JPS62196421A - Roller bearing device for linear motion - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to two parallel rails, which are guided movably along the rail in the axial direction of the rail, spaced apart in the axial direction of the rail, and substantially perpendicular to the axis. a bearing body having an end;
at least one set of rolling element circuits, each rolling element circuit of the set of rolling element circuits transmitting a linear load that engages a loaded rolling surface parallel to the axis of the bearing body. It has one row of rolling elements, one row of rolling elements to be returned, and two rows of arcuate rolling elements, and further the row of rolling elements to be returned is guided by a substantially axis-parallel return path in the bearing. , furthermore, an end plate is attached to the end, which end plate is provided with a deflection surface for the arcuate rolling element array, and further comprises axis-parallel retaining webs on the end plate that are aligned with each other and join together at the end. The present invention relates to a rolling bearing for linear motion of the type in which the retaining webs keep the load-transmitting rolling element rows engaged with the loaded rolling surfaces of the bearing body.

BACKGROUND OF THE INVENTION Rolling bearing devices of the type described above 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 case a plastic holder consisting of two parts is divided perpendicularly to the axial plane. The device consists of end plates each provided with a ball return notch and having five injection molded retaining webs. The disadvantages of this arrangement are that a large number of retaining webs are used to guide the four loaded hole rows, that complicated and uneconomical injection molding tooling is required, and that a large amount of material is required. . Further adjacent s,%
- Due to the deflection of the seal at the outlet or inlet to the wheel rolling path, the bearing body must be heavily rounded or beveled, resulting in the necessity of considerable machining. If this is not done, the load on the supporting zeal will be suddenly removed or applied, resulting in extreme edge loads at the transition of the end plate, which will impede progress and shorten the service life. Be significantly reduced. Despite the rounding, the arrangement disclosed in German Patent Application No. 32 279'02 is not sufficient. This is because the inner and outer deflection radii do not form concentric semicircles, so the deflected gel 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 the linear guide, machining is required in the bearing body by providing a lubrication hole and a plurality of connecting channels (DE 32 27 902). 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 Φ injection-molded cage retaining webs for the two seel rows, three additional strips are used which are screwed onto the bearing body. ing. This makes the bearing device even more complex. Other points are west 1:'
This corresponds to what has been described in the specification of Japanese Patent Application No. 3227902.

From EP 3 303 831 A1 a sol displacement bearing device with two plastic cage halves is known.

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 support 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. 2523.669, a cage is shown in an open rail guide basin with two rows of sails. This cage is made of metal or plastic and has features like the cages described above. The end plates and the ball guides of both rolling surfaces of both cage halves are integral as shown in FIGS. 4 and 5. Sol deflection takes place at the end plate. S? −
Post-processing is necessary to achieve a good transition, low wear and a quiet process at the sol inlet or sol outlet. In this case, NishiP Italy Patent Application Publication No. 32279
As already mentioned in No. 02 and No. 3,148,331, nevertheless a sufficient force progression 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, there are also known longitudinal guide bearing members that can achieve good sol transfer and quiet sol rolling without requiring extensive post-processing of the rolling surfaces that receive the load of the bearing body. West P
Italian Patent Application Publication No. 3005579, No. 1425
No. 966, No. 3313129, No. 3304895
No. 331357.5 uses a semi-cylindrical deflector whose radius corresponds to 1/2 of the sol diameter. The deflector is arranged in a recess between the end plate and the end face of the bearing body and guides the sole from the inside. External pole guidance is provided by known U-shaped recesses in the side plates. These solutions have structural similarities. That is, the end plate with the single deflection part and the retaining web are manufactured separately and assembled. This results in a large number of parts and therefore a large number of butt points and sources of error which greatly increases manufacturing and assembly costs.

Problem to be Solved by the Invention It is an object of the invention to provide a rolling bearing device that is easy to manufacture. In this case, demands for easy manufacture are particularly placed on the bearing body and on the retainer consisting of the end plate and the retaining web.

Means for Solving the Problem The problem of the present invention is to solve the problem in the rolling bearing mentioned at the beginning.
The two load-transmitting rolling element rows of both rolling element circuits of a pair are arranged between two load-transmitting rolling element rows which are unique, mutually aligned, and belong in each case to an end plate. The solution is that the bearing body is kept engaged with each rolling surface of the bearing body by a common group of two retaining webs.

In an embodiment of the invention, the cage parts, each consisting of an end plate and a retaining 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-transferring 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 a dovetail or similar joint.

