DE10164848B4 - Rolling bearing, has mutually adjoining rolling elements crossing each other alternately, and the outside diameters of the respective rolling elements always contacted at two points with the raceway surfaces of the first and second race - Google Patents

Abstract

Rolling elements (5) are located in the raceway groove between outer and inner races (1,2). The rolling elements have the outside diameters serving as the rolling contact surfaces and each has a curvature in the axial direction as well as having a radius smaller than the radius of the raceway surfaces of the outer and inner races. The rolling elements are arranged so that the mutually adjoining rolling elements cross each other alternately, and also the outside diameters of the respective rolling elements are always contacted at two points (11,12) with the raceway surfaces of the first and second race. Each of the rolling elements includes two mutually opposing flat surfaces, and preferably, each of the elements is a top and bottom cut-shaped ball which is formed by cutting upper and lower portions of the ball, to define the two mutually opposing and flat surfaces. At least one raceway surface, and rolling elements include a stainless steel, a ceramic material, or a resin material. A lubricant containing polymer is disposed in the internal space of the bearing. An independent claim is given for a rolling bearing for a compressor pulley.

Description

The The present invention relates to a rolling bearing having the features of Patent claim 1. Such a rolling bearing is for picking up a radial load, axial loads in two directions and a load moment in the situation. The warehouse can be for different Applications such as e.g. an industrial machine, a robot, a medical device, a semiconductor / liquid crystal manufacturing apparatus optical device, an opto-electronic device etc. be used.

Bearings are from the pamphlets DE 100 27 105 A1 . JP 09 126 233 A . US 1,235,116 DE / WO 32 48 980 A1, DE 44 11 287 A1 . JP 11270552 A , WO 99/43962 A1, US 5,441,350 A . DE 6 920 874 U . U.S. 3,674,357 . US 5 501 530 A . DE 196 54 545 A1 . DE 197 29 450 C2 . DE 41 42 313 A1 . JP 200 00 650 72 A and DE 2645287 A1 known.

Conventionally, as a bearing to be contained in the bearings, a radial load, thrust load in two directions and a load torque, a cross roller bearing and a four point contact roller bearing are known. In the conventional cross roller bearing and a four-point contact roller bearing known. In a conventional cross roller bearing is between an inner ring 100 and an outer ring 200 a cylindrical roller 300 installed (see 94 ). On the other hand, in the conventional four-point contact ball bearing between an inner ring 100 and an outer ring 200 a ball 400 installed (see 95 ).

• (1) Da im Falle des Kreuz-Rollenlagers ein Wälzelement eine zylindrisch geformte Rolle 300 und die Wälzkontaktfläche 301 der Rolle 300 im Linienkontakt mit einer Laufbahnnut 500 ist, wird ein großes Drehmoment erzeugt.
• (2) Da im Falle des Vierpunktkontakt-Kugellagers ein Wälzelement eine Kugel ist, erzeugt, wenn das Lager eine reine Axiallast aufnimmt oder wenn eine Axiallast über eine Radiallast dominiert, das Vierpunktkontakt-Kugellager ein kleineres Drehmoment, als das Kreuz-Rollenlager der gleichen Größe.

However, in the conventional cross roller bearing and the four point contact ball bearing, the following problems to be solved have been found out.

• (1) In the case of the cross roller bearing, since a rolling element has a cylindrically shaped roller 300 and the rolling contact surface 301 the role 300 in line contact with a track groove 500 is, a large torque is generated.
• (2) In the case of the four-point contact ball bearing, since a rolling element is a ball, when the bearing receives a pure thrust load or when axial load dominates over a radial load, the four-point contact ball bearing generates a smaller torque than the cross roller bearing of the same size ,

On the other hand, if a radial load dominates over an axial load or if the bearing receives a radial load, then each ball is 400 with a track groove 500 at four points 401 . 401 . 401 and 401 in contact, and therefore a spin slip occurs between the ball 400 and the track groove 500 on what results in a large torque.

As a bearing to be used in the high-speed rotary machine, such as the machine tool spindle, has been used in the prior art, an angular contact ball bearing or a four-point contact ball bearings in terms of their speed and axial rigidity, as in 96 to 98 is shown. The reference number 900 denotes a rotary shaft.

In 96 The radial load is due to two cylindrical roller bearings 600 supported, and axial loads in two directions are borne or the axial displacements are limited by two angular contact ball bearings 700 ,

In 97 carry the four angular contact ball bearings 700 the radial loads together with a cylindrical roller bearing 600 while the axial loads are carried in the two directions or the axial displacements are restricted.

In 98 The radial load is due to the two cylindrical roller bearings 600 , as in 96 , but the axial loads in the two directions are borne or the axial displacements are limited by a four point contact ball bearing 800 , as in 99 is shown.

In these figures, the reference numeral designates 801 an outer ring; the reference number 802 an inner ring; the reference number 803 a rolling element; and reference number 804 a cage.

Of the The prior art, if described, has the following problem on.

In the structures of 96 and 97 that the angular contact ball bearing 700 this can be an angular contact ball bearing 700 only carry the axial load in one direction. To carry the axial loads in two directions, it is therefore common to have two or more angular contact ball bearings 700 to use in combination.

However, the bearing to be used in the high-speed rotary machine, such as the machine tool spindle, requires high precision and therefore has a high price. If the number of angular contact ball bearings 700 In addition, as the sizes to be arranged become larger, the axial size of the bearing device becomes larger. Therefore, the bearing device and, accordingly, the entire system can not be made compact, which causes a problem that the cost of the entire device increases.

In the structure using the four-point contact ball bearing disclosed in US Pat 98 and 99 In addition, the individual can be shown Bearings the radial load, the axial loads in two directions and the load moment wear, so that the single four-point ball bearing 800 can realize the functions of the two angular contact ball bearings. Therefore, this structure has advantages in terms of compact size and low cost. However, where the radial load dominates over the axial loads or where a pure radial load is borne, the individual spheres represent 803 of four-point contact ball bearing 800 Contacts at four points with the rings 801 and 802 ago. Therefore, the balls rotate 803 to a great extent, causing a problem such that low spin wear performance can not be achieved. This problem is particularly severe by the effect of centrifugal force, especially in the case of the machine tool rotating at a high speed.

Around the spin wear behavior even just a little bit better, the distance between the Usually store positively determined. As a result, the stiffness of the bearings reduced, which adversely affects the rigidity of the entirety of Storage system for supporting causes the rotary shaft.

Of the present invention is based on the object, a rolling bearing which creates a spin slip between a rolling element and a raceway groove and can reduce the rolling resistance, to realize a low torque, thereby able to be a radial load, axial loads in two directions and one Take load moment, while the rolling elements held securely are.

These Task is by a rolling bearing solved with the features of claim 1.

at an embodiment of the rolling bearing can each of the rolling elements at least a flat surface exhibit.

at another embodiment of the rolling bearing can each of the rolling elements include two opposing and flat surfaces.

at the rolling bearing According to the present invention it is advantageous that each of the rolling elements a ball cut off on at least one side is which is formed by cutting off a portion of the sphere, so as to form at least one of the flat surfaces.

each the rolling elements can also be one at opposite Sides cut off shaped ball.

at the rolling bearing According to the present invention it is advantageous that the first race comprises first and second raceway surfaces.

at the rolling bearing According to the present invention it is advantageous that the first race is divided and also a fastening device has for fixing of the first and second raceway surfaces each Raceway with each other.

at the rolling bearing According to the present invention it is advantageous that the second race has first and second raceway surfaces.

at the rolling bearing According to the present invention it is advantageous that the second race is divided and also a fastening device has for fixing the first and second raceway surface each Race part together.

at the rolling bearing According to the present invention it is advantageous that the positioning device a cage is having circumferentially arranged holding portions, which the rolling elements on both sides in the direction of the alternately crossed axes of rotation hold.

at the rolling bearing According to the present invention it is advantageous that the positioning device is a plurality of spacers, from each of which has a diameter smaller than a diameter each of the rolling elements is as well as two recess-shaped Having curved grooves on opposite surfaces crossed.

at the rolling bearing According to the present invention it is advantageous that the positioning device a cage is having a number of recesses in which a same number of rolling elements are alternately inserted crossed, with the recesses along the circumferential direction of the cage are arranged offset and arranged at a predetermined distance in the circumferential direction are.

at the rolling bearing According to the present invention it is advantageous that at least one raceway surface and / or the plurality of rolling elements a stainless steel included.

at the rolling bearing According to the present invention it is advantageous that at least one raceway surface and / or the plurality of rolling elements a ceramic material included.

at the rolling bearing According to the present invention it is advantageous that at least one raceway surface and / or the plurality of rolling elements contain a plastic material.

at the rolling bearing According to the present invention it is advantageous that at least one raceway surface and / or the plurality of rolling elements have a corrosion resistant coating on a surface.

at the rolling bearing According to the present invention, it is advantageous also to have a flange include, formed on the first race and / or second race is.

at the rolling bearing According to the present invention, it is advantageous, in addition, a lubricant-containing To include polymer element, which is arranged in an interior of the bearing.

In the rolling bearing According to the present invention it is advantageous that an inner distance of the bearing has a negative value.

The Rolling bearing according to the invention is particularly suitable for a compressor pulley for supporting a rotary shaft and the like.

SHORT DESCRIPTION THE DRAWINGS

1 is a longitudinal sectional view of a first rolling bearing;

2A is an enlarged perspective view of a rolling element;

2 B Fig. 10 is an enlarged perspective view of another rolling element;

3 is a longitudinal sectional view of a second rolling bearing;

4 is a longitudinal sectional view of a third rolling bearing;

5 is a longitudinal sectional view of a fourth rolling bearing;

6 is a longitudinal sectional view of a fifth rolling bearing;

7 Fig. 10 is an enlarged perspective view of a spacer;

8th is a longitudinal sectional view of a sixth rolling bearing;

9 is an enlarged perspective view of a rolling element;

10 is a longitudinal sectional view of a seventh roller bearing;

11 is a longitudinal sectional view of an eighth rolling bearing;

12 is a longitudinal sectional view of a ninth roller bearing;

13 is a longitudinal sectional view of a tenth rolling bearing;

14 Fig. 10 is an enlarged perspective view of a spacer;

15 is a longitudinal sectional view of an eleventh rolling bearing;

16 is an enlarged perspective view;

17 is a longitudinal section, a first embodiment of a bearing of the present invention;

18 Fig. 10 is a perspective view showing an embodiment of a rolling element;

19 Fig. 10 is a perspective view showing another embodiment of a rolling element;

20 Fig. 10 is a perspective view showing an embodiment of a cage;

21 Fig. 10 is a perspective view showing an embodiment of a spacer.

22 is a longitudinal section of a roller bearing according to a second embodiment of the present invention;

23 Fig. 10 is an enlarged perspective view showing an example of a rolling element;

24 Fig. 10 is an enlarged perspective view showing another example of a rolling element;

25 is an enlarged perspective view of a cage;

26 Fig. 10 is an enlarged perspective view showing an example of a spacer;

27 Fig. 12 is a longitudinal section of a second example of the roller bearing with portions thereof omitted;

28 Fig. 15 is a longitudinal section of a third example of the roller bearing with portions thereof omitted;

29 Fig. 15 is a longitudinal section of a fourth example of the roller bearing with portions thereof omitted;

30 Fig. 15 is a longitudinal section of a fifth example of the roller bearing with portions thereof omitted;

31 Fig. 15 is a longitudinal section of a sixth example of the roller bearing with portions thereof omitted;

32 Fig. 15 is a longitudinal section of a seventh example of the roller bearing with portions thereof omitted;

33 Fig. 15 is a longitudinal section of an eighth example of the roller bearing with portions thereof omitted;

34 Fig. 15 is a longitudinal section of a ninth example of the roller bearing with portions thereof omitted;

35 Fig. 15 is a longitudinal section of a tenth example of the roller bearing with portions thereof omitted;

36 Fig. 11 is a longitudinal section of a first example of a roller bearing according to a third embodiment of the present invention;

37 Fig. 15 is a longitudinal section of a second example of the roller bearing with portions thereof omitted;

38 Fig. 15 is a longitudinal sectional view of a third example of the roller bearing with portions thereof omitted;

39 Fig. 15 is a longitudinal section of a fourth example of the roller bearing with portions thereof omitted;

40 Fig. 15 is a longitudinal section of a fifth example of the roller bearing with portions thereof omitted;

41 Fig. 15 is a longitudinal sectional view of a sixth example of the roller bearing with portions thereof omitted;

42 Fig. 15 is a longitudinal section of a seventh example of the roller bearing with portions thereof omitted;

43 Fig. 15 is a longitudinal section of an eighth example of the roller bearing with portions thereof omitted;

44 Fig. 15 is a longitudinal section of a ninth example of the roller bearing with portions thereof omitted;

45 Fig. 15 is a longitudinal section of a tenth example of the roller bearing with portions thereof omitted;

46 Fig. 15 is a longitudinal section of an eleventh example of the roller bearing with portions thereof omitted;

47 Fig. 15 is a longitudinal section of a twelfth example of the roller bearing with portions thereof omitted;

48 Fig. 15 is a longitudinal section of a thirteenth example of the roller bearing with portions thereof omitted;

49 Fig. 15 is a longitudinal section of a fourteenth example of the roller bearing with portions thereof omitted;

50 Fig. 15 is a longitudinal section of a fifteenth example of the roller bearing with portions thereof omitted;

51 Fig. 15 is a longitudinal section of a sixteenth example of the roller bearing with portions thereof omitted;

52 Fig. 15 is a longitudinal section of a seventeenth example of the roller bearing with portions thereof omitted;

53 Fig. 15 is a longitudinal section of an eighteenth example of the roller bearing with portions thereof omitted;

54 Fig. 15 is a longitudinal section of a nineteenth example of the roller bearing with portions thereof omitted;

55 Fig. 15 is a longitudinal section of a twentieth example of the roller bearing with portions thereof omitted;

56 Fig. 15 is a longitudinal section of a twenty-first example of the roller bearing with portions thereof omitted;

57 is a longitudinal section of a first example of a roller bearing;

58 is a longitudinal section of a second Example of the roller bearing, with portions thereof omitted;

59 is a longitudinal section of a fourth embodiment of a roller bearing according to the present invention;

60 is a graph showing results of a comparison test relating to a torque; and

61 is a graph showing results of a comparison test relating to a torque resistance.

62 is a longitudinal section of a fifth embodiment of the invention;

63 Fig. 10 is an enlarged perspective view to show an example of a rolling element of the fifth embodiment;

64 Fig. 10 is an enlarged perspective view to show another example of a rolling element of the fifth embodiment;

65 Fig. 10 is a perspective view to show an example of a cage of the fifth embodiment;

66 Fig. 10 is a perspective view to show an example of a spacer of the fifth embodiment;

67 is a longitudinal section of a sixth embodiment of the invention;

68 is a longitudinal section of a seventh embodiment of the invention;

69 is a longitudinal section of an eighth embodiment of the invention;

70 Fig. 10 is an enlarged perspective view to show a modification of a rolling element in the eighth embodiment;

71A FIG. 11 is a sectional view showing an enlarged scale portion of a rolling bearing constituting a rolling bearing device of the present invention; and FIG 71B is a perspective view of a rolling element, which in the in 71A to be installed bearing shown;

72 Fig. 10 is a sectional view showing a rolling bearing;

73 is a sectional view of another embodiment of the rolling bearing;

74A is a sectional view showing a rolling bearing, and 74B is a perspective view showing a rolling element, which in the in 74A to be installed bearing shown;

75A is a sectional view showing another embodiment of the rolling bearing, and 75B is a perspective view showing a rolling element, which in the in 75A to be installed bearing shown;

76 is a partially enlarged view showing an embodiment of a cage, which in the camp of 75 is to be installed;

77A is a partially sectioned schematic view of a recess portion of the cage of 76 , and 77B Fig. 16 is a partially sectional view showing another embodiment;

78 Fig. 4 is a partially enlarged view showing another embodiment of the cage;

79 is a sectional view of the recess portion of the cage of 78 ;

80 is a perspective view of a spacer for the in 75B shown rolling element;

81 Fig. 10 is a sectional view showing a shape of the bearing apparatus of the present invention;

82 Fig. 10 is a sectional view showing a shape of the bearing apparatus of the present invention;

83 Fig. 11 is a sectional view to show another embodiment of a rolling bearing of the invention;

84 Fig. 12 is a perspective view to show an embodiment of a rolling element incorporated in the rolling bearing of the invention;

85 Fig. 10 is a development to show an embodiment of a cage incorporated in the rolling bearing of the invention with a part omitted;

86 is a sectional view taken on the line IV-IV in 85 runs;

87 is a sectional view to a modified embodiment of 85 to show;

88 is a transaction to another To show embodiment of a cage;

89 is a sectional view taken on the line VII-VII in 88 runs;

90 Fig. 10 is a perspective view to show an embodiment of a spacer;

91 is a sectional view to show a further embodiment of the invention;

92 is a sectional view to show a further embodiment of the invention;

93 is a sectional view to show a further embodiment of the invention;

94 Fig. 15 is a longitudinal sectional view of a conventional cross roller bearing; and

95 is a longitudinal sectional view of a conventional four-point contact ball bearing.

96 is a sectional view of a prior art;

97 Fig. 10 is a sectional view of another prior art;

98 is a sectional view of another prior art; and

99 is a sectional view of a four-point contact ball bearing, which in 98 is used.

below Now, a description will be made of a way to execute a roller bearing according to the invention with reference to the accompanying drawings given.

The rolling bearing comprises a race (as an outer ring) 1 , another race (as an inner ring) 2 , a track groove 3 passing through the inner diameter of the race 1 and the outer diameter of the race 2 is limited and arranged between them, and a plurality of rolling elements 5 . 5 ---, each in the track groove 3 are installed.

The two races 1 and 2 are constructed such that a raceway groove 3 has a desired shape through raceway surfaces 1a . 1b and 2a . 2 B can be formed, each on the inner diameter of the one race (outer ring) 1 and on the outer diameter of the other ring (inner ring) 2 are formed. As a rolling bearing, a rolling bearing of a type may be used in which one or both races 1 and 2 in the middle of the same is divided into two raceway sections in the axial direction, or use a rolling bearing of a type in which neither of the two races 1 and 2 shared.

As a two-part type rolling bearing, there is also available a rolling bearing which is an integrated body using a screw or a rivet 4 can be mounted.

The raceway groove 3 is through the raceway surfaces 1a . 1b and 2a . 2 B each of which has a radius greater than the radius of each of the rolling elements 5 ,

Each of the raceway surfaces 1a . 1b and 2a . 2 B in any shape, such as a shape having an arcuate portion, having a V-like shape, having a curved shape or having a linear shape, provided that they are for the rolling motion of the rolling element 5 suitable is. That is, the shape of the raceway surface is not limited to a specific shape, but the shape of a Gothic arch can be used.

Each of the rolling elements 5 can have any shape, provided that its outer diameter 5a serving as its rolling contact surface, at least one curvature in the axial direction of the rolling element 5 whose radius is smaller than the radius of the respective raceway surface 1a . 1b and 2a . 2 B is. In other words, as in 2 is shown, has each of the rolling elements 5 a rolling contact peripheral surface S defined by rotating a curved bus line Y about its rotation axis X. The curved bus line Y has at least one predetermined curvature, each of which is smaller than one of the radii of the raceway surfaces of the respective raceway surfaces 1a . 1b and 2a . 2 B ,

However, in this embodiment, the curved bus line Y has a single predetermined curvature smaller than one of the radii of the raceway surfaces of the respective raceway surfaces 1a . 1b and 2a . 2 B ,

The rolling elements 5 are arranged in such a manner that the mutually adjacent ones of the rolling elements alternately intersect each other while the respective outer diameters 5a the rolling elements 5 always at two points with the raceway surfaces 1a . 1b of a race 1 and the raceway surfaces 2a . 2 B the other race 2 is in contact.

