DE10152847B4 - Rolling bearing for supporting spindle of machine tool, satisfies preset inequality involving radial and axial lengths of retainer and pitch circle diameter of each roller held by retainer - Google Patents

Abstract

A retainer (14), made from resin, holds the rollers (13) between the outer ring (11) and the inner ring (12) of a rolling bearing (10). The retainer comprises of a pair of axially spaced annular portions joined by a columnar portion. Axial and radial lengths of a section of the annular portion and the pitch circle diameter of each roller satisfies a preset inequality. - An INDEPENDENT CLAIM is also included for a spindle apparatus for a machine tool.

Description

The The present invention relates to a rolling bearing, in particular for storage a spindle shaft of a machine tool, moving at high speed rotates, and on a spindle device for the machine tool, the the rolling bearing used.

Of the The state of the art is described using the example of a cylindrical roller bearing. A warehouse for the storage of a spindle shaft of a machine tool requires a high rotational accuracy and rigidity to the machining accuracy to hold up. The cylindrical roller bearing used for this purpose becomes usually used with an inner game of bearing, with a small game Game of about 5 μm, after the rolling bearing in the spindle shaft and a housing was installed.

on the other hand There is an increasing tendency for the spindle device to be high Use speed to improve the processing efficiency, and it is thus necessary that the Stock of this elevated Speed equals. As a warehouse that meets this requirement, is a cylindrical roller bearing, which is an inner ring with ribs and an outer ring without Borde (N-type) used which lighter the supplied lubricating oil to the outside of the bearing can output as a cylindrical roller bearing, which has an outer ring with ribs and an inner ring without ribs has (NU type) used. Furthermore come as a holder guide type (Holder positioning type) which is currently widely used a leadership type with inner ring for use, in which the holder or the holding device is made of a copper alloy, and in which the holding device through the outer surface of the Borde of the inner ring led and a roll guide type for use, wherein the holding device made of synthetic resin is and guided by the rollers becomes.

Farther be in conventional rolling bearings, rolling such as balls, rollers or the like between the treads, the on the outer surface of the inner ring and the inner surface of the outer ring are formed, arranged. In this rolling bearing is to the rolling elements on the running surface at equal intervals in the circumferential direction of the bearing, a circular one Holding device between the outer ring and the inner ring inserted.

One Warehouse for a spindle device of the machine tool, which is an example of roller bearing is supposed to have a low vibration and a low noise, to improve the machining accuracy. Furthermore, the Stock lately demanded that its performance be high Can provide rotational speeds (that is, in a stable manner at used a high rotational speed over a long period of time can be), with a lubrication that is in terms of easy handling, the environment and the costs prove effective. To meet these requirements, Conventionally, a holding device has been used which easy, a towering Sliding feature and made of synthetic resin, the reinforcing fibers for one Improvement in strength were added.

The 34 and 35 show a conventional rolling bearing comprising a holding device of the type of outer ring guide and a double-sided guide. 35 is a sectional view taken along the line XXXIV-XXXIV in 34 , A rolling bearing 200 is schematically an outer ring 201 , an inner ring 202 , Rolling elements 203 and a holding device 204 built up.

As in 35 is shown, both have axial ends of the inner ring 202 Borde 202a on, projecting to the side of the outer ring in the radial direction.

The holding device 204 is made of synthetic resin and has pocket sections 205 for holding the rolling elements 203 in the circumferential direction at intervals. Furthermore, the holding device 204 side walls 204b . 204b which are provided upright on both axial sides toward the side of the outer ring in the radial direction. The leading end face of the sidewall 204b facing the outer ring 201 is (this is a guided surface in this example 204a ) comes into sliding or tight contact with the outer ring 201 , As the holding device 204 by the sliding contact of the guided surface 204a with the inner surface (guide surface) of the outer ring 201 is guided, so the holder rotates 204 relative to the outer ring 201 ,

Further, the above-described synthetic resin-made holding device is made by injection molding, and has been used in a bearing for a machine tool, which is often used with very small amounts of grease or lubricating oil used to generate heat during the process Minimize operations runs. Thus, in the bearing for the machine tool, the substantially minimum amounts of the lubricant are used so as to suppress a resistance to movement of the lubricant such as the grease or lubricating oil and heat generation caused by the movement resistance. As a method of manufacturing such a resin-made holding device, a radial draw type of injection molding method is used.

36 shows a partially sectioned view of a mold 210 used in the radial draw type of the injection molding process. Part of the mold 210 consists schematically of a movable mold 211 , a first sliding core 212 and a second slide core 213 ,

The mobile form 211 has an outer surface with a cylindrical shape that forms an inner surface of the holder. At the outer periphery of the movable mold 211 a plurality of (not shown) sliding cores are arranged, which form an outer surface of the holding device and pocket parts for holding the rolling elements in the closed state of the mold. The first slide core 212 and the second slide core 213 The many sliding cores have a convex cross-sectional shape, and they are circular arc-shaped base parts 212a . 213a running along the outer surface of the movable mold 211 are arranged, and columnar projections 212b . 213b built up, upright, substantially perpendicular, to the surfaces of the side of the movable mold 211 the base parts extend, and form the pocket parts of the holding device.

If the mold 210 is firmly closed, so come the projections 212b . 213b the sliding cores 212 . 213 in contact with the predetermined positions on the outer surface of the movable mold 211 , and the adjacent side surfaces 212c . 213c the basic parts 212a . 213a the sliding cores come into contact with each other, wherein a cavity is formed in the holding device. Then, by injecting the resin into the cavity, an annular holding device 220 formed of synthetic resin, which has pocket portions arranged at intervals in the circumferential direction.

37 shows a side view of the holding device 220 passing through the mold 210 was trained. A dividing line PL caused by the mutual contact of the side surfaces 212c . 213c the sliding cores 212 . 213 Formed at the time of injection molding is between adjacent pockets of the many pocket parts 221 on the outer surface of the holding device 220 formed. 38 is a top view of the fixture when viewed from the direction XXXVII in 37 considered.

Furthermore is in the rolling bearing, in which the leadership type the holding device of a guide type an inner ring or a guide type an outer ring exists, a suitable distance (guide distance) between the surface the inner diameter of the holding device (or the surface of the outer diameter), in contact with a race (the inner ring and the outer ring) stands, and a contact surface provided the race rings. The guide distance is referred to as a difference between a diameter of a guide surface of Holding device of the race and a diameter of the guided surface of the Holding device formed. Furthermore, to the rolling element respectively and to maintain a distance (pocket spacing) between the rolling element provided in the pocket of the holder and the bag.

Conventionally, in this type of rolling bearing used for high-speed rotation, a guide clearance is used 5 the holding device in the size of 0.4 to 1.0% of a guide diameter d1 (inner diameter 4a the holding device) and a pocket distance 6 in the size of 2 to 4% of the ball diameter, which is 0.5 to 2 times the above guide distance 5 corresponds to 39 ).

When the bearing rotates at high speed in the operation of the machine tool, grease filled in the bearing or lubricating oil supplied by oil-air lubrication is thrown by the centrifugal force to the side of the outer ring, so that Case of the holding device with the inner ring guide is the possibility that a lubricating defect on the guided surface 15 caused a seizure. Further, in the high-speed rotation, by the expansion of the raceway of the inner ring and the cooling of the outer ring by the centrifugal force, and the increase of the temperature difference of the inner / outer ring by the influence of an engine installed in the engine, the Inner distance of the bearing during the run negative, so that in addition there is the problem that the Wälzkörperbelastung increases. Furthermore, the holding device is loaded by the centrifugal force in a high-speed rotation, and in the holding device made of synthetic resin is, there is also the problem that the extent of deformation is large when the Festig speed of the holding device is low. Specifically, in the case of a rolling-element guide holding device, which retains the rolling elements and is guided by the rolling elements, the rolling element in the pocket part is obstructed and the function is disturbed when the holding device is twisted by the influence of the centrifugal force or when the amount of deformation is large is. Furthermore, an exaggerated load on the holding device is exerted by the rolling elements, so that there is a risk that the holding device breaks.

When the bearing having the above outer ring holding device is used as the bearing for the spindle device of the machine tool, as the spindle shaft rotates at high speed. Dirt filled in the bearing is thrown by the centrifugal force to the side of the outer ring of the bearing, so that the distributed grease to the side of the holding device emerges through the holding device and forms a void. By leaking a very small amount of the base oil in this state, the rolling element surface and the guided surface of the holder are lubricated. However, because the guided surface 209a the holding device 204 through the inner surface of the outer ring 201 (or the outer surface of the inner ring 20 ) is guided, then, when the oil film is interrupted, the guided surface 204a the holding device 204 worn and the outer ring 201 or the inner ring 202 is made by the reinforcing fiber that has been added to the strength of the fixture 204 to increase, worn out. In this condition, it is possible that abrasion dust on the tread and the guided surface 204a is generated, the lubrication is impaired.

