be transferred to the deflection body, which can be produced by injection molding independently of the end plate and without further processing.

Further, the lubricant supply section is provided on the end surface of the end plate extending parallel to the support surface of the end plate, and a lubricant device connected to the lubricant supply section generates a pressing force on the end surface perpendicular to the support surface. It is advantageous to be like this. This results in the support pressure of the device crimping the end plate to the bearing body, preventing extrusion from between the end plate and the bearing body.

The concept of a rolling bearing according to the invention is particularly advantageous when used in rolling bearings in which the bearing body has two sets of rolling element circuits facing each other, and these rolling element circuits receive a rail between them. It is. In this case, a rail profile with an approximately rectangular cross section results. A recess is arranged in the two mutually facing sides, the edges of which are provided with the rolling surfaces of the rails, between which the retaining web is arranged.

In connection with simple manufacturing, it is advantageous if the rolling element circuit is arranged on the U-leg of the bearing body with the advantage that it is arranged parallel to the U-shaped web of the bearing body.

In addition to constructing the bearing body in one piece, it is also possible to provide opposite sets of rolling element circuits in the bearing body part, the spacing of which can be varied. In this way, the bearing body part can be produced as a standard part that can be arranged at different spacings to suit different rail widths. In this case, the bearing body parts are either connected to one another by suitable connections or are attached directly to the individual machine parts to be guided. This arrangement is in principle independent of the construction of the cage part according to the invention.

Furthermore, the rail itself can also be constructed from two profiled parts with a load-bearing rolling surface and at least one intermediate part. This makes it possible to construct rails of different widths from standardized parts that can be produced in large quantities and at low cost.

In order to prevent dirt from entering the area of the metal particle rolling element circuit, for example if the rolling bearing is used for guiding a carriage on a machine tool, it is necessary to Attach the seal plate to the end face opposite to the support body,
Advantageously, the sealing plate has a sealing edge that at least substantially follows the profile of the rail over at least a portion of its outer surface.
Of course, in this case, the sealing edge is constructed so as to be in close contact with the rail profile surface as much as possible. In order to protect the sealing plate, on the one hand, and, on the other hand, not to spoil the favorable appearance of the bearing body and the end plate, the sealing plate can be received in a recess in the end face in alignment with the end face.
This allows the construction length to be reduced compared to designs with end-mounted sealing plates.

From the point of view of simple installation, the sealing plate can be fixed onto the end plate by means of a snap connection. In this case, the snap connection can be constructed in the form of a push-button and can consist, for example, of a C-shaped profile and a raised profile that engage on the inside and the outside.

In order to ensure a more complete sealing of the rolling element circuit against the ingress of dirt, for example through fixed openings in the rail, it is necessary to A parallel sealing strip can be mounted on the load-transmitting rolling element row and can be brought into sliding contact with the rail.

If the cross-section of the bearing body is U-shaped and a load condition is provided in which the web of the U-shaped cross-section tends to move away from the rail, this load condition means an expansion for the U-shaped leg. In order to increase the stability of the U-shaped cross section against such expansion, it is necessary to
The U-shaped leg has a support surface remote from the rail for contacting the mechanical part, and the U-shaped leg is connected to the mechanical part by a pin joint or the like, and the pin joint or the like is connected to the U-shaped leg. Advantageously, it is arranged close to and possibly approximately in the middle of the U-leg. The configuration of the present invention is particularly suitable for arranging the pin joint between the U-shaped legs in this manner. This is because, according to the invention, there is no cage part in the area of the U-shaped web.

This means that the invention has a bearing body and a plastic cage that are easy to manufacture, which plastic cage allows for a smooth running and perfect rolling element deflection with low wear, and at the same time provides a lubricant. A rolling bearing device is provided which ensures the distribution and reception of the sealing element. The entire bearing device is manufactured from a small number of economically producible parts without requiring further machining for the rolling element deflection in the bearing body.

According to a first embodiment, the rolling element circuit is a ball circuit.

In this case, the load-transmitting ball rows of the ball circuits in the set are in contact with the rolling groove of the bearing body on one side of the plane containing the axes of both load-transmitting ball circuits, and on the opposite side of this plane. Advantageously, it is configured such that mutually opposite circumferential areas abut the retaining web and mutually opposite circumferential areas abut the rolling groove of the rail.

For reasons of ease of manufacture, adjacent arcuate ball rows of a pair of ball circuits are assigned a common semi-cylindrical deflection body which is received in a common semi-cylindrical deflection body receiving trough. It is advantageous to have

Furthermore, for quiet operation, it is advantageous if the outer deflection surface and the inner deflection surface form a deflection channel with an approximately constant cross section.

From the perspective of further expanding the support value and moment load, the rolling element circuit is a roller circuit, the rolling element row that transmits the load is a roller row that transmits the load, and the rolling element row that is returned is a roller circuit that is returned. It is advantageous if the row of arcuate rolling elements is a row of arcuate rollers.

The construction of rolling bearings with rollers is usually more convenient than rolling bearings with balls, especially when limited space is available for locating the roller circuit, especially when viewed in cross-section perpendicular to the rail axis. Have difficulty.

A first possibility for roller circuits, which also allows the roller circuits to be arranged in narrow spaces, is to arrange the roller circuits of a set in intersecting planes. In this case, the line of intersection of these planes lies parallel to the axis of the rail. Further, the arcuate roller row rails belonging to the same end plate of the roller circuits forming the set are spaced apart from each other in the axial direction and intersect with each other, and in each roller circuit, the rollers of the roller row that receive the load and the rollers that are returned The rollers in the row and the rollers in the arc roller row are axially parallel to each other.