For example, the rolling element 5 have a structure consisting of a ball formed on two opposite sides (top and bottom) with a cut (top-and-bottom-cut-shaped Ball), which is a series of opposing surfaces 5a and 5b (That is, a structure obtained when the upper and lower portions of a ball are cut off thereby the opposing surfaces 5a and 5b to build; this term will also be used below). The rolling elements 5 . 5 , --- are each in the track groove 3 installed in such a way that their respective axes of rotation 5c perpendicular to their respective opposite surfaces 5b and 5b intersect each other, and at the same time their respective outer diameters 5a the rolling elements 5 always at two points with the raceway surfaces 1a . 1b of a race 1 and the raceway surfaces 2a . 2 B the other race 2 in contact.

The cutting widths of the upper and lower regions of the rolling element 5 are not limited to any specific dimensions, and these two cutting widths may or may not be equal to each other; and a ratio between the two cutting widths can be arbitrarily selected without departing from the scope of the invention. In other words, the opposing surfaces 5b and 5b of the rolling element 5 may be symmetrical or asymmetrical, that is, each of the symmetrical and asymmetric determinations falls within the scope of the invention.

Incidentally, the entire shape of the rolling element 5 , the presence or absence of opposing surfaces 5b . 5b and the size of the curvature of the outer diameter 5a in the axial direction thereof are not limited to those described above, but may be arbitrarily changed without departing from the scope of the invention. That is, for example, the rolling element 5 instead of opposing surfaces 5b . 5b include two surfaces that are not parallel to each other and can also have their own axis of rotation 5c which is perpendicular to these two non-parallel surfaces.

While the rolling elements 5 . 5 , --- are built in such a way that the axes of rotation 5c . 5c the two mutually adjacent rolling elements 5 . 5 each perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b Alternating with each other, the kind of crossing may be provided at right angles thereof or not at right angles.

The type of intersection of the rolling elements 5 is not limited to a specific type of crossing, provided that the intersecting rolling elements 5 in their total number on both sides are the same. That is, the rolling elements 5 can cross each other one to one; or they may cross in the manner of two, one, one, and two, provided that the intersecting rolling elements are equal in their total number on both sides thereof. Each of the types of intersection falls within the scope of the invention.

The movements of the respective rolling elements 5 . 5 can through a cage 6 . 6 ' or a spacer (a spacer) 8th be guided.

The shape of the cage 6 . 6 ' or the spacer (spacer) 8th is not limited to a specific form, provided that they are holding areas 7 , ---, recesses 13 , --- or grooves 9 . 9 includes. That is, the shape of the cage 6 or spacer (spacer) 8th can be arbitrarily and arbitrarily changed without departing from the scope of the invention.

In addition, the guide system of the cage 6 . 6 ' not limited to a specific one as described above. An inner ring guide type, an outer ring guide type or a rolling element guide type may also be used instead. Further, a structure of the cage 6 . 6 ' not limited to a specific one as described above. Namely, not only a single unit type but also a divided race component type can be used.

For example, in the case of the cage 6 are in the circumferential direction of the same alternately two holding areas 7 . 7 (or the recesses 13 , --- of the cage 6 ' ), in which the mutually adjacent rolling elements 5 . 5 can be installed in such a way as described above that the axes of rotation 5c . 5c the same perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b alternately crossing each other.

The spacer 8th has a diameter that is smaller than the diameter of each rolling element 5 , and in their opposite surfaces 10 . 10 are two recess-shaped arc grooves 9 . 9 formed in a mutually intersecting manner, which are each capable of the mutually adjacent rolling elements 5 . 5 to hold in such a way that, as described above, the Rotationsach sen 5c . 5c the same perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b to cross each other.

The curvature of the curved groove 9 may be arbitrary, ie, it may be substantially equal to or greater than the curvature of the outer diameter 5a of the rolling element 5 be set.

The Way of applying a preload between the rolling element and the raceway area is not limited to a specific one. That is, the preload can be in be applied to the storage manufacturing stage or not, both these modes of use fall within the scope of the invention.

As a material for making the races 1 . 2 and the rolling elements 5 Rolling bearing is usually used a bearing steel. However, other material such as stainless steel, ceramics or the like, which is suitable for increasing wear resistance or heat resistance, is also selectable in accordance with the environmental use of the rolling bearing.

Additionally is also available as a cage 6 . 6 ' used in the present invention, a machined cage, a pressed cage, a resin cage or the like selectable according to the requirements. Correspondingly, a metal material (eg brass, steel or the like) or a synthetic resin (eg polyamide 66 (Nylon 66 ), Polyphenylsulfide (PPS) or the like) suitable for it are used selected.

When next a description of rolling bearings will be given below.

1 shows a first rolling bearing.

Each of the rolling elements 5 . 5 , as in 2A consists of a ball formed at the top and bottom with a cut, which is a set of opposing surfaces 5b and 5b includes; and the rolling element 5 is in a track groove 3 installed between an outer ring 1 , which is integrally formed with the rolling bearing, and two split inner rings 2 . 2 is trained.

The raceway groove 3 is formed in a Gothic arch, which runs through the raceway surfaces 1a . 1b and 2a . 2 B is limited to the respective outer and inner ring, each having a radius which is greater than the radius of the rolling element 5 ; and the opposing surfaces 5b and 5b of the rolling element (ball formed at the top and bottom with a cut) are formed to have a symmetry.

The rotation axes 5c . 5c the rolling elements 5 . 5 that are perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b are arranged so as to alternately cross each other, and the movements of the rolling elements 5 . 5 be through the holding areas 7 . 7 a cage 6 guided.

In the case of the cage 6 may alternately two holding areas in the circumferential direction thereof 7 . 7 be formed, in which the mutually adjacent rolling elements 5 . 5 can be installed in such a way that, as described above, the axes of rotation 5c . 5c the same perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b alternately cross each other.

Therefore, according to the first embodiment, the outer diameter 5a of the rolling element 5 at two points (the contact points are with 11 . 11 designated) with the raceway surface 1a of the outer ring 1 and the raceway area 2 B of the inner ring 2 in contact, which are arranged opposite to each other, while the mutually adjacent rolling elements 5 each (the contact points are with 12 . 12 designated) with the raceway surface 1b of the outer ring 1 and the raceway area 2a of the inner ring 2 stay in contact.

As the contact angle of the rolling elements 5 . 5 alternating with each other, the single bearing is able to absorb a radial load, thrust loads in two directions and a load moment.

As well as a rolling element 5 only at the two points ( 11 . 11 ) with the raceway surfaces 1a . 2 B is in point contact and the other rolling element 5 only at the two points ( 12 . 12 ) with the raceway surfaces 1b . 2a In point contact, such a large spin motion can be eliminated as in the conventional four point contact bearing.

There continues to be the way of contact between the rolling elements 5 . 5 and the outer and inner ring 1 . 2 the same as in the conventional ball bearing, a low rolling resistance can be generated as compared with a cross roller bearing, which makes it possible to realize a low torque.

Now shows 3 a second rolling bearing. Two divided inner rings 2 and 2 are together by a screw or a rivet 4 fixed to thereby eliminate the need for adjusting a preload or a gap between them.

The remaining structures and work effects are the same as those of the first rolling bearing.

4 shows a third rolling bearing. Instead of the one-piece outer ring 1 and the two split inner rings 2 . 2 , which are used respectively in the first embodiment, become two divided outer rings 1 . 1 and a one-piece inner ring 2 used.

The other remaining structures and work effects are the same as those of the first Wälzla gers.

5 shows a fourth bearing. The two divided outer rings 1 . 1 that are used in the third rolling bearing are together by a screw or a rivet 4 fastened together, thereby eliminating the need for setting a preload or a gap between them.

The other remaining structures and labor effects are the same, like those of the first rolling bearing.

6 shows a fifth bearing. As in 6 shown are a one-piece outer ring 1 and a one-piece inner ring 2 used. In the outer ring 1 a rolling element insertion hole is formed. Also, instead of the cage 6 used in the first rolling bearing as enlarged in 7 shown is a spacer 8th used; ie that the rolling elements 5 . 5 through the spacer 8th be guided.

With By using this structure, the rolling bearing can be made more compact.

The other remaining structures and labor effects are the same, like those of the first rolling bearing.

The spacer 8th has a diameter that is smaller than the diameter of each rolling element 5 , and in the two opposite surfaces 10 of the spacer 8th are recess-shaped arc grooves 9 . 9 formed, which are each used to the rolling elements 5 . 5 in such a way that, as described above, the axes of rotation 5c . 5c the same perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b to cross each other.

8th shows a sixth rolling bearing. This is suitable for use with a high speed rotary housing.

Instead of the rolling element 5 that have two symmetrical opposing surfaces 5b . 5b includes, as used in the first rolling bearing, a rolling element (a ball formed at the top and bottom with a cut) 5 ' used that two asymmetric opposing surfaces 5b ' . 5b ' , as in 9 is shown, and the rolling element 5 ' is arranged in such a way that the larger ends 5d ' the two opposite surfaces 5b ' . 5b ' the same opposite to the inner ring 2 are arranged of the existing rolling bearing. With the use of this structure, the rotation of the rolling element 5 be further stabilized, which makes it possible to further realize a reduced torque.

The other remaining structures and labor effects are the same, like those of the first rolling bearing.

10 shows a seventh roller bearing. The two split inner rings 2 and 2 are connected to each other by a screw or a rivet 4 fixed, thereby eliminating the need for adjustment of a preload or a gap between them.

The other remaining structures and labor effects are the same, like those of the sixth bearing.

11 shows an eighth bearing. Instead of the one-piece outer ring 1 and the two split inner rings 2 . 2 used in the first embodiment become two divided outer rings 1 . 1 and a one-piece inner ring 2 used.

The other remaining structures and labor effects are the same, like those of the sixth bearing.

12 shows a ninth roller bearing. The two divided outer rings 1 . 1 used in the eighth embodiment are connected to each other by a screw or a rivet 4 fixed, thereby eliminating the need for adjustment of a preload or a gap between them. The other remaining structures and work effects are the same as those of the sixth rolling bearing.

13 shows a tenth rolling bearing. As in 13 is shown, a one-piece outer ring 1 and a one-piece inner ring 2 used. In the outer ring 1 a rolling element insertion hole is formed. Also, instead of the cage 6 used in the first embodiment and as enlarged in FIG 14 shown is a spacer (spacer) 8th used; ie the rolling elements 5 . 5 be through the spacer 8th guided. With the use of this structure, the rolling bearing can be made more compact.

The other remaining structures and labor effects are the same, like those of the sixth bearing.

The 15 to 16 show an eleventh rolling bearing according to the invention. 15 is a longitudinal sectional view. 16 Fig. 10 is an enlarged perspective view of an example of a cage also used in the invention. 2 B is an enlarged perspective view of an example of a rolling bearing, which is used in the invention.

In the rolling bearing is instead of a cage 6 used in rolling bearings, etc., a machined cage 6 ' (an annular cage), as in 16 is shown used in such a way that a holding position of each rolling element 5 through the machined cage 6 ' is maintained.

The cage 6 ' has a number of recesses 13 , in which the same number of rolling elements 5 . 5 are respectively inserted while the axes of rotation 5c . 5c from one of the mutually adjacent rolling elements perpendicular to their associated opposite surfaces 5b . 5b and 5b . 5b to cross each other. The recesses 13 , --- are alternately on a peripheral area of the cage 6 ' arranged in a staggered manner at a predetermined distance in the circumferential direction thereof.

Both side surfaces 13a . 13b every recess 13 in the axial direction of the cage 6 ' extend parallel to each other, but their extension directions are neither parallel nor perpendicular to the axial direction of the bearing are located. Each of the extension directions limits a predetermined angle (inclined angle) relative to the axial direction of the rolling bearing, while the predetermined angle (inclined angle) is set to a level substantially equal to a contact angle of the respective rolling element 5 is.

A distance between the side surfaces 13a . 13b is made slightly larger than a width of the rolling element 5 ,

It is to be noted that the entire shape of each recess is not limited to a specific shape as described above. The shape of the recess may be modified while maintaining a construction such that the recess 13 the parallel extending inclined side surfaces 13a . 13b has and also a distance between the side surfaces 13a . 13b is set slightly larger than the width of the rolling element 5 ,

Although at the eleventh bearing the rolling elements 5 , --- and the recesses 13 ---, whose total number is the same as that of the rolling elements, each with a predetermined gap in the circumferential direction are arranged and alternately on the peripheral portion of the cage 6 In a staggered manner, a configuration of the cage according to the present invention is not limited to such a specific configuration. If the total number of recesses is the same as that of the rolling elements, it is possible to modify the configuration in such a way that the axes of rotation 5c . 5c the mutually adjacent one of the rolling elements 5 Two to two cross each other or they can cross in the manner of two, one, one and two.

In addition, a material of the cage 6 ' not limited to a specific material. For example, a metal material (eg, brass, steel, or the like) or a synthetic resin (eg, polyamide 66 (Nylon 66 ), Polyphenylsulfide (PPS) or the like) may be used. Further, a guide system of the cage 6 ' not limited to a specific management system. An inner ring guide type, an outer ring guide type or a rolling element guide type may be used. Further, a structure of the cage 6 . 6 ' not limited to a specific structure. Not only a single unit type but also a shared career component type may be selectively used.

It it is possible, that a turning or a skew of the rolling element during the Rotation of the rolling element occurs because of the influence, based on different species of factors. Correspondingly, in the case where the Wälzstellung of the rolling element not Well controlled, the possibility that a rotational resistance of the rolling bearing is increased and turn a uniform Rotation of the rolling element deteriorated.

However, in the present invention, each recess has 13 of the cage 6 ' parallel extending inclined side surfaces 13a . 13b which are inclined relative to the axial direction of the rolling bearing at a predetermined angle, which is substantially equal to the level of the contact angle of the rolling element 5 is. The side surfaces 13a . 13b can change the position of the rolling element 5 suppress, which by the turning or the skew of the rolling element 5 is effected, so that a position of the rolling element can be stably maintained to thereby realize a reduced torque of the rolling bearing.

The other remaining structures and labor effects are the same, like those of the first to fourth and those of the sixth to ninth Bearing.

Although both the outer ring 1 as well as the inner ring 2 are made of a single unit type, a structure of each race is not limited to such a specific structure. It is possible to modify it in such a way that one or both of the inner and outer rings is made of a split race component type in which the race is divided into two components at a middle position in the width direction, or one or both of the inner race and outer race is made of the split race component type. It should be noted that, as an example of the split race component type, there is a mounted type that can be achieved by coupling the divided raceway component types by a screw / rivet 4 is made in a mounted single unit.

In addition, though, as in 2 B the rolling elements 5 are the same as those of the first rolling bearing, it is instead possible, the rolling elements 5 through the rolling elements 5 ' to be used in the sixth to ninth bearings. That is, it becomes a rolling element (a ball formed at the top and bottom with a cut) 5 ' used the two asymmetric, opposing surfaces 5b ' . 5b ' includes, as in 9 is shown, and the rolling element 5 ' is arranged in such a way that the larger ends 5d ' of the two opposing surfaces 5b ' . 5b ' the same opposite to the inner surface 2 are arranged of the existing rolling bearing. With the use of this structure, the rotation of the rolling element 5 ' be further stabilized, which makes it possible to realize a further reduced torque. According to the present invention, since it has the above-described structure, it is possible for a single bearing to receive a radial load, thrust loads in two directions, and a load torque.

Also, in addition to the above effect, the following effects can also be achieved:
That is, since the rolling elements are always in contact with the raceway surface at two points, it is possible to control an increase in the torque caused by the large spin of the ball in the conventional four-point contact bearing.

There also the rolling element is formed in such a manner that its outer diameter serves as its Wälzkontaktfläche, a curvature in the axial direction in the same can, compared with a Cross roller bearing of the rolling resistance of the rolling element be diminished, what it possible makes to realize a low torque.

A first embodiment of the present invention will be described with reference to FIG 17 described.

In the drawings, the reference numeral designates 1 an outer ring; numeral 2 an inner ring; numeral 23 a pulley; numeral 5 a rolling element; numeral 16 a cage and reference number 20 a sealing plate.

One roller bearing The present invention can be broadly within the scope of protection used in the present invention, if it is in a compressor pulley is used, and it should not be interpreted in a particularly restrictive way. For example, the rolling bearing not only for The pulley of a compressor used to be an electromagnetic Clutch used, but also for a throttle pulley a compressor that does not use an electromagnetic clutch.

The outer ring 1 has two right and left separate races.

The two right and left raceway surfaces 1a and 1b are different at their midpoint of axial curvature.

The radius of curvature of the raceway surfaces 1a and 1b is set larger than that of the rolling element 5 and set to a value of 50.3 to 54% of the diameter of the rolling element in the present invention.

The inner ring 2 has career surfaces 2a and 2 B formed in the shaped portion of a Gothic arc, and the radius of curvature of the two groove ends is larger than that of the groove center.

The individual raceway surfaces are provided at areas slightly offset from the groove center are.

The radius of curvature of the raceway surfaces 2a and 2 B is like the outer ring 1 set larger than that of the rolling element 5 and is set to a value of 50.3 to 54% of the diameter of the rolling element in the present invention.

in this connection the inner ring of the embodiment shown is given a structure, in which the raceway surfaces a non-bow shape are ground simultaneously. Where this sanding work difficult because of the problem of equipment, but can a Schleifabstandsnut be formed in the Nutmitte to form two arcuate grooves, their individual centers of curvature are in different places.

In addition, the construction of the sealing grooves should 1c and 2c of the outer ring 1 and the inner ring 2 not specifically limited, but may be suitably modified within the scope of the present invention.

at According to the present invention, the rolling element can not be in the raceway the one-piece structure be incorporated, so that at least one race a split Structure is given.

In the present embodiment, the outer ring 1 is given the split structure with a press fit so that it can easily maintain a preload. However, the present invention should not be interpreted to be restrictive, but may include a structure in which the inner ring 2 is divided or in which both the inner ring 2 as well as the outer ring 1 are divided within their scope.

In addition, the outer ring 1 with an oversize on the diameter surface of the compressor pulley 23 Press-fit, and is by applying a pressure until the split surface 1c comes into contact, installed. The size of the individual areas are handled so that a suitable preload can be applied when the pressure is applied until the divided area 1c comes into contact.

After the outer ring 1 on the pulley 23 attached by pressing, this pulley is 23 additionally attached to its end face, leaving the outer ring 1 can not move axially to change the preload.

The compressor pulley 23 should not be specifically limiting, but may be arbitrary constructed / modified within the scope of the present invention. A steel bushing is welded to the inner diameter of the pulley, which was rolled, for example, from a steel sheet.

In the rolling element 5 has an outer diameter 5a for a Wälzkontaktfläche any shape in which it has a curvature in the axial direction, and also has a smaller radius than the individual radii of the raceway surfaces 1a and 1b , and 2a and 2 B , The two rolling elements adjoining in the circumferential direction are installed so that they are alternately directed differently to have contact angles with inverse values. At the same time the outer diameter leads 5a each rolling element 5 always two point contacts, either with the raceway surface 1a of a race 1 and the raceway area 2 B the other race 2 or with the track surface 1b of a race 1 and the raceway area 2a the other race 2 ,

The Number of rolling elements is for made the two-point contact even.

For example, the rolling element 5 a ball cut off at two ends, which is a set of opposite surfaces 5b and 5b has (ie, a structure, the opposite surfaces 5b and 5b by cutting off the two ends of a sphere in a planar manner, as explained below) ( 18 ). The individual rolling elements 5 . 5 , ---, etc. are installed so that the axes of rotation 5c perpendicular to the opposite surfaces 5b and 5b intersect each other, and the outside diameter 5a each rolling element 5 carries two-point contacts either with the raceway surface 1a of a race 1 and the raceway area 2 B the other race 2 or with the track surface 2 B of a race 1 and the raceway area 2a the other race 2 out.