Further, when the spindle rotation of the machine tool is increased, it is not uncommon for the spindle shaft to be rotated in a range in which, for example, a Dmn value (bearing pitch circle diameter (mm) × rotational speed (rpm)) exceeds the value of 1 × 10 ⁶ lies. In the case of such a high rotational speed, since the grease exits to the outside of the guided surface by the centrifugal force, the grease can not be on the guided surface 204a the holding device 204 being held. Thus, it is difficult to keep the oil film on the guided surface 204a the holding device 204 train. It's not just the guided surface 204a It also erodes, but it also becomes the inner surface of the outer ring 201 that of the holding device 204 is opposite, by the reinforcing fiber, the holding device 34 for improving the strength, eroded so that the grease is destroyed early by the abrasion dust generated at that time.

in the Case of a holding device of the type of a guide through the inner ring will the surface of the Side wall of the holding device, which is opposite to the inner ring, a guided Surface, and the outer surface of the inner ring, that of the guided surface across from lies, becomes a guiding surface. In In this case, when the inner ring turns, the grease becomes on the sliding guided surface the holding device by the centrifugal force to the side of the outer ring spun. Thus, the lubrication between the guided surface of the Holding device and the guide surface of noticeable from inside ring; this causes an early breaking of the holding device and the inner ring.

Furthermore, as shown in 38 is shown, the dividing line PL, which on the outer surface of the holding device 220 was formed by the Radialzugtyp of the injection molding process, a ridge which protrudes in the radial direction of the holding device, wherein the projecting ridge extends axially. This ridge comes while holding device 220 is introduced into the bearing, in sliding contact with the inner surface of the outer ring of the bearing and thus causes wear and thus generates abrasion dust, or it causes a rotational force variation, and thus interferes with the rotation of the bearing.

conventionally, the burr was made by cutting or tumbling, before the injection-molded Holding device has been inserted into the bearing, removed, causing a proper rotation of the camp was reached.

The However, work to remove the burr is complicated, resulting in a increase the cost of the rolling bearing leads.

Furthermore, if one considers the distance of the holding device, as the conventional guide distance 5 is large so that it corresponds to 0.4 to 1.0% of the guide diameter d1 when the holding device 4 twisted during a high-speed rotation, the balls arranged unevenly, which has an influence on the running accuracy of the shaft.

The Frequency of this non-round run (hereinafter this may be referred to as "unbalance Fc") is a rotation frequency of the fixture and it makes a difference from a rotation frequency of the shaft.

If the bearing used in a spindle device for a machine tool is, then, when this imbalance Fc is generated, the possibility the existence Influence in the Regarding the deterioration of the appearance of the machined surface (a problem of creating a sink mark) occurs.

Especially 39 shows a schematic representation of a general rolling bearing of the type of guide on the inner ring. The holding device 4 is rotated while passing through the guide surface 2a (outer diameter d2) of the inner ring 2 to be led. In particular, in the case of a high-speed rotation, when the holding device 4 when starting is not in equilibrium, the holding device begins 4 their rotational movement.

This rotational movement becomes, as a center of the bag 4b outside the evenly aligned position of the ball 3 is located, an uneven arrangement of the ball 3 generated. In the drawing figure represents the reference number 1 the outer ring, the reference letter P is a uniformly applied position of the ball and the reference letter R represents a non-uniform arrangement angle of the ball.

Furthermore, like that in 39 shown when the pocket distance 6 less than the guide distance 5 is, even if the ball 3 it tends to return to the equilibrium position, they do not return there, so that the uneven arrangement becomes large.

Due to this uneven arrangement of the ball 3 the radial rigidity of the bearing changes in the circumferential direction and a displacement in the center of the shaft is generated. This displacement is generated at a frequency corresponding to the rotational frequency of the holder and causes the unbalance Fc of the non-round barrel.

One Ball bearing with an inner ring having an outer surface; an outer ring, the one inner surface comprises, a plurality of rolling elements, which are rotatably disposed between the inner ring and the outer ring; and a Haltevorrich device for holding the rolling elements, with respect to the inner surface of the outer ring or the outer surface of the inner ring is positioned, and a pair of annular parts, which are arranged in the axial direction of the bearing parallel to each other are, and a columnar Part of the ring-shaped Parts connects, includes, is from the catalog "Ball Holders and Cages "the German star Kugelhalter GmbH, March issue Known in 1981.

It The object of the present invention to provide a rolling bearing, which has a high reliability, especially at high speeds.

These The object is achieved by a rolling bearing with the characteristics of the independent Patent claim 1.

preferred Further developments of the subject invention are set forth in the dependent claims.

Thereby becomes a rolling bearing provided in which the lubricity is improved, and in which the deformation and the break of the holding device are suppressed can, and further, a spindle device for a machine tool be provided, which uses this rolling bearing.

Farther becomes a rolling bearing provided in which the lubricity can be improved and where a stability guaranteed at high speed can be.

Farther becomes a rolling bearing provided, in which the steps can be reduced, and at that no defect is generated during operation.

Farther becomes a rolling bearing provided in which the generation of a non-round barrel Fc of Wave caused by a twisting of the holding device during a rotation caused at high speed is reduced.

According to the disclosed technical teaching, the holding device with respect to the inner Oberflä That is, the guided surface of the holding device is provided in the outer surface of the holding device opposite to the running surface of the outer ring. Thus, a distance between the outer surface of the inner ring and the inner surface of the holder or a distance between the inner surface of the outer ring and the outer surface of the holder can be made to be comparatively large. Thus, lubricating oil, which is introduced from a nozzle for oil-air lubrication or oil mist lubrication safely into the bearing of the comparatively large distance, wherein the lubricating oil is thrown by the centrifugal force to the side of the outer ring, so that the guided surface of the holding device is evenly lubricated.

The Holding device is thus through the outer ring or the inner Ring led, wherein the rotational size of the holding device controlled at high speed by the guide distance at the time of the rotation can be. Furthermore, as the material of the holding device Resin material used in which seizure hardly occurs, even if only a little lubrication is present, and in which the above expression (1) where H is the radial length of the section of the circular Partly, L the axial length of this Part and dm of the PCD of the rolling element is, creating a higher Stiffening than in a conventional holding device is possible, and wherein the deformation is high speed rotation repressed can be.

For the resin material the holding device can be phenolic resin, polyamide 46, polyamide 66, Polyphenylene sulfide, thermoplastic polyimide, polyetheretherketone and the like can be used as a base material. Continue to be approximately 10 to 40 weight percent glass fiber, 10 to 30 weight percent carbon fiber or 10 to 30 weight percent aramid fiber added to the strength of the fixture to improve. To use at a high rotational speed to enable For example, the carbon fiber or the aramid fiber is more preferable. Dependent on From the use of a glass fiber can be selected. In case the Amount of added Carbon fiber or aramid fiber at 10% by weight or less The strength can not be maintained sufficiently to be obtained. In the event that the amount 30% by weight or more becomes the molding property deteriorates, and also the external appearance is bad. It is even better if the added amount the carbon fiber or aramid fiber is 20 to 30 weight percent, thereby improves both the strength and the molding property becomes. When adding Of glass fibers, the amount is preferably for the above reasons at 10 to 40 weight percent.

in the Case of a cylindrical roller bearing exists when the axial width the holding device of the type of guide on the outer ring is adjusted so that she satisfies the above expression (1), the danger that one introductory Part of the tread the outer ring, which is intended to smooth insertion of the cylindrical rolling elements achieve, with the guided surface the holding device by the axial movement of the inner ring due to an insertion error and by the extent of the wave during the run into the enclosure comes. Thus, there is the disadvantage that a braking effect on the running of the holding device is carried out, and that the out surface wears. In contrast, a bevel and tapering of the peripheral part the guided surface the holding device used, and there is a distance of 0.5 mm or more axially to the point of intersection of the tread of the outer ring and the introduction part provided, whereby this disadvantage can be avoided.

Further Be a notch in at least one of the four corners in each bag the holding device for holding the rolling elements provided, making it possible is, the lubricating oil, that of the tread of the inner ring and the ribs, according to the rotational speed of the bearing to move through the notch to the tread of the outer ring.

Farther has a Wälzkörper- or Ball guide part in the circumferential direction of the bag has a flat surface, which runs parallel to the shaft supporting the bearing. Thus, a snap-in part for the Holding the roller or the ball with respect to the amount of movement of the holding device and the dimensional tolerance be designed so that it too in the worst case with the roll or the bullet during the Run does not come into the enclosure, and it can be a rotation with high Speed can be realized without the movement of the roller or disturb the ball. additionally is to stabilize the holding device at high speeds to maintain the bilateral leadership, which causes an inclination of the holding device, preferably.

According to one embodiment, the guided surface of the holding device lies opposite the inner surface of the outer ring or the outer surface of the inner ring and is on the order of tion of the holding device, which comes into sliding contact with the outer ring or the inner ring arranged.