In order to connect the retaining webs belonging to mutually opposite end plates to each other at their abutment points and to ensure a precise profile alignment of the retaining webs, the mutually opposed ends of the mutually aligned retaining webs are fitted with bayonet joints or the like. It is proposed to connect them to each other with objects.

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 is achieved by the arcuate rolling element array following 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 ensured by the provision of a lubricant supply lubricant on the supporting surface of at least one end plate, which lubricant supply trough. It is connected to the lubricant supply of the end plate 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 has become. Starting from the fact that the end plate is cast or injection molded from plastic, the lubricant supply trough can be manufactured in a 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 receiving part on the back side remote from the inner deflection surface of the deflection body, the transverse holes extending the longitudinal distribution trough to each arcuate rolling body row. It is 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 would be advantageous if it were 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. be. In this case, a rail profile with an approximately rectangular cross section results. A recess is arranged in the two mutually facing sides, and at the edges of the recess a rolling surface of the rail is provided, between which the retaining web is arranged.

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

In addition to constructing the bearing body in one piece, it is also possible to provide opposite pairs of rolling element circuits on the bearing body part, such that the spacing between the two bearing body parts 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.

In addition, the rail itself has at least one load-bearing rolling surface.
It can also consist of two molded body parts with one intermediate part. This makes it possible to construct rails of various 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 Advantageously, a sealing plate is mounted on the end face opposite the bearing body, and this knoll plate is provided with a sealing edge that at least approximately follows the profile of the rail over at least a portion of its outer surface.

Of course, in this case, the seal edge force is configured so that it can be brought into 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 structures 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, for example consisting of a C-shaped section and a raised section that engage on the inside and 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 apply loads on both sides of the rolling element row, which transmits the load to the bearing body and possibly to the end plate. A parallel sealing strip can be mounted on the 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 loading condition is such that the web of the U-shaped cross-section tends to move away from the rail, this loading condition implies an expansion for the U-shaped leg. In order to increase the stability of the U-shaped cross section against such expansion, the U-shaped leg of the bearing body has a support surface remote from the rail for contacting the mechanical part, and It is advantageous if the connection is made by a pin joint or the like, and this pin joint or the like is arranged close to the U-leg and if appropriate 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, in the present invention, there is no cage portion in the area of the zero-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 a perfect rolling element deflection with low wear, while at the same time providing lubricant distribution. A rolling bearing device is provided which ensures reception of the sealing member. 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 row of balls that transmit the load of the i-le circuit in the set is in contact with the rolling groove of the bearing body on one side of the plane containing the axis of the seel circuit that transmits both loads, 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 rows of a pair of deflector circuits are assigned a common semi-cylindrical deflection body which is received in a common semi-cylindrical deflection body receiving trough. It is advantageous if the

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 advantageous than rolling bearings with gears, where limited space is provided 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 circuit to be placed in narrow spaces, is
The roller circuits of the set are arranged 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 a set are spaced apart from each other in the axial direction and intersect, and in each roller circuit, the rollers of the roller row receiving the load and the roller row of the roller row returning The rollers and the rollers of the arcuate roller array 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 arc roller rows, i.e. the one furthest from the bearing body, has an outer deflection surface, which deflection surface is located on the end plate. The inner deflecting surface is formed by an outer deflecting body and an inner deflecting body, and the inner arcuate roller row, that is, closer to the bearing body, has an outer deflecting surface, and this deflecting surface has an inner deflection surface which is partly constituted by an outer deflector and partly by a recess in the end plate and which is constituted by an inner deflector.

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 pair of roller circuits has approximately the same length in the axial direction of the rail, and one of the roller circuits has one end. It is advantageous to form an inner arcuate roller row in the region of the plate and an outer arcuate roller row in the region of the other end plate.

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

In this embodiment, one arcuate roller row is the outer
namely a deflection surface from the bearing body, which deflection surface is formed by a recess in each end plate, and a first conical partial deflection from the two outer partial deflection surfaces, i.e. tangent to the outer circumferential surface of the roller. and a second outer conical partial deflection surface which is in contact with the end face of the rollers of the arcuate roller row, and each arcuate roller row has an inner deflection surface, which is closer to the bearing body. , this deflection surface is formed from a deflection body embedded in each end plate, and is formed from two inner partial deflection surfaces, that is, a first inner conical partial deflection surface which is the outer peripheral surface of the rollers of the arcuate roller array. and a second inner conical partial deflection surface that is in contact with the other end surface of the roller of the arcuate roller array.

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

For reasons of manufacturing simplicity, 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. .

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 over conical deflection surfaces, in the region of an arcuate roller bank, the spacing between the opening and the opening is given at one end of the roller. It is advantageous to provide individual spacer elements.