The rolling element 5 should not be limited in the cutting widths at both its ends, and the cutting widths of the two ends may be the same or may not be the same, so that their ratio which has been arbitrarily selected is within the scope of the present invention. In other words, the opposing surfaces 5b and 5b of the rolling element 5 may be symmetrical or asymmetrical, and either this symmetrical definition or asymmetric definition is within the scope of the present invention.

Here, the entire shape of the rolling element should 5 , the presence or absence of opposing surfaces 5b and 5b and the size of the curvature of the outer diameter 5a in the axial direction are not limited to the specific sizes explained above, but can be arbitrarily changed within the scope of the present invention.

That is, the rolling element 5 can instead of opposing surfaces 5b and 5b include two surfaces that are not parallel to each other, and can also have their own axis of rotation, for example 5c have that is perpendicular to the two surfaces.

In addition, the use of the in 19 shown rolling element also within the scope of the present invention. That is, a rolling element 5 ' (Or a ball cut off at two ends), the asymmetrical opposite surfaces 5b ' and 5d ' is used, and the opposing surfaces 5b ' and 5d ' are arranged such that the larger front side 5d ' the inner ring 2 facing the camp. Then the rotation of the rolling element 5 ' be stabilized better to realize a lower torque.

In addition, the rolling element 5 . 5 , ---, etc. built in such a way that the Rotationsach sen 5c and 5c perpendicular to the individual opposite surfaces 5b and 5b . 5b and 5b the adjacent rolling elements 5 and 5 can cross each other alternately. In addition, the intersection types may be performed at right angles or not at right angles.

The movements of the individual rolling elements 5 and 5 be through the cage 16 guided.

The cage 16 As illustrated by the present embodiment, an in 20 shown annular cage to the position of the individual rolling elements 5 to keep.

The cage 16 is made of a resin material, such as nylon 66 , Nylon 46 or polyphenylene sulfide poured.

The cage 16 is held by rolling elements, but could be passed through the inner ring or the outer ring.

To control the position of a rolling element in rotation, each of a plurality of recesses 16b as seen in the circumferential direction of an annular element 16a of the cage 16 are formed, with two parallel side surfaces 16c and 16d at the same level as the contact angle of the rolling element 5 intended. Therefore, the position of the rolling element 5 be maintained to realize a low torque of the bearing.

It is possible, too, a machined cage to use, made by cutting brass or steel material becomes.

The distance between the two side surfaces 16d and 16d every recess 16b is made slightly larger than the width of the rolling element 5 ,

The shape of the recess 16b should not be interpreted restrictively in its entire form, but may be modified within the scope of the present invention if it is shaped to have two inclined side surfaces 16c and 16d and a fairly large distance between the two side surfaces 16c and 16d as the width of the rolling element 5 having.

In addition, the structure of the cage should 16 be neither particularly limited, but may be of monolithic type or consist of different areas.

The cage 16 should not be particularly limited if it is shaped to have an area for restraining and guiding the rolling element 5 but may be arbitrarily selected and changed within the scope of the present invention.

In addition, also falls the camp, in which a spacer (or spacer) 8th recess-shaped arc grooves 9 and 9 , as in 21 is also within the scope of the present invention.

The spacer 8th has a smaller diameter than that of the rolling element 5 , In opposite surfaces 10 and 10 are in a cross shape, the recess-shaped arc grooves 9 and 9 for holding the individual adjacent rolling elements 5 and 5 designed such that the axes of rotation 5c and 5c perpendicular to the opposite surfaces 5b and 5b , and 5b and 5b can cross each other as previously described.

The curvature of these arc grooves 9 is arbitrary and may be substantially equal to or greater than that of the outer diameter 5a of the rolling element 5 be.

If the spacer 8th is used in this way, the bearing can be made compact as a whole.

The sealing plate 20 is a plate gasket having a core coated with rubber or a resin. The mounting area (or outer diameter) of the gasket plate 20 is with the groove 1c fixed, which is formed in the outer ring, and the sealing lip (or the inner diameter) is in sliding contact with the cylindrical surface 2c of the inner ring, leaving the sealing plate 20 is not influenced in its sealing behavior by the machining inaccuracies of the size of the individual areas in the axial direction.

at the present embodiment is the contact type seal taken over, but this by a non-contact type seal or a contactless Shielding can be replaced. This seal should not be special but can be suitably distinguished from the well-known Molds are selected within the scope of the present invention.

Furthermore the presence or absence of the nucleus is free, and the Type with or without the core can be used separately if necessary, but not restrictive should be interpreted.

With the structure thus far described, according to the present invention, the rolling element makes contact with only one point with each race so that it can hardly slip by Spin movements to reduce the displacement wear during spin movement.

Furthermore are the rolling elements alternately arranged so as to intersect on the circumference such that the two circumferentially adjacent rolling one of the rolling elements, which are in contact with one of the two raceway surfaces, the formed on each race, with the other raceway surface in contact can stand. Therefore the bearing has a high moment stiffness.

Therefore Is it possible, to provide a bearing which is more compact than the double row Bearings of the prior art and which in terms of moment stiffness and the spin wear retention Superior three-point contact bearing is, although the sizes are the same to those of the three-point contact bearing are. As a result, can the entire device can be made compact and easy and can be improved in terms of life and low cost become.

below Other preferred embodiments which is explained according to the present invention.

As in the 22 to 35 is shown, a roller bearing according to the present invention comprises a ring (outer ring) 1 ; another ring (inner ring) 2 ; a variety of rolling elements 5 . 5 , ... in a track groove 3 are installed, wherein the groove between the inner diameter of the outer ring 1 and the outer diameter of the inner ring 2 is limited; and sealing plates 20 placed between the outer and inner ring 1 and 2 are interposed.

The raceway groove 3 is in a desired shape by means of raceway grooves 1a and 1b shaped along the inside diameter of the race (outer ring) 1 and by means of treads 2a and 2 B shaped along the outer diameter of the raceway (inner ring) 2 are shaped. A roller bearing (roller bearing) that supports the races 1 and 2 of the non-disconnected type or includes a roller bearing housing the races 1 and 2 where either or both are axially separated into two parts along the widthwise center thereof is used.

Some Double-separation type ball bearings are being used in one part mounted by screws or rivets. If a ball bearing of double-separation type fastened using screws or rivets, is unnecessary the need for a preload or distance settings.

The raceway groove 3 is through the raceway surfaces 1a . 1b . 2a and 2 B limited, each larger in radius than the rolling element 5 ,

Each of the raceway surfaces 1a . 1b . 2a and 2 B can take any shape, such as a cross-sectional profile of a sheet, a letter V, a curve or a straight line, as long as the raceway surface assumes a geometry that is suitable for a rolling process of the rolling elements 5 suitable is. In short, the raceway surface is not limited to a particular shape. For example, the cross-sectional profile of a gothic arch is transferred to a surface.

The rolling element 5 can take any shape, which has an axial curvature to an outer diameter 5a which serves as a rolling contact surface and is smaller in radius than each of the raceway surfaces 1a . 1b . 2a and 2 B , The rolling elements 5 are arranged in such a manner that the alternating rolling elements 5 to cross each other with angles. Two contact points exist between the outer diameter 5a each rolling element 5 and the track groove 3 at any time, namely the outside diameter 5a remains in contact with the raceway surfaces 1a and 2 B or the outside diameter 5a remains in contact with the raceway surfaces 1b and 2a ,

For example, the rolling element takes 5 the shape of a ball, which are truncated at the top and bottom, with the flattened surfaces opposite surfaces 5b . 5b (More specifically, a structure formed by flattening the top and bottom of a sphere, thereby forming the opposite surfaces 5a and 5b to shape, and in the description that follows, the same thing was applied to any counterparts). The rolling elements 5 . 5 , ... are in the track groove 3 installed such that a Rotationsmittelachse 5c perpendicular to the opposite surfaces 5b . 5b a rotating element 5 is that of the other adjacent rotating element 5 crosses. Two contact points always exist between the outer diameter 5a each rolling element 5 and the raceway surfaces, namely the outer diameter 5a remains in contact with the raceway surfaces 1a and 2 B or the outside diameter 5a remains in contact with the raceway surfaces 1b and 2a ,

No specific dimensional limitations are the cutting widths at the top and bottom of the rolling element 5 imposed. The cutting widths can be the same or different from each other. A ratio between the cutting widths may be arbitrarily selected within the scope of the invention. The opposite surfaces 5b . 5b of the rolling element 5 may be symmetric or asymmetric, and both symmetric and asymmetric opposite Surfaces are within the scope of the invention.

The entire geometry of a rolling element 5 , the presence or absence of opposite surfaces 5b . 5b and the size of the axial curvature of the outer diameter 5a are not limited to specific specified geometries; they are approved for any modifications without departing from the scope of the invention.

For example, a rolling element 5 non-parallel surfaces instead of opposing surfaces 5b . 5b have, as well as a rotation axis 5c perpendicular to the surfaces.

The use of a rolling element, as eg in 24 is also within the scope of the invention. More in detail are rolling elements 5 ' that are asymmetrical and opposite surfaces 5b ' . 5d ' have (the elements, which consist of balls that are flattened at the top and bottom) used. The rolling elements 5 ' are arranged such that a larger area 5d ' the opposing surfaces 5b ' . 5d ' to the inner ring 2 of the warehouse. As a result, the rotation of the rolling element becomes 5 ' more stable, and a low rotating element can be achieved. The ball bearing described in connection with the first aspect of the invention is primarily used for high speed applications.

The rolling elements 5 . 5 , ... are built in such a way that the rotation center axis 5c perpendicular to the opposite surfaces 5b . 5b of a rolling element 5 that of the other adjacent rolling element 5 crosses at a right angle or any angle.

If the rolling elements 5 that are aligned in a direction equal in number to those aligned in the other direction, crossing may occur at any number of rolling elements. In other words, the rolling elements 5 intersect alternately. In addition, provided the rolling elements 5 , which are aligned in a direction equal in number to those aligned in the other direction, the rolling elements can 5 intersect with the other two elements each, or in a pattern of two elements in a first orientation, an element in a second orientation, an element in the first orientation, and two elements in the second orientation. All of the rolling elements that are indicated fall within the scope of the invention.

The movements of the respective rolling elements 5 . 5 , ... are through a cage 6 guided. The cage 6 which has been described in connection with the first aspect is an annular cage, such as that in FIG 25 is shown. The annular cage 6 holds the respective rolling elements 5 in position.

recesses 6b are in the circumference of an annular cage element 6a of the cage 6 formed with uniform spaces and in a staggered arrangement to be identical in number to the rolling elements 6 to be. The rolling elements 5 can in the recesses 6b be fitted such that the rotation center axis 5c perpendicular to a pair of opposite surfaces 5b . 5b one rolling element that of another adjacent rolling element 5 crosses.

faces 6c . 6d every recess 6b are parallel to each other and are tapered with respect to the axis of rotation of the bearing at a certain angle, ie, an angle substantially identical to a contact angle of the rolling element 5 is.

The axial distance between the side surfaces 6c and 6d every recess 6 is set to be slightly wider than the width of the rolling element 5 ,

The entire geometry of the recess 6 is not limiting to a specific geometry unless the recess 6b parallel tapered surfaces 6c and 6d has and is configured such that the distance between the side surfaces 6c and 6d slightly larger than the width of the rolling element 5 is. The geometry of the recess 6 is allowed to be modified without departing from the scope of the invention.

In the first aspect, the recesses are 6b , which are identical in number with the rolling elements 5 are, with uniform intervals in the circumferential direction of the cage 6 formed in a staggered arrangement. The structure of the recesses 6b is not limited to any specific structure. Unless the recesses 6b that are tapered in one direction, in number are equal to those that are tapered in the other direction, the recesses can 6b be arranged in a staggered pattern, which may be arranged alternately or in a pattern of two recesses which are tapered in the first direction, wherein a recess is tapered in a second direction, a recess is tapered in the first direction, and two recesses are tapered in the second direction. The cages 6 all of the geometries indicated are within the scope of the invention.

No specific limitation will be the way of managing the cage 6 imposed. The cage 6 can lead to an inner ring, an outer ring or rolling elements.

The configuration of the cage 6 is not limited to any specific configuration. The cage 6 may be integrally formed or may be mounted from different pieces.

It there is a chance of spin or skew, which is at a rolling element while the rotation developed due to various factors. If the Positions of the rolling elements can not be controlled well, increases the rotational resistance of a bearing, or the rolling elements are unable to themselves uniform to turn.

In the first aspect of the invention, each of the recesses has 6b in the cage 6 are formed, parallel side surfaces 6c and 6d which are tapered at a certain angle, that is, at an angle substantially identical to the contact angle of the rolling element 5 is. The side surfaces 6c and 6d the recess 6b suppress the occurrence of changes in the rolling element 5 , such as a spin or a skew. Since the position of the bearing can be maintained, a bearing with a low torque can be embodied.

The geometry of the cage 6 is not limited to any specific geometry, provided the cage 6 Areas for restraining and guiding the rolling elements 5 Has. The geometry of the cage 6 is authorized for any selection or modification without departing from the scope of the invention.

A preferred cage is as the cage 6 selected from a machined cage, a pressed cage, a resin cage or the like as required. Correspondingly, metal (eg brass, steel or the like) or synthetic resin (eg polyamide 66 (ie nylon 66 ), Polyphenylsulfide (PPS) or the like), without departing from the scope of the invention.

A spacer (spacer) 8th , the arcuate recessed grooves 9 . 9 such as that in 26 is within the scope of the invention.

The spacer 8th is smaller in diameter than the rolling element 5 , The arcuate recessed grooves 9 . 9 are in respective opposite areas 10 . 10 designed so that they cross each other and the rolling elements 5 . 5 hold back such that the rotation center axis 5c perpendicular to the opposite surfaces 5c . 5c with the other adjacent rolling element 5 crosses.

The curvature of the arcuate groove 9 may be arbitrary, namely that the curvature is substantially identical to or greater than that of the outer diameter 5a of the rolling element 5 is executed.

The Use of such a spacer makes the entire camp compact.

None specific limitation is imposed on the state of a preload between the rolling element and the track area is applied. In other words, the preload can during the Manufacturing process or not, each one Fall within the scope of the present invention.

Bearing steel is commonly used as the material of the races 1 and 2 and that of the rolling elements 5 of the warehouse. If an attempt is made to improve the corrosion resistance or the heat resistance of a bearing in accordance with a use environment, stainless steel, heat resistant steel (eg M50) or ceramic may be selected as required.

The sealing plate 20 corresponds to either a contact seal or a non-contact seal. No specific limitation is the geometry of the gasket plate 20 imposed; a known geometry may be selected as required without departing from the scope of the invention.

No specific limitation is the arrangement of the gasket plate 20 imposed. If necessary, the sealing plate can 20 be provided on one side of the bearing or be provided on both sides of the bearing, each case falling within the scope of the invention. A sealing surface of the sealing plate 20 may point to the outer ring or the inner ring, each case falling within the scope of the invention.

None specific restriction is the geometry of a gasket, such as the geometry of a Lip imposed. A linear contact or a surface contact can in Reference to a sealing surface arise, each case falls within the scope of the invention.

Either the presence or absence of a metal core is arbitrarily selectable. A gasket having a metal core or a gasket which does not have a metal core may be selected as required, wherein the present invention The invention is not specifically designed for a bearing of any type.

No specific restrictions will be imposed on the seal groove structure of the outer ring 1 or that of the inner ring 2 imposed; the seal groove structure being allowed to be modified as required without departing from the scope of the invention.

As explained above, the gaskets are 20 provided because a case may arise where there is a need for a roller bearing according to the present invention having a sealing characteristic that depends on the conditions of use. For example, when a roller bearing is to be used in an ultra-clean environment, severe limitations are imposed on the escape of a lubricant or gas from a bearing. Further, when a roller bearing is to be used in a dusty environment, there is a requirement for preventing the entry of a pollutant into the interior of a bearing.

If the sealing plates 20 are arranged in this manner, leakage of lubricant or a dangerous gas from the inside of a bearing to the outside or the prevention of the entry of a pollutant into the interior of a bearing can be prevented or reduced.

More specific Descriptions of the roller bearing according to the second embodiment of the present invention are provided as follows.

[FIRST EXAMPLE]

22 shows a roller bearing according to a first example of the second embodiment of the present invention.

As in 23 is shown, is each of the rolling elements 5 . 5 formed of a top and bottom flattened ball, which has a pair of opposite surfaces 5b . 5b having. The rolling elements 5 are in a track groove 4 installed between an outer ring 1 and an inner ring 2 is limited. The rolling elements 5 . 5 be through an in 25 Retained and guided cage shown.

The sealing plates 20 are of contact type. A sealing surface 20a The seal is obtained as a sealing surface and is in hermetic contact with an inner bottom 4a a sealing groove 4 of the inner ring 2 brought.

The sealing plate 20 used in the present example represents a rough concept of the geometry thereof and is not to be construed as limiting the illustrated geometry. The present example is only an example in which the sealing surface 20a the seal is obtained as a closed contact surface.

The raceway groove 3 according to the present example takes the shape of a Gothic arch and is formed of two raceway surfaces 1a and 1b or 2a and 2 B wherein each raceway surface is larger in radius than the rolling element 5 is. Further, the opposite surfaces 5b . 5b of the rolling element 5 (which consists of a top and bottom flattened ball) symmetrically manufactured.

The rotation center axis 5c that are perpendicular to the opposite surfaces 5b . 5b a rolling element 5 is, crosses that of the other, adjacent rolling element 5 , The movements of the adjacent rolling elements 5 . 5 be through the recesses 6b . 6b of the cage 6 guided.

recesses 6b . 6b are alternately in the cage 6 designed such that a recess 6b formed in one side, another recess formed in the other side with respect to the direction of the circumference of the cage 6 , crosses, thereby installing the rolling elements 5 . 5 in the track groove 3 to allow such a way that the rotation center axis 5c that are perpendicular to the opposite surfaces 5b . 5b a rolling element 5 is that of the other, adjacent rolling element 5 crosses.

According to the first example, there is a point contact 11 between the outside diameter 5a of the rolling element 5 and the raceway area 1a of the outer ring 1 and another point contact 11 exists between the outer diameter 5a of the rolling element 5 and a track surface 5b of the inner ring 2 , There is also a point contact 12 between the outside diameter 5a another adjacent rolling element 5 and the raceway area 1b of the outer ring 1 and another point contact 12 exists between the outer diameter 5a of the rolling element 5 and the raceway area 2a of the inner ring 2 ,

The contact angle of the rolling elements 5 . 5 turn in turn. Therefore, a bearing can receive a radial load, axial load in two directions and a load torque.

Only two point contacts ( 11 . 11 ) exist between the rolling element 5 and the raceway surfaces 1a . 2 B and only two point contacts ( 12 . 12 ) exist between another neighboring one rolling 5 and the raceway surfaces 1b . 2a , Therefore, the chance of occurrence of a larger spin motion can be avoided, which would otherwise occur in a related four-point contact bearing of the prior art.

The rolling elements 5 . 5 come in contact with the outer and inner ring 1 and 2 in the same way as in the usual ball bearing. Therefore, the ball bearing according to the present invention can realize a rolling resistance and a torque which are smaller than those developing in a cross-roll.

[SECOND EXAMPLE]

The 27 and 28 show a roller bearing according to a second example of the present invention.

In the present example, a contact seal becomes the seal plate 20 used, and a sealing surface 20b the seal is obtained as a sealing surface. The sealing surface 20b becomes in hermetic contact with an end face 4b the sealing groove 4 of the inner ring 2 brought. In other respects, the roller bearing according to the present example is identical in configuration and working effect to that described in connection with the first example. The same reference numerals are assigned to those elements which are the same as described in connection with the first example. Therefore, their repeated explanations are omitted.