In order to make the fabrication of the deflection surfaces possible in such an embodiment in a customary technical manner, the deflection surfaces of the intersecting rows of circular arcs must be placed on each end plate and on the deflection body embedded in this end plate, i.e. on the outside. It is advantageous if there is a deflection body located inside, ie close to the bearing body, and an inner deflection body, ie close to the bearing body.

A feature of the advantageous embodiment in this case is that the outer one of the two intersecting rows of arc rollers, i.e. that is farthest from the bearing body, has an outer deflection surface, which deflection surface is located in the recess in the end plate. The inner deflection surface is formed by an outer deflection body and an inner deflection body, and the inner arcuate roller row, that is, closer to the support body, has an outer deflection surface, and this deflection surface is partially It has an inner deflection surface defined by an outer deflection body and partially by a recess in the end plate and an inner deflection body.

In this embodiment as well, lubricant supply can take place via the deflector.

With respect to the unique shape of the two end plates and the associated retaining web, the roller circuits of the pairs have approximately the same length in the axial direction of the rail, one of the roller circuits being different from the other. It is advantageous to form an inner arcuate roller row in the region of one end plate and an outer arcuate roller row in the region of the other end plate.

Another embodiment with rollers is provided in a plane in which the roller circuits of the pair have intersecting lines that are substantially parallel to each other or parallel to the rail axis direction that intersect at an acute angle outside the roller circuits. In each roller circuit, the rollers of the load-transmitting roller bank on the one hand and the rollers of the return roller bank on the other hand are arranged in a mutually inclined plane common to the roller axis, and the rollers of the arc roller bank are It consists of a conical surface arranged along the axis.

In this embodiment, one arcuate roller bank has an outer deflection surface, ie from the bearing body, which deflection surface is formed by a recess in each end plate, and two outer partial deflection surfaces. In other words, it is composed of a first conical partial deflection surface in contact with the outer circumferential surface of the roller and a second outer conical partial deflection surface in contact with the end surface of the roller of each arcuate roller row, and each of the arcuate roller rows has an inner deflection surface, i.e. close to the bearing body, which deflection surface is formed from a deflection body embedded in each end plate, and from the two inner partial deflection surfaces, i.e. the first inner conical It is composed of a partial deflection surface that is in contact with the outer circumferential surface of the roller in the arcuate roller array, and a second inner conical partial deflection surface that is in contact with the other end surface of the roller in the arcuate roller array. There is.

In this embodiment as well, the lubricant supply can take place via the deflection body receptacle or the deflection body itself.

For reasons of simplicity in manufacturing technology, it is advantageous if one common deflection element is assigned to both roller circuits of a set.

In both embodiments of the roller rolling bearing device, the rollers can be rolled individually, so that it is no longer necessary to connect the rollers to one another by chains or belts, as is known, for example, from European Patent No. 138,360. Become. However, it is not excluded to connect the rollers to each other with such chains or with such belts.

Particularly in the last-mentioned embodiment in which the rollers roll via a conical deflection surface and in the range of an arcuate roller bank the spacing between the rollers is given at one end of the rollers, there are no gaps between the rollers. It is advantageous to provide a spacer element of.

The invention will now be explained with reference to the drawings: In FIGS. 1, 2a and 2b the rail guide according to the invention is shown as a bearing unit. 4 ball circuits A, B, C,
The support body 1 has ball rows A1, B1, .
12, D12 to provide a longitudinal movement of the mutually movable parts, even when the bearing body 1 or the rail 2 is loaded with a rotational moment. The returned ball rows A2, B2 are guided by the return holes A21, B21, etc. inside the support body 1, so the four ball circuits A, B,
C and D are ball rows A1 and B1 that transmit the load...
It has arcuate ball rows A3, B3, . . . that connect the returned ball rows A2, B2, . The two ball circuits A, B; C, D are each located in a plane perpendicular to the plane of symmetry S--S of the bearing unit.

The support body 1 is fixed by means of a pin joint having a through hole 15. The through hole 15 has a plane of symmetry S
- in the outer region of the bearing body 1 with respect to S and in this plane of symmetry S-S, i.e. 15a
It is located where indicated. In other embodiments (second
(Fig. c, Fig. 2d), screw holes 16, 16a may be provided instead of the through hole 15a. The central fixability of the bearing body prevents the bearing body from deflecting under lateral displacing loads and thus increases the rigidity of the bearing unit. The rail 2 is screwed to the base body through a central hole 17.

3 and 4 are a view from inside and a sectional view of a plastic cage divided into two parts in a plane perpendicular to the axis. The cage comprises an end plate 1 having a support surface 19 and two axially extending retaining webs 20a, 20b.
It consists of 8. The holding webs 20a, 20b are constructed integrally with the end plate 18 and guide the load-transmitting ball rows A1, B1 in the bearing body 1 during the course of the movement, that is, via the holding grooves A14, B14... This is useful for holding the rolling grooves A11 and B11 of No. 1. Moreover, this means that the ball rows that transmit the load are in the rolling grooves A12 and B1 that receive the load of the rail 2.
This is done before the assembly of the bearing body and the rail 2, which are brought into engagement with the rail 2. For this purpose, rolling grooves and holding grooves A11, B11..., A12, B12..., A
Ball rows A1, B1... in contact with 14, B14...
See FIG. 2e, where the outer circumferential range of... is designated by α, γ or β. The sum of angles α+β is
Greater than 180°.