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. Four J's? - Le Circuit A, B.

The support body 1 has ball rows Al, Bl... extending in the axial direction and receiving a load, and the bearing body 1 has three rolling grooves A12, B12, C12, provided in the rail 2.
In cooperation with D12, a longitudinal movement of the mutually movable parts can be provided even when the bearing body 1 or the rail 2 is loaded with a rotational moment. The return rows A2 and B2 are inserted into the return holes A21 and B2 inside the support body 1.
1..., so the four pole seats l-A, B, C, D are guided by the ball row Al that transmits the load.
, Bl... and the ball row A2. It has circular arc ball rows A3, B3, . . . that connect B2, .

The two ball circuits A, B; C, D are each located in a plane perpendicular to the plane of symmetry S-8 of the bearing unit.

The support body 1 is fixed by means of a pin joint with a through hole 15. The through hole 15 lies in the outer region of the bearing body] with respect to the plane of symmetry S-8, and
8, ie, at the location indicated by reference numeral 15a.

In other embodiments (FIGS. 2C and 2D), the through hole 15a
A screw hole 16.16a can also be provided instead. 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. Rail 2 has center hole 1
It is connected to the base body via 7 with screws.

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 retainer has a support surface 19 and two axially extending retaining webs 20a.
, 20b. Retaining web 20a.

20b is constructed integrally with the end plate 18 and guides the load-transmitting ball row Al, 81 in the bearing body 1 during the movement course, ie the holding groove A14. It is useful for holding in the rolling grooves A11 and B11 of the support body 1 via B14...

Moreover, this is done before the rail 2 is assembled with the support body in which the load-transmitting ball rows are brought into engagement with the load-receiving rolling grooves A12, B12 of the rail 2. For this purpose, rolling grooves and holding grooves A11, B11...

A12, B12..., A14. Please refer to FIG. 2e, in which the outer circumferential range of the ball rows Al, Bl, . . . in contact with B14, . The sum of angles α+β is larger than 1800.

This ensures that the sail is held securely in the bearing body even outside the rail. In order to avoid sailing friction, the contact between the sail and the bearing body is interrupted in region 1 by a small cutout. Holding web 20a+2
The friction of the sail at 0b is interrupted by a suitable play in the range β after combination with the rail.

The four U-shaped notches 22 in the end plate 18 form the arcuate ball row A3. An outer deflection surface 22a for B3... is formed. The end plate 18 is arranged in a recess forming the end face ld 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-8 of the end plate 18.

In this plane of symmetry S-8 the two circuits A, B, C are connected through lubrication holes 27 with threaded connections.

Lubricant is supplied to D. Plastic retainer half 1a
, 20a, 20b to the bearing body 1 of the bearing device, the two holes 27 and cutouts 28 in the end plate 18 allow the integration of the sealing plate 29. The fixing of the sealing plate 29 takes place via a number of snap connections 30.39 (
4, 7, 12, 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. Sol rows Al and B that transmit the load
attached to the bearing body 1 and the end plate 18 immediately above (40) or immediately below (41) the sealing plate 29;
An additionally provided sealing strip extending up to 0° 41 prevents dirt, which may have entered the bearing device via the rail bore 17, from reaching the contact zone with the dial or the rail 2.

This allows for an almost airtight sealing of the transfer area.

In FIG. 5 the cutout 28 for receiving the sealing plate 29 is shown, and in FIGS. 5, 7, 12 and 13 the position of the snap coupling members 30, 39 is shown. ing.

FIG. 6 shows the retaining web 20b of FIG. 3 on an enlarged scale. In order to guide the sol rows Al and Bl that transmit the load, the retaining grooves A14.A14. B14 is integrally molded. The retaining web 20 is secured in a corresponding groove 32a of the bearing body so that it does not bend.
It is reinforced along its entire length by a key 32b that engages with the key 32b. Additionally, the two cage halves are connected to each other by a pin 33'a which is inserted into the 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. 2
Tongue-shaped portion 34il-1 curved into two circular arcs: recess 35
Together with this, a C-shaped molded portion is formed. A raised molding 39 (FIG. 13) molded into the sealing plate 29 is snapped onto the C-shaped molding by bending the resilient tongue 34 away.

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. The two horizontal holes 37 in the deflection body 26 connect the vertical distribution groove 26a to the circular arc sole row A3.
゜Connect with B3. This horizontal hole 37 passes through an inner deflection surface 36a integrally formed on the deflection body 36.

The inner deflection surface 36a is a circular arc sole row A3. It takes over the inner guidance of B3 and is useful for achieving quiet ball rolling.