As in 27 is shown, the sealing surface 20b in contact with a sealing groove face (bearing face) 4b of the inner ring 2 to be brought. Alternatively, as in 28 shown is the face 4b be tapered and in an inclined contact with the sealing surface 20b be brought.

[THIRD EXAMPLE]

29 shows a third example of the roller bearing according to the present invention.

In the present example, a contact seal becomes the seal plate 20 used. sealing surfaces 20a and 20b the contact seal are obtained as sealing surfaces. The sealing surface 20a is in hermetic contact with the inner bottom 4a brought, and the sealing surface 20b is in hermetic contact with the face 4b brought.

In In other respects, the roller bearing is according to the present Example in the configuration and the working effect with the identical which has been described in connection with the first example. The like reference numerals are assigned to those elements which the same as those associated with the first example have been described. Therefore, their repeated explanations omitted.

[FOURTH EXAMPLE]

30 shows a fourth example of the roller bearing according to the present invention.

According to the present example, a noncontact seal becomes the seal plate 20 used. The sealing surface 20a The seal is obtained as a sealing surface, and a non-contact sealing portion is interposed between the sealing surface 20a and the inner floor 4a the sealing groove 4 of the inner ring 2 educated.

In In other respects, the roller bearing is according to the present Example in the configuration and the working effect with the identical, which has been described in connection with the first example. The like reference numerals are assigned to those elements which the are the same as described in connection with the first example. Therefore, their repeated explanations are omitted.

[FIFTH EXAMPLE]

31 shows a fifth example of the roller bearing according to the present invention.

According to the present example, a noncontact seal becomes the seal plate 20 used. The sealing surface 20b The seal is obtained as a seal surface, and a non-contact seal portion becomes the seal surface 20b and the face 4b the sealing groove 4 of the inner ring 2 educated.

In In other respects, the roller bearing is according to the present Example in the configuration and the working effect with the identical, which has been described in connection with the first example. The like reference numerals are assigned to those elements which the are the same as described in connection with the first example. Therefore, their repeated explanations are omitted.

[SIXTH EXAMPLE]

32 shows a sixth example of the roller bearing according to the present invention.

According to the present example becomes a noncontact seal as the seal plate 20 used. sealing surfaces 20a and 20b the contact seal are obtained as sealing surfaces. A non-contact seal portion becomes between the sealing surface 20a and the inner floor 4a the sealing groove of the inner ring 2 formed, and another non-contact sealing portion is between the sealing surface 20b and the face 4b the sealing groove 4 of the inner ring 2 educated.

In In other respects, the roller bearing is according to the present Example in the configuration and the working effect with the identical, which has been described in connection with the first example. The like reference numerals are assigned to those elements which the same as those associated with the first example have been described. Therefore, its repeated explanation omitted.

[SEVENTH EXAMPLE]

33 shows a seventh example of the roller bearing according to the present invention.

According to the present example, a noncontact seal becomes the seal plate 20 used. The sealing surface 20a The seal is obtained as a sealing surface, and a non-contact sealing portion is interposed between the sealing surface 20a and the inner floor 4a the sealing groove 4 of the inner ring 2 educated.

In In other respects, the roller bearing is according to the present Example in the configuration and the working effect with the identical, which has been described in connection with the first example. The like reference numerals are assigned to those elements which the same as those associated with the first example has been described. Therefore, its repeated explanation omitted.

[EIGHT EXAMPLE]

The 34 and 35 show an eighth example of the roller bearing according to the present invention.

According to the present example, a noncontact seal becomes the seal plate 20 used. The sealing surface 20a the seal is obtained as a sealing surface.

At the in 34 example shown, the sealing surface 20b the sealing plate 20 as the sealing surface, and a non-contact sealing portion is interposed between the sealing surface 20b and the face 4b the sealing groove 4 of the inner ring 2 educated.

At the in 35 shown example, the sealing surfaces 20a and 20b the sealing plate 20 obtained as sealing surfaces. A non-contact seal portion becomes between the sealing surface 20a and the inner floor 4a the sealing groove 4 formed of the inner ring. Another non-contact sealing portion is between the sealing surface 20b and the face 4b the sealing groove 4 of the inner ring 2 receive.

In In other respects, the roller bearing is according to the present Example in the configuration and the working effect with the identical, which has been described in connection with the first example. The like reference numerals are assigned to those elements which the same as those associated with the first example have been described. Therefore, its repeated explanation omitted.

A roller bearing according to the third embodiment of the present invention includes a ring (outer ring) 1 ; another ring (inner ring) 2 ; a variety of rolling elements 5 . 5 , ..., in a career groove 3 are installed, wherein the groove between the inner diameter of the outer ring 1 and the outer diameter of the inner ring 2 is limited; and a flange 13 that on one or both of the outer ring 1 and the inner ring 2 is provided.

Save the flange 13 For example, the roller bearing according to the second aspect is identical in configuration, operation and advantage to that described in connection with the first aspect of the invention. Therefore, the explanations are applied in its existing form to the roller bearing according to the second aspect. In relation to the common configuration and the working effect, the same reference numerals are assigned to the same elements, and their repetitive explanation is omitted.

No specific limitation is imposed on the geometry, construction and arrangement of the flange 13 imposed. The axial dimension of the flange may be symmetrical or asymmetrical. No restrictions are imposed on the axial dimensions of the flange 13 imposed.

A hole (tap) can be made in the flange to increase the mounting accuracy of the flange 13 be formed with a counterpart component. In the case of a double split ring, if the flange 13 is provided on each ring half, the ring halves together by means of attachment of the flanges 13 be attached.

In the present example, the gaskets are 20 installed in the ball bearing, as shown is placed. The sealing plate 20 The roller bearing according to the present aspect is not indispensable and can be arbitrarily selected. The seal plate can be arbitrarily applied to the structures described in connection with the first aspect of the present invention.

As explained above, one goal is the use of the flange 13 in the present invention, the operation of the flange 13 and an advantage of the flange 13 , as follows.

In the case of a bearing of a different type, the bearing of this type usually uses the inner ring 2 which is fixed with a shaft and the outer ring 1 which is fixed with a housing (in the related art).

• (1) Es existiert ein strenges Erfordernis für eine Abmessungsgenauigkeit einer Passfläche eines Lagers.
• (2) Wenn eine Presspassung zwischen Passflächen existiert, besteht eine Notwendigkeit für die Verwendung eines Spezialwerkzeuges oder einer Spezialmaschine zur Montage und Demontage eines Lagers.
• (3) Da ein Spezialwerkzeug oder eine Spezialmaschine für die Montage und Demontage eines Lagers verwendet werden kann, werden strukturelle Beschränkungen der Gegenstückkomponente eines Lagerbefestigungsabschnitts auferlegt. (Zum Beispiel um einen Innenring aus einem Lager durch die Verwendung einer Herausziehvorrichtung zu entnehmen, besteht eine Notwendigkeit zur Gestaltung der Schulterhöhe einer Welle, die etwas kleiner ist als die Querschnittshöhe des Innenrings des Lagers in der ursprünglichen Gestaltung einer Gegenstückkomponente, die zu befestigen ist. Wenn jedoch die Schulterhöhe der Welle übermäßig klein wird, kann die Gefahr entstehen, dass die Positionierung der Schulterhöhe der Welle unbestimmt wird. Besonders in dem Fall eines dünnen Lagers, das eine vergleichsweise kleine Querschnittslagergröße hat, erwächst ein Problem.
• (4) Das Auswechseln eines Lagers involviert den Verbrauch von sehr viel Zeit.
• (5) Es besteht die Notwendigkeit für ein Gehäuse zum Stützen eines Lagers. Als ein Ergebnis wird die Größe des Umfangs eines Lagers erhöht, was wiederum der Miniaturisierung eines Erzeugnisses entgegenwirkt und in einer Erhöhung der Gesamtkosten resultiert.

Such a construction poses the following problems to be solved.

• (1) There is a strict requirement for a dimensional accuracy of a mating surface of a bearing.
• (2) When there is an interference fit between mating surfaces, there is a need to use a special tool or a special machine to assemble and disassemble a bearing.
• (3) Since a special tool or machine can be used for assembling and disassembling a bearing, structural restrictions are imposed on the counterpart component of a bearing mounting portion. (For example, to remove an inner ring from a bearing through the use of a puller, there is a need to design the shoulder height of a shaft that is slightly smaller than the cross sectional height of the inner ring of the bearing in the original design of a counterpart component to be fastened. However, if the shoulder height of the shaft becomes excessively small, there may arise a risk that the positioning of the shoulder height of the shaft becomes indeterminate, especially in the case of a thin bearing having a comparatively small cross-sectional bearing size, a problem arises.
• (4) Replacing a warehouse involves a lot of time consuming.
• (5) There is a need for a housing for supporting a bearing. As a result, the size of the periphery of a bearing is increased, which in turn counteracts the miniaturization of a product and results in an increase in the overall cost.

The The aforementioned configuration of the invention enables the Integration of a race and a flange of a bearing. When a result may be the dimensional accuracy of an outer or inner peripheral surface of a Be set low. A bearing and a counterpart component can be fast and easily fastened together or dismantled by means of a flange and by using a screw. Thus be the installation costs reduced.

Further Needless the need for a housing, making a product compact and the total cost be lowered (see the aim and the working effect of the invention).

More specific Descriptions of the roller bearing according to the second aspect of the present invention are provided as follows.

[FIRST EXAMPLE]

In the bearing according to the present example of the third embodiment, the outer ring 1 divided into two parts, and the inner ring 2 is one piece. The flange 13 is with one of the two parts of the outer ring 1 attached (see 36 ).

[SECOND EXAMPLE]

In the bearing according to the present example, the outer ring 1 in one piece and the inner ring 2 is divided into two parts. The flange 13 is with the outer ring 1 attached (see 37 ).

[THIRD EXAMPLE]

In the bearing according to the present example, each is from the outer ring 1 and the inner ring 2 divided in two parts. The flange 13 is with one of the two parts of the outer ring 1 attached (see 38 ).

[FOURTH EXAMPLE]

In the bearing according to the present example, each of the outer ring 1 and the inner ring 2 integrally. The flange 13 is with the outer ring 1 attached (see 39 ).

[FIFTH EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided into two parts, and the inner ring 2 is in one piece. The flange 13 is with each of the two parts, which is the outer ring 1 form, fastened, and the flange 13 assumes an axially symmetric geometry (see 40 ).

[SIXTH EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided in two parts, and the inner ring 2 is in one piece. The flange 13 is with each of the two parts, which is the outer ring 1 form, fastened, and the flange 13 assumes an axially asymmetric geometry.

In the present example, mutual alignment of the cores of the flange halves 13 To facilitate a hole structure (tap structure) in the flanges 13 trained (see 41 ).

[SEVENTH EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided into two parts, and the inner ring 2 is in one piece. The flange 13 is with one of the two parts, which is the outer ring 1 form, attached. In the present example, the orientation of a core of the flange is 13 with a counterpart component, a hole structure in the flange 13 trained (see 42 ).

[EIGHT EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided into two parts, and the inner ring 2 is in one piece. The flange 13 is with the inner ring 2 attached (see 43 ).

[NINE EXAMPLE]

In the bearing according to the present example, the outer ring 1 in one piece, and the inner ring 2 is divided into two parts. The flange 13 is with one of the two parts of the inner ring 2 attached (see 44 ).

[TENTH EXAMPLE]

In the bearing according to the present example, each of the outer ring 1 and the inner ring 2 divided in two parts. The flange 13 is with one of the two parts of the inner ring 2 attached (see 45 ).

[ELEVENTH EXAMPLE]

In the bearing according to the present example, each of the outer ring 1 and the inner ring 2 integrally. The flange 13 is with the inner ring 2 attached (see 46 ).

[TWELFTH EXAMPLE]

In the bearing according to the present example, the outer ring 1 in one piece, and the inner ring 2 is divided into two parts. The flange 13 is with each two parts, which is the inner ring 2 form, fastened, and the flange 13 assumes an axially symmetric geometry (see 47 ).

[THIRD EXAMPLE]

In the bearing according to the present example, the outer ring 1 in one piece and the inner ring 2 is divided into two parts. The flange 13 is with each of the two parts, which is the inner ring 2 form, fastened, and the flange 13 assumes an axially asymmetric geometry. In the present example, the orientation of cores of the flange is 13 To facilitate each other, a hole structure in the flanges 13 trained (see 48 ).

[FOURTEENTH EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided into two parts, and the inner ring 2 is in one piece. The flange 13 is with the inner ring 2 attached. In the present example, the orientation of the flange 13 with a counterpart component is a hole structure in the flanges 13 trained (see 49 ).

[FIFTEENTH EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided into two parts, and the inner ring 2 is in one piece. The flange 13 is attached to one of the two parts, which is the outer ring 1 and the inner ring 2 form ( 50 ).

[SIXTEEN EXAMPLE]

In the bearing according to the present example, the outer ring 1 in one piece, and the inner ring 2 is divided into two parts. The flange 13 with the outer ring 1 and one of the two parts of the inner ring 2 attached (see 51 ).

[SEVENTEEN EXAMPLE]

In the bearing according to the present example, each of the outer ring 1 and the inner ring 2 divided in two parts. The flange 13 is with one of the two parts, which is the outer ring 1 Form and with one of the two parts, the inner ring 2 form fastened (see 52 ).

[EIGHTEEN EXAMPLE]

In the bearing according to the present example, each of the outer ring 1 and the inner ring 2 integrally. The flange 13 is with the outer ring 1 and the inner ring 2 attached (see 53 ).

[NINETEENTH EXAMPLE]

At the warehouse according to the present the example is everyone from the outer ring 1 and the inner ring 2 divided in two parts. The flange 13 is with each of the two parts, which is the outer ring 1 and with each of the two parts, the inner ring 2 form, attached. The flange 13 assumes an axially symmetric geometry (see 54 ).

[TWENTIETH EXAMPLE]

In the bearing according to the present example, each of the outer ring 1 and the inner ring 2 divided in two parts. The flange 13 is with each of the two parts, which is the outer ring 1 Form and with each of the two parts, the inner ring 2 form, attached. The flange 13 assumes an axially symmetric geometry.

In order to facilitate the alignment of the cores of the flange with each other in the present example, there is a hole structure in the flanges 13 trained (see 55 ).

[TWENTY-NINE EXAMPLE]

In the bearing according to the present example, the outer ring 1 divided in two parts. The flange 13 is with one of the two parts, which is the outer ring 1 form and the inner ring 2 attached. To align the flanges 13 with counterpart components is a hole structure in the flanges 13 trained (see 56 ).

A roller bearing in another rolling bearing comprises a race (outer ring) 1 ; another ring (inner ring) 2 ; a variety of rolling elements 5 . 5 , ..., in a career groove 3 are installed, wherein the groove between the inner diameter of the outer ring 1 and the outer diameter of the inner ring 2 is limited; and a lubricant-containing polymer element 14 filling a space inside the warehouse.

Except the lubricant-containing polymer element 14 , which fills the space within a bearing, the roller bearing according to the third aspect in the configuration and the working effect is identical to that described in connection with the first aspect of the invention. Therefore, the explanations in their present form are applied to the roller bearing according to the second aspect. In relation to the common configuration and the joint working effect, the same reference numerals are assigned to the same elements, and their repetitive explanation is omitted.

In the present example, except as otherwise specified, the lubricant-containing polymer element is 14 by mixing at least one type of polymer selected from a poly-olefin polymer-based group comprising polyethylene, polypropylene, polybutylene and polymethylpentene as a lubricant, at least one type of oil selected from a paraffin-based hydrocarbon oil , such as poly-olefin oils, naphthene-based hydrocarbon oils, petrolatum, ether oils such as dialkyldiphenyl ethers and ester oils such as phthalate esters and trimellitate.

at In the present invention, a grease containing a lubricant, like a basic oil, be used instead of the lubricant. In this case, a suitable amount of a known metallic soap, e.g. Lithium soap, added to a lubricant, to make fat.

Polymers are of the same molecular structure and have different average molecular weights. Average molecular weights of polymers range from 1 × 10 ³ to 5 × 10 ⁶ . Comparatively low molecular weight polymers having an average value of 1 × 10 ³ to 1 × 10 ⁶ or ultra-high molecular weight polymers having an average value of 1 × 10 ⁶ to 5 × 10 ⁶ are used alone or in a mixed manner and Way, as needed, used.

When the polymer of the lubricant-containing polymer material, polypropylene, which is a highly oil-absorptive polymer is polystyrene, polyethylene, polyurethane, acrylic resin, e.g. polyethyl or Polynolbornan.

One mixing ratio the lubricant-containing polymer element is such that the polyα-based olefin-based polymer forms 20% to 80% of the total weight of the polymer element and that the lubricant forms 80% to 20% of the total weight. If the polyα-based olefin-based polymer may be less than 20% by weight no polymer element with a certain level of hardness and Strength are achieved. When the polyα-based olefin-based Polymer forms 80% by weight or more (i.e., when the lubricant less than 20% by weight), the amount of lubricant, to feed the is, smaller, and as a result becomes an effect of degradation reduces the abrasion of a sliding portion. Various additives, such as. an oxidation inhibitor, a rust preventive, an abrasion preventive, an antifoaming agent and an extreme pressure agent, as required, are added to the polymer element.

Especially when a need exists for heat resistance, it is preferable to use a lubricant-containing polymer element based on a thermosetting resin, such as each described below instead of the above-described polyalpha polyolefin-based polymer.

The thermosetting Resin closes Diallyl phthalate, phenolic resin and polycarbodiimide. More in detail includes Diallyl phthalate further comprises a homopolymer consisting of a monomer or a prepolymer, e.g. Diallyl phthalate, diallyl isophthalate and Diallyl terephthalate; includes a copolymer consisting of two or more monomers or prepolymers consists of those selected above, and includes one Mixture of the homopolymer and the copolymer.

diallyl phthalate can not be heated or cured be in its existing form. Therefore, a peroxide usually needs as a curing agent (Polymerization initiator) can be used. As peroxide, benzoyl peroxide, m-toluoyl peroxide, t-butyl peroxide, t-butyl peroxide benzoate, di-t-butyl peroxide isophthalate, 2,5-dimethyl-2,5-di (benzoylperoxi) hexane and dicumyl peroxide. Such a curing agent is added to the resin, to form various weight percentages, usually 1% or thereabouts to form at the time of polymerization.

Phenolic resin, which can be used in the present invention includes pure Resole type phenol resin, novolak type pure phenolic resin and various denatured phenolic resins. For example, as denatured phenolic resins cashew-modified phenolic resins (cashew-modified phenolic resins resin) (of the novolak or resol type) and an oil-modified phenolic resin (des Novolaktyps) can be used.

phenolic resin of the novolak type hardens not in unmodified form, with hexamine or phenolic resin of the Rexol type as a curing agent must be added to the phenol resin of the Novo laktyps. In contrast For this, phenolic resin of the resol type is heated and cured without use an additive.

The oil modified Phenolic resin has a low ability of retaining a lubricant at the time of curing and can not be used alone. That is why the Need to use an oil-modified phenolic resin in combination with another phenolic resin.

polycarbodiimide, which can be used in the present invention is without the use of additives heated and cured.

One Lubricant used in the present invention in combination with the thermosetting resin must be compatible with the thermosetting Resin indicated above have. For example, as such a lubricant Diisodecyl phthalate, di-2-ethylhexyl sebacate, an ester oil, e.g. Tri-2-ethylhexyl trimellitate, a POE, Octadecyldiphenyl ether, tetraphenyl ether, and a phenyl ether oil, e.g. Pentaphenyl ether mentioned become.

