JP2021188660A - Plural-row ball bearing - Google Patents

Abstract

To provide a plural-row ball bearing capable of making the ball rows of rolling elements into three or more rows to improve a load capacity.SOLUTION: A plural-row ball bearing 100 comprises, in a ball bearing, an integrated outer ring 114 in which three or more rows of raceway grooves 120, 122, 124 are formed on an inner peripheral surface 118, a split type inner ring 116 that is split in an axial direction, raceway grooves 132, 134, 136 formed on outer peripheral surfaces 130, 136 of the inner ring 116, and the same number of ball rows 160, 162, 164 as the raceway grooves.SELECTED DRAWING: Figure 2

Description

The present invention relates to a double row ball bearing in which a ball as a rolling element rolls between an outer ring and an inner ring.

The planetary gear mechanism is a mechanism that functions as a speed increaser or a speed reducer, and includes, for example, a rotating sun gear, a ring gear, and a plurality of pinion gears. The plurality of pinion gears revolve while rotating while the gear teeth (tooth surfaces) mesh with each other between the outer peripheral surface of the sun gear and the inner peripheral surface of the ring gear.

Patent Document 1 describes as a pinion gear a ball bearing integrated with a pinion gear (hereinafter referred to as a pinion gear integrated bearing). In this pinion gear integrated bearing, a ball as a rolling element rolls between the outer ring and the inner ring in a frictional contact state, the inner ring also serves as a support shaft (pinion shaft), and the sun gear and the ring gear are on the outer peripheral surface of the outer ring. The tooth surface that meshes with the tooth surface is integrally formed.

In the conventional planetary gear mechanism for automobiles, roller bearings (needle bearings) are exclusively used for pinion gears, but Patent Document 1 proposes ball bearings. The ball as a rolling element has less friction than the roller. Therefore, when the pinion gear integrated bearing of Patent Document 1 is installed in, for example, a transmission of an automobile, fuel efficiency can be improved as compared with the case where a roller bearing is installed.

Japanese Unexamined Patent Publication No. 2018-44638

On the other hand, the ball of the rolling element has a smaller load capacity than the roller. Therefore, in the pinion gear integrated bearing, in order to improve the load capacity, it is conceivable to make a plurality of rows of balls rolling between the outer ring and the inner ring. Also in Patent Document 1, a double-row ball bearing is shown in FIG. However, the pinion gear integrated bearing of Patent Document 1 is merely a two-row double-row ball bearing, and there is room for improvement in improving the load capacity.

Further, the double-row ball bearing is not limited to a pinion gear integrated bearing in which a tooth surface is formed on the outer peripheral surface of the outer ring, and a double-row ball bearing separate from the pinion gear is also known. However, even in such a double-row ball bearing, it is difficult to make a double-row of three or more balls of balls rolling between the outer ring and the inner ring, as in the case of the pinion gear integrated bearing.

In view of such a problem, it is an object of the present invention to provide a double row ball bearing capable of improving the load capacity by making the ball rows of the rolling elements into a double row of three or more rows.

In order to solve the above problems, a typical configuration of the double-row ball bearing according to the present invention is an integrated outer ring in which three or more rows of raceway grooves are formed on the inner peripheral surface of the ball bearing, and an axial direction. It is characterized by including a divided split type inner ring, a raceway groove formed on the outer peripheral surface of the inner ring, and a ball array having the same number as the raceway grooves.

In the above configuration, in the ball bearing, by combining the integrated outer ring and the split type inner ring, the raceway grooves in which the ball rolls between the outer ring and the inner ring are formed into a double row of three or more rows. The "integrated type" means that the outer ring is one member and includes all the raceway grooves. The "divided type" means that it is divided in the axial direction, and is not intended to be divided in the circumferential direction. According to the above configuration, even in a ball bearing using a ball having a smaller load capacity than a roller as a rolling element, three or more rows of raceway grooves are formed between the integrated outer ring and the split inner ring. Since the same number of ball rows can be arranged, the load capacity can be improved.

Of the ball bearings generally called double rows, those with two rows are actually produced and sold, but those with three or more rows are not seen in patent applications, let alone production and sales. This is because it is difficult to insert a ball between the outer ring and the inner ring having three or more rows of raceway grooves. As an embodiment, when attempting to configure three or more rows of bearings, three or more single-row ball bearings are arranged, or a single-row ball bearing and two-row ball bearings are arranged side by side. On the other hand, in the present invention, the outer ring is integrated and only the inner ring is a split type, so that it is possible to insert a ball into the raceway grooves of three or more rows, and the problem is solved.