This ensures that the ball is held in the bearing body even outside the rail. In order to avoid boring friction, the contact between the ball and the bearing body is interrupted in region 1 by a small recess. The friction of the balls on the retaining webs 20a, 20b is interrupted by a suitable play in the range β after assembly with the rails. An outer deflection surface 22a is formed. The end plate 18 is arranged in a recess forming the end face 1d of the bearing body. Furthermore, a semi-cylindrical deflector receiving groove 25 is present in the end plate. A suitable semi-cylindrical deflector 36 is positioned within this deflector receiving groove 25 during assembly. As an extension of the deflector receiving groove 25, a lubricant supply groove 26 with a semi-cylindrical cross section extends to the plane of symmetry S--S of the end plate 18. Lubricant is supplied to the four ball circuits A, B, C, D via lubricating holes 27 with threaded connections in this plane of symmetry S--S. Plastic retainer halves 18, 20a, 2
The fixing of 0b to the bearing body 1 of the bearing device takes place via two holes 27a in the end plate 18.

Cutout 28 allows integration of sealing plate 29. Fixing of the sealing plate 29 takes place via a number of snap connections 30, 39 (fourth
(Fig. 7, Fig. 12, Fig. 13).

A sealing plate 29 integrated into the plastic holder prevents the ingress of dirt with a sealing edge 29a that follows the profile of the rail 2. additionally provided sealing strips 40, 41 which are attached to the bearing body 1 and the end plate 18 directly above (40) or directly below (41) the load-transmitting ball rows A1, B1 and which extend up to the sealing plate 29; It is ensured that dirt, which may have entered the bearing device through the rail holes 17, does not reach the contact zone with the ball or the rail 2. This allows an almost air-tight sealing of the rolling area.

FIG. 5 shows a notch 28 for receiving a seal plate 29, and FIGS.
In the figure and FIG. 13, the snap coupling member 3
Positions 0,39 are shown.

FIG. 6 shows the retaining web 20b of FIG. 3 on an enlarged scale. Ball row A that transmits the load
1 and B1, holding grooves A14 and B14 matched to the diameter of the sphere are integrally molded on the holding web 20b. The retaining web 20 is reinforced over its entire length by keys 32b which engage in corresponding grooves 32a in the bearing body to prevent bending.
Additionally, the two cage halves are connected to each other by a pin 33a inserted into a hole 33b.

FIG. 7 shows the structure of the C-shaped molded portion 30 of the snap connection that fixes the seal plate 29 to the end plate 18. Two arcuate tongues 3
4 forms a C-shaped molded part together with the recess 35. A raised molding 39 (FIG. 13) molded into the seal plate 29 is snapped onto the C-shaped molding by bending apart the resilient tongue 34.

In FIG. 8, a cross section taken along the - line in FIG. 3 is shown. The symmetrical lubricant supply groove 26 (see FIG. 3), which is U-shaped in its course, has a semi-cylindrical cross section.

The semi-cylindrical deflection body 36 shown in FIGS. 9, 9a, 10, 10a and 11 has a lubricant supply groove having the aforementioned semi-cylindrical cross section in the flat back surface 36b. It has a vertical distribution groove 26a as an extension of 26. Two horizontal holes 37 in the deflector 26 connect the vertical distribution groove 26a to the arc ball rows A3, B3. This horizontal hole 37 passes through an inner deflection surface 36a integrally formed on the deflection body 36. The inner deflection surface 36a serves to guide the arcuate ball rows A3 and B3 inward, thereby achieving quiet ball rolling.

From Figure 9, Figures 10, 10a and 11
It can be seen that the center points of the horizontal holes 37 of the deflector 36 on the inner side of the figure are not located at the center of both notches 22, but are located closer to each other. The reason for this is that it is desired that the horizontal hole 37 not impede the rolling of the ball within the range of the inner deflection surface 36a. In order to achieve the same effect, it is of course possible to widen the distance between the center points of the horizontal holes 37.

12 and 13 show the outer and inner shapes of the seal plate 29 and the shape of the seal lip 29a. The sealing plate 29 is fixed by a snap connection. This snap connection connects the seal plate 29 to the plastic retainer halves 18,
20a and 20b. Seal plate 2
9 is made of a relatively soft plastic or rubber material.

FIG. 14 shows an expansion of the possibilities for using rolling bearings. For example, it is advantageous for the intended use to divide the bearing body in order to make it possible to assemble wide rails. Due to the location of the ball circuit and the resulting cage structure having only one set of retaining webs 20a, 20b aligned with each other for the two rows of balls transmitting the load, the bearing It becomes possible to divide the body and the cage along the plane of symmetry S--S with relatively little outlay. In this case, only the lubricant supply device needs to be changed so that the two bearing body parts 40a, 40b resulting from the split are lubricated separately. rail 2
If the rail 2 is also divided into two profiled parts 42a and 42b and possibly an intermediate part 42c, the range of use of the bearing device is further expanded. As a result, it is possible in principle to construct a longitudinal guide device having an arbitrary width. Intermediate member 42c is given appropriate dimensions.