In dependence on the type of thermosetting Resin can be changed the type of lubricant that has the compatibility. Even if resin uniform before curing triggered A case can occur where resin is from a lubricant or a fat after curing is disconnected. Therefore, there is a need for a combination to pay attention to resin and a lubricant.

diallyl phthalate is compatible with the lubricant or all types of grease. Therefore, any combination between the lubricant and Give the fat a mixture that has a lubricity have. However, when phenol resin or carbodiimide resin is used becomes, become restrictions a combination imposed. desired Close combinations e.g. a combination of pure phenolic resin and a polyphenyl ether oil, a Combination of acajoumodifizierte in phenolic resin and a Diesteröl or Polyolesteröl and a Combination of oil-modified Phenol resin and a polyphenyl ether oil or alkylpolyphenyl ether oil. Further In the case of the polycarbodiimide resin, it is desirable to use a polyphenylene ether oil.

In In terms of reinforcement a mechanical strength or the improvement of moldability may be an extender to the lubricant-containing polymer element added be, e.g. Minerals, e.g. Calcium carbonate, talc, silica, Clay, mica, inorganic whisker, e.g. potassium titanate and Bomylaluminiumwhisker, inorganic fibers, such. glass fibers, Asbestos, quartz wool and metal fibers and a fabric made of any this extender is woven. In the case of an organic compound can be used as an extender of any of various thermosetting Resins, e.g. Soot, Graphite powder, graphite fibers, aramid fibers, polyester fibers, polyimide and polybenzimidazole added become. With a view to improving the thermal conductivity of a lubricant-containing Polymer element, can to the polymer element, graphite fibers, metal fibers, graphite powder, Metal powder or zinc oxide powder can be added.

The Production of such a lubricant-containing polymer element will now be described.

in the Case of a lubricant-containing polymer element based on a poly-α-olefin polymer a mixture consisting of polymer and a lubricant, in a predetermined mold filled, and the mixture is heated and melted at a temperature the higher as the melting point of the polymer. Subsequently, the polymer chilled and cured.

in the Case of a lubricant-containing polymer element on a thermosetting Resin based, after being filled into a predetermined mold, a mixture consisting of the polymer and a lubricant, heated to a suitable temperature so that the mixture can cure.

No sealing plate is received in the roller bearing according to the present example. However, the case where a seal plate is received in the roller bearing is also within the scope of the invention. In this case, the structure of the seal plate 20 used in connection with the first aspect of the invention. Furthermore, the structure can be assumed, in which the flange 13 , which has been described in connection with the second aspect of the inven tion, either on the outer ring 1 or the inner ring 2 be provided, 59 ,

As explained above, the filling of the space of a bearing with the lubricant-containing polymer element 14 In the present invention, the following purpose and results in the following work effects.

fat becomes common for lubricant purposes used (in the relevant State of the art).

In However, with respect to a roller bearing adapted to receive a radial load, of axial loads in two directions and a load torque through the Use of a single bearing, e.g. that, that is described in connection with the present invention consists, When fat is used as a lubricant, the need for it for one Maintenance process, such as Periodic lubrication to supplement Fat. Furthermore, there is a problem of leakage of grease, the the environment of a warehouse soiled.

Accordingly, in the present invention, a lubricant over a long period of time becomes a lubricated portion of a roller bearing through the lubricant-containing polymer element 14 fed. Therefore, a good lubrication between the raceway surfaces of the outer and inner ring 1 and 2 and a rolling contact surface, thereby obviating the need for maintenance operations, such as supplementing a lubricant that has heretofore been required when using grease to lubricate a bearing. Further, the occurrence of fouling of the environment of a bearing which would otherwise be caused by grease leaking from the end face of the bearing can be prevented. Further, the lubricant-containing polymer element 14 liquid and does not flow and also has a dust-proofing property. Therefore, extending the life of a bearing in a water / dirt environment can also be expected (the goal and the working effect of the invention).

More specific Descriptions of the roller bearing will be as follows.

According to the first example, in a roller bearing, which is the rolling elements 5 through the use of the cage 6 leads, the space of a bearing with the lubricant-containing polymer element 14 filled ( 57 ).

Although the present example, the rolling elements 5 used in 23 are shown and described in connection with the first aspect and the cage 4 used in 25 is shown, the rolling elements 5 and the cage 6 imposes no specific restrictions. Further, the geometry of the outer ring 1 and the geometry of the inner ring 2 no special restrictions imposed.

According to the present example is in a roller bearing, which the rolling elements 5 through the use of the spacer 8th leads, the space of a bearing with the lubricant-containing polymer element 14 filled ( 58 ).

Although the present example, the rolling elements 5 used in 23 are shown and described in connection with the first aspect and the spacer 8th used in 26 is shown, the rolling elements 5 and the spacer 8th imposes no specific restrictions. Furthermore, the geometry of the outer ring 1 and the inner ring 2 no special restriction imposed.

Corresponding According to the present invention, a roller bearing has the above-mentioned Construction, and a single bearing can be a radial load, axial loads in two directions and take a load moment.

The The present invention provides the following working effect in addition to the above-mentioned work effects.

There are always two point contacts zwi to prevent each of the rolling elements and a raceway groove of a race, thereby preventing the occurrence of an increase in the torque, which would otherwise caused by a large spin movement effect of balls in the related four-point contact bearing according to the prior art.

One rolling is formed such that the outer diameter of the rolling element, i.e. a rolling contact surface of rolling element, a curvature in an axial direction. Unlike a cross roller bearing the bearing has a smaller rolling resistance and achieves a lower torque.

According to the second embodiment of the invention are sealing plates ( 59 ) provided in a warehouse. A roller bearing having the structure described in connection with the present invention can reduce or prevent the escape of a lubricant or a pollutant from the bearing to the outside or the entry of hazardous substances into the bearing.

Corresponding the third embodiment of Invention is dependent from the conditions of use a flange on an inner ring or an outer ring of a warehouse or on external and inner ring of the bearing provided. As a result, the dimensional accuracy of the foreign and inner circumference of the bearing are set low.

Further can be a quick and easy attachment of a warehouse with a Contrast element or dismantling the bearing from the counterpart component, which reduces the assembly costs. Furthermore, there is no need for a housing, whereby a product is made compact and minimizes the overall cost.

Of the Interior of a bearing can with a lubricant-containing polymer element filled so that thereby a maintenance process, such as e.g. the completion of Grease, which until now was required when storing with grease filled was, is unnecessary. Thus, a maintenance-free roller bearing can be performed. Furthermore, the Contamination of the environment of a bearing can be prevented, which otherwise by the leakage of grease from the face of the Warehouse would cause. Furthermore, the extension the life expectancy of a bearing in a water / dust environment become.

A another embodiment A roller bearing according to the present invention will be described below described. This embodiment can however, to any of the bearings of the other embodiments be applied to the present invention, and therefore a detailed description of its construction avoided.

at the other. embodiment a bearing clearance is set to a negative value.

It should be noted that the presence / absence of the sealing plate 20 no special restrictions are imposed. Regardless of whether the sealing plate 20 is provided in a roller bearing, the roller bearing of this third embodiment falls within the scope of the present invention.

In relation to the torque and the torque resistance, a test was carried out by means of the comparison of the roller bearing ( 1 ) according to the further embodiment, whose inside distance has been set to a negative value to a four-point contact ball bearing and a cross roller bearing.

The test results show ( 60 ) that the roller bearing according to the present embodiment, in which the distance was set to a negative value, results in a torque that is smaller than that achieved by the cross roller bearing as in the case of the four-point contact ball bearing, and the torque resistance, the was achieved by the bearing is higher than that achieved by the four-point contact ball bearing, as in the case of the cross roller bearing.

The Roller bearing according to the present embodiment, for which the distance was set to a negative value results in a low Torque in the same way as the four-point contact ball bearing does while a high torque stiffness is achieved in the same way like the cross roller bearing.

There the present invention has been embodied in the manner explained above, arise at a camp where the distance is at a negative value was set, a point contact between the rolling elements and races as in the case of a four-point contact ball bearing. The rolling resistance, the develops in the bearing becomes smaller than that of a line contact cross roll, and therefore the bearing gives a low torque.

There a preload is applied to the inside of a bearing, the occurrence of a decrease in the strength can be prevented which otherwise causes by an inner distance of a bearing would, when the bearing receives a load, thereby high torque stability to achieve.

below becomes a fifth embodiment explained according to the present invention.

Under Reference now to the accompanying drawings become preferred embodiments the rolling bearing of the invention.

The embodiments are only embodiments, to describe the bearings of the Invention are disclosed and it is understood that the invention not on the specific embodiments limited to the same is, and that the combination and arrangement of parts use without the spirit and scope of the invention leave.

The rolling bearing comprises a plurality of rolling elements 36 . 36 ... who are in a career groove 33 are installed between the inner diameter of a raceway (outer ring) 31 and the outer diameter of a race (inner ring) 32 is trained.

The races 31 and 32 can each be one piece or both or both of the races 31 and 32 may be divided into two parts axially at any desired position in the width direction and mounted in a part with a screw, a rivet, etc.

The raceway groove 33 is made of track surfaces 34 and 35 formed, each of which has a larger radius than the radius of the rolling element 36 , The raceway surface 34 . 35 the raceway groove 3 at least one of the races 31 and 32 becomes two raceway surfaces 34a and 34b . 35a and 35b formed, each of which has a larger radius than the radius of the rolling element 36 ,

Every raceway surface 34 ( 34a and 34b ) 35 ( 35a and 35b ) may have any shape such as a curve or V in cross section and may be shaped like a curve, a line or the like and is not limited if it has a shape suitable for rolling the rolling element 36 , For example, a Gothic bow, etc. formed of both circular arcs having circle centers positioned like a cross is applied.

at the embodiment is an undercut at the intersection of the raceway surfaces to Facilitated grinding, but with a raceway groove, which is shaped like a continuous ellipse, also formed can be without forming the relief.

The rolling element 36 has any shape and has an outer diameter 36a as a rolling contact surface having a curvature in the axial direction, and has a smaller radius than the radius of the raceway surface 34 ( 34a and 34b ) 35 ( 35a and 35b ). The adjacent rolling elements 36 are alternately positioned like a cross, and the outside diameter 36a each rolling element 36 is always in contact with a point on the raceway surface 34 ( 34a and 34b ) of a raceway 31 and a point on the track surface 35 ( 35a and 35b ) of the other race 32 ,

For example, the rolling element 36 a ball formed at the top and bottom with a cut that is a pair of opposing surfaces 36b and 36b has (is of a structure in which the upper and lower parts of the ball are cut away to the opposite surfaces 36b and 36b to build). The rolling elements 36 . 36 ..., are built in such a way that the rotation center axes 36c perpendicular to the opposite surfaces 36b and 36b intersect each other, and the outside diameter 36a each rolling element 36 is always in contact with a point on the raceway surface 34 (or 34a and 34b ) of a raceway 31 and a point on the track surface 36 (or 35a and 35b ) of the other race 32 ,

The cutting widths at the top and bottom of the rolling element 36 are not limited, and the cut percentage at the top and bottom may be the same or may be unequal and may be selected as desired without departing from the spirit and scope of the invention. That is, the opposite surfaces 36b and 36b of the rolling element 36 may be symmetric or asymmetric; the symmetrical opposing surfaces and the asymmetrically opposing surfaces are within the spirit and scope of the invention.

The whole shape of the rolling element 36 , the presence or absence of the opposite surfaces 36b and 36b , the size of the curvature in the axial direction of the outer diameter 36 and the like are not limited to the specific forms described above and may be changed as desired without departing from the spirit and scope of the invention. That is, for example, the rolling element may comprise both surfaces in a non-parallel manner rather than the opposing surfaces 36b and 36b and can be a rotation center axis 36c which is perpendicular to both of the surfaces.

The rolling elements 36 . 36 ..., are built in such a way that the rotation center axes 36c and 36c perpendicular to the planes 36b and 36b . 36b and 36b at the adjacent rolling elements 36 and 36 intersect alternately, and the crossing state may or may not be orthogonal be orthogonal.

The way in which the rolling elements 36 how a cross is positioned is not limited if only the number of rolling elements is the same as those of the rolling elements crossing the rolling elements. That is, the rolling elements 36 may be placed like a cross or may be placed like a cross all two rolling elements or may be placed like a cross in such a way of two rolling elements, a rolling element, a rolling element, two rolling elements, if only the number of rolling elements is the same, like those of the rolling elements crossing the rolling elements; each manner falls within the spirit and scope of the invention.

The movement of each rolling element 36 . 36 gets through a cage 37 or a spacer (spacer) 39 guided.

The cage 37 or the spacer (spacer) 39 is not limited if it (it) is of a shape that has a recess 38 for retaining and guiding the rolling elements 36 or grooves 40 and 40 having; the shape may be selected or changed as desired without departing from the spirit and scope of the invention.

The type of leadership of the cage 37 is not limited and may be an inner ring guide, an outer ring guide or a Wälzelementführung. The structure, the shape and the like of the cage 37 are not limited; for example, the cage 37 a one-piece type or may be formed of different parts.

For example, the cage is 37 so constructed that so many recesses 38 like the number of rolling elements 36 are present, with the adjacent rolling elements 36 . 36 can be installed so that the rotating central axes 36c and 36c which alternately intersect each other, are positioned at the same distance as a cross alternately on the circumference of an annular ring.

Both sides 38a and 38b every recess 38 are parallel to each other, are neither perpendicular nor parallel to the axis of rotation of the bearing and are not at a constant angle (slope) with an equal level to the contact angle of the rolling element 36 educated.

The distance between both sides 38a and 38b every bag 38 in the axial direction thereof is made slightly larger than the width of the rolling element 36 ,

The entire shape of the recess 38 is not limited if the recess 38 both parallel sides 38a and 38b has, each of which is shaped like a slope and the distance between both sides 38a and 38b is slightly larger than the width of the rolling element 36 ; the entire shape of the recess 38 can be changed without departing from the spirit and scope of the invention.

In the embodiment, so many recesses 38 ... like the number of rolling elements 36 ... with an equal distance and like a cross positioned alternately on the circumference, but the invention is not limited thereto. The recesses 38 ... can be positioned like a cross all two recesses or can be positioned like a cross in such a way of two recesses, one recess, one recess, two recesses, if the number of recesses is the same as that of the recesses, which cross the recesses; each manner falls within the spirit and scope of the invention.

It it is possible, that a spin movement or a skew in the rolling element, the turns, can occur because of the effects of various factors, and if the position of the rolling element can not be well controlled, there is a possibility that the rotational resistance of the camp grows up or that it is impossible becomes, a uniform To create a turn.

Therefore, according to the embodiment, each recess comprises 38 of the cage 37 the two parallel sides 38a and 38b that are almost equal to the constant angle with the same level to the contact angle of the rolling elements 36 are executed and the change in position of the rolling element 36 , which is caused by a spin movement, a skew, etc. of the rolling element, can pass through both sides 38a and 38b to maintain the position of the bearing can be suppressed, so that a low torque of the bearing can be created.

The spacer 39 is formed with a smaller diameter than the diameter of the rolling element 36 and is with concave circular arc grooves 40 and 40 like a cross in opposite planes 41 and 41 for maintaining the adjacent retained rolling elements 36 and 36 formed so that the rotational center axes 36c and 36c perpendicular to the opposite surfaces 36b and 36b . 36b and 36b cross each other as described above.

The radius of curvature of the circular arc groove 10 may be roughly the same or greater than the radius of curvature of the outer diameter sers 36a of the rolling element 36 be; and can be arbitrary.

If the spacers 39 used in this way, the entire camp can be compact.

Of the Condition in which a preload between the rolling element and the track area granted is, is not limited, namely, it may be a preload or can not be a preload be issued in the manufacturing state, the issue of a Preloading and no preloading in the manufacturing state are within the spirit and scope of the invention.

Normally, a bearing steel is used as the material of the races 31 and 32 and the rolling elements 35 but a corrosion-preventing coating, stainless steel, heat-resistant steel such as M50, ceramics and the like are suitably selected, and the materials are not limited to improve the corrosion resistance and the heat resistance in response to the use environment.

As a machine-made cage, a press cage, a resin cage or the like as the material of the cage 37 is suitably selected, for example, brass metal, iron, etc. or synthetic resin, such as polyamide 66 (Nylon) or polyphenylsulfide (PPS) is selected in the spirit and scope of the invention.

64 shows an embodiment of a rolling element 36 ' with opposite surfaces that are asymmetrical. The rolling element 36 ' The embodiment is particularly used for high-speed rotation.

The rolling element 36 ' the embodiment is a rolling element (a ball formed at the top and bottom with a cut) 36 ' that have asymmetrically opposite surfaces 36b ' and 36d ' has and is positioned so that the larger end 36d ' the opposite surfaces 36b ' and 36d ' to the inner ring 32 the bearing is directed, whereby the rotation of the rolling element 36 ' becomes more stable and a lower torque can be created. The reference number 36a ' denotes an outer diameter, and the reference number 36d ' denotes a rotation center axis.

Other components and advantages are the same as those of the rolling element 36 , which has been described above, and will not be explained again.

Of the Gap in the bearing can be set small or negative (minus) to be set as required. According enough, can be a higher one Torque resistance of the bearing are created.

The reference number 44 in the figure denotes a sealing plate. As the sealing plate 44 For example, any contact gasket, contactless gasket or contact shield, and the shape of the gasket plate are used 44 is not limited, and a seal plate of a known shape is suitably selected without departing from the spirit and scope of the invention.

The reference number 44a in the figure, a sealing surface of the sealing plate 44 (Hermetic sealing surface), which in intimate contact with the inner bottom of an inner ring sealing groove 32a comes.

The positioning of the sealing plate 44 is not limited, and the sealing plate 44 may be positioned on either side or a single page as required; wherein the positioning of the sealing plate 44 on both sides and positioning the seal plate 44 are on a single page within the spirit and scope of the invention. The sealing surface may be on the outer ring side or the inner ring side; each case is within the spirit and scope of the invention.

The Shape of the gasket, e.g. a lip shape, is not limited, and a line contact with the sealing surface and surface contact with the sealing surface are included within the spirit and scope of the invention.

If a cored rod exists may be determined as desired and the type that has a coreed rod, and the type who has a rod without a core, can suitably, as required.

The sealing groove structures of the outer ring 31 and the inner ring 32 each are not limited and may be changed whenever necessary without departing from the spirit and scope of the invention.

The presence or absence of the sealing plate 44 is not limited, and the sealing plate 44 can be installed or does not need to be installed as required; installing the gasket plate 44 and not installing a seal plate 44 are included within the spirit and scope of the invention.

[BEISPEILE]

Next, specific embodiments of the invention will be described with reference to FIG the accompanying drawings are explained.

FIRST EXAMPLE:

62 shows a first example of a rolling bearing of the fifth embodiment according to the present invention.

Each rolling element 36 . 36 is a ball shaped at the top and bottom with a cut that has a pair of opposing surfaces 36b and 36b has, as in 63 is shown, and the rolling bearing comprises outer rings 31 and 1 , which are divided into two parts, an inner ring 32 formed in one piece and raceway grooves 33 and 33 ,

In the example, there is a track groove 33 from two raceway surfaces 34a and 34b each of which has a larger radius than the rolling element 36 , and another career groove 33 is from a career area 35 manufactured, which has a larger radius, than that of the rolling element 36 , and the opposite surfaces 36b and 36b of the rolling element (ball, which is formed at the top and bottom with a cut) 36 , are made symmetrical.

The rolling elements 36 . 36 are positioned so that the rotation center axes 36c and 36c the rolling elements perpendicular to the opposite surfaces 36b and 36b intersect each other alternately, and the movement of each rolling element 36 . 36 is through a recess 38 . 38 a cage 37 guided.

In the cage 36 There are so many recesses 38 ... like the number of rolling elements 36 ..., in which the adjacent rolling elements 36 . 36 can be installed so that the rotational center axes 36c and 36c perpendicular to the opposite surfaces 36b and 36b . 36b and 36b alternately crossing each other equidistant and like a cross being alternately positioned on the circumference of an annular ring, as described above.