It is preferable that the split type inner ring has a plurality of Conrad type first inner rings having one row or two rows of raceway grooves, and the raceway grooves of the plurality of first inner rings have three or more rows in total. Here, the Conrad type is a method in which the inner ring is brought closer to one side of the outer ring, and a ball, which is a rolling element, is filled in the crescent-shaped gap formed between the other side of the outer ring and the inner ring. In the above configuration, a plurality of Conrad type first inner rings are combined as the split type inner rings so that the total number of raceway grooves is three or more. As an example, in order to make three rows of raceway grooves, three first inner rings having one row of raceway grooves may be combined, or one first inner ring having two rows of raceway grooves and one row of raceway grooves may be included. It may be combined with one first inner ring. As described above, according to the above configuration, it is possible to surely form three or more rows of raceway grooves between the outer ring and the plurality of Conrad type first inner rings.

The split type inner ring may have two counterbore type second inner rings. Here, the outer ring has two rows of raceway grooves and counterbore-shaped raceway grooves located on both ends of the two rows of raceway grooves and having shoulders dropped. Thereby, the outer ring can be separably combined with the two counterbore type second inner rings, and four rows of raceway grooves can be formed between the two second inner rings. Further, in the counterbore type, the number of balls in the ball row can be increased as compared with the Conrad type, so that the ball density for each ball row can be increased. Therefore, as in the above configuration, the load capacity can be improved by using two counterbore type second inner rings as the split type inner rings.

The split type inner ring may have a Conrad type first inner ring having one or more rows of raceway grooves and one or two counterbore type second inner rings. Thereby, as the split type inner ring, the Conrad type first inner ring and the counterbore type second inner ring can be combined. According to the above configuration, among the raceway grooves of the outer ring, the raceway grooves formed between the outer ring and the first inner ring of the Conrad type are formed in multiple rows (for example, infinite stages), and the raceway grooves having two rows at one end or four rows at both ends are further formed. It can be formed between the counterbore type second inner ring. By doing so, it is possible to increase the load capacity by increasing the ball density for each ball row by using the Conrad method to make the track grooves infinitely large and making the ball rows into multiple rows, and by using the counterbore method.

According to the present invention, it is possible to provide a double row ball bearing capable of improving the load capacity by making the ball rows of the rolling elements into a double row of three or more rows.

It is a perspective view which shows the schematic structure of the planetary gear mechanism to which a double row ball bearing in an embodiment of this invention is applied. It is a figure which shows the inside of the double row ball bearing of FIG. It is a figure which shows the procedure of assembling the double row ball bearing of FIG. 2 (a). It is a figure which shows the inside of the double row ball bearing in the modification of this invention. It is a figure which shows the double row ball bearing in another embodiment of this invention, and the procedure for assembling it. It is a figure which shows the double row ball bearing in another modification of this invention, and the procedure for assembling it.

Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiment are merely examples for facilitating the understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and the drawings, elements having substantially the same function and configuration are designated by the same reference numerals to omit duplicate description, and elements not directly related to the present invention are not shown. do.

FIG. 1 is a perspective view showing a schematic configuration of a planetary gear mechanism 102 to which the double row ball bearing 100 according to the embodiment of the present invention is applied. The planetary gear mechanism 102 is a mechanism that functions as a speed increaser or a speed reducer, and is arranged on a rotating sun gear 104, a ring gear 106, a plurality of (here, three) pinion gears 107, and a plurality of pinion gears 107. A row ball bearing 100 is provided.

Gear teeth (tooth surface 108) are formed on the outer peripheral surface of the sun gear 104. The ring gear 106 is fixed to a casing (not shown) and is arranged concentrically with the sun gear 104 in the casing. Further, a tooth surface 110 is formed on the inner peripheral surface of the ring gear 106. The planetary gear mechanism may also have a configuration in which the ring gear 106 is not fixed.

A tooth surface 112 is formed on the outer peripheral surface of the pinion gear 107. In the pinion gear 107 in which the double-row ball bearing 100 is arranged, the outer peripheral surface of the sun gear 104 is in a state where the tooth surface 112 of the outer peripheral surface is meshed with the tooth surface 108 of the sun gear 104 and the tooth surface 110 of the ring gear 106 as shown in the figure. It revolves while rotating between the ring gear 106 and the inner peripheral surface of the ring gear 106.