Furthermore, it can be seen from FIG. 5 that the lubricant connection portion 27 of the end plate is provided on the end surface 19a of the end plate.
When a lubricant press is installed to press lubricant into the lubricant supply device 26, the lubricant press is attached to the end plate 1.
8 is balanced by the force produced by the pressure of the lubricant in the lubricant supply groove 26. This prevents the plastic end plate 18 from moving away from the end face 1d of the bearing body 1 in contact with the end plate 18. As a result, the lubricant is prevented from seeping out from between the end face 1d and the end face 19 of the end plate 18, and giving the impression that all the parts of the rolling bearing device to be lubricated are already sufficiently lubricated. Ru.

15 to 22 show embodiments with rollers. Identical parts are numbered by adding 100 to the numbers used in FIGS. 1 to 14.

In FIG. 15, the end plate 118 is shown with a support surface 19 facing the bearing body (not shown) and having a lubricant supply groove 126. Two sets of roller circuits are shown on each side of the rail (not shown). In this case, only the left half of FIG. 15, in which roller circuits A and B are shown, will be described. Roller circuits A and B are arranged in mutually intersecting planes 145 and 146. This plane 1
45, 146 intersect with a rail (not shown) at an intersection line E, which is parallel to the longitudinal axis of the bearing body. The roller rows that transmit the load are marked A1 and B.
1 and the returned roller rows are referenced B2 and A2.
It is shown in Roller row A1 that transmits the load,
B1 is the rolling surface B12, A1 that receives the load from the rail.
2. Returned roller rows A2 and B
2 are return passages A21 and B21 with square cross sections;
You will be guided to As can be seen from FIGS. 17 and 18, the arcuate roller rows B3 and A3 are offset in the axial direction of the rail and intersect at the top. The arc roller row B3 far from the bearing body is shown as the outer arc roller row, and the arc roller row A3 closer to the support body is shown as the inner arc roller row.
The outer circular arc roller row B3 has an outer deflection surface 147 formed by a recess 148 in the end plate 118.
have. Furthermore, the outer arcuate roller row B3 has an inner deflection surface 149, and this inner deflection surface 1
49 is partly formed by an outer deflector 150, namely in the part marked 149a, and partly by an inner deflector 151, namely in the part marked 149b. has been done. The inner circular arc roller row A3 is the outer deflection surface 1
25, this deflection surface 125 is partly formed by the outer deflection body 150, namely in the part designated by 152a, and partly by a recess, namely in the part designated by 152b. 148. Further inside arc roller row A
3 has an inner deflection surface 153 formed by an inner deflection body 151.

The deflection bodies 150 and 151 are butted against each other in the recess 148, and the partial range 149a of the inner deflection surface 149 of the outer arc roller row B3 is the same as the partial range 149a of the deflection surface 149 of the outer arc roller row B3.
b, and the partial range 152a of the outer deflection surface 152 of the inner circular arc roller row is connected to the partial range 152b of the outer deflection surface 152 of the inner circular arc roller row A3.
It is arranged so that it is connected to.

As can be seen from FIGS. 17 and 18, the inner deflector 151 has a back surface 151b flush with the support surface 119 of the end plate 118. A vertical distribution groove 126a is formed in the back surface 151b of the inner deflection body 151, which is connected to the lubricant supply groove 126 and connected to the inner arcuate roller row A3 through a horizontal hole 137.

The end plate 118 has retaining webs 120b and 120a.
are integrally molded, and these retaining webs 12
0b and 120a keep the load-transmitting roller arrays A1 and B1 engaged with rolling surfaces (not shown) of the bearing body.

Since the end plates 118 at both ends of the bearing body are assumed to be identical, only one mold needs to be used to fabricate the end plates. This is in relation to Figures 15, 17, and 18,
The arc roller row A3 belonging to the roller circuit A1 of the facing end plate is the outer arc roller row, and the arc roller row B3 of the roller circuit B1 belonging to the facing end plate is the inner arc roller row. It means that. In this type, the lengths of roller circuits A and B are equal and the shapes of both end plates are the same. Additionally, this ensures that each roller circuit A and B is lubricated as shown in FIGS. 17 and 18.

Furthermore, FIG. 22 shows how projections 154 on the end plate or bearing body prevent the loaded roller arrays A1 and B1 from falling off. Corresponding projections can also be provided on the holding webs 120a, 120b. The retaining webs 120a, 120b are attached to the end plate 118.
Since it can likewise be made of a relatively soft-elastic material, it is simply possible to bring the rollers beyond the projections 154 into a working position in the roller rows A1, B1 which transmit the load. The rollers are preferably arranged on the separating sides of the two holding webs 120a. In this case, during assembly the two cage halves 118 are spread out in accordance with the roller diameter. This assembly possibility is also available in other embodiments, embodiments with balls.

All other structural features, in particular those relating to the sealing plates and sealing strips, are shown in FIGS.
4 is given in the same way as the embodiments up to Figure 4.

Linear bearings using rollers have the advantage of being able to support larger loads. The rollers can be configured as cylindrical rollers, as shown in FIGS. 15 to 21.
However, this roller can also be designed as a barrel-shaped roller, that is to say a roller with a medium height, or with a very small diameter, like a needle.

The embodiment according to FIGS. 15 to 21 has the advantage that both roller circuits A and B can be arranged in a relatively small space, as shown in FIG. However, one has to accept the disadvantage that the two roller circuits are offset relative to each other in the longitudinal direction of the rail. However, this disadvantage results in only a relatively small lengthening of the bearing device. The service life of the bearing device remains unchanged in practice even with respect to torques.