Therefore, according to the first example, the outer diameter of the rolling element comes 36 in contact with a point on the raceway surface 34a of the outer ring 31 and a point on the track surface 35 of the inner ring 32 (the contact points are with 42 and 42 designated, wherein the outer and inner surfaces facing each other, and the adjacent rolling element 36 comes in contact with a point on the raceway surface 34b of the outer ring 31 and a point on the track surface 35 of the inner ring 32 (the contact points are with 43 and 43 designated).

Since the rolling elements 36 and 36 Alternating with the contact angle, a bearing can receive a radial load, thrust loads in both directions, and a load moment.

A rolling element 36 is in a point contact with only one point on the raceway surface 34a ( 42 ) and a point on the raceway surface 35 ( 42 ), and another rolling element 36 is in point contact with only one point on the raceway surface 34b ( 43 ) and a point on the raceway surface 35 ( 43 ), so that a large spin motion can be avoided in the four-point contact ball bearing in the related art.

Furthermore, the manner in which the rolling element 36 . 36 and the outer ring 31 , the inner ring 32 in contact with each other, the same as that of a general ball bearing, so that the rolling resistance is small and low torque can be provided as compared with the cross roller bearing.

67 shows a sixth. Embodiment of the invention. In the embodiment has an outer ring 31 a raceway surface, and an inner ring 32 has two raceway surfaces; the outer ring 31 is a one-piece type and the inner ring 32 is a bipartite type.

Other Components and benefits are the same as those in the first one Example.

68 shows a seventh embodiment of the invention. In the embodiment has an outer ring 31 two raceway surfaces 31a and 31b , and an inner ring 32 has two raceway surfaces 32a and 32b ; the outer ring 31 is of the split-type and the inner ring 32 is a one-piece type.

Other Components and advantages are the same as those in the first example.

Everyone from the outer ring 31 and inner ring 32 can consist of two races, as in the example, and the outer ring 31 can of the one-piece type and the inner ring 32 may be of the two-part type or both the outer ring 31 as well as the inner ring 32 can be of the two-division type.

In the invention, between the outer ring and the inner ring, the rolling elements are positioned so that they alternately intersect on the circumference, so that a bearing can absorb a radial load, axial loads in both directions and a load torque. Since each rolling element is always in contact with only two points on the outer and inner ring, the slippage caused by large spin motion in the four-point contact ball bearing or the three-point contact ball bearing is caused in the related art Technique is small, and the spin wear resistance performance can be improved.

There the bearing clearance can be set small or negative, As required, high torque resistance can be provided become. Furthermore, the rolling element a ball, and the rolling element and the race come into point contact with each other, so that the rolling resistance is small and low torque compared to the cross roller bearing can be created. As a result, the entire apparatus can be made compact, reduced in weight and improved in life, and the costs can be too be reduced.

Under Reference now to the accompanying drawings become preferred embodiments of rolling bearings of the invention.

The embodiments are only embodiments, to describe the bearings of the Invention, and it is to be understood that the invention not on the specific embodiments limited to the same is, and that of the combination and arrangement of parts can use be made without the spirit and scope of the invention to leave.

The roller bearing of the invention is e.g. in a corrosive atmospheric High humidity environment, water spray, underwater, acid, alkali, reactive gas, etc. in a conveyor, a food machine, a cleaning device, a Fishing machine, chemical plants, a medical device, one Semiconductor / liquid crystal manufacturing apparatus etc., and the corrosion resistance is for the rolling bearing required.

The rolling bearing comprises a plurality of rolling elements 36 . 36 ... who are in a career groove 33 are installed between the inner diameter of a raceway (outer ring) 31 and the outer diameter of a race (inner ring) 32 is trained.

The races 31 and 32 each can be one piece or both of the races 31 and 32 can be divided axially into two parts at any desired widthwise position and assembled in one piece with a screw, rivet, etc. When the raceway is divided into two parts and a flange part exists, the flange part may also be fixed for fixing the raceway divided into two parts. In this case, the shape and the structure of the flange are not limited, and the axial dimension of the flange may be symmetrical or asymmetrical and is not limited, and the structure may be changed without departing from the spirit and scope of the invention. In order to improve the fixing position accuracy of the flange and the part to which the flange is fastened, the flange may be formed with a hole structure, etc.

The raceway groove 33 is made of track surfaces 34 and 35 each of which has a larger radius than the radius of the rolling element 36 , The raceway surfaces 34 . 35 the raceway groove 33 of at least one of the races 31 and 32 is made up of two raceway surfaces 34a and 34b . 35a and 35b formed, each of which has a larger radius than the radius of the rolling element 36 ,

Every raceway surface 34 ( 34a and 34b ) 35 ( 35a and 35b ) may be of any shape such as a curve or a V in cross section and may be shaped like a curve, a line or the like, and is not limited if it has a shape suitable for rolling the rolling element 36 suitable is. For example, a Gothic arch, etc. formed of two circular arcs having centers positioned like a cross is applied.

In the embodiment is an undercut at the intersection of the raceway surfaces to Facilitated grinding, but with a raceway groove, which is shaped like a continuous ellipse without forming the relief can be formed.

The rolling element 36 is of any shape and has an outside diameter 36a as a rolling contact surface having a curvature in the axial direction and a radius smaller than the radius of the raceway surface 34 ( 34a and 34b ) 35 ( 35a and 35b ). The adjacent rolling elements 36 are alternately positioned like a cross, and the outside diameter 36a each rolling element 36 is always in contact with a point on the raceway surface 34 ( 34a and 34b ) of a raceway 31 and a point on the track surface 35 ( 35a and 35b ) of the other race 32 ,

For example, the rolling element 36 , this in 65 is shown a ball formed at the top and bottom with a cut and which has a pair of planes (opposite surfaces) 36b and 36b has (a structure in which the top and bottom part of the ball is cut to levels 36b and 36b to build). The rolling elements 36 . 36 ..., are built in such a way that the rotation center axes 36c perpendicular to the planes 36b and 36b intersect each other, and the outside diameter 36a each rolling element 36 is always in contact with a point on the track surface 34 ( 34a and 34b ) of a raceway 31 and a point on the track surface 35 ( 35a and 35b ) the other race 32 ,

The cutting widths at the top and bottom of the rolling element 36 are not limited, and the cut percentage of the top and bottom may be the same or different, and may be selected as desired without departing from the spirit and scope of the invention. That is, the opposite surfaces 36b and 36b of the rolling element 36 may be symmetric or asymmetric; the symmetrically opposed surfaces and the asymmetrically opposed surfaces being within the spirit and scope of the invention.

64 shows an example of a rolling element having two planes which are asymmetrical. The embodiment is used especially for high speed rotation.

The rolling element 36 ' the embodiment has asymmetric planes (opposite surfaces) 36b ' and 36d ' and is positioned so that the big end 36d the planes (the opposite surfaces) 36b ' and 36d ' to the inner ring 32 directed the bearing, wherein the rotation of the rolling element 36 ' becomes more stable and a lower torque can be generated. The reference number 36a ' denotes an outer diameter and the reference number 36c ' denotes a rotation center axis.

Other components and advantages are the same as those of the rolling element 36 ' , referring to 63 was described and will not be explained again.

The rolling element 36 may be shaped like a ball comprising a plane formed by cutting off the top or bottom of the ball, as in FIG 70 is shown.

The entire shape of the rolling element 36 , the presence or absence of opposing surfaces 36b and 36b ( 36d ), the size of the curvature in the axial direction at the outer diameter 36 and the like are not limited to the specific forms described above and may be changed as desired without departing from the spirit and scope of the invention. That is, for example, the rolling element may comprise two non-parallel surfaces instead of the opposite surfaces 36b and 36b and can be a rotation center axis 36c which is perpendicular to both surfaces.

The rolling elements 36 . 36 ..., are built in such a way that the rotation center axes 36c and 36c that are perpendicular to the planes 36b and 36b . 36b and 36b at the adjacent rolling elements 36 and 36 intersect alternately, and the crossing state may be orthogonal or may not be orthogonal.

The way in which the rolling elements 36 how a cross is positioned is not limited if the number of rolling elements is the same as that of the rolling elements crossing the rolling elements. That is, the rolling elements 36 For example, like each other, a rolling element may be positioned like a cross, or may be positioned like a cross of all two rolling elements, or may be positioned like a cross in such a manner of two rolling elements, one rolling element, one rolling element, two rolling elements 36 , ... when the number of rolling elements is the same as that of the rolling elements crossing the rolling elements; each manner being within the spirit and scope of the invention.

The movement of each rolling element 36 . 36 gets through a cage 37 or a spacer (spacer) 39 guided.

The cage 37 or the spacer (the spacer) 39 is not limited if it is of a shape that has a recess 38 for holding and guiding the rolling element 36 or grooves 40 and 40 having; the shape may be selected or changed as desired without departing from the spirit and scope of the invention.

The type of leadership of the cage 37 is not limited and may be an inner ring guide, an outer ring guide or a Wälzelementführung.

The structure, shape and the like of the cage 37 are not limited; for example, the cage 37 a one-piece type or may be formed of different parts.

The Material of the cage is not limited. There a machined cage, a press cage, a resin cage or the like is suitably selected, e.g. Brass metal, Iron, stainless steel, etc., or synthetic resin, e.g. Polyethylene (PE) resin, Polypropylene (PP) resin, polyacetal (POM) resin, polyarylansulfide resin, which is represented by polyphenylsulfide (PPS) resin, polyether ether ketone (PEEK), polyether nitrile (PEN), aromatic polyimide (PI), thermoplastic Polyimide (TPI), polyamide-imide (PAI), aromatic polyester (LCP) or fluorine-containing resin, is selected within the spirit and Scope of the invention.

For example, the cage is 37 so constructed that so many recesses 38 ... like the number of rolling elements 36 ... are present, with the adjacent rolling elements 36 . 36 so who built that can, that the Rotationsmittelachsen 36c and 36c alternately crossing each other and being equally spaced and positioned like a cross alternately on the circumference of an annular ring.

Both sides 38a and 38b every recess 38 in the axial direction of the same are parallel to each other, are neither perpendicular nor parallel to the axis of rotation of the bearing and are at a constant angle (a constant slope) with an equal level to the contact angle of the rolling element 36 located.

The distance between both sides 38a and 38b every recess 38 in the axial direction thereof is made slightly larger than the width of the rolling element 36 ,

The entire shape of the recess 38 is not limited if both parallel sides 38a and 38b the recess 38 how a slant is formed and the distance between both sides 38a and 38b is slightly larger than the width of the rolling element 36 ; the entire shape of the recess 38 can be changed without departing from the spirit and scope of the invention.

In the embodiment are so many recesses 38 ... like the number of rolling elements 36 ... are present and are equidistant and positioned like a cross alternately on the perimeter, but the invention is not limited thereto. The recesses 38 ... can be like a cross all two recesses or can be positioned like a cross in such a way of two recesses, a recess, a recess, two recesses, ..., if the number of recesses is the same as the the recesses that intersect the recesses; each manner falls within the spirit and scope of the invention.

It it is possible, that a spin movement or a skew in the rolling element, that is rotated occurs because of the effects of various factors, and when the position of the rolling element is not well controlled, there is a possibility that the rotational resistance of the Camp is getting big or that a uniform rotation impossible can be generated.

Therefore, according to the embodiment, each recess comprises 38 of the cage 37 the two parallel sides 38a and 38b which are made almost equal to the constant angle at the same level to the contact angle of the rolling element 36 , and the change in position of the rolling element 36 caused by a spin movement, skew, etc. of the rolling element 36 can be effected by both sides 38a and 38b the recess for maintaining the position of the bearing are suppressed, so that a low torque of the bearing can be generated.

The spacer 39 who in 66 is shown as a smaller diameter than the diameter of the rolling element 36 shaped and is with concave circular arc grooves 40 and 40 like a cross in opposite planes 41 and 41 for holding the adjacent retained rolling elements 36 and 36 formed so that the rotational center axes 36c and 36c intersect each other as described above. The radius of curvature of the circular arc groove 40 may be roughly equal or greater than the radius of curvature of the outer diameter 36a of the rolling element 36 ; he can be arbitrary.

If the spacers 39 can be used in this way, the entire camp can be made compact.

Of the Condition in which a preload between the rolling element and the track area granted is, is not limited, it can indeed be given a preload in the manufacturing stage or not issuing a preload and not submitting a preload at the manufacturing stage in the spirit and the scope of protection the invention lie.

Of the Gap in the bearing may be small or negative (minus) as required be set. Correspondingly, a higher torque resistance of the camp.

The reference number 44 in the figure denotes a sealing plate. As a sealing plate 44 For example, a contact seal, a non-contact seal, or a contact shield, and the shape of the seal plate are used 44 is not limited if a gasket of a known shape is suitably selected without departing from the spirit and scope of the invention.

The reference number 44a in the figure, a sealing surface of the sealing plate 44 (Hermetic sealing surface), which comes into intimate contact with the inner bottom of an inner ring sealing groove. The material of the gasket or the shield is not limited; it is preferably nitrile rubber or stainless steel.

The positioning type of the seal plate is not limited, and the seal plate 44 can be positioned as required on either side or a single page; wherein the positioning of the sealing plate 44 on both sides and positioning the seal plate 44 on one side in the spirit and the scope of the invention lie. The sealing surface may be on an outer ring side or the inner ring side; each case is within the spirit and scope of the invention.

The Shape of the gasket, e.g. a lip shape, is not limited, and a line contact with the sealing surface and a surface contact with the sealing surface are within the spirit and scope of the invention.

If a cored rod exists may be determined as desired and the type that has a coreed rod, and the type having a rod without a core can on suitable way, as required, are used.

The sealing groove structures of the outer ring 31 and the inner ring 32 each are not limited and may be changed whenever necessary without departing from the spirit and scope of the invention.

The presence or absence of the sealing plate 44 is not limited, and the sealing plate 44 can be installed or can not be installed as required; installing the gasket plate 44 and no installing the seal plate 44 are within the spirit and scope of the invention.

In the invention, stainless steel, ceramics, resin, etc. are used as the material of all or at least one of the three elements of the race (outer ring). 31 , the raceway (inner ring) 32 and the rolling elements 36 or an anti-corrosive coating treatment is applied to the surfaces of all or at least one of the three elements of the outer ring 31 , the inner ring 32 and the rolling elements 36 which depends on the environment usage (corrosive atmospheric environment).

The "stainless steel" is not limited and can austenitic stainless steel, martensitic stainless Steel or the family of precipitation hardened stainless steel belong and can change without departing from the spirit and scope of the invention.

Of the Type "ceramic Materials "is not limited, and ceramic material for the structure, e.g. the alumina family, zirconia family, Silicon nitride family or silicon carbide family can be selected.

The Base material of the "corrosion-inhibiting Coating "is not limited; e.g. is suitably bearing steel, carburized steel, stainless Steel, ceramics, etc. selected. The "corrosion-inhibiting Coating "is not limited; e.g. is a soft metal, e.g. Gold, silver or lead or one layered compound, such as e.g. Molybdenum disulfide or tungsten disulfide, Graphite, fluororesin, e.g. Polytetrafluoroethylene, hard chrome plating, electroless Nickel plating, low-temperature chromium fluoride coating, Ceramic coating, etc. selected in a suitable manner. Further The corrosion-inhibiting coating can be a single coating or a composite coating; every case in the mind and the scope of the invention.

The "resin material" is not limited; preferred Way, it is polyethylene (PE) resin, Polypropylene (PP) resin, polyacetal (POM) resin, polyarylansulfide resin, which is represented by polyphenylene sulfide (PPS) resin, polyether ether ketone (PEEK), polyether nitride (PEN), aromatic polyimide (PI), thermoplastic Polyimide (TPI), polyamide-imide (PAI), aromatic polyester (LCP) or fluorine-containing resin. The fluorine-containing resin is not limited; Tetrafluoroethylene-perfluoroalkyl ether copolymer (PFA), tetrafluoroethylene-ethylene copolymer (ETFE), polyvinylidene fluoride (PVDF), tetrafluoroethylene-hexafluoropropylene copolymer (FEP), polychlorotrifluoroethylene (PCTFE), Chlorotrifluoroethylene-ethylene copolymer (ECTFE), etc. may be named become.

One Fiber extender can be used with the resin used in the invention will be mixed to the mechanical strength, the heat resistance and the dimensional stability etc. to improve. The fiber extender is not limited; Bonsäure aluminum whisker, Potassium titanate whiskers, carbon whiskers, aramid fibers, aromatic Polyimide fibers, liquid crystal polyester fibers, Graphite whiskers, glass fibers, carbon fibers, boron fibers, silicon carbide whiskers, Silicon nitride whisk, aluminum whisker, aluminum nitride whisker, wollastonite etc. can be named. Various accessories can without the spirit and scope of the invention to leave.

To the Example may be an antioxidant, a heat stabilizer, an ultraviolet absorber, a sunscreen, a fire retardant, a chemical Electrical charge removal means, a fluidity improver, a means of issuing incoherent Properties, a crystallization accelerator, a core enhancer, Be named pigment, dye, etc.

Next, examples will be explained based on the specific eighth embodiment shown in FIG 69 is shown. Bearings in the Bei Play 1 through 9 have the following common base structure:
First, each of the bearings in the examples is basically a raceway (outer ring). 31 , a race (inner ring) 32 and rolling elements (balls, each of which is formed at the top and bottom with a cut) 36 educated. The race (outer ring) 31 has a track groove 33 consisting of two raceway surfaces 34a and 34b each of which has a larger radius than the radius of the rolling element 36 , this in 69 is shown, with the raceway (inner ring) 32 a track groove 33 that has two career surfaces 35a and 35b each of which has a radius greater than the radius of the rolling element 36 , this in 69 is shown, and the shape of the rolling element (a ball, which is formed at the top and bottom with a cut) 36 , in the 63 is shown with planes (opposite surfaces) 36b and 36b , which are symmetrical, is adopted.

The rolling elements are positioned so that rotational center axes 36c and 36c the rolling elements are perpendicular to the planes (opposite surfaces) 36b and 36b intersect each other and the movement of each rolling element 36 . 36 is through a recess 38 . 38 a cage 37 who in 65 shown is guided.

At the cage 37 There are so many recesses 38 ... like the number of rolling elements 36 ... present, in which the adjacent rolling elements can be installed so that the rotation center axes 36c and 36c alternately intersect each other and are positioned at an equal distance and alternately like a cross on the circumference of an annular ring, as described above.

EXAMPLE 1:

In example 1 are an outer ring 31 , an inner ring 32 and rolling elements 36 all made of stainless steel material.
Outer and inner rings: martensitic stainless steel
Cage: resin
Lubricant: Fat of the lithium family
Sealing plate: contact rubber gasket made of nitrile rubber Corrosive environment in which the bearing is used: the bearing is used in a highly humid environment.
Characteristic: According to the example, a corrosion resistance more excellent than that of a bearing using bearing steel can be provided.

EXAMPLE 2

In example 2, the outer ring 31 and the inner ring 32 formed of stainless steel material, and the rolling elements 36 are made of a ceramic material.
Outer and inner rings: martensitic stainless steel
Rolling elements: Ceramic of the silicon nitride family
Cage: fluororesin
Lubricant: water-resistant grease
Sealing plate: Shield made of stainless steel (non-contact sealing plate)
Corrosive environment in which the bearing is used: the bearing is used in a high humidity, water spray and underwater environment.
Feature: According to the example, while the bearing has a corrosion resistance, it has a longer life than the bearing in Example 1 in a water environment.