In an embodiment having recesses in the guided surface, even if it is used in such a high rotation range that a Dmn value exceeds 1 x 10 ⁶ , not only the grease on the guided surface of the holder made of synthetic resin can be made is, are held, but it can also be an oil film formed by the fat in a suitable manner, since a wedge effect is generated in the recess part. Namely, the distance between the guided surface of the holder and the guide surface of the race is large at the point where the recess is provided, and it is small at the other points, and the grease held in the recess is abutted to the Points are drawn where the distance is small. Thus, the guided surface of the holding device is prevented from being worn by sliding with the raceways of the outer ring and the inner ring, and a rolling bearing capable of superior stability at high speed (low torque, low noise, low speed) can be used Vibration, a seizure resistance). Further, since the rolling bearing of the rolling bearing can suppress the occurrence of iron dust caused by abrasion, destruction of the grease is prevented, so that a long service life becomes possible.

At the above construction is the depth of the recess part in the radial direction of the holding device preferably 0.3 mm or more. Thus, on the guided surface of the Holding device, which is made of synthetic resin, enough grease being held.

Farther the object is achieved by a rolling bearing with the characteristics of the independent Patent claim 9.

preferred Further developments of the subject invention are set forth in the dependent claims.

Here means "outer circumference the holding device "an outer surface, the in the radial direction completely outside at the annular Holding device is arranged, that is, an outer surface, the outside of the radial direction the holding device of a dividing line formed on the outer surface is arranged except for at least the outer surface is.

Farther It is beneficial if the depression is on the outermost surface is formed, has such a depth that the dividing line in the Groove part is formed, not over the outermost surface of the Holding device protrudes.

At the roller bearing according to one embodiment can, because the dividing line, on the outer surface of the Holding device is formed, not from the outermost surface of the Protruding holding device, the holding device are inserted into the camp, without one Post-treatment after the manufacture of the holding device by means Injection molding necessary becomes. Thus, the assembly of the rolling bearing can be simplified and the yield of the parts of the holding device can also be improved become. Furthermore, when the holding device in the camp is inserted, the dividing line on the outer surface of the Holding device not in sliding contact with the inner surface of the outer ring of the camp. Thus, during the barrel of the rolling bearing the bad operation due to wear of the dividing line and a change the torque does not cause.

Farther comprises in this case a casting mold a solid form for the shaping of one end of the holding device, a columnar, movable Form for the shaping of the inner surface the holding device and the other end, and a plurality of Sliding cores that are outside the movable mold are arranged, which have a convex cross-section and the outer surface of the Form the holding device and the pocket parts. The sliding cores point a circular arc Base part of side by side with the outer surface of the movable mold is brought, and a projection on the Surface of the Side of the movable mold of the base part erected almost at right angles is on.

When the mold is tightened, the leading end face of the protrusion of the slide core comes into contact with the outer surface of the movable mold, and the side faces of the base parts of the slide cores which are juxtaposed contact each other, whereby a cavity is formed on the circumference of the movable mold resin material is injected into the cavity to form a retainer. In an apparatus for manufacturing a bearing holding device thus forming the holding device, it is preferable that a projecting member projecting toward the movable mold side is provided on the inner surface of the contact part of the base part, thereby becoming an outer one When the side surfaces of the base parts which are adjacent to each other come into contact with each other, and when the dividing line formed on the outermost surface of the holding device when the synthetic resin is injected, in the depression portion formed by the protruding element is formed, is formed.

at this device for producing the rolling bearing holding device is it, because the dividing line, on the outermost surface of the Holding device is formed, not from the outermost surface the holding device protrudes, not necessary, an aftertreatment execute after the preparation of the holding device by injection molding. Consequently can be the assembly of the rolling bearing be simplified, and the yield of the parts of the holding device can also be improved.

following the present invention will be related to embodiments with the attached Drawings closer described and explained. In the drawings show:

1 Fig. 10 is an axial sectional view showing a bearing apparatus according to a first embodiment of the rolling bearing;

2 Fig. 10 is an enlarged view showing only the bearing of this embodiment;

3 is a representation, viewed from a direction of an arrow III in 1 in which FIG. 1 shows an outer ring of the bearing device of FIG 1 was removed;

4 is a representation showing a state in which an inner ring of the in 1 has been removed, the view extends in the axial direction;

5A to 5C Figs. 10 are diagrams showing modified examples of a shape of a holding device;

6 Fig. 10 is a diagram showing a test result in the embodiment and a comparative example in a cylindrical roller bearing apparatus;

7 is a sectional view of a cylindrical roller bearing device according to a second embodiment of the rolling bearing, wherein the view similar to the sectional view in 2 is;

8th is a sectional view of a cylindrical roller bearing apparatus according to a third embodiment of the rolling bearing, wherein they are similar to the sectional view in FIG 2 is;

9 is a sectional view of an angular contact ball bearing device according to a fourth embodiment of the rolling bearing, wherein it is similar to the sectional view in FIG 2 is;

10 is a sectional view of an angular contact ball bearing device according to a fifth embodiment of the rolling bearing, wherein it is similar to the sectional view in FIG 2 is;

11 is a sectional view of an angular contact ball bearing device according to a sixth embodiment of the rolling bearing, wherein it is similar to the sectional view in FIG 2 is;

12 is a sectional view of an angular contact ball bearing device according to a seventh embodiment of the rolling bearing, wherein it is similar to the sectional view in FIG 2 is;

13 Fig. 15 is a diagram showing a test result in the embodiment and a comparative example in the angular ball bearing apparatus;

14 is a diagram showing a modified example of the bearing device in 1 shows, similar to the representation in 1 is;

15 is a diagram showing a modified example of the bearing device in 1 shows, similar to the representation in 4 is;

16 Fig. 11 is a complete side view of a cylindrical roller bearing apparatus according to an eighth embodiment of the rolling bearing;

17 is a partially enlarged view of an in 16 shown holding device;

18A to 18C are illustrations showing the modified examples of the holding device in FIG 16 demonstrate;

19 Fig. 11 is a complete side view of a cylindrical roller bearing apparatus according to a ninth embodiment of the rolling bearing;

20 is a partially enlarged view of an in 19 shown holding device;

21 is a view that is part of a side view of a holding device 110 a rolling bearing according to a tenth embodiment of the rolling bearing shows;

22 is a view that is part of a supervision on the in 21 shown holding device 110 shows;

23 is a partially sectioned view forming part of a mold 120 for the molding of in 21 shown holding device 110 shows;

24 is a view that is part of the supervision of a holding device 130 a rolling bearing according to an eleventh embodiment of the rolling bearing shows;

25 Fig. 12 is a view showing a part of a plan view of a holding device of a rolling bearing according to a twelfth embodiment of the rolling bearing;

26 is a view that is part of a side view of a holding device 150 a rolling bearing according to a thirteenth embodiment of the rolling bearing;

27 is a view that is part of a supervision on the in 26 shown holding device 150 shows;

28 Fig. 15 is a diagram showing an analysis result of a guide distance of the jig and the unbalance Fc;

29 is a view of a test machine, in which a rolling bearing of the rolling bearing is installed;

30 Fig. 12 is a diagram showing the relationship between the guide distance of the jig and the unbalance Fc;

31 Fig. 10 is a diagram showing the relationship between the pocket distance and the unbalance Fc;

32 Fig. 10 is a front view showing another embodiment of the holder;

33 is a side view of the 32 ;

34 Fig. 10 is a complete side view showing a conventional cylindrical roller bearing;

35 is a sectional view taken along a line XXXIV-XXXIV in 34 ;

36 is a sectional view showing a mold 210 a conventional Radialzugtyps shows;

37 Fig. 4 is an illustration showing part of a side view showing a holder 220 of a conventional warehouse shows;

38 is a representation that is part of a supervision on the in 37 shown holding device 220 shows; and

39 is a schematic representation of a general rolling bearing.

1 FIG. 10 is an axial sectional view showing a rolling bearing device according to a first embodiment of the rolling bearing. FIG. 2 Fig. 10 is an enlarged view showing only the rolling bearing of this embodiment. A rolling bearing 10 includes an outer ring 11 without a rib, an inner ring 12 with shelves 12a at both ends, a plurality of rolling elements (roller elements) 13 that rotates between the two rings 11 and 12 are arranged, and a holding device 14 for holding the rolling elements 13 , In 1 is a lubricant delivery device 20 for oil-air lubrication or oil mist lubrication next to the rolling bearing 10 intended. A feed channel 20a the lubricating oil delivery device 20 is to the inside of the rolling bearing 10 directed so as to lubricate the oil, which is supplied from the outside with pressure, into the interior of the bearing 10 eject.

The holding device 14 is in relation to the inner circumference of the outer ring 11 positioned, and an outer surface 14a the holding device 14 that the tread 11a of the outer ring 11 opposite, serves as a guided surface of the holding device 14 , Thus, it is possible to have a distance between an outer surface 12b , the rib 12a of the inner ring 12 and an inner surface 14b the holding device 14 to make relatively large. Thus, the lubricating oil coming from the feed channel 20a the lubricating oil delivery device 20 is ejected, as indicated by an arrow in 1 is shown, safe by this relatively far distance to the interior of the bearing 10 guided, and the lubricating oil is by the centrifugal force to the side of the outer ring 11 hurled so that the guided surface of the holding device 14 can be lubricated evenly.