In FIGS. 23 to 27 a further embodiment with rollers is shown. Similar components are designated by the reference numerals in FIGS. 1 through 14 plus 200.

In the embodiment of FIG. 23, the roller circuits A, B with the loaded roller rows A1, B1 and the returned roller rows A2, B2 are arranged in mutually parallel planes F, G. The planes F, G are inclined at acute angles to each other, and the roller circuits A,
It may be crossed outside B.

Roller rows A1 and B1 that transmit the load roll on rolling surfaces A12 and B12 of rails (not shown). The roller rows A2, B2 to be returned are guided in return passages A21, B21 of the bearing body. The return passages A21, B21 are not shown in FIG. 23 and extend upward perpendicularly to the drawing plane. A recess 248 is formed in the end plate 218, and the recess 248 forms a deflection surface. The outer deflection surface 255 has two outer partial deflection surfaces 255a.
and 255b. Both partial deflection surfaces 255a, 255b are conical about axis H. Along the partial deflection surface 255a, the rollers of the arcuate roller array A3 roll in a circumferential range. The end surfaces of the rollers of the arcuate roller array A3 slide along the partial deflection surface 255b. A deflection body 256 having an inner deflection surface 257 is embedded in the recess 248 . The inner deflection surface 257 is composed of partial deflection surfaces 257a and 257b. That is, while the partial deflection surface 257a serves for rolling the circumferential surface of the rollers of the arcuate roller row A3, the partial deflection surface 257a
Partial deflection surfaces 257a and 257b with which the other end surface of the roller contacts 57b are also conical surfaces centered on the axis H.

The back surface 219 of the deflector 256 is flush with the support surface 219 of the end plate 218 . This back 258
A vertical distribution groove 226a is formed therein. This vertical distribution groove 226a is connected to a lubricant supply groove in the end plate 218. A horizontal hole 237 communicates with the inner deflection surface 257 from the vertical distribution groove 226a.

The deflection body 256 has inner deflection surfaces for the arcuate roller rows A3 and B3 of both roller circuits A and B.

This embodiment, like the embodiments shown in FIGS. 15 to 21, allows both roller circuits A, B to be arranged in a small space as shown in FIG. It has the advantage of There is no need for the arcuate roller rows to intersect. The lengths of both roller circuits A, B in the bearing body and in the end plate are the same. The difficulties caused by guiding the arcuate roller arrays A3 and B3 with mutually inclined roller axes are due to the above-mentioned configuration of the deflection surfaces, especially when the deflection bodies and end plates have poor sliding properties. If it is made of good plastic it will be easily removed.

A spacer member 270 may be provided between successive rollers as shown in FIGS. 28 and 29. These spacer members 270
has a double trapezoidal configuration when viewed in a plane determined by the axes of two successive rollers, and has a circumferential groove for receiving the successive rollers, as shown in the enlarged view of FIG. It has 271.
This spacer member significantly improves the rolling condition of the rollers in the arcuate roller row.

Advantageously, the loaded roller arrays A1 and B1 are secured in a manner similar to that illustrated by the projections 154 in FIG.

Additionally, retaining webs 220a and 220b may also be integrally molded onto end plate 218 in this embodiment. Both end plates 218 can have the same shape.

Additionally, in this embodiment, the retaining webs are configured separately from the end plates, and the retaining webs are arranged separately from the end plates to form the retainer.
Two components can be used: two end plates and two retaining webs. In this case, it is advantageous if the holding web engages at both ends in the end plate and is held there, preferably non-rotatably.

[Brief explanation of drawings]

The drawings show a plurality of embodiments of the present invention, in which Fig. 1 is an overall view of the rolling bearing device of the invention, and Fig. 2a is a half-sectional view of the rail guide device in which the retaining web is incorporated. 2b is a side view of the rail guiding device; FIG. 2c is an end view corresponding to FIG. 2a of another embodiment of the invention; FIG. 2d is a diagram 2b of another embodiment of the invention. 2e is an enlarged view of the ball row that transmits the load, FIG. 3 is a view of the end plate seen from inside, FIG. 4 is a sectional view taken along the - line in FIG. Fig. 5 is an external view of the end plate, Fig. 6 is an enlarged view of the retaining web shown in Fig. 3, Fig. 7 is an enlarged view of the snap connection indicated by the symbol in Fig. 4, and Fig. 8 is an enlarged view of the retaining web shown in Fig. 4. Figure 3 is a cross-sectional view taken along the - line, Figure 9 is a view showing the built-in deflector, Figure 9a is a cross-sectional view taken along line a-a in Figure 9, and Figure 10 is a semi-cylindrical shape. Figure 10a is a side view of the flat side of the deflector of Figure 10.
11 is a plan view of the deflector shown in FIG. 10, FIG. 12 is a view of the seal plate seen from the outside, and FIG. 13 is a sectional view taken along X-X in FIG. 12. , FIG. 14 is a view showing a modified embodiment of the bearing member, FIG. 15 is a view showing the supporting surface of the end plate of the bearing device having intersecting roller circuits, and FIG.
Figure 6 is a sectional view taken along - in Figure 15, Figure 17 is a sectional view taken along line XX in Figure 15,
Fig. 18 is a sectional view taken along line X-X in Fig. 15, Fig. 19 is a view showing the inner and outer deflectors of the embodiments from Fig. 15 to Fig. 18, and Fig. 20 is a diagram showing the inner and outer deflectors. Diagram showing the outer deflector rotated 90 degrees,
21 is a perspective view of FIGS. 19 and 20, FIG. 22 shows a modified embodiment of the embodiment shown in FIG. 15 with securing elements for the rollers, and FIG. 23 shows a modified embodiment of the embodiment shown in FIG. FIG. 24 is a diagram showing the support surface of the end plate of another embodiment of the present invention, and FIG.
25 is a perspective view of the deflector shown in FIG. 23, and FIG. 26 is a cross-sectional view taken along line XX.
View from the direction, Figure 27 is Figure 25 XX
28 is a diagram showing a spacer member between consecutive rollers in an arcuate roller row, and FIG. 29 is a diagram showing a spacer member between consecutive rollers in a roller row that transmits a load or a roller row that is returned. It is a figure showing a member. DESCRIPTION OF SYMBOLS 1... Bearing body, 2... Rail, 18... End plate, 20... Holding web, 29... Seal plate, 36... Deflection body, 118... End plate, 150...
... Deflection body, 151 ... Deflection body, 218 ... End plate,
256...Deflector.