EXAMPLE 3

In example 3 are the outer ring 31 and the inner ring 32 made of ceramic material and the rolling elements 36 are made of a stainless steel material.
Outer and inner rings: ceramic of the silicon nitride family
Rolling elements: martensitic stainless steel
Cage: fluororesin
Lubricant: water-resistant grease
Sealing plate: Shield made of stainless steel (contactless sealing plate)
Corrosive environment in which the bearing is used: the bearing is used in a high humidity, water spray and underwater environment.
Feature: According to the example, while the bearing has a corrosion resistance, it has a longer life than the bearing in Example 1 in a water environment.

EXAMPLE 4

In Example 4, the outer ring 31 and the inner ring 32 made of stainless steel material and the rolling elements 36 are made of ceramic material.
Outer and inner rings: family of precipitation hardening stainless steel
Rolling elements: Ceramic of the silicon nitride family
Cage: fluororesin
Lubricant: solid lubricant
Sealing plate: Shield made of stainless steel (contactless sealing plate)
Corrosive environment in which the bearing is used: the bearing becomes strong moist, water spray, underwater and fumigate environments.
Feature: According to the example, the bearing has a higher corrosion resistance than the bearing made of martensitic stainless steel. Preferably, the bearing is used in the example for a low load, although the use of the bearing is not limited.

EXAMPLE 5

Example 5 illustrates a bearing with a corrosion-preventing coating, wherein the outer ring 31 and the inner ring 32 covered with a corrosion-preventing coating and the rolling elements are formed of stainless steel material.
Outer and inner rings: stainless steel + low-temperature chromium fluoride coating
Rolling elements: stainless steel
Cage: fluororesin
Lubricant: water-resistant grease
Sealing plate: Shield made of nitrile rubber (contact sealing plate)
Corrosive environment in which the bearing is used: the bearing is used in a highly humid, water-spray underwater and fumigant environment.
Characteristic: According to the example, the bearing has a higher corrosion resistance and a more excellent life than the bearing of Example 1 in environments of water, fuming acid, etc.

EXAMPLE 6

Example 6 provides a bearing with a corrosion preventive coating, with the anti-corrosion coating treatment for all of the outer ring 31 , Inner ring 32 and rolling elements 36 is carried out.
Outer and inner rings: martensitic stainless steel + nickel alloy coating
Rolling elements: martensitic stainless steel + nickel alloy coating
Cage: fluororesin
Lubricant: water-resistant grease
Sealing plate: Shield made of stainless steel (contactless sealing plate)
Corrosive environment in which the bearing is used: the bearing is used in a highly humid, water-spray underwater, fumigant, chemical and alkali environment.
Feature: According to the example, the bearing has a higher corrosion resistance and a higher hardness than the bearing, which uses martensitic stainless steel and hard chrome plating.

EXAMPLE 7

In example 7, all are the outer ring 31 , the inner ring 32 and the rolling elements 36 made of ceramic material. In the example, no sealing plate is used.
Outer and inner rings: ceramics of the alumina family
Rolling elements: silicon nitride ceramic
Cage: fluororesin
Lubricant: solid lubricant
Corrosive environment in which the bearing is used: the bearing is used in a highly humid, water spray, underwater, weak acid and alkali environment.
Feature: According to the example, the bearing has a longer life than the bearing in example 1 or 2. The advantage that alumina family ceramics are cheaper than other ceramics is also created.

EXAMPLE 8

In example 8, all are the outer ring 31 , the inner ring 32 and the rolling elements 36 made of ceramic material. In the example, no sealing plate is used.
Outer and inner rings: ceramics of the silicon carbide family
Rolling elements: ceramics of the silicon carbide family
Cage: fluororesin
Lubricant: solid lubricant
Corrosive environment in which the bearing is used: the bearing is used in a highly humid, water-spray, underwater, fumigate, strong acid, strong alkali and reactive gas environment.
Feature: In the example, the ceramic materials used for the outer and inner rings and the rolling elements have a higher corrosion resistance than other ceramic materials, so that the bearing in the example has a longer life even in a strong acid environment.

EXAMPLE 9

In Example 9, the outer ring 31 and the inner ring 32 formed of resin material, and the rolling elements 36 are made of ceramic material.
Outer and inner rings: fluororesin
Rolling elements: ceramics
Cage: fluororesin
Lubricant: solid lubricant
Corrosive environment in which the bearing is used: the bearing is used in a highly humid, water-spray, underwater, fumed acid, strong acid, strong alkali and reactive gas environment.
Feature: according to the example, has the bearing a longer life than the bearing of Example 1 at a low load. It also has a corrosion resistance equal to the bearing using the ceramic material for the outer and inner ring. The bearing in the example also has low cost.

Therefore, according to the examples, the outer diameter comes 36a of the rolling element 36 in contact with a point on the raceway surface 34a of the outer ring 31 and a point on the track surface 35b of the inner ring 32 (the contact points are with 42 and 42 designated), the outer and inner rings facing each other, and the adjacent rolling elements 36 come into contact with a point on the track surface 34b of the outer ring 31 and a point on the track surface 35a of the inner ring 32 (the contact points are with 43 and 43 designated).

Since the rolling elements 36 and 36 Alternating with a contact angle, a bearing can receive a radial load, thrust loads in both directions, and a load moment.

A rolling element 36 is in point contact with only one point on the raceway surface 34a ( 42 ) and a point on the raceway surface 35b ( 42 ), and another rolling element 36 is only in point contact with a point on the raceway surface 34b ( 43 ) and a point on the raceway surface 35a ( 43 ), so that slippage small by a strong spin motion in the four-point contact ball bearing or the three-point contact ball bearing in the related art, and the spin wear performance can be improved.

Furthermore, the rolling element come 36 . 36 and the outer ring 31 , the inner ring 32 in point contact with each other so that the rolling resistance is small and a low torque can be generated as compared with the cross roller bearing.

As a result, The entire device can be made compact, in weight be reduced and improved in life, and costs can also be reduced.

stainless Steel, ceramics, resin and the like are used for the inner ring, the outer ring and the rolling elements the bearing used, the corrosion resistance of the bearing is improved and a corrosion-preventing coating treatment carried out is, wherein the anti-corrosive substance does not directly the can corrode underlying area of the bearing material and Thus, the bearing can be equipped with a long life can.

Corresponding the invention are between the outer and inner ring, the rolling elements positioned so that they alternate on the perimeter each other cross so that a bearing has a radial load, axial load in both Directions and a load torque can absorb. As each rolling element always in contact with only two points on the outer and inner ring is a slip caused by a strong spin movement in the four-point contact ball bearing or causes the three-point contact ball bearing in the relevant related art becomes small, and the spin wear resistance performance can be improved. Since the bearing clearance is set small or negative is as required, a torque resistance can be provided become. Furthermore, the rolling element come and the race in point contact with each other, so that the rolling resistance is small and a low torque can be provided compared with the cross roller bearing. As a result, the entire device can be compact accomplished be reduced in weight and improved in life be, and the costs can be also be reduced.

stainless Steel, ceramics, resin and the like are used for the inner ring, the outer ring and the rolling elements the bearing used, the corrosion resistance of the bearing is improved and a corrosion-preventing coating treatment carried out with the corrosive substance not directly below it lying region of the bearing material can corrode, and thus the bearing can be equipped with a long life.

The other embodiments a rolling bearing device The present invention will be described with reference to the accompanying drawings. A cage and a role are the same as those explained above Embodiment, so that a detailed description thereof will be omitted.

The Rolling device The present invention is constructed such that the spindle of a Machine tool or the rotation shaft of another in general high-speed rotary machine using at least one roller bearing supported which has the following construction. In other words, the number of rolling bearings, which should support the rotation shaft not particularly limited but could be one or more, as appropriate, as appropriate. About that In addition, this rolling bearing in combination with another type of bearing, such as e.g. a cylindrical roller bearing used become.

71 shows an example of the type having a one-piece outer ring and a split inner ring, which two raceway surfaces 34a and 34b . 35a and 35b each have; 72 shows an example of the type having a one-piece outer ring and a split inner ring, wherein the outer ring has a raceway surface 34 has on, wherein the inner ring two raceway surfaces 35a and 35b having; and 73 shows an example of the type having a split outer ring and a one-piece inner ring, each having two raceway surfaces 34a and 34b and 35a and 35b exhibit.

The rolling element 36 is a top / bottom cut ball that has a set of flat surfaces (or opposing surfaces) 36b . 36b has (ie, a structure, the opposite surfaces 36b and 36b by cutting off the upper and lower portions of a ball as in the following). The individual rolling elements 36 . 36 , ---, etc. are installed so that the axes of rotation 36c perpendicular to the flat surfaces 36b and 36b intersect each other, and the outside diameter 36a each rolling element 36 always produces single two-point contacts, either with the raceway surface 34 ) ( 34a of a race 31 and the raceway area 35 ( 35b ) of the other race 32 or with the track surface 34 ( 34b ) of a raceway 31 and the raceway area 35 ( 35a ) of the other race 32 ,

The rolling element 36 should not be particularly limited in the cutting widths of the upper / lower portions, and the cutting widths of the upper / lower ends may be equal or different, so that their ratio may be arbitrarily selected within the scope of the present invention. In other words, the opposing surfaces 36b and 36b of the rolling element 36 may be defined symmetrically or asymmetrically, and any of these symmetrical or asymmetric definitions fall within the scope of the present invention.

The 74A and 64B show an embodiment of a rolling element having a set of asymmetric flat surfaces, as used particularly in the case of high speed rotations.

The rolling element 36 In the present embodiment, the asymmetric flat surfaces (or opposing surfaces) 36b and 36d and is able to better stabilize its rotation and lower torque by arranging the enlarged ends 36d the flat surfaces (or opposing surfaces) to the inner ring 32 to realize. The reference number 36a be distinguished the outer diameter, and the reference numerals 36c denote the axes of rotation.

The remaining constructions, effects and effects are omitted because they are equal to those of the rolling element 36 which are by reference to 71 has been described.

In addition, the rolling element 36 have a spherical shape (or one-sided truncated spherical shape) by cutting either the upper or lower area to a flat surface (or cut surface) 36e to form, as in the 75A and 75B is shown. The cut (or removed) width of this one-sided cut surface 36e should not be particularly limited, and the shape of the cut surface 36e should not be limited to a flat surface, but any shape can be selected. This one-side truncated sphere construction thus produced has fewer machined areas than the above-mentioned truncated sphere so that it can be manufactured at a lower cost.

Here, the entire shape of the rolling element should 36 , the presence or absence of opposing surfaces 36b and 36b (and 36d ) and the value of the curvature in the axial direction of the outer diameter 36a are not limited to the specific values explained above, but may be arbitrarily modified within the scope of the invention. For example, the opposing surfaces 36b and 36b be replaced by two non-parallel surfaces, and may have axes of rotation which are perpendicular to the two surfaces.

In a cage 37 who in 76 is shown, are alternately in the circumferential direction recesses 38 . 38 , ---, etc. formed, which the adjacent individual rolling elements 36 . 36 , ---, etc. can alternately include, so that the axes of rotation 36c and 36c perpendicular to the cut surfaces 36e and 36e can cross each other.

The recess 38 is formed in a dome shape, as seen in a plan view, around an arc surface 38c having a slightly larger diameter than that of the rolling element 36 , and a flat surface 38d to have the end areas of the arc surface 38c combines. A page 38e on the side of the outside diameter 7a and a page 38f on the side of the inside diameter 37b are over an inclined surface 38g from the outside diameter 37a to the inside diameter 37b connected, and an opening width W31 on the side of the outer diameter 37a is made diametrically smaller than the opening width w32 on the inner diameter side 37b (as in 76 and 77A is shown).

In addition, the centers of the arc surfaces 37a the individual recesses 38 , which adjoin in the circumferential direction, arranged on a common circumference, and the one side 38e on the side of the outside diameter 37a is offset in the width direction, as seen in a plan view. In other words, the individual recesses 38 which are adjacent in the circumferential direction are arranged so that they have their inclined surfaces 38g alternately on the right and left side of the individual recesses 38 have (referring to 76 ).

If the cage 37 Therefore, as illustrated in the present embodiment, it becomes the rolling element 36 that in every recess 38 is arranged, held, so that their cut surfaces 36e and 36e to the outside diameter 37a directed to the outer ring 31 is directed so that the axes of rotation 36c and 36c the individual rolling elements 36 and 36 can alternately cross each other.

As in 77B In addition, a structure may be adopted in which a one-side fall prevention element (one-side case member) 38h is designed to from the outside diameter 37a on the extension of the inclined surface 38g to rise with an equal slope. The one-side fall prevention element 38h should not be limited particularly to the shape shown, but a construction that does not affect the rotation of the rolling element 36 would fall within the scope of the present invention.

The cage 37 can also take a cage structure in 78 is shown.

In the present embodiment, the recess 38 formed in a rectangular shape, as shown in a plan view. One side 38e extending in the circumferential direction on the side of the outer diameter 37a extends and one side 38f , which are below the former on the side of the inside diameter 37b are arranged on the inclined surface 38b and the outside diameter 37a to the inside diameter 37b connected, and the opening width W31 on the side of the outer diameter 37a is made diametrically smaller than the opening width w32 on the inner diameter side 37b (as in 78 and 79 is shown).

In addition, the individual recesses 38 , which are to be arranged in the circumferential direction, alternately arranged offset in a plan view.

In other words, the individual recesses 38 that are adjacent in the circumferential direction are alternately offset at each recess 38 arranged offset (as in 78 shown).

At the cage 37 In the present embodiment, a larger fat retention space can be obtained than in the cage 37 from 76 , The other effects and effects are those of the mode of operation in 86 the same cage.

In addition, the arrangement of a spacer (or spacer) also falls 39 , the (that) a recessed area 42 has, as in 80 is also within the scope of the present invention.

The spacer 39 is made to have a smaller diameter than the rolling element 36 , and the recessed areas 42 and 42 are so on opposing surfaces 41 and 41 formed, that the individual rolling elements 36 and 36 , which are to be held adjacent to each other, are held so that the axes of rotation 36c and 36c perpendicular to the cut surfaces 36e and 36e can cross each other as previously described. In short, the cut surface 36e of the rolling element held so that it is a stepped portion 42a the recessed area 42 opposite. Here, the spacer mold as illustrated in the present embodiment is only one embodiment, so that it can be arbitrarily modified in construction without any limitation.

Of the Condition in which a preload between the rolling element and the race is used up, is not limiting. In particular, can the preloading is consumed in the manufacturing stage or not, and each of these variants falls within the scope of the present invention. The application of the preload is for Improvement of the strength of the bearing advantageous.

Furthermore the clearance in the bearing is set smaller than necessary or negative (or minus). Then it is possible, one higher To realize torque stability of the bearing.

The Presence or absence of the sealing plate is not especially restrictive, and the seal plate may or may not be within the scope of protection be mounted of the present invention.

The seal plate may be any one of a contact type seal, a contact type seal, and a shield type. The shape is not particularly limitative, but can be suitably selected from the well-known forms. The material for the seal or shield is not particularly restrictive, but may preferably be nitrile rubber or stainless steel.

The Arrangement of the sealing plate is not particularly limiting. The Sealing plate can be on both sides or on one side, if necessary, within the scope of the present invention Be arranged invention. The sealing surface may be on the side of the outer ring or the inner ring within the scope of the present invention be provided.

The Sealing shape is not particularly limited to a lip shape and may make a line contact or surface contact with the sealing surface within the scope of the present invention.

Furthermore the presence or absence of the nucleus is arbitrary, and the type with and without the core can be used separately if necessary, and should not be interpreted in a particularly restrictive way.

This shows 73 the case where the inner ring 32 is integral, with the outer ring 31 is halved and in which a sealing plate (or contact seal) 43 on the end face of the outer ring 31 is arranged. The reference numerals 43a denote the sealing surface of a sealing plate 44 which comes into close contact with the inner bottom of the inner ring seal groove.

In addition, the sealing groove structures of the outer ring 31 and the inner ring 32 not particularly limiting, but may be suitably modified within the scope of the present invention.

The material for the outer ring 31 , the inner ring 32 and the rolling element 36 should not be particularly limiting, but may be exemplified by any material of bearing steel, bladder steel, stainless steel, heat resistant steel such as M50, and ceramics, and these materials are within the scope of the present invention.

Of the Stainless steel is not particularly limited in its components, but can be as austenitic stainless steel, martensitic stainless Steel or stainless precipitation hardening steel within the scope of protection modified the present invention.

The Types of ceramic materials are not particularly limiting, but can structural ceramics including alumina, zirconia, Silicon nitride and silicon carbide.

Moreover, it is not limiting, the common material for the outer ring 31 , the inner ring 32 and the rolling element 36 to use. If necessary, individual different materials may be used (as a hybrid) for a modification falling within the scope of the present invention. For example, as a material for the outer ring 31 and the inner ring 32 Use bearing steel as an example and as a material for the rolling element ceramic (eg silicon nitride) can serve as an example.

The surface treatment of the outer ring 31 , the inner ring 32 and the rolling element 36 is not particularly limitative, but curvature treatment or a nitriding surface hardening treatment or a surface layer treatment within the scope of the present invention may be exemplified. In the coating treatment, a metal, a metal compound or a ceramic layer is suitably selected as a layer material. The layer may be either a single or a composite layer within the scope of the present invention. For example, the rolling element 36 coated on its surface with a silicon nitride layer.

The Lubricant for The camp is not particularly limited, but it can be fat, oil or water to serve as an example. About that In addition, the lubrication method is not particularly limited, but can grease, a circulation feed, a spray feed, an oil-air feed or nozzle feed in a suitable way.

This embodiment is constructed using two conventional cylindrical roller bearings 45 and the above-explained rolling bearing on the outer circumference of the shaft 44 , In particular, in the present embodiment, the rolling bearing which is in 71 is shown, in which the outer ring 31 and the inner ring 32 from the two races 34a and 34b and 35a and 35b different curvatures exists and in which the outer ring 31 is integral, and wherein the inner ring 32 divided, instead of the two ball bearings used in the bearing device according to the prior art. In order to further improve the axial strength of the bearing device, the inner distance of the bearing is set negative.

This embodiment is using a conventional cylindrical roller bearing 45 and two previously discussed rolling bearings on the outer circumference of a shaft 44 built up. In particular, in the present embodiment, the rolling bearing which is in 71 it is shown in which of the Au ßenring 31 and the inner ring 32 from two races 34a and 34b and 35a and 35b exist with different curvatures, and in which the outer ring 31 is integral and wherein the inner ring 32 divided is used instead of the four angular contact ball bearings in the bearing device according to the prior art.

Therefore, the rolling elements 36 between the outer and inner rings 31 and 32 arranged so that they are alternately offset on the circumference, so that they can bear the radial load, the axial loads in the two directions and the load torque through the single bearing. This single bearing acts like two angular bearings. In addition, each rolling element is available 36 at only two areas with the outer and inner raceway surfaces 34 and 35 so that a strong skid, which could otherwise be caused by the prior art four-point contact ball bearing, is reduced while the spin resistance wear performance is improved. If necessary, moreover, the bearing clearance can be set small or negative to realize high strength. In addition, lead the rolling element and the outer and inner rings 31 and 32 the point contacts, so that the rolling resistance can be reduced to realize high-speed rotations.

By using the warehouse, as in 71 1, a high-speed rotation support device such as the spindle of a machine tool according to this invention can realize the functions of two angular bearings by the single bearing. Moreover, higher spin wear resistance, lower torque, and higher strength than the four-point contact ball bearing can be achieved to make the axial size of the prior art support bearing apparatus smaller, so that the entire apparatus can be made compact and easy, and in terms of Life and cost can be improved.

Under Reference now to the accompanying drawings becomes a 23rd embodiment a rolling bearing explained according to the present invention.

The embodiments are only embodiments, to describe the bearings of the Invention, and it is understood that the invention not on the specific embodiments limited to the same is and the combination and arrangement of parts can be use be made without the spirit and scope of the invention to leave.