From FIG. 9, it can be seen that the hole center point of the horizontal hole 37 of the inner deflector 36 in FIGS.
It can be seen that they are not located at the center of the map, but are located closer to each other.

The reason for this is that the horizontal hole 37 has a 2-
This is because they want to ensure that their transfers are not hindered. 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 shape and inner shape 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 integrates the sealing plate 29 into the plastic retainer halves 1a, 20a, 20b. The sealing plate 29 consists of a relatively soft plastic or rubber material.

FIG. 14 shows an expansion of the possibilities for using rolling bearings. It is advantageous for the purpose of use to have the bearing body divided, for example in order to make it possible to assemble wide rails.

Due to the location of the sol circuit and the resulting cage structure, which has only one set of retaining webs 20a, 20b aligned with each other for the two sol rows transmitting the load, the bearing body and the retaining It becomes possible to divide the container over the plane of symmetry S-8 at a relatively low cost. In this case, only the lubricant supply device is changed, and the two bearing body parts 408.
It is necessary to ensure that 40b is lubricated separately. If the rail 2 is also divided, that is to say that the rail 2 also has two molded parts 428 and 42b and possibly one intermediate part 42.
C, 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 19aK of the end plate. When a lubricant press is installed to press lubricant into the lubricant supply device 26, the force with which the lubricant press is pressed against the end plate 18 is equal to the force generated by the pressure of the lubricant in the lubricant supply groove 26. He is made to run. 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 members are numbered by adding 100 to the reference numerals 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, B are arranged in mutually intersecting planes 145 and 146.

These planes 145, 146 intersect the rail (not shown) at an intersection line E, which is parallel to the longitudinal axis of the bearing body. The rows of rollers transmitting the load are designated A1 and 81, and the rows of rollers being returned are designated B2 and A2. The roller rows Al and Bl that transmit the load are on the rolling surface B12. which receives the load of the rail. It is brought into contact with A12.

The returned roller rows A2 and B2 are guided in return channels A21 and 821 with a rectangular cross section. 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 arcuate roller row B3 has an outer deflection surface 147 formed by a recess 148 in the end plate 118. Furthermore, the outer arcuate roller row B3 has an inner deflection surface 149 which is partially formed by an outer deflection body 150 in the section indicated by the dot 149a and partially Specifically, the portion indicated by the reference numeral 149b is formed by the inner deflector 151. The inner circular arc roller row A3 has an outer deflection surface 125.
5 is partly formed by the outer deflector 150, namely in the part indicated by 152a;
The portion designated by the housing symbol 152b is formed by a recess 148. Furthermore, the inner arcuate roller row A3 has an inner deflection surface 1 formed by the inner deflection body 151.
It has 53.

The deflection bodies 150 and 151 are butted against each other in the recess 148, and are located on the inner deflection surface 14 of the outer arcuate roller row B3.
9 is connected to the deflection surface 1490 partial range 149b of the outer arc roller row B3, and the partial range 152a of the outer deflection surface 152 of the inner arc roller row is connected to the outer deflection surface 1490 of the inner arc roller row A3. 152 subrange 1
52b.

As can be seen from FIGS. 17 and 18, the inner deflector 15
1 is a back surface 15 that is flush with the support surface 119 of the end plate 118;
1b. Back surface 151 of inner deflector 151
b, a vertical distribution groove 12 connected to the lubricant supply groove 126 and connected to the inner circular arc roller row A3 by a horizontal hole 137;
6a is formed.

Retaining webs 120b and 1.20a are integrally formed on the end plate 118, and these retaining webs 120b and 1.20a
a maintains the load-transmitting roller arrays A1 and B1 in engagement with a rolling surface (not shown) of the support body.

Since the end faces 118 at both ends of the bearing body are assumed to be identical, only one mold needs to be used to produce the end plate. This is Figure 15, 17
In relation to FIG. This means that it is a circular arc roller row. In this manner, the lengths of roller circuits A and B are equal and the shape of both end plates is the same. Furthermore, this ensures that each roller circuit A and 8 is lubricated as shown in FIGS. 17 and 18.

Furthermore, FIG. 22 shows how the projections 154 on the end plate or bearing body prevent the loaded roller arrays A1 and 81 from falling off. Corresponding projections can also be provided on the retaining webs 120a, 120b. The retaining webs 120as 120b, as well as the end plates 118, can consist of a relatively soft elastic material, so that it is not possible to bring the rollers into the working position in the roller rows Al, Bl transmitting the load beyond the projections 15. It's easily possible. 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 zeal.

All other structural features, in particular those regarding the sealing plate and the sealing strip, are provided as in the embodiments according to FIGS. 1 to 14.