Claims (1)

[Scope of Claims] 1. A support body 1 that is movably guided along the rail 2 in the axial direction of the rail 2 and has two end surfaces 1d spaced apart from each other in the axial direction of the rail 2 and substantially orthogonal to the axis. and at least one set of rolling element circuits A and B, each of which forms one set of rolling element circuits A and B, which is provided parallel to the axis of the support body 1 and receives a load, rolling paths A11 and B11. and a rolling path A that receives a load and is provided parallel to the axis of the rail 2.
12, B12, one linear rolling element row A1, B2 that transmits the load, one rolling element row A2, B2 that is guided back, and two circular arc rolling element rows A3, B3. The rolling element rows A2 and B2 to be returned are guided to return guide passages A21 and B21 in the support body 1 which are substantially parallel to the axis, and an end plate 18 is attached to the end surface 1d of the support body 1. , these end plates 18 are provided with circular arc rolling element rows A3 and B3.
The deflection surfaces 22a and 36a for the circular arc rolling element row A
3, provided for B3, both end plates 1
8, axis-parallel retaining webs 20a, 20 in mutually aligned positions and abutting each other at their ends;
b are integrally constructed, and holding webs 20a,
The length of 20b corresponds to 1/2 of the length of the bearing body 1 measured between the end faces 1d of the bearing body 1, and these holding webs 20a and 20b support the rolling element row that transmits the load. In a rolling bearing device for linear motion of the type in which the rolling bearings are kept engaged with the rolling paths A11 and B11 that receive loads in the main body 1, both of the rolling element circuits A and B forming the pair transmit the loads. The rolling element rows A1, B1 each belong to one end plate 18, and the only common holding web consists of two mutually aligned holding webs 20a, 20b arranged between the load-transmitting rolling element rows. The retaining webs 20a and 20b are held in the bearing body 1 by keyway joints extending in the longitudinal direction of the bearing body 1. and each circular arc rolling element row A3, B3
is provided on the support surface 19 of the end plate 18 to which it belongs: an outer deflection surface 22a, i.e. a deflection surface 22a remote from the bearing body 1, and an inner deflection surface 36a, i.e. the deflection surface 36a closer to the bearing body 1. for linear motion, characterized in that the inner deflection surface 36a is formed on at least one deflection member 36 received in the deflection member receptacle 25 on the support surface 19 of the end plate 18. Kotori bearing device. 2 Holding paths A14, B14 for rolling element rows A1, B1 to which the holding webs 20a, 20d transmit loads
A rolling bearing device according to claim 1, having: 3. The rolling bearing device according to claim 1 or 2, wherein the holding webs 20a, 20b are supported on the support body 1 by dovetail-shaped or similar keyway joints. 4. According to one of the claims 1 to 3, the mutually opposing ends of the mutually aligned retaining webs 20a, 20b are connected to each other by means of a bayonet joint or the like. bearing device. 5. The rolling bearing device according to any one of claims 1 to 4, wherein the deflecting member receiving portion 25 in the end plate 18 is configured in a semi-cylindrical shape. 6. The arc rolling element array A3, B3 according to any one of claims 1 to 5, wherein the arcuate rolling element rows A3 and B3 extend approximately along a semicircle over at least a portion of their length. Rolling bearing device. 7 A lubricant supply trough 26 is provided on the support surface 19 of at least one end plate 18 , which lubricant supply trough 26 is connected to the lubricant supply 27 of the end plate 18 and is connected to the deflection body receiver 25 . I understand,
Lubricant distribution system 26 inside the deflector receiver 25
Rolling bearing device according to claim 5 or 6, characterized in that lubricant is supplied to at least one rolling element circuit A, B via a, 37. 8 The lubricant supply section 27 is attached to the end plate end surface 19a of the end plate 18 parallel to the support surface 19, and the lubricant device connected to the lubricant supply section 27 is mounted perpendicular to the support surface 19. 8. Rolling bearing device according to claim 7, which generates a pressing force on the end plate 18. 9 The lubricant distribution system 26a, 37 has a vertical distribution trough 26a and a horizontal hole 37 on the back surface 36b on the inner side of the deflection body 36, opposite to the deflection surface 36a, and the horizontal hole 37 connects the vertical distribution trough 26a with each circular arc. Rolling element row A
3. The rolling bearing device according to claim 7 or 8, which is connected to the inner deflection surface 36a of B3. 10. The rolling bearing device according to claim 9, wherein the opening of the lateral hole 37 to the inner deflection surface 36a is performed at a location that is not important for guiding the rolling elements. 11 A patent in which the bearing body 1 has two sets of rolling element circuits A, B, C, and D facing each other, and these rolling element circuits A, B, C, and D receive a rail 2 between them. Claims 1 to 10
The rolling bearing device described in any one of the preceding paragraphs. 12. The bearing body 1 surrounds the rail 2 in a U-shape, and the rolling element circuits A, B, C, D are arranged on the U-shaped legs 1a of the bearing body 1, as claimed in claim 11. Rolling bearing device. 13 The rolling element circuits A, B, C, and D in the U-shaped leg 1b of the bearing body 1 are the U-shaped leg 1 of the bearing body 1.