A roller bearing according to the present invention comprises a race (outer ring) 61 ; another race (inner ring) 62 ; a variety of rolling elements 65 . 65 , ..., in a career groove 63 are installed, wherein the groove between the inner diameter of the outer ring 61 and the outer diameter of the inner ring 62 is limited.

The outer ring 61 can be a track groove 63 have that in a desired shape by means of raceway surfaces 61a and 61b are formed along the inner diameter of the raceway (outer ring) 61 are formed. A roller bearing, the races 61 and 62 a non-pitching type or a roller bearing, the raceways 61 and 62 may be used, one or both of which are divided axially into two parts along the width center thereof.

Some Ball bearings of the double separation type are in one piece using screws or Rivets mounted. When using a double-separation type ball bearing using fastened by screws or rivets, there is no need for a Preload or distance adjustment.

The bearing includes an inner ring 61 and an outer ring 62 , A variety of rolling elements 65 . 65 , ... are rotatable between the raceway grooves 63 interposed. If only one of the raceways consists of two raceway surfaces, the raceway, which consists of two raceway surfaces, has each raceway surface 61a . 61a ' ( 62a . 62a ' ) has a larger radius than the rolling element 65 and the raceway made of a raceway surface has the raceway surface 61a ( 62a ) has a larger radius than the rolling element 65 , If each race consists of two raceway surfaces, each of the raceway surfaces has 61a and 61a ' and 62a and 62a ' a larger radius than the rolling element 65 ,

Every raceway surface 61a ( 61a ' ) 62a ( 62a ' ) may be of a certain shape such as a curve or a V in cross section and may be shaped like a curve, a line or the like, and is not limited if the shape is suitable for rolling the rolling element 65 , For example, a gothic bow, etc. is applied.

Each of the rolling elements 65 has an outer diameter portion serving as a rolling contact surface having a radius of curvature in an axial direction thereof. As in 84 shown is the rolling element 65 shaped into a sphere with a cutting area. The ball has a radius that is smaller than a radius of curvature of the raceway surfaces 61a ( 61a ' ) and 62a ( 62a ' ) of the inner or outer ring. Namely, the rolling element has a spherical shape (or a one-side truncated spherical shape) by cutting from either the upper or lower region to a flat surface (or Schnittflä che) 65b to build.

The rolling elements are arranged in a circumferential direction of the bearing in such a manner that the cut surfaces 65b the adjacent rolling elements intersect alternately and the outer diameter range 65a each rolling element is always in contact at two points with a raceway surface 61a (or 61a ' ) of the race 61 and the raceway area 62a ( 62a ' ) of the race 62 ,

For example, the rolling elements 65 mounted in such a way that their rotational center axes, which are perpendicular to the cut surfaces 65b extend, alternating are cutting (crossing), while the outer diameter range 65a each rolling element 65 always in contact at two points with one of the raceway surface 61a (or 61a ' ) of the race 61 and the raceway area 62a ( 62a ' ) of the race 62 is in contact.

The cutting width of the cut surface 65b one side of the rolling element 65 is not limited, and the shape of the cut surface 65b is not limited to a flat surface and may be selected as desired without departing from the spirit and scope of the invention.

in the Generally can as rolling elements of same size balls with lower costs and with higher ones Accuracy can be made as rolls.

The closer the shape of the rolling element is to a complete ball, the lower the manufacturing cost of the rolling element. In the embodiment, the rolling element 65 the outer shape such as a ball with a cut side, and the number of parts to be machined is smaller than in a rolling element, which is shaped like a ball and is trimmed on both sides; wherein the rolling element in the embodiment can be manufactured at a lower cost.

The rolling elements 65 . 65 , ... are built in such a way that the rotation center axis 65c perpendicular to the opposite surfaces 65b . 65b of a rolling element 65 that of another, adjacent rolling element 65 crosses at a right angle or any angle.

If the rolling elements 65 aligned in one direction, equal in number to those aligned in the other direction, crossing may occur any number of rolling elements. In other words, the rolling elements 65 can intersect alternately. Further, provided the rolling elements 65 that are aligned in one direction to the number with those aligned in the other direction, the rolling elements 65 each other intersect each other or in a pattern of two elements in a first orientation, an element in a second orientation, an element in the first orientation, and two elements in the second orientation. All rolling elements that are indicated fall within the scope of the invention.

The movements of the respective rolling elements 65 . 65 ... be through a cage 6 guided.

The cage 66 is formed like an annular ring, the recesses 67 ... for holding and guiding the rolling elements 65 having. The shape of the cage 66 is not limited to the form shown in the embodiment and can be selected or changed as desired without departing from the spirit and scope of the invention.

The type of leadership of the cage 66 is not limited and may be an inner ring guide, an outer ring guide or a Wälzelementführung. The structure of the cage 66 is not limited; the cage 6 may be of one-piece type or may be formed of multiple parts.

For example, the cage is 66 with recesses 67 . 67 ... formed alternately in a circumferential direction, wherein the adjacent rolling elements 65 . 65 can be installed so that the rotating central axes 65c and 65c perpendicular to the cut surfaces 65b and 65b alternately cross each other.

The recess 67 is formed like a dome in a plan view, consisting of a circular arched surface 67a is formed, which is shaped like a slightly larger diameter than that of the rolling element and a flat surface 67c is formed, which are the end portions of the circular arc surface 67a connects, and a page 67b on one side of the outside diameter 66a and a page 67b on the side of the inside diameter 66b stand together on a slope 67c from the side of the outside diameter 66a to the side of the inner diameter 66b and an opening width w2 on the inside diameter side 66b is designed to have a larger diameter than an opening width w1 on the side of the outer diameter 66a ( 85 and 86 ).

The centers of the circular arc surface 67a the recesses 67 adjacent in the circumferential direction are positioned on the same circumference and the position of the one side 67b on the side of the outside diameter 66a is offset in the width direction of the plan view. That is, the slopes 67c the recesses 67 are adjacent in the circumferential direction left and right alternately posi tioned (see 85 ).

If therefore the cage 66 used in the embodiment will become the rolling elements 65 that in the recesses 67 are placed, held, so that the cut surfaces 65b and 65b to the side of the outside diameter 66a directed towards, namely to the side of the outer ring 61 out, so that the rotation center axes 65c and 65c the adjacent rolling elements 65 alternately crossing each other.

A structure made with a one-side fall prevention element 67d is provided on the outside diameter 66a like a slope on the extension of the slope 67c is formed, can also be adopted. The one-side fall prevention element 67d is not limited to the shape shown in the figure, and if the shape of the one-side fall prevention element 67d not a rotation of the rolling element 65 it is within the spirit and scope of the invention.

For the cage can be a structure of a cage 66 ' , in the 88 shown is also taken.

In the embodiment, there is a recess 67 ' like a rectangle formed in plan view, and a side 67'a on the side of the outside diameter 66a extending in the circumferential direction and one side 67'a on the side of the inside diameter 66b below one side 67'a stand together on a slope 67'c from the side of the outside diameter 66a to the side of the inside diameter 66b in connection, and an opening width w2 on the inner diameter side 66b is designed so that it has a larger diameter than an opening width w1 on the side of the outer diameter 66a ( 88 and 89 ).

The recesses 67'a which are positioned in the circumferential direction are positioned offset in position alternately in the width direction of the plan view.

That is, the recesses 67 ' adjacent in the circumferential direction have the slopes 67'c alternately offset to the left and right ( 88 ).

If the cage 66 In the embodiment, a larger fat retention space may be used over that of the cage 66 in 85 be created. Other advantages are those of the cage in 55 equal.

A rolling bearing, the spacer (spacers) 68 includes, the concave surfaces 69 , as in 89 is also within the spirit and scope of the invention.

The spacer 68 is smaller in diameter than the diameter of the rolling element 65 shaped and is with the concave surfaces 69 and 69 like a cross in opposite planes 70 and 70 for holding the adjacent retained rolling elements 65 and 65 formed so that the rotational center axes 65c and 65c perpendicular to the cut surfaces 65b and 65b cross each other as described above. That is, the cut surface 65b of the rolling element 65 is opposite to a stepped part 69a the concave surface 69 for holding the rolling element. The spacer shape shown in the embodiment is only one embodiment and may be changed in construction as desired without limitation.

Of the Condition in which a preload between the rolling element and the track area granted is, is not limited, it can indeed be given a preload in the manufacturing stage or not be granted; wherein granting a preload and granting no prejudice in the manufacturing stage in the spirit and scope of the Invention lie.

Of the Gap in the bearing may be small or negative (minus) as required be set. Correspondingly, a higher torque resistance of the camp.

Usually, bearing steel is used as the material of the races 61 and 62 and the rolling elements 65 but stainless steel, ceramics and the like are suitably selected to improve the corrosion resistance and the heat resistance in response to the use environment.

As a machined cage, a press cage, a resin cage or the like suitably as a material of the cage 66 . 66 ' is selected, for example, brass metal, iron, etc., or synthetic resin, such as polyamide 66 (Nylon), polyphenylene sulfide (PPS) or fluororesin are selected within the spirit and scope of the invention.

When next become specific embodiments of the invention with reference to the accompanying drawings.

83 shows a further embodiment, as well 91 . 92 and 93 , The specific embodiments described below are only embodiments, and the invention is not limited to the embodiments.

In the embodiment according to 83 there is an outer ring 61 from two raceway surfaces 61a and 61a ' , an inner ring 62 is from a career area 62a executed and rolling elements 65 each have a cut surface 65b leading to the side of the outer ring 61 directed and like a cross are alternately positioned on the perimeter ( 83 ).

In the embodiment, a Gothic arch that consists of two raceway surfaces 61a and 61a ' each having a larger diameter than the radius of the rolling element 65 , accepted. The reference number 73 in the figure denotes a seal plate (seal or shield).

The rolling elements 65 are placed so that rotation center axes 65c and 65c the rolling elements are perpendicular to the cut surfaces 65b and 65b intersect each other, and the movement of each rolling element 65 is through a recess 67 a cage 66 guided.

As the cage 66 will the in the 85 and 86 used cage shown. The cage 66 ' in the 88 and 89 can be used.

Therefore, according to the 23rd embodiment, in order to use any desired kinds of loads such as a radial load, thrust loads in both directions, and a load torque, the outer diameter comes 65a of the rolling element 65 in contact with a point on the raceway surface 61a of the outer ring 61 and a point on the track surface 62a of the inner ring 62 (the contact points are with 71 and 71 designated), wherein the outer and inner rings facing each other, and the adjacent rolling elements 65 comes in contact with a point on the raceway surface 61a ' of the outer ring 61 and a point on the track surface 62a of the inner ring 62 (the contact points are with 72 and 72 designated).

As the rolling elements 65 and 65 alternately intersect with a contact angle, a bearing can receive a radial load, axial loads in both directions and a load torque.

A rolling element 65 is only in point contact with a point on the raceway surface 61a ( 71 ) and a point on the raceway surface 62a ( 71 ), and another rolling element 65 is only in point contact with a point on the raceway surface 61a ' ( 72 ) and a point on the raceway surface 62a ( 72 ) so that a large spin movement in the four-point contact ball bearing in the related art can be avoided.

Furthermore, the manner in which the rolling element 65 . 65 and the outer ring 61 and the inner ring 62 contacting each other is the same as a general ball bearing, so that the rolling resistance is low, and low torque compared with the cross roller bearing can be provided.

In the embodiment according to 91 is an outer ring 61 with a track surface 61a executed, an inner ring 62 consists of two raceway surfaces 62a and 62a ' , and the rolling elements 65 have every cut surface 65b to the side of the inner ring 62 directed and are alternately positioned like a cross on the circumference ( 91 ).

Therefore, according to the embodiment, in order to use any desired kinds of loads such as a radial load, axial loads in both directions and a load torque, one of the adjacent rolling elements comes 65 in contact with the raceway surface 1a of the outer ring 61 and the raceway area 62a of the inner ring 62 , wherein the raceway surfaces face each other, and the other of the adjacent rolling elements 65 comes into point contact with the raceway surface 1a of the outer ring 61 and the raceway area 62a ' of the inner ring 62 ,

Other Component and advantages are the same as those in the 23rd embodiment.

In the 24th embodiment, the shape of the recess of the cage to that used in the 23rd embodiment is reversed at the front and the back of the recess (see FIG 91 ).

That is, the cage 66 of the type in which an opening width w1 on the outer diameter side 66a is designed so that it has a larger diameter than the opening width w2 on the side of the inner diameter 66b has and a slope 67c in the direction of the outside diameter 66a is directed is used.

In the embodiment, the way in which the outer ring 61 not divided into two parts, incorporated into the description; however, the way in which the outer ring 61 is divided into two parts, as an embodiment can be adopted, and the way in which the inner ring 62 not shared, can also be taken over.

In the embodiment according to 92 there is an outer ring 61 from two raceway surfaces 61a and 61a ' , an inner ring 62 consists of two raceway surfaces 62a and 62a ' and the rolling elements 65 each have a cut surface 65b facing the side of the outer ring 61 is directed and positioned like a cross alternately on the circumference.

Therefore, to accommodate an axial load and a load moment, comes one of the adjacent rolling elements 65 in contact with the raceway surface 61a of the outer ring 61 and the raceway area 62a of the inner ring 62 , wherein the raceway surfaces face each other, and the other of the adjacent rolling elements 65 comes into point contact with the raceway surface 61a ' of the outer ring 61 and the raceway area 62a ' of the inner ring 62 , In order to accommodate a radial load, the rolling element and the races come into contact with each other in a total of three points, depending on the load condition.

The configuration and advantages of the 25th embodiment are the same as those of the 23rd embodiment except that the inner ring 62 two raceway surfaces 62a and 62a ' Has.

In the 25th embodiment, the type where the inner ring 62 not divided into two parts, incorporated into the description; however, the way in which the inner ring 62 is divided into two parts, as an embodiment can be adopted, and the way in which the outer ring 61 not shared, can also be adopted.

In the embodiment according to 93 there is an outer ring 61 from two raceway surfaces 61a and 61a ' , an inner ring 62 consists of two raceway surfaces 62a and 62a ' and the rolling elements 65 each have a cut surface 65b leading to the side of the inner ring 62 is directed and are like a cross alternately positioned on the perimeter.

Therefore, to accommodate an axial load and a load moment, one of the adjacent rolling elements come 65 in point contact with the raceway surface 61a of the outer ring 61 and the raceway area 62a of the inner ring 62 , wherein the raceway surfaces face each other, and the other of the adjacent rolling elements 65 comes into point contact with the raceway surface 61a ' of the outer ring 61 and the raceway area 62a ' of the inner ring 62 , In order to accommodate a radial load, the rolling element and the races come into contact with each other in a total of three points, which depends on the load condition 5 depend.

The configuration and advantages of this embodiment are the same as those of the previous except that the outer ring 61 two raceway surfaces 61a and 61a ' Has.

In the embodiment, the way in which the outer ring 61 not divided into two parts, incorporated into the description; however, the way in which the outer ring 61 is divided into two parts, can be adopted as an embodiment, and the way in which the inner ring is not divided, can also be adopted.

at The invention is the use of a rolling element, which is like a ball is shaped with a cut off page the number of workpieces Parts smaller than the rolling element, the like a ball is formed with two cut sides when related State of the art; wherein the rolling element can be processed at low cost.

Between the outside and the inner rings are the rolling elements, each of which is shaped like a sphere, with a truncated one Side, are positioned so that they alternate on the circumference, and each rolling element is always in point contact with only two points on the outside and inner ring, so that while the advantage of the low cost described above is created the rolling bearing a radial load, axial loads in both directions and a load torque can take while it has excellent low torque properties, high torque resistance, high spin wear resistance, etc.

Claims (27)

Roller bearing, which has: a first race and a second race, from each having at least one raceway surface; a variety of rolling elements, rotatably disposed between the first race and the second race are, wherein each of the rolling elements has a Wälzkontaktumfangsfläche, by rotating a curved one Line is determined about an axis of rotation of the rolling element, and at least a sealing plate between the first and second races is arranged in a respective groove of both races, wherein the curved line a predetermined curvature which is smaller than a radius of the at least one raceway, wherein the rolling contact peripheral surface of each the rolling elements always exactly one point on each of the assigned at least one Track surface of the first race and the associated at least one raceway surface of the contacted second race and wherein each adjacent rolling elements arranged in a positioning device in such a manner are that their axes of rotation alternately in the circumferential direction of the rolling bearing intersect each other, each of the rolling elements one at least One side cut off shaped ball is formed so to speak at least one flat surface to build. roller bearing according to claim 1, characterized in that each of the rolling elements at least one flat surface includes. roller bearing according to claim 2, characterized in that each of the rolling elements includes two opposing and flat surfaces. roller bearing according to claim 2, characterized in that each of the rolling elements one at the opposite Side cut off shaped ball is. roller bearing according to claim 1, characterized in that the first race having a first and a second raceway surface. roller bearing according to claim 5, characterized in that the first race is divided, and further comprises a fastening device, the for securing the first and second raceway surfaces of each raceway member together serves. roller bearing according to claim 1, characterized in that the second race a first and a second raceway surface comprises. roller bearing according to claim 7, characterized in that the second race divided, and further comprising a fastening device which for securing the first and second raceway surfaces of each raceway member together serves. roller bearing according to claim 1, characterized in that the positioning device a cage is having circumferentially arranged holding portions, which the rolling elements on both sides in the direction of the alternating crossed axes of rotation hold. roller bearing according to claim 1, characterized in that the positioning device is a variety of spacers, each of which has a diameter which is smaller than a diameter of each of the rolling elements, as well as two shaped recess Having curved grooves on opposite surfaces crossed. roller bearing according to claim 1, characterized in that the positioning device a cage is that has a number of recesses into which an equal Number of rolling elements each is inserted alternately crossed, the recesses offset along the circumferential direction of the cage and in a predetermined Distance are arranged in the circumferential direction. roller bearing according to claim 1, characterized in that the at least one Raceway surface and / or the plurality of rolling elements a stainless steel included. roller bearing according to claim 1, characterized in that the at least one Raceway surface and / or the plurality of rolling elements contain a ceramic material. roller bearing according to claim 1, characterized in that the at least one Raceway surface and / or the plurality of rolling elements contain a plastic. roller bearing according to claim 1, characterized in that the at least one Raceway surface and / or the plurality of rolling elements have a corrosion-preventing coating on a surface. roller bearing according to claim 1, characterized in that this a flange having formed on the first race and / or second race is. roller bearing according to claim 1, characterized in that this is a lubricant-containing polymer element has, which is arranged in an interior of the bearing. roller bearing according to claim 1, characterized in that the races to each other are biased. roller bearing according to one of the preceding claims, characterized that the right and left raceway surfaces of inner and outer ring at its center of axial curvature are different. roller bearing according to one of the preceding claims, characterized that the radii of curvature the raceway surfaces greater than the rolling element and in particular to a value of 50.3 to 54% of the diameter set the rolling element are. roller bearing according to one of the preceding claims, characterized that the radius of curvature the raceway surface in particular of the inner ring larger at the outer ends as is at the middle. roller bearing according to one of the preceding claims, characterized a fastening area of the sealing plate is fastened to a groove is that in the outer ring is formed, and a sealing lip in the groove of the inner ring is arranged. roller bearing according to one of the preceding claims, characterized the seal plate is a non-contact type seal. Rolling bearing according to one of the preceding Claims, characterized in that the sealing plate is a contact type seal. roller bearing according to one of the preceding claims, characterized that a sealing surface the sealing plate to the outer ring or facing the inner ring. roller bearing according to one of the preceding claims, characterized in that the sealing plate has a sealing surface which contacts with an inner bottom of a corresponding groove and / or a sealing surface in contact with a face having the corresponding groove of the race. roller bearing according to claim 26, characterized in that the end face is tapered and in inclined contact with the sealing surface of the sealing plate is.