Furthermore, the holding device 14 the type of guide on the outer ring, the rotational size of the holding device 14 steer at a high speed through the guide distance. As the base material of the holding device 14 can phenolic resin, polyamide 46 , Polyamide 66 , Polyphenylene sulfide, thermoplastic polyimide, polyether ether ketone and the like. To further improve the strength of the fixture, it is advantageous to add 10 to 40 weight percent glass fiber, 10 to 30 weight percent carbon fiber or 10 to 30 weight percent aramid fiber. In order to enable use in a high-speed rotation, the carbon fiber or the aramid fiber is more preferable. Depending on the application, however, the glass fiber can also be selected. If the added amount of the carbon fiber or the aramid fiber is 10% by weight or less, it is insufficient to maintain the strength, and if the amount is 30% by weight or more, the molding property is deteriorated and the external appearance is also bad. Further, it is even better if the added amount of the carbon fiber or the aramid fiber is 20 to 30% by weight, thereby improving both the strength and the moldability. The amount of glass fiber added is preferably between 10 and 40 weight percent for the reasons given above.

Furthermore, as shown in 2 is shown, the holding device 14 a pair of annular parts 14r which are arranged directly adjacent to each other axially, and a columnar part 14p on top of the annular parts 14r combines. The holding device 14 also satisfies the following equations: Al = (LH 3 )/dm 2 (1) Al ≥ 0.025 mm (2) where H is a radial length of a portion of the annular part 14r L is an axial length of the same section and dm is the pitch circle diameter (PCD) of the rolling elements 13 is. The thus designed holding device 14 can have a high rigidity as compared with a conventional holding device, and can suppress the amount of deformation in a high-speed rotation.

However, if the annular part 14r (this is the pocket shape) of the type of holding device 14 is formed with a guide on the outer ring so that the two expressions (1) and (2) are met, there is a risk that an insertion part 11b which is provided to the cylindrical rolling elements 13 smoothly insert and in the end section of the tread 11a of the outer ring 1 is formed, with the guided surface 14a the holding device 14 by the axial movement of the inner ring 12 due to an insertion error and an extension of the shaft when running overlap. This causes the disadvantage that braking on the barrel of the holding device 14 is exercised, or that the guided surface 14a the holding device 14 eroded. In the case of this embodiment, a bevel (or sharpening) 14c at the outer peripheral end of the guided surface 14a the holding device 14 intended, and the inner end of the chamfer 14c is axially away from an intersection of the tread 11a and the introduction part 11b of the outer one 10 Rings arranged in a size of 0.5 mm or more, whereby the above disadvantage is avoided.

3 is a representation taken from the direction of an arrow III in 1 is considered, in which the outer ring is removed from the camp. The 4 is an axial view in which the inner ring from the bearing in 1 is removed. As in 3 is shown has a pocket 14d the holding device 14 for holding the rolling elements 13 notch 14g at its four corners, which makes it possible to quickly deliver the supplied lubricating oil to the tread and rims of the inner ring 12 , and according to the rotational speed of the bearing 10 through these notches 14g to the tread 11a of the outer ring 11 to move.

A rolling element guide surface 14e in the circumferential direction of the bag 14d is formed in a flat shape with an axial width a. Furthermore come on a circumferential length b axial guide surfaces 14h the holding device 14 in contact with both end surfaces of the rolling elements 13 (please refer 4 ). The width a of the guide surface 14e is set to 20 to 80 percent of the rolling element length L2, the length b of the guide surface 14h is set to 40 to 80 percent of the rolling body diameter, and the height c (see 4 ) of the guide surface 14h from the pitch circle diameter of the rolling elements 13 is on 20 to 40 percent of the outer diameter D of the rolling elements 13 set, thus the contact area of the rolling element 13 and the holding device 14 reduce, and the interference between the beveled part 13a the role 13 and the guide surface 14h to suppress. A bevel angle of a snap-in part 14f is preferably set to 25 to 60 degrees. Furthermore, the Einrastteil 14f designed so that even if the holding device 14 moved radially by the guide distance, and when the rolling element 13 moved in the circumferential direction by the pocket spacing, the latching part is not connected to the rolling elements 13 overlaps. In addition, this embodiment uses the double-sided guide, the inclination of the holding device 14 causes a stabilization of the holding device 14 to achieve at high speed, but also the one-sided leadership can be used.

The axial guide surface 14h the holding device 14 As in a modified example that can be found in the 14 and 15 is shown to be omitted as long as a space through which the lubricating oil can pass is provided. Furthermore, the above arrangement is also similar to a type of the holding device with a guide on the inner ring, which serves as a holder for lubrication on the inner ring. Thus, although the guide is made through the outer ring, the guide can also be made through the inner ring. In the above embodiment, although a cylindrical roller bearing has been described, the technical teaching can also be applied to ball bearings. Embodiments of these bearings will be described below with reference to the drawings.

7 is a sectional view of a cylindrical roller bearing according to a second embodiment of the rolling bearing, wherein the sectional view in 2 is similar. In 7 has a warehouse 30 an outer ring 31 without a board, an inner ring 32 with ribs at both ends, a plurality of rolling elements (rolling elements) 33 that rotates between both rings 31 and 32 are provided, and a holding device 34 for holding the rolling elements 33 on. A lubricating oil delivery device for an oil-air lubrication or an oil mist lubrication (the in 7 not shown) is next to the rolling bearing 30 intended.

Similarly to the embodiment described in 2 is shown, the holding device 34 also in relation to the inner circumference of the outer ring 31 positioned. In this embodiment, however, a guided surface of the holder is only on an outer surface 34a of the annular part 34r on the right in 7 opposite a tread 31a of the outer ring 31 intended. In this embodiment, H is a radial length of the portion of the right annular part 34r the holding device 34 , and L is an axial length of the same part. The other constitution is the same as in the above-described embodiment, and the function and effect can be similarly obtained.

8th is a sectional view of a cylindrical roller bearing according to a third embodiment of the rolling bearing, wherein they are similar to the sectional view in FIG 2 is. In 8th has the warehouse 40 an outer ring 41 with shelves, an inner ring 42 , a plurality of rolling elements (rolling elements) 43 that rotates between the two rings 41 and 42 are arranged, and a holding device 44 for holding the rolling elements 43 on. A lubricating oil delivery device for oil-air lubrication or oil mist lubrication (in 8th not shown) is next to the rolling bearing 40 intended.

Similar to the in 2 the embodiment shown is the holding device 44 also with respect to the inner circumference of the outer ring 41 positioned, and a guided surface of the holding device 41 is on an outer surface 44a the holding device against a tread 41a of the outer ring 41 intended. The basic construction with the exception that the inner ring 42 has no shelves is the same as in the above-described embodiment, and the function and effect can be similarly obtained.

9 is a sectional view of an angular contact ball bearing according to a fourth embodiment of the rolling bearing, wherein they are similar to the sectional view in FIG 2 is. In 9 has a warehouse 50 an outer ring 51 , an inner ring 52 , a plurality of balls (rolling elements) 53 that rotates between both rings 51 and 52 are provided, and a holding device 54 for holding the balls 53 on. A lubricating oil delivery device for an oil-air lubrication or an oil mist lubrication (the in 9 not shown) is next to the camp 50 intended.

Similar to the in 2 the embodiment shown is the holding device 54 also in relation to the inner circumference of the outer ring 51 positioned. In this embodiment, however, a guided surface of the holding device 54 only on an outer surface 54a an annular part 54r on the right in 9 opposite an inner surface 51a on the outer ring 51 intended. In this embodiment, H is a radial length of a portion of the right annular part 54r the holding device 54 , and L is an axial length thereof. Other than the above main different point, the other structure is the same as in the above-described embodiment, and the function and effect can be similarly achieved.

10 is a sectional view of an angular contact ball bearing according to a fifth embodiment of the rolling bearing, which is similar to the sectional view in FIG 2 is. In 10 has a warehouse 60 an outer ring 61 , an inner ring 62 , several balls (rolling elements) 63 that rotates between the two rings 61 and 62 are provided, and a holding device 64 for holding the balls 63 on. As in 10 shown are oil supply openings 62b for lubrication during the run for the inner ring 62 provided, and lubricating oil becomes the inner surface 64a the holding device 64 delivered.

The holding device 64 is in this embodiment with respect to the outer circumference of the inner ring 62 positioned so that a guided surface of the holding device 64 on the inner surface 64a the holding device against an outer surface 62a of the inner ring 62 is provided. The basic structure is the same as the above-described embodiment except for the above-mentioned main discrimination point, and the function and the effect can be similarly achieved.