13. Rolling bearing device according to claim 12, which is arranged parallel to b. 14. A patent claim in which mutually facing sets A, B, C, D of rolling element circuits A, B, C, D are arranged in parts 40a, 40b of the bearing body 1, the mutual spacing between them being variable. The rolling bearing device according to any one of items 11 to 13. 15 Rail 2 has a rolling surface that receives a load 2
15. Rolling bearing device according to claim 11, characterized in that it consists of two molded parts 42a, 42b and at least one intermediate part 42c. 16 A sealing plate 29 is attached to the end face 19a of the end plate 18 opposite to the bearing body 1, and this sealing plate 29 is attached to the profile of the rail 2 at least substantially over a portion of the outer surface of the rail 2. 16. Rolling bearing device according to claim 1, characterized in that it has a trailing sealing edge 29a. 17. The rolling bearing device according to claim 16, wherein the seal plate 29 is arranged in the notch 28 of the end surface 19a so as to be substantially flush with the end surface 19a. 18. Rolling bearing device according to claim 16 or 17, in which the sealing plate 29 is fixed to the end plate 18 by snap connections 30, 29. 19 A C-forming part 30 and a raised molding part 39 in which push-button-like snap connections engage each other inwardly and outwardly.
A rolling bearing device according to claim 18, comprising: 20 In the bearing body 1 and possibly the end plate 18, on both sides of the rolling element rows A1, B1 that transmit the load of a pair of rolling element circuits A, B, with respect to the rolling element rows A1, B1. parallel sealing strips 40,4
1 are installed and these sealing strips 4
The rolling bearing device according to any one of claims 1 to 19, wherein 0 and 41 are in contact with the rail 2. 21 The U-shaped web 1b of the bearing body 1 has a support surface 1c remote from the rail for contacting the bearing body 1 with the mechanical part, and the U-shaped web 1b is connected to the mechanical part with a pin joint 15 or the like. and this pin joint or something similar is placed near the U-leg 1a, and in some cases a pin joint 15 placed in the middle of the U-leg 1a.
The rolling bearing device according to claim 12 or 13, in which a is used. 22 Looking at the cross section perpendicular to the axis of the rail 2, the rolling paths A12 and B that receive the load of the rail 2
22. A rolling bearing device according to any one of claims 1 to 21, wherein the bearing member 12 is expanded toward the bearing body 1. 23 The rolling element circuit is ball circuit A,
In B, the linear rolling element row that transmits the load is the ball row A1, B1, the rolling element row that is guided back is the ball row that is guided back, and the arcuate rolling element row is the arcuate ball row A3. , B3, and the rolling paths A11 and B11 of the support body 1 and the rolling path A of the rail 2.
12, B12 and the holding paths A14, B14 of the holding webs 20a, 20b are configured as rolling grooves or holding grooves.
The rolling bearing device described in any one of items up to item 2. 24 Ball rows A1, B1 transmitting the loads of a pair of ball circuits A, B are connected to both ball rows A1, B1 transmitting the loads of the ball circuits A, B.
Contacting the rolling grooves A11, B11 of the support body 1 on one side of the plane PP including the axes A13, B13 of B1,
The rolling groove A1 of the rail 2 is in contact with the holding webs 20a, 20b in the outer circumferential range β facing each other on the opposite side of this plane P-P, and in the outer circumferential range γ separated from each other.
2, Claim 23 bordering on B12
Rolling bearing device as described in section. 25 A common semi-cylindrical deflection body 36 is assigned to the adjacent arcuate ball rows A3 and B3 of a pair of ball circuits A and B, and this deflection body 36
25. Rolling bearing device according to claim 23 or claim 24, wherein the deflector receiving grooves are received in a common semi-cylindrical deflector receiving groove. 26 Outer deflection surface 22a and inner deflection surface 36a
26. Rolling bearing device according to claim 23, characterized in that the deflection channels and the deflection passages have a substantially constant cross section. 27. Any one of claims 23 to 26, wherein the opening of the horizontal hole 37 relative to the inner deflection surface 36a is shifted with respect to a plane containing the ball center point of each arcuate ball row. Rolling bearing device. 28 The rolling element circuit is roller circuit A,
In B, the rolling element row that transmits the load is the roller row A1, B1 that transmits the load, and the rolling element row that is guided back is the roller row A2, B2 that is guided back.
, and the arc rolling element rows are arc roller rows A3 and B3.
A rolling bearing device according to any one of claims 1 to 22. 29 A pair of roller circuits A and B are arranged on intersecting planes 145 and 146, and an intersecting line E is located on these planes 145 and 146 parallel to the axis of the rail, and belong to the same end plate 118. Roller circuits A and B intersect with each other at intervals in the axial direction of the rail, and the rollers of the roller rows A2 and B2 that receive the load, the rollers of the roller rows A2 and B2 that are guided back, and the arc rollers. Column A3, B3
29. A rolling bearing device according to claim 28, wherein the rollers are axially parallel to each other in each roller circuit A, B. 30 The deflection surfaces 147, 149, 152, 153 of the intersecting circular arc roller rows B3, A3 are each end plate 118