Linear bearings using rollers have the advantage of being able to support larger loads.The zero rollers can be constructed 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 embodiments according to FIGS. 15 to 21 have the advantage that both rollers A and B can be arranged in a relatively small space as shown in FIG.

However, one has to accept the disadvantage that both 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 shown in Figures 1 to 1.
4 are shown with 200 added to them.

In the embodiment of FIG. 23, the roller row A1 receiving the load is
, B1 and returning roller rows A2, B2 are arranged in mutually parallel planes F, G. The planes F1G may be inclined at acute angles to each other and intersect outside the roller circuits A, B.

The roller rows A1 and 81 that transmit the load roll on rolling surfaces A12 and B12 of rails (not shown). The roller rows A2 and B2 to be returned are the return passages A21 and B21 of the support body.
are guided by.

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
A deflection surface is formed. The outer deflection surface 255 is composed of two outer partial deflection surfaces 255a and 255b. Both partial deflection surfaces 255a, 255b are conical about axis H. On the partial deflection surface 255a, the rollers of the arcuate roller array A3 roll over the circumferential surface range. Once accumulated on the partial deflection surface 255b, the end surfaces of the rollers of the arcuate roller array A3 slide. A deflection body 256 having an inner deflection surface 257 is embedded in the recess 248 . Inner deflection surface 2
57 is composed of partial deflection surfaces 257a and 257b. That is, the partial deflection surface 257a is the circular arc roller array A3.
The circumferential surface of the roller serves for rolling, while the partial deflection surfaces 257a and 257b, with which the other end surface of the roller contacts the partial deflection surface 257b, are also conical surfaces centered on the axis H.

The back surface 219 of the deflector 256 is the support surface 219 of the end plate 218.
It forms one plane. This back surface 258 has vertical distribution grooves 2.
26a is configured. 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 i-body 256 has inner deflection surfaces for the R-arc roller rows A3 and B3 of both roller circuits A and B. - In this embodiment, like the embodiments shown in FIGS. 15 to 21, both roller circuits A, B are
As shown in Figure 3, it has the advantage of being able to be placed in a small space. 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 can be overcome by the above-mentioned construction of the deflection surfaces, especially if the deflection bodies and end plates are made of plastic with good sliding properties. If so, it can be easily removed.

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

The loaded roller arrays A1 and 81 are advantageously secured in a manner similar to that indicated by the projections 154 in FIG.

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

Furthermore, in this embodiment, the retaining web is configured separately from the end plate, and includes two components to form the retainer.
That is, two end plates and two retaining webs can be used. In this case, it is advantageous if the retaining web engages at both ends in the end plate and is preferably held there in a non-rotatable manner.

[Brief explanation of drawings]

The drawings show several embodiments of the invention, the first
The figure shows an overall view of the rolling bearing device of the present invention, FIG.
Figure C is an end view corresponding to Figure 2a of another embodiment of the invention; Figure 2d is a sectional view corresponding to Figure 2b of another embodiment of the invention; Figure 2e is a load-transmitting ball; Enlarged view of columns,
Figure 3 is a view of the end plate from inside, Figure 4 is IV of Figure 3.
- a sectional view along the line IV; FIG. 5 is an external view of the end plate; FIG. 6 is an enlarged view of the retaining web indicated by ■ in FIG. 3;
Figure 7 is an enlarged view of the sunasozo coupling indicated by the symbol ■ in Figure 4, Figure 8 is a cross-sectional view taken along the line ■-■ in Figure 3, and Figure 9 is a diagram showing the incorporated deflector. , Figure 9a is 1X in Figure 9
10 is a side view of the flat side of the semi-cylindrical deflector; FIG. 10a is a cross-sectional view taken along line xa-IXa of FIG.
xa, FIG. 11 is a plan view of the deflection body in FIG. 1.0, FIG. 12 is a view of the seal plate seen from the outside, and FIG. 14 shows the variant implementation of the bearing member, FIG. 15 shows the supporting surface of the end plate of the bearing device with intersecting roller circuits, and FIG. 16 shows the xm of FIG. 15. -xm, Fig. 17 is a sectional view along the line X-X in Fig. 15, Fig. 18 is a cross-sectional view taken along the line X-X in Fig. 15, Fig. 19 FIG. 22 of the embodiment shown in FIGS. 15 to 18 shows a modified embodiment of the embodiment shown in FIG. 15 with a securing member for the roller, and FIG. 24 is a sectional view taken along the line XXIV-xxrv in FIG. 23, FIG. 25 is a perspective view of the deflection body in FIG. 23, and FIG. The figure is number 25
27 is a view of FIG. 25 as seen from the XXV1 direction, FIG. 28 is a view showing a spacer member between successive rollers in an arcuate roller row,
FIG. 29 shows a spacer member between successive rollers in a load-transmitting or returning roller row. 1... Support body, 2... Rail, 18... End plate,
20... Holding web, 29... Seal plate 3
6... Deflection body, 118... End plate, 150... Deflection body, 151... Deflection body, 218... End plate, 256...
... Deflector = 0: 1