11 is a sectional view of an angular contact ball bearing according to a sixth embodiment of the rolling bearing, wherein the sectional view in 2 is similar. In 11 has a warehouse 70 an outer ring 71 , an inner ring 72 , a plurality of balls (rolling elements) 73 that rotates between both rings 71 and 72 are provided, and a holding device 74 for holding the balls 73 on. A lubricating oil delivery device for an oil-air lubrication or an oil mist lubrication (the in 11 not shown) is next to the camp 70 intended.

Similar to the in 2 the embodiment shown is the holding device 74 also in relation to the inner circumference of the outer ring 71 positioned. In this embodiment, however, a guided surface of the holding device 74 only on an outer surface 74a an annular part 74r on the right in 11 opposite to an inner 5 surface 71a of the outer ring 71 intended. And step sections 74s pointing inward are on the outer surfaces of a pair of annular parts 74r the holding device 74 educated. In this embodiment, H is a radial length of a portion of the right annular part 74r the holding device 74 , and L is an axial length thereof. Other than the above main different points, the other structure is the same as in the above-described embodiment, and the function and the effect can be similarly achieved.

12 is a sectional view of an angular contact ball bearing according to a seventh embodiment of the rolling bearing, wherein they are similar to the sectional view in FIG 2 is. In 12 has a warehouse 80 an outer ring 81 , an inner ring 82 , a plurality of balls (rolling elements) 83 that rotates between both rings 81 and 82 are provided, and a holding device 84 for holding the balls 83 on. A lubricating oil delivery device for an oil-air lubrication or an oil mist lubrication (the in 12 not shown) is next to the camp 80 intended.

Similar to the in 2 the embodiment shown is the holding device 84 also in terms of the inner circumference of the outer ring 81 positioned, and a guided Oberflä surface of the holding device 84 is on an outer surface 84a the holding device against an inner surface 81a of the outer ring 81 intended. In this embodiment, H is a radial length of a portion of an annular part 84r the holding device 84 , and L is an axial length thereof. Other than the above main different point, the other structure is the same as in the above-described embodiment, and the function and the effect can be similarly achieved.

The Embodiments, which are applied to the cylindrical roller bearings will become hereafter described. A result of the calculation of the different cross-sectional shapes in the embodiments shown.

(Calculation Conditions)

• Dimension of the outer diameter the holding device: 99, 5 mm
• rolling element: 9 mm
• roller length; 9 mm
• Number of rolling elements: 20
• Rolling element rolling body (dm): 91 mm
• Material of the fixture: PEEK resin
• Rotation speed: 25000 rpm
• Guiding distance: 0.4 mm
• Imbalance of the holding device: 0.5 g × cm

A calculation result of the amount of deformation of a holder under the above conditions is shown in Table 1. Table 1

Out this calculation result reaches the condition 1, which is shown in Table 1, the smallest amount of deformation. If you look at this size of deformation the holding device in a high-speed rotation considered, so an Al ≥ 0.025 required.

• (a) zugespitztes Relief: 5A
• (b) C-förmig abgeschrägtes Relief: 5B
• (c) R-förmig abgeschrägtes Relief: 5C

In consideration of the axial distance between the guided surface of the holder and the effective width of the tread of the outer ring, a position P of the guided surface of the holder is chosen to be axially remote from the point of intersection of the insert 11b and the inner surface 11a of the outer ring is more than 0.5 mm apart. In this state, the calculation is made by further changing a relief shape of the outer surface 14a the holding device performed as in the 5A to 5C is shown.

• (a) pointed relief: 5A
• (b) C-shaped bevelled relief: 5B
• (c) R-bevelled relief: 5C

It it was found out that it in all forms no problems.

The Test copy and the test conditions of a comparison test, the carried out is described below.

• Warehouse copy: N-type cylindrical roller bearings
• Inner diameter: 70 mm
• Outer diameter: 110 mm
• rolling element: 9 mm
• Rolling element length: 9 mm
• Rolling element pitch circle diameter (dm): 91 mm

Embodiment: Holding device of the type with an outer ring guide 35

• Material: PEEK
• guiding distance the holding device: 0.4 mm
• Width of the holding device: 18.5 mm
• Thickness of the holding device: 5.2 mm

Comparative Example: Holding device of Wälzkörperführungstyps

• Material: Polyamide 66
• Width of the holding device: 11.8 mm
• Thickness of the fixture: 4.3 mm

Test condition:

• Radial inner distance during installation: 0 μm
• Lubrication: oil-air lubrication
• Rotation speed: Increase until the bearing rotation becomes impossible.

One result of this comparison test is in 6 shown. According to this test, the rolling element guide type holding device of the comparative example broke when the rotation speed was increased to 18,000 rpm. The reason was that the strength of the holding device itself was low, the pocket part overlapped with the movement of the rolling elements by the centrifugal force, and an extreme load was applied to the holding device.

on the other hand was in the holding device of the outer ring guide type of this embodiment increase the temperature also lower than that in the roll-guided holding device of the comparative example, wherein the limit rotation speed also dramatically increased, and there was no problem, even then, when the rotation speed was increased to 31000 rpm, so that be confirmed could that the Shape of the embodiment was effective.

When next become embodiments, on an angular contact ball bearing be applied described. A result of the calculation at different Cross-section shapes of the embodiments will be shown.

(Calculation Conditions)

• Inner diameter of the bearing: 65 mm
• Outer diameter the holding device: 86 mm
• Ball diameter: 7.144 mm
• Number of balls: 28
• Ball pitch diameter (dm): 82 mm
• Material of the fixture: PEEK resin
• Rotation speed: 30000 rpm
• Guiding distance: 0.4 mm
• Holder imbalance: 0.5 g × cm

A calculation result of the amount of deformation under the above conditions is shown in Table 2. Table 2

Out this calculation result reaches the condition 1, which is shown in Table 2, the smallest size of a Deformation. When you look at the size of the deformation the holding device in a high-speed rotation considered, so an Al ≥ 0.025 required.

The Test copy / the test conditions of a comparative test that has been carried out are described below.

• Test copy: angular contact ball bearings
• Inner diameter: 65 mm
• Outer diameter: 105 mm
• Ball diameter: 7.144 mm
• Ball pitch diameter (dm): 82 mm
• Number of balls: 28
• Combination: two-row rear-to-rear combination (DB combination, constant position preloaded)

test condition

• Axial spring constant during installation: 100 N / μm
• Lubrication: oil-air
• Amount of oil supplied: 0.03 cc / 16 min
• Rotation speed: increase until the rotation of the bearing impossible becomes

Embodiment: Holding device of the outer ring guide type (Al = 0.040)

• Material: PEEK resin
• guiding distance the holding device: 0.4 mm
• Width of the holding device: 16 mm
• Thickness of the fixture: 4 mm

Comparative Example 1 Holding device of the ball guide type (conventional holding device)

• Material: Polyamide 66
• Width of the holder: 15 mm
• Thickness of holding device: 2.5 mm

Comparative Example 2: Holding device of the outer ring guide type (Al = 0.013)

• Material: PEEK resin
• guiding distance the holding device: 0.4 mm
• Width of the holding device: 14 mm
• Thickness of holding device: 3 mm

A result of the comparison test is in 13 shown. According to this test, the ball guide type holding device of Comparative Example 1 melted as the rotational speed was increased to 22,000 rpm. This was based on the reason that the strength of the jig itself (cross-sectional shape, material) was small, that the pocket part exceeded the running of the ball by the centrifugal force and the amount of radial deformation, and that the jig by frictional heat for melting and breaking was brought.

on the other hand was the holding device of the outer ring guide type in the comparative example 2 of the holding device in Comparative Example 1 with respect to temperature increase and think the high speed. However, if the rotation speed was increased to 29000 rpm, was the guided surface of the Holding device eroded so that the bag column broke. Compared with Comparative Example 1, although the movement the holding device in the high-speed region by the outer ring guide stable was, the cross-sectional strength of the holder insufficient and the deformation size during the Runtime got big, so that the oil film education on the guided surface became difficult, and the guided surface eroded. That was based on the reason that an imbalance on the holding device caused by the wear, and because the deformation became great causing an excessive burden was generated in the fixture, and the column broke.

on the other hand is in the holding device of the outer ring guide type this embodiment the temperature increase lower than Comparative Example 1, and the limit of the rotational speed is higher than in Comparative Example 2. In this embodiment, a test machine stopped, as the rotational speed has been increased to 33000 rpm was. In the case where the test machine was taken apart, could not do any abnormality be found in the holding device, and the tread of the inner Rings 1 was just annealed. It could be assumed that these Holding device continue to run at a higher speed can, and it could be confirmed be that the Shape of the bearing effective was.

Even though the technical teaching with respect to the embodiments described above has been described, the technical teaching in a similar way to a grease lubrication the technical teaching is not based on the above embodiments limited should remain, and being different modifications and improvements of the rolling bearing possible are.

According to the technical The teaching becomes a bearing and a spindle device for a machine tool, which uses the bearing provided, whereby the lubrication improves is, and the deformation and breakup, of a holding device repressed can be.