A deflector 150 embedded in this end plate 118,
29. Rolling bearing device according to claim 29, characterized in that it is configured with an outer deflection body 150, ie remote from the bearing body, and an inner deflection body 151, ie close to the bearing body. 31 Of the two intersecting arc roller rows B3 and A3, the outer arc roller row B3 that is far from the support body
is an outer deflection surface 147 configured in the recess 148 of the end plate 118, and an inner deflection surface 149 composed of an outer deflection body 150 and an inner deflection body 151.
and a circular arc roller row A close to the inner support body.
3 has an outer deflection surface 152 formed partly by the outer deflection body 150 and partly by the recess 148 of the end plate 118 and an inner deflection surface formed from the inner deflection body 151. 153,
A rolling bearing device according to claim 30. 32 The inner deflection body 151 has a longitudinal distribution groove 126a for the lubricant on its back side 151b facing the bearing body, which longitudinal distribution groove 126a is connected to the lubricant supply trough 126 and the inner deflection body 151 has a longitudinal distribution groove 126a for the lubricant. The inner circular arc roller row A3 is
32. The rolling bearing device according to claim 31, wherein the rolling bearing device is connected to an inner deflection surface 153 of the roller. 33 The roller circuits A and B forming a pair have approximately the same length in the axial direction of the rail, and in this case, one of the roller circuits A and B has an inner arcuate roller row A3 within the range of one end plate 118. 33. Rolling bearing device according to one of claims 29 to 32, characterized in that it forms an outer arcuate roller row in the area of the other end plate (118). 34. Both end plates 118 with deflectors 150, 151 and associated holding webs 120a, 120b
have substantially the same shape.
The rolling bearing device described in Section 3. 35 Planes F and G in which a pair of roller supports A and B intersect with planes A and B that are substantially parallel to each other or at an acute angle outside the roller supports A and B at an intersecting line that is parallel to the axis of the rail. placed in
In each roller stack A, B, the roller axes of the rollers in the roller rows A1, B1 that transmit the load and the roller axes of the rollers in the roller rows A2, B2 that return the load are arranged in a common plane inclined to each other, and the arcuate rollers 29. The rolling bearing device according to claim 28, wherein the roller shafts of rows A3 and B3 are arranged on a conical surface. 36 The arcuate roller array A3 has a remote outer deflection surface 255 on the bearing body, which deflection surface 255 is formed by a recess 248 in each end plate 218;
two partial deflection surfaces 255a, 255b, a first outer conical partial deflection surface 255a in contact with the outer circumferential surface of the roller of the arcuate roller array A3 and a second outer conical partial deflection surface 255 in contact with the end surface of the roller.
Each arc roller row A3 has an inner deflection surface 257 close to the support body, and this deflection surface 257 is formed on a deflection body 256 disposed in a recessed manner in each end plate 218. and two inner partial deflection surfaces 257a, 257b, that is, a first inner conical partial deflection surface 257a that is in contact with the outer circumferential surface of the rollers of the arcuate roller row A3 and an arcuate roller row A3.
36. Rolling bearing device according to claim 35, comprising a second inner conical partial deflection surface 257b in contact with the end face of the roller. 37 Deflection body 256 supports support surface 21 of each end plate 218
37. Rolling bearing device according to claim 36, having a back surface 258 aligned with 9. 38 Patent, in which a longitudinal distribution trough 226a is configured on the rear surface 258, which is connected to the lubricant supply trough 226 and to the inner deflection surface 257 by a transverse hole 237 passing through the deflection body 256. A rolling bearing device according to claim 37. 39. Rolling bearing device according to any one of claims 36 to 38, in which a common deflection body 256 is assigned to both roller circuits A, B of the pair. 40. Rolling bearing device according to any one of claims 28 to 39, wherein the roller is configured as a cylindrical roller. 41. Rolling bearing device according to any one of claims 28 to 39, wherein the rollers are constructed as barrel-shaped rollers. 42. Rolling bearing device according to one of the claims 28 to 39, characterized in that the rollers are constructed as cylindrical needles. 43. Rolling bearing device according to any one of claims 28 to 42, wherein the roller circuit consists of loosely continuous rollers, the rollers being not connected to each other. 44 Claim 2, in which a loose spacing member 270 is arranged between successive rollers.
The rolling bearing device according to any one of paragraphs 8 to 42. 45 The spacer member 270 has an approximately double trapezoidal shape when viewed in a direction perpendicular to the plane defined by the axes of two successive rollers, and is provided with a groove 271 on the side facing the rollers; Groove 271
45. Rolling bearing device according to claim 44, wherein the length of parallel to the roller axis corresponds approximately to the roller length. 46. Rolling bearing device according to one of the claims 28 to 45, characterized in that the arcuate roller arrays A3, B3 are guided by deflection paths with a substantially constant cross section.