Claims (1)

[Scope of Claims] 1. 2 spaced apart substantially perpendicular to the axis of the rail (2), guided movably along the rail (2) in the axial direction of the rail (2); one end face (1d)
and at least one set of rolling element circuits (A, B), each rolling element circuit (A, B) of the set of rolling element circuits having a load parallel to the axis of the bearing body. One rolling element row (A1
, B1), one rolling element row (A2, B2) to be returned, and two circular arc rolling element rows (A3, B3),
The row of rolling elements (A2, B2) that is further returned is the support (1)
It is guided by return passages (A21, B21) that are substantially axially parallel to
) is attached to the end plate (18), and the deflection surfaces (22a, 36a) of the arcuate rolling element rows (A3, B3) are provided on the end plate (18). Axis-parallel retaining webs (20a, 20b) that join together at , B11), both rolling element circuits (A, B) of a set of rolling element circuits
two retaining webs arranged between the load-transmitting rolling element rows (A1, B1), which are aligned with one another and each belong to an end plate (18); (20a, 20b) for each rolling surface (A11, B1) of the bearing body (1).
1) A rolling bearing device for linear motion, characterized in that it is maintained in an engaged state. 2. Retaining surfaces (A14, B14) for rolling element rows (A1, B1) on which the retaining webs (20a, 20b) transmit loads
)have. A rolling bearing device according to claim 1. 3. The retaining webs (20a, 20b) are connected to the keyway joint flats (32
a, 32b), in particular in the form of a dovetail or the like, resting on the bearing body (1) according to claim 1 or 2. 4. Any one of claims 1 to 3, wherein the mutually opposing ends of the mutually aligned retaining webs (20a, 20b) are connected to each other by bayonet joints or the like. Rolling bearing device as described in one heading. 5. The circular arc rolling element rows (A3, B3) are provided on the support surface (19) of the end plate (16) on the outer side, that is, on the support body (1).
) and an inner deflection surface (36a), i.e. close to the bearing body (1), the inner deflection surface (36a) forming at least one deflection body (36). The deflector (36) is attached to the end plate (1
8) The rolling bearing device according to any one of claims 1 to 4, which is received in a deflector receptacle (25) on the support surface (19) of claim 8). 6. Rolling bearing device according to claim 5, wherein the arcuate rolling element row (A3, B3) extends approximately along a semicircle over at least part of its length. 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) serves as a lubricant supply (27) of the end plate (18).
The lubricant distribution system (2) is connected to the deflector receiver (25) and is connected to the
6a, 37) for lubricating the at least one rolling element circuit (A, B).
or the rolling bearing device described in paragraph 6. 8. The lubricant supply part (27) is connected to the support surface (1) of the end plate (18).
A lubricant device connected to the lubricant supply (27) is attached to the end face (19a) of the end plate (18) parallel to the support surface (19) of the end plate (18). 8. Rolling bearing device according to claim 7, which generates a pressing force perpendicular to the rolling bearing device. 9. The lubricant distribution system (26a, 37) has a longitudinal distribution trough (26a) and a transverse hole (37) on the back surface (36b) set back from the inner deflection surface of the deflection body (36); a hole (37) connects the longitudinal distribution trough (26a) with the inner deflection surface (36a) of each arcuate rolling element row (A3, B3);
A rolling bearing device according to claim 7 or 8. 10. Rolling bearing device according to claim 9, characterized in that the opening of the transverse hole (37) to the inner deflection surface (36a) takes place at a location that is not important for the guidance of the rolling elements. 11. The bearing body (1) has two sets of rolling element circuits (A, B, C, D) facing each other, and these rolling element circuits (A, B, C, D) have a rail ( 2). Rolling bearing device according to any one of claims 1 to 10. 12. The bearing body (1) surrounds the rail (2) in a U-shape, and the rolling element circuit (A, B, C, D) is arranged on the U-shaped leg (1a) of the bearing body (1). A rolling bearing device according to claim 11. 13. The rolling element circuit (A, B, C, D) in the U-shaped leg (1b) of the bearing body (1) is arranged parallel to the U-shaped leg (1b) of the bearing body (1), A rolling bearing device according to claim 12. 14. Mutually opposing sets (A, B; C, D) of rolling element circuits (A, B, C, D) are arranged in the parts (40a, 40b) of the bearing body (1), and their mutual 14. Rolling bearing device according to claim 11, wherein the spacing is variable. 15. Claims 11 to 14, in which the rail (2) is composed of two molded parts (42a, 42b) with load-bearing rolling surfaces and at least one intermediate member (42c). Rolling bearing device as described in any one of the preceding paragraphs. 