Next shows 16 a complete side view of a single row cylindrical roller bearing (hereinafter referred to as "rolling bearing") 90 according to an eighth embodiment of the rolling bearing. The rolling bearing 90 has a holding device 94 the type of a two-sided guide and an outer ring guide, which is made of synthetic resin on. 17 shows a main part of the holding device 94 , in the 16 is shown, in perspective view.

This in 16 shown bearings 90 consists schematically of an outer ring 91 having a tread of the outer ring on an inner surface, an inner ring 92 having a running surface of the inner ring on an outer surface, a plurality of rolling elements 93 , which are used as a rolling element, and which are arranged between the running surface of the outer ring and the raceway of the inner ring, and in the circumferential direction of the rolling bearing 90 are arranged, and the holding device 94 for arranging the rolling elements 93 at equal intervals in the circumferential direction of the rolling bearing 90 ,

The holding device 94 is formed in a cylindrical shape having a predetermined width, and the pocket parts 95 for holding the rolling elements at intervals in the circumferential direction, as in 17 is shown. side walls 94b . 94b which extend to the side of the radial outer ring are respectively at both axial ends of the holding device 94 educated.

The holding device 94 is made of synthetic resin.

When the inner ring 92 turns, so are the leading end surfaces (guided surfaces 94a ) of the side walls 94b . 94b the holding device sliding to the inner surface (guide surface) of the outer ring 91 , which lies opposite the leading end faces, guided, which causes the holding device 94 relative to the outer ring 91 rotates.

In the guided surface 94a that is the guide surface of the outer ring 91 is opposed, a plurality of recesses C are provided at intervals in the circumferential direction.

Here, the recesses C, which are rectangular when viewed from the side, one after the other in the vicinity
of a center between the rollers when viewed from one side (near a pillar part) 94d ). The recess C becomes with a sufficient depth in the radial direction of the side wall 94b the holding device 94 designed to hold the fat.

The Depth of the recess C is in terms of their function, to keep the fat, preferably 0.3 mm or more.

Furthermore, a rounding on a connecting part 94c between the guided surface 94a the holding device 94 and the recess C are made, with their radius more than 0.2 mm, so as to prevent edge contact.

Here is the number of wells C that are on the guided surface 94a the holding device 94 be formed, set to two or more. This is because the guided surface 94a the holding device can not be sufficiently lubricated by a single recess C.

The 18A to 18C show respectively modified examples of the well C in the guided surface 94a the holding device 94 is designed according to the technical teaching.

In 18A A recess C has a semicircular shape when viewed from the side. In 18B far a depression C a V-shape when viewed from the side. In 18C has a recess C substantially a C-shaped cross-section, when viewed from the side. As has been described above, as long as the depression C is on the guided surface 94a the holding device 94 that can hold fat, they take any form.

Furthermore, if any of the above recesses are formed, it is advantageous if a rounding at a connecting part 94c between the guided surface 94a the holding device 94 and the recess C is formed with a radius of more than 0.2 mm to prevent edge contact.

Next shows 19 an entire side view of a rolling bearing 100 that is a holding device 104 made of synthetic resin with a guide on both sides and of the type of an inner ring guide, according to a ninth embodiment of the rolling bearing. The basic structure is the same as the rolling bearing 90 in 16 ,

As in 20 shown are guided surfaces 104a the side walls 104b . 104b the holding device 104 against an outer surface of an inner ring 102 , and they have a plurality of recesses C on. The recesses C are rectangular when viewed from the side, similar to the recess in FIG 16 , always one between the pockets 105 the holding device 104 located.

In this embodiment, the recess C is formed by a groove formed in a columnar part 104d the holding device is formed, and extending axially formed. The groove C has a depth in the radial direction, and the depth is preferably 0.3 mm or more similarly to the eighth embodiment.

Furthermore, it is advantageous if a rounding on a connecting part 104c between the guided surface 104a the holding device 104 and the recess C is formed with a radius of more than 0.2 mm to prevent edge contact.

In order to confirm an effect in the case where more than two recesses are formed on the guided surface of the holding device as in the prior art rolling bearing, the following became Life test performed at high speed.

The bearing that was used in this test is a single row cylindrical bearing that is in 16 and it is a product corresponding to the designation number N1014 (outer diameter 110 mm, inner diameter 70 mm, rolling element diameter: 9 mm, rolling element length 9 mm, number of rolling elements 20) manufactured by NSK Ltd.

Furthermore, as a holding device of the bearing, the holding device of the type with a mutual guide / an outer ring guide was used, as shown in the 16 and 17 having an outside diameter of 99.5 mm and made of PEEK (polyether-ether-carbon-carbon reinforced grade).

at the lubrication was made isoflex NBU 15 manufactured by NOK Kluber K.K. is for used a grease lubrication.

Farther was a rounding on a connecting part between the guided surface of the Holding device of the recess with a radius of more than 0.2 mm, as previously described, attached to edge contact to prevent.

The to be reached lifetime was set to 1000 hours, and the state of wear of the led surface of the outer ring and the state of the fat became at a rotational speed of 16500 rpm (Dmn value 1500000).

Table 1 shows the life and condition of the guide surface of the outer ring and the grease in cases where the number of recesses formed on the guided surface of the holder is 0, 1, 2, 3, 10 and 20. Table 3

Looking at sample 1, a test machine will have about 200 hours after the start the abnormal increase in temperature stopped. At this time, it could be confirmed that the wear caused on the guide surface of the outer ring had a width equal to the width of the holder and had a depth of 10 μm. Furthermore, the color of the fat changed to black and the iron content of the fat was 5% by weight, which is well above the value of 0.1% by weight, which is considered as the target of destruction.

If Looking at the sample 2, it stopped 600 hours after the start a test machine by the abnormal increase in temperature similar to at the sample 1.

The Samples 3, 4, 5 and 6 could Achieve the goal life of 1000 hours without problems. It showed no wear on the guide surface of the outer ring and no destruction of fat, and their guiding surfaces and the fat was in good condition and in a condition at continuous use was possible.

Based This test result was confirmed that by providing more as two recesses formed on the guide surface of the holding device Be it possible was, the wear of the led surface of the outer ring and the destruction to prevent the fat, and that one ensures long life of the bearing could be.

Farther the technical teaching is not based on the aforementioned embodiments limited, but suitable modifications and improvements are possible.

Even though the recesses individually between the pockets in the above embodiments have been provided so can they are provided in all other parts of the bag, or the majority the depressions can be provided between the pockets parts.

Farther is, although the depression was formed so that they columnar Part of the holding device corresponds to the technical teaching not limited to this. For example, it may be formed in a position that the rolling element (Role) corresponds to the holding device.

As has been described above, it is according to the technical teaching, since the depressions at more than two points on the guided surface of the Holding device can be formed, even if the bearing at high rotational speeds is possible, the possible Wear of the guide surfaces of the outer ring and suppress the inner ring and the destruction of the fat, so that it possible is, a rolling bearing, the one outstanding Lubrication and stability at high speeds (low torque, low noise, low Vibration, resistant against seizure).

21 is a side view, which is part of a holding device 110 , which has been installed in a rolling bearing, according to a tenth embodiment of the rolling bearing shows. 22 is a plan view, which is part of the fixture 110 , seen in the direction of an arrow A in 21 shows.

As in 21 is shown, the holding device 110 made of resin, it is formed in a cylindrical shape with the predetermined width, and it has pocket parts 111 for holding the rolling elements at a distance in the circumferential direction of the holding device. Furthermore, on the outer surface of the holding device 110 a depression 112 which extends in the axial direction of the holding device, between the pocket parts 111 formed side by side, and a dividing line PL is in the recess 122 educated.

As in 22 is shown is a cross section of the recess 112 formed in a substantially semi-circular shape, which is curved from the outer surface of the holding device to the inside of the holding device. The dividing line. PL is essentially at the center of the well 112 educated.

23 shows a part of a mold 120 which is used when the in 21 shown holding device 110 is formed. Part of the mold 120 consists schematically of a movable mold 121 , a first sliding core 122 and a second slide core 123 ,

The mobile form 121 is formed in a cylindrical shape, wherein its outer surface forms an inner surface of the holding device. If you have the first slide core 122 and the second slide core 123 that form part of the many sliding cores and those on the perimeter of the movable mold 121 when viewed, the respective portions of the cores are formed in a substantially convex shape, and they are side by side along the outer surface of the movable mold 121 arranged. The cores 122 and 123 are made of circular bases 122a . 123a , which form the outer surface of the holding device, and columnar projections 122b . 123b which are substantially perpendicular to the surfaces of the movable mold 121 are arranged on the side of the base parts, and which form the pocket parts of the holding device constructed. The projecting elements 122d . 123d are at the end parts of the inner surfaces of the base parts 122a . 123a the sliding cores 122 . 123 on the side of the movable mold 121 educated.

If the mold 120 closed, and the side surfaces 122c . 123c the basic parts 122a . 123a the sliding cores, which are located next to each other, come into contact with each other, so come the above elements 122d . 123d in contact with each other and are united to a head start 112a to shape.

Then, the resin material is injected into a cavity, thus forming the annular holder 110 made of synthetic resin 47 is made, and which has the pocket portions which are circumferentially spaced form.

According to the structure of this embodiment, the dividing line PL stands on the outer surface of the holding device 110 is formed, not from the outer surface of the holding device 110 before, like this in 22 is shown. Thus, it is not necessary to have a post-treatment such as removal of the burr after the injection molding of the holding device 110 perform. Thus, the assembly of the rolling bearing can be simplified, and the yield of the parts of the holding device 110 can also be improved. Furthermore, if the holding device 110 is installed in the bearing, the dividing line PL, which on the outer surface of the holding device 110 is formed, not in sliding contact with the inner surface of the outer ring of the rolling bearing. Thus, during the running of the rolling bearing, the bad operation is not caused by the wear and the rotational force change. In this embodiment, the protruding elements for all of the many sliding cores that are in the outer periphery of the movable. shape 121 are arranged provided.

24 shows a part of a plan view of a holding device 131 a rolling bearing in an eleventh embodiment of the rolling bearing.

In the holding device 130 , in the 24 is shown is a depression 132 on the outer surface of the holding device 130 formed with a substantially triangular cross-sectional shape. The depression 132 namely, is formed in the shape of a triangle which extends convexly from the outer periphery of the holding device toward the inner periphery. Thus, the shape of a slide core becomes a shape for the recess 132 simple, so that the production of the mold is facilitated. The other construction and the other procedure are the same as those in the above tenth embodiment.

25 shows a part of a plan view of a holding device 140 a rolling bearing according to a twelfth embodiment of the rolling bearing.

In the in 25 shown holding device 140 is a depression 142 on the outer surface of the holding device 140 formed in a substantially rectangular cross-sectional shape. Here, since a bottom surface of the substantially rectangular recess 142 is formed wide, this depression effectively when a dividing line PL is formed wide. The other construction and the other function are the same as those in the tenth embodiment described above.

26 shows a side view of a holding device 150 a rolling bearing according to a thirteenth embodiment of the rolling bearing. Further shows 27 a view of the holding device 150 if you look in the direction of an arrow A in 26 considered.

In the 26 shown holding device 150 has a step part 153 on the outer surface near an axial end part of the holding device 150 on, with this outward in the radial direction of the holding device 150 with respect to the remaining outer surfaces of the fixture 150 protrudes. Furthermore, a dividing line PL, which is in the step part 153 is formed, a dividing line PL, axially on the outer surface of the holding device 150 is formed within a depression 152 formed of substantially semicircular cross-section.

In such a structure of this embodiment, since the holding device 150 the step part 153 having an outermost surface of the holding device 150 forms, the step part 153 in sliding contact with an inner surface of an outer ring during the course of the rolling bearing. By forming the depression part 152 , the dividing line PL in the step part 153 the holding device 150 Namely, is the dividing line PL, which is on the outer surface of the holding device 150 is formed, not from the outermost surface of the holding device 150 in front. Thus, it is not necessary to have a post-treatment such as removing a burr on the outer surface of the holder 150 make. Furthermore, even if the holding device is installed in the rolling bearing, since the step part 153 the holding device 150 comes into sliding contact with the inner surface of the outer ring of the rolling bearing during the running of the rolling bearing, the bad operation, which is caused by a wear and a change in the rotational force, not caused.

Although the step part 153 is formed in the vicinity of an axial end portion of the holding device in this embodiment, the step portions can be formed in the vicinity of both end portions.

Farther the technical teaching is not based on the aforementioned embodiments limited, but it can appropriate modifications and improvements are made.

According to the technical Teaching can, although a holding device of a ball bearing as a holding device a rolling bearing is shown, a holding device used a roller bearing become.

According to the technical Teaching is the form of deepening not limited. As long as this Form can accommodate the dividing line, it can be pentagonal or hexagonal.

Farther can the position of the dividing line in the tenth to thirteenth embodiments to the recesses in the eighth and ninth embodiments be applied.

As has been described above, according to the rolling bearing the embodiments, since the distance processing of the ridge of the dividing line is superfluous, the fixture with low cost and easily manufactured inserted; and because the ridge of the dividing line is not in contact with the inner surface of the outer ring of the rolling bearing while the barrel of the rolling bearing comes, the bad operation, which is due to a wear and tear the change the torque is caused, not caused.

When next hereinafter is a fourteenth embodiment of the rolling bearing described.

The rolling bearing in this embodiment consists of an outer ring 1 , an inner ring 2 and a plurality of rolling elements (balls) 3 between the outer and inner rings 1 . 2 are included, and a holding device 4 for holding and guiding the many rolling elements 3 , With the exception that the guide distance 5 the holding device and a pocket distance 6 are formed in the following manner, the structure of the outer ring 1 , the inner ring 2 , the rolling elements 3 and the holding device 4 the same as in the general structure, which in 39 is shown.

Furthermore, in this embodiment, the guide type 35 the holding device 4 from an inner ring guide.

The guide distance 5 the holding device (difference between a diameter d1 of a guided surface (inner diameter surface) 4a the holding device and a diameter d2 of a guide surface of the holding device (surface of the outer diameter) 2a of the inner ring 2 ) is set at 0.05 to 0.4% of a guide diameter (diameter) d1 of the fixture 4 set.

The surface roughness of the metal surface is usually about 1 μm, and the unbalance Fc in this case is set to not less than 0.2 μm, streaks appear on the machined surface, and the appearance of the machined surface becomes poor. However, it has been known that, in case the guide distance becomes 0.4% or less of the guide diameter d1 of the holder 4 Since the non-round barrel Fc could be kept smaller than 0.2 μm, the machined surface could be improved (there were no visible streaks on the machined surface).

Further, if the guide distance is made too small, there is a danger that on the guided Surface seizure occurs. Thus, it is necessary to ensure that the guide distance 5 a size of 0.05% or more of the guide diameter d1 of the holder 4 having.

The pocket distance 6 the holding device (distance between the bag 4b the holder and the ball 3 ) is 0.8 to 1.8 times the size of the guide distance 5 ,

By adjusting the pocket distance 6 0.8 to 1.8 times the size of the guide distance 5 the unbalance Fc can be made small. In the case where the pocket distance 6 much smaller than 0.8 times the size of the guide distance 5 is there is an increased likelihood that upon rotation of the holding device, the ball 3 barely in a uniform position.

On the other hand, if the pocket distance 6 much larger than 1.8 times the size of the guide distance 5 is the increased probability that the ball 3 in a position with a very uneven arrangement angle.

The structure of the rolling bearing is not specifically limited, except that the outer ring 1 , the inner ring 2 , the rolling element 3 and the holding device 4 have the above structure.

These embodiment is simply an embodiment which was described to be the rolling bearing of the roller bearing to explain the technical teaching is not limited to this embodiment, but different changes be freely combined within the scope of technical teaching can. Of the Type of bearing can also fit in the manner of an angular contact ball bearing, a deep groove ball bearing, a roller bearing and the like in the frame of the rolling bearing selected become.

Furthermore, in this embodiment, although the holding device 4 of the inner leadership type is, and the ball 3 is used as the rolling element, the holding device of the outer ring guide type, and the rolling element may also consist of a roller.

As long as the guide distance 5 the holding device and the pocket distance 6 the holding device are set in the above-mentioned shape, the overall shape of the holding device and the shape of the bag can be formed in any manner, while they are not limited to a particular shape.

Of the guiding distance and the pocket spacing of this embodiment may also to the previously mentioned first to thirteenth embodiments be applied.

Here shows the 28 an analysis result showing the relationship between a guide distance of a holding device of an angular ball bearing and the unbalance Fc.