16. A seal plate (29) is attached to the end face (19a) of the end plate (18) opposite to the support body (1), and this seal plate (29) conforms to the profile of the rail (2). Rolling according to any one of claims 1 to 15, characterized in that it has a sealing edge (29a) that follows at least substantially over at least a part of the outer surface of the rail (2). Bearing device. 17. The rolling bearing device according to claim 16, wherein the seal plate (29) is arranged in the notch (28) of the end face (19a) so as to be substantially flush with this end face (19a). 18. Rolling bearing device according to claim 16 or 17, characterized in that the sealing plate (29) is fixed to the end plate (18) by a snap connection (30, 29). 19. Rolling bearing device according to claim 18, characterized in that the push-button snap connection consists of a C-shaped profile (30) and a raised profile (39), which engage each other inwardly and outwardly. 20. Rollers transmitting the load on both sides of the rolling element array (A1, B1) transmitting the load of a set of rolling element circuits (A, B) to the bearing body (1) and optionally to the end plate (18). Seal strips (40, 4) parallel to the moving body rows (A1, B1)
1) are installed and these sealing strips (40,
Rolling bearing device according to any one of claims 1 to 19, characterized in that the rail (2) is in contact with the rail (2). 21. The U-shaped web (1b) of the bearing body (1) has a supporting surface (1c) remote from the rail for contacting the mechanical part, and the U-shaped web (1b) has a pin joint flat (15) on the mechanical part.
or the like, and this pin joint or something similar is placed near the U-shaped leg (1a), or in some cases in the middle of the U-shaped leg (1a). 14. The rolling bearing device according to claim 12 or 13, wherein a pin joint flat (15a) is used. 22, the rolling surfaces (A12, B1) that receive the load of the rail (2) when viewed in a cross section perpendicular to the axis of the rail (2)
Rolling bearing device according to one of claims 1 to 21, characterized in that 2) is widened towards the bearing body (1). 23. The rolling element circuit is a ball circuit (A, B)
The linear rolling element row that transmits the load is a ball row (A1, B1), the returning rolling element row is a returning ball row, and the arcuate rolling element row is an arcuate ball row (A3, B3). The rolling surface (A11, B11) of the bearing body (1), the rolling surface (A12, B12) of the rail (2), and the holding web (
23. The rolling bearing device according to claim 1, wherein the holding surfaces (A14, B14) of the parts 20a, 20b) are configured as rolling grooves or holding grooves. 24. The ball rows (A1, B1) transmitting the loads of one set of ball circuits (A, B) are the axes (A13, B) of both ball rows (A1, B1) transmitting the loads of one set.
13) is in contact with the rolling grooves (A11, B11) of the bearing body (1) on one side of the plane (P-P), and this plane (P-P)
are in contact with the retaining webs (20a, 20b) in circumferential areas (β) facing each other on the opposite side of the frame and in contact with the rolling grooves (A12, B12) of the rail (2) in mutually distant circumferential areas (γ), A rolling bearing device according to claim 23. 25. A common semi-cylindrical deflection body (36) is assigned to the adjacent arcuate ball rows (A3, B3) of one set of ball circuits (A, B), and this deflection body (36
25. Rolling bearing device according to claim 23 or 24, characterized in that the deflector-receiving grooves (25) are received in a common semi-cylindrical deflector-receiving groove (25). 26, outer deflection surface (22a) and inner deflection surface (36a)
26. Rolling bearing device according to any one of claims 23 to 25, characterized in that the deflection passages (1) and (2) form a deflection channel with a substantially constant cross section. 27. Claims 23 to 26, wherein the opening to the deflecting surface (36a) inside the horizontal hole (37) is shifted with respect to the plane containing the ball center point of each arcuate ball row.
Rolling bearing device as described in any one of the preceding paragraphs. 28. The rolling element circuit is a roller circuit (A, B)
The rolling element row that transmits a load is a roller row (A1, B1) that transmits a load, the rolling element row that is returned is a roller row that is returned (A2, B2), and the arc rolling element row is a circular arc row. Rolling bearing device according to any one of claims 1 to 22, which is a roller row A3, B3). 29, a pair of roller circuits (A, B) are arranged in intersecting planes (145, 146), and these planes (1
45, 146) are located parallel to the axis of the rail, and the roller circuits (A, B) belonging to the same end plate (118) are spaced apart in the axial direction of the rail. The roller rows (A2, B2
), the rollers of the returned roller bank (A2, B2) and the rollers of the circular roller bank (A3, B3) are axial to each other in each roller circuit (A, B). Rolling bearing device as described in section. 30. Deflection surface of intersecting arc roller rows (B3, A3) (