[Condition]

• Inner diameter: 85 mm
• pitch circle diameter: 107 mm
• Ball diameter: 12.7 mm
• Number of balls: 22
• Ball: ceramic ball
• Contact angle: 20 °
• Rotational speed 14000 rpm
• Axial load: 1000 kgf

• 1) Die Beziehung zwischen dem Führungsabstand der Haltevorrichtung und dem ungleichmäßigen Anordnungswinkel der Kugel wird folgendermaßen angenommen: Δi = Δ c/dm × cosθi (A)

  Δ c:

  Führungsabstand

  dm:

  Kugel-Wälzkreisdurchmesser

  θi:

  Anordnungswinkel (rad) der i-ten Kugel

  Δθi:

  ungleichmäßiger Anordnungswinkel (rad), der in der i-ten Kugel erzeugt wird

  (Wenn die Haltevorrichtung sich durch den Führungsabstand verdreht, so wird der zentrale Teil jeder Tasche geometrisch um den Wert des Ausdrucks (A) verschoben. Der Ausdruck (A) basiert auf dem Gedanken, daß ein Zentrum der Kugel sich im Mittel in einem Zentrum der Tasche befindet).
• 2) Wenn die ungleichmäßige Winkelanordnung gemäß dem Ausdruck (A) bei jeder Kugel erzeugt wird, und der innere Ring des Lagers sich durch die Aufnahme der axialen Belastung dreht, A) eine Kraft, die auf jede Kugel von den inneren und äußeren Ringen ausgeübt wird B) eine Zentrifugalkraft jeder Kugel C) eine externe Kraft D) eine elastische Annäherung jeder Kugel und der inneren und äußeren Ringe E) ein Versatz des Zentrums des Lagers

The analysis procedure is as follows:

• 1) The relationship between the guide distance of the holder and the uneven arrangement angle of the ball is assumed as follows. Δi = Δc / dm × cosθi (A)

  Δc:

  guiding distance

  dm:

  Ball pitch diameter

  θi:

  Arrangement angle (rad) of the i-th sphere

  Δθi:

  non-uniform arrangement angle (rad) generated in the i-th sphere

  (As the retainer rotates through the guide distance, the central part of each pocket is geometrically shifted by the value of the expression (A).) The expression (A) is based on the idea that a center of the sphere is centered in a center of the sphere Bag is located).
• 2) When the uneven angular arrangement according to the expression (A) is generated at each ball, and the inner ring of the bearing rotates by receiving the axial load, A) a force exerted on each ball by the inner and outer rings B) a centrifugal force of each ball C) an external force D) an elastic approach of each ball and the inner and outer rings E) an offset of the center of the bearing

Of the Offset of the bearing where the totality of A), B) and C) is 0 and in D) and E) no contradiction is generated, is by a obtained convergent calculation. Double the offset of this radial Offset results in the imbalance Fc.

From the result of 28 It is known that when the guide distance is made very small, the unbalance Fc can be reduced.

Next is a test warehouse in a test machine, which in 29 is shown, and the relationship between the guide distance and the unbalance Fc and the relationship between the pocket distance and the unbalance Fc are respectively tested. The reference numerals D and E, which in 29 are shown test beds.

[Condition]

• Test camp: Angular bearing (constant position specified,
• Back-to-back combination, Holding device of the inner ring guide type)
• Inner diameter: 85 mm
• pitch circle diameter: 107 mm
• Ball diameter: 12.7 mm
• Number of balls: 22
• Ball: ceramic ball 5
• Contact angle: 20 °
• Rotation speed: 5000 to 18000 rpm

The effectiveness of the rolling bearing of technical teaching can be determined by measuring the imbalance of a point a in 29 shown during the rotation are confirmed.

In this test, only the holding device 4 changed while the same outer ring 1 , the inner ring 2 and the ball 3 is used, and the influence of the guide distance 5 the holding device and the pocket distance 6 was confirmed.

The 30 and 31 show test results. 30 shows the relationship between the guidance distance 5 and the imbalance Fc, and 31 shows the relationship between the pocket distance 6 and the imbalance Fc.

When the guide distance 5 the holding device is made small, so the unbalance Fc can be reduced (see 25 ). The unbalance Fc becomes large in a high speed rotation of more than 14000 rpm. In contrast, during low-speed rotation, there is little effect due to the twisting of the fixture 4 gives, the unbalance Fc small, and there is no correlation between the guide distance 5 and the imbalance Fc.

If the size of the pocket distance 6 is changed when the pocket distance 6 0.8 to 1.8 times the size of the guide distance, so there is little influence on the unbalance Fc (please refer 31 ). When the pocket distance 6 becomes smaller than this size, the unbalance Fc becomes larger.

As the material for the holder, polyimide resin was used. Thereby, as compared with the conventional copper alloy holding device, the friction coefficient of the guided surface can be reduced, and even if the guide distance 5 made small, seizure of the guided surface can be prevented.

Farther the material of the holding device is not on the above material limited, but it can be part of the rolling bearing appropriately selected and used. For example, even if a heat-resistant plastic is used, which has a high rigidity, such as PEEK (polyether ether ketone), which prevents seizure of the guided surface become.

The test result in 30 tends to fall in with the analysis result 28 together.

Since the analysis in 28 the analysis of this bearing only, it differs from the test result that the deformation of the shaft as in 30 includes, in an absolute value of the Fc shift by two times. However, the tendencies coincide so that the effectiveness of the rolling bearing of the technical teaching can be confirmed from both aspects of analysis and experiment.

The 32 and 33 show another embodiment of the rolling bearing. In this embodiment, to prevent seizure, when a guide distance 5 a holding device of the outer ring guide type is small, oil discharge grooves 7 as they are in the 32 and 33 are shown on a guided surface 4c the holding device 4 intended. Thus, the heat generation by the oil on the guided surface 4c reduced, and seizure can be prevented.

According to the technical Teaching, as described above, the guide distance the holding device smaller than in a conventional holding device made, the twisting of the fixture is reduced, and the size of the pocket distance is related to the guide distance set to an appropriate value, eliminating the uneven arrangement the ball is reduced by the rotation of the holding device, and the rotational accuracy of the bearing can be improved. According to the rolling bearing can namely the unbalance Fc reduced at the time of running at high speed be, and if this rolling bearing is used in the spindle device of a machine tool, so can the quality the machined surface be improved.

Especially requires a machine tool that performs a surface treatment of a metal mold, a high processing speed and a surface roughness of a few microns. When the imbalance Fc about 20% or more in terms of this roughness, there are streaks in appearance, these are a problem with the finished surface can. According to the technical Teaching is however, the guide distance 0.4% or less of the size of the guide diameter, whereby the unbalance Fc with respect to the target of the surface roughness can be made sufficiently small, making the machined surface better can be trained. Further, the guide distance is 0.05% or more the size of the guide diameter is, There is no risk of seizure on the guided surface.

If the pocket distance is made much smaller than the guide distance, so, when the fixture twists, there is an increased likelihood that the Ball does not keep close to the uniform arrangement position can. On the other hand, if the pocket distance is much larger than the guide distance is made, there is an increased Probability that the Ball in the position of the big one nonuniform Arrangement angle is. According to the technical Teaching is the pocket distance 0.8 to 1.8 times the size of the guide distance, causing the Imbalance Fc can be reduced.

Claims (14)

Rolling bearing, comprising: an inner ring ( 12 - 82 ) having an outer surface; an outer ring ( 11 - 81 ) having an inner surface; a plurality of rolling elements ( 13 - 83 ) rotatably disposed between the inner ring and the outer ring; and a holding device ( 14 - 84 ) for holding the rolling elements, wherein the holding device made of a resin material, it is positioned with respect to the inner surface of the outer ring or the outer surface of the inner ring, and a pair of annular parts arranged in parallel to each other in the axial direction of the bearing, and a columnar member forming the annular one Includes parts, including the following expression: Al = LH 3 /dm 2 ≥ 0.025 mm 2 . wherein H is a radial length of a portion of the annular member, L is an axial length thereof and dm is the pitch circle diameter of the rolling element, and the retaining device further comprises a plurality of pockets holding the rolling elements, a guide clearance between the inner surface of the outer ring or outer surface of the inner ring and a guided surface of the holding device is 0.05 to 0.4% of the diameter of the guided surface of the holding device; and the distance ( 6 ) Between the pockets of the holding device and the rolling elements is 0.8 to 1.8% of the guide distance. roller bearing according to claim 1, wherein the holding device with respect to the inner surface of the outer ring is arranged. roller bearing according to claim 1, wherein the holding device with respect to the outer surface of the inner ring is arranged. roller bearing according to claim 2, wherein the inner ring has shelves at both ends, and the rolling element a cylindrical roller is. roller bearing according to claim 3, wherein the outer ring has shelves at both ends, and the rolling element is a cylindrical Role is. roller bearing according to claim 2 or 3, wherein the rolling element is a ball. roller bearing according to at least one of the claims 1 to 6, wherein the holding device has a recess which axially on an outer circumference the holding device extends. roller bearing according to claim 7, wherein the depression has a dividing line (PL), the injection molding is formed having. Rolling bearing comprising: an inner ring; an outer ring; a plurality of rolling elements rotatably disposed between the inner ring and the outer ring; and a holding device ( 110 . 130 . 140 . 150 ) for holding the rolling elements, wherein the holding device ( 110 . 130 . 140 . 150 ) is made of a resin material and molded by injection molding, and the holding device ( 110 . 130 . 140 . 150 ) a recess ( 112 . 132 . 142 . 152 ) which extends axially on an outer circumference of the holding device ( 110 . 130 . 140 . 150 ) extends; the depression ( 112 . 132 . 142 . 152 ) has a dividing line (PL) formed during injection molding. roller bearing according to claim 9, wherein a depth of the recess has a value of 0.3 mm or more. roller bearing according to claim 9, wherein the recess has a semicircular shape. roller bearing according to claim 9, wherein the recess has a V-shape. roller bearing according to claim 9, wherein the recess is substantially a C-shape having. Spindle device for a machine tool with a rolling bearing according to at least one of the claims 1 to 13.