147, 149; 152, 153) are each end face (118)
A deflector (150,
151), i.e. an outer deflection body (150), i.e. far from the bearing body, and an inner deflection body (151), i.e. close to the bearing body. Bearing device. 31. Of the two intersecting arc roller rows (B3, A3), the outer arc roller row (
B3) is an outer deflection surface (147) configured in the recess (148) of the end plate (118), and an inner deflection consisting of an outer deflection body (150) and an inner deflection body (151). The inner arcuate roller array (A3), which has a surface (149) and is closer to the bearing body, is partially connected to the outer deflection body (149).
50) partially into the recess (148) of the end plate (118)
an outer deflection surface (152) formed by an inner deflection surface (153) formed by an inner deflection body (151);
) The rolling bearing device according to claim 30, comprising: 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 is connected to the inner arcuate roller row (A3
32. 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, B) of the pair have approximately the same length in the axial direction of the rail, in which case one of the roller circuits (A, B) has an inner surface in the area of one end plate (118). The roller according to any one of claims 29 to 32, forming an arc roller row (A3) and forming an outer arc roller row in the area of the other end plate. Bearing device. 34. According to claim 33, both end plates (116) with deflection bodies (150, 151) and optionally associated retaining webs (120a, 120b) have approximately the same shape. Rolling bearing device. 35. A plane in which the roller circuits (A, B) forming a set are substantially parallel to each other or intersect at an acute angle outside the roller circuits (A, B) with an intersecting line parallel to the axial direction of the rail. (F, G) and transmit the load in each roller circuit (A, B) (A1,
The rollers of B1) and the rollers of the returned roller rows (A2, B2) are arranged in a common mutually inclined plane with the roller axis, and the arcuate roller rows (A3, B3) are arranged on a conical surface with the roller axis. 29. The rolling bearing device according to claim 28, wherein the rolling bearing device is 36, the arcuate roller array (A3) has a deflection surface (255) on the outside, i.e. remote from the bearing body, and this deflection surface (255
) is formed by a recess (248) in each end plate (218), two partial deflection surfaces (255a, 255b),
That is, it is composed of a first outer partial deflection surface (255a) in contact with the outer circumferential surface of the roller and a second outer conical partial deflection surface (255b) in contact with the end surface of the roller of the arcuate roller array (A3), Furthermore, each arcuate roller row (A3) has an inner deflection surface (257) close to the support body, and this deflection surface is recessed in each end plate of the deflection body (256).
) and two inner partial deflection surfaces (257
a, 257b), that is, the first inner conical partial deflection surface (2
36. Rolling bearing device according to claim 35, comprising a second inner conical partial deflection surface (257b) that contacts the end face of the rollers of the arcuate roller array (A3). 37. Rolling bearing device according to claim 36, wherein the deflector (256) has a back surface (258) aligned with the support surface of each end plate (218). 38, a vertical distribution trough (226a) is configured on the back surface (258), and this vertical distribution trough (226a) is connected to the lubricant supply trough (226), and is connected to the inner side by a horizontal hole (237) passing through the deflection body (256). 38. Rolling bearing device according to claim 37, wherein the rolling bearing device is connected to a deflection surface (257) of. 39. Rolling 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. Bearing device. 40. Rolling bearing device according to any one of claims 28 to 39, wherein the rollers are configured as cylindrical rollers. 41. Rolling bearing device according to one of claims 28 to 39, wherein the rollers are configured as barrel rollers. 42. Rolling bearing device according to any one of claims 28 to 39, wherein the rollers are configured 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. Rolling bearing device according to any one of claims 28 to 43, in which a loose spacer member is arranged between successive rollers. 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 the two successive rollers and is provided with a groove (271) on the side facing the rollers; 45. Rolling bearing device according to claim 44, wherein the length of this groove (271) corresponds approximately to the length of the roller parallel to the roller axis. 46. Any one of claims 28 to 45, wherein the row of arcuate rollers (A3, B3) is guided by a row of arcuate rollers (A3, B3) having a substantially constant cross section. Rolling bearing device described in .