FIG. 2 is a diagram showing the inside of the double row ball bearing 100 of FIG. FIG. 2A is a sectional view taken along the line AA of the double row ball bearing 100 of FIG. The double row ball bearing 100 has an integrated outer ring 114 and a split inner ring 116.

2 (b) and 2 (c) show an integrated outer ring 114 and a split inner ring 116, respectively. The outer ring 114 is one member and is an integral type having all the raceway grooves. As shown in FIG. 2B, a plurality of (here, three rows) of raceway grooves 120, 122, and 124 are formed on the inner peripheral surface 118 of the outer ring 114.

The inner ring 116 is a split type divided in the axial direction, and has two first inner rings 126 and 128 of the Conrad type (described later) as shown in FIG. 2 (c). Two rows of raceway grooves 132 and 134 are formed on the outer peripheral surface 130 of the first inner ring 126. A row of raceway grooves 138 is formed on the outer peripheral surface 136 of the first inner ring 128. As described above, the split type inner ring 116 has three rows of raceway grooves 132, 134, 138 as a whole by combining the two first inner rings 126, 128.

Further, in the split type inner ring 116, the pinion shaft 144 is inserted into the inner peripheral surfaces 140 and 142 of the split type inner ring 116 in a state where the two first inner rings 126 and 128 are combined as shown in FIG. 2 (a). The pinion shaft 144 is connected to the carrier 146. In FIG. 1, the pinion shaft 144 and the carrier 146 are omitted.

The double row ball bearing 100 further comprises balls 148, 150, 152 as rolling elements and cages 154, 156, 158. The balls 148, 150, 152 roll between the integrated outer ring 114 and the split inner ring 116, and form the same number of ball rows 160, 162, 164 as the raceway grooves 120, 122, 124 of the outer ring 114, that is, three rows of balls 160, 162, 164. Form.

The cages 154, 156, and 158 are provided between the integrated outer ring 114 and the split inner ring 116 to hold the balls 148, 150, and 152. As a result, the cages 154, 156, and 158 have a role of keeping the balls 148, 150, and 152 apart and preventing the balls 148, 150, and 152 from rubbing against each other.

Here, of the split type inner rings 116, the first inner ring 126 presses the pinion shaft 144 into the inner peripheral surface 140 thereof to fix the pinion shaft 144 (tightening). On the other hand, the first inner ring 128 enables proper alignment with respect to the first inner ring 126 by inserting the pinion shaft 144 in a slightly looser state than the first inner ring 126 (gap fit).

Further, in the first inner ring 128, the radial gap Δra between the raceway groove 124 of the outer ring 114 and the ball 152 is smaller than the radial gap Δrb between the raceway grooves 120 and 122 of the outer ring 114 and the balls 148 and 150 in the first inner ring 126. It is set. As a result, the axial position of the first inner ring 126 is fixed to the pinion shaft 144, and the position of the first inner ring 128 follows the first inner ring 126 via the outer ring 114 (centering force acts). Therefore, even if the inner ring 116 is a split type, the distance between the inner rings in the axial direction does not shift, and it is possible to prevent an unnecessary load from being generated between the ball and the raceway groove.

In this way, in the double row ball bearing 100, by combining the integrated outer ring 114 and the split type inner ring 116, three rows of ball rows 160, 162, 164 can be arranged between the outer ring 114 and the inner ring 116. The load capacity can be improved as compared with the two-row double-row ball bearings.

Therefore, the double row ball bearing 100 having an improved load capacity can be installed in, for example, an automobile mission. Furthermore, the ball as a rolling element has less friction than the roller. Therefore, by installing the double row ball bearing 100 in the mission of the automobile, it is possible to improve the fuel efficiency as compared with the case where the roller bearing is installed.

FIG. 3 is a diagram showing a procedure for assembling the double row ball bearing 100 of FIG. 2 (a). In the figure, the integrated outer ring 114 and the split type inner ring 116 having two Conrad type first inner rings 126 and 128 are combined, and three rows of ball rows 160, 162, 164 are formed in the three rows of raceway grooves. The procedure for arranging each is shown. The Conrad type is a method in which the inner ring is brought closer to one side of the outer ring, and a ball, which is a rolling element, is filled in the crescent-shaped gap formed between the other side of the outer ring and the inner ring.

Specifically, first, as shown in FIG. 3A, the inner peripheral surface 118 of the integrated outer ring 114 has two rows of raceway grooves 132 and 134 (see FIG. 2C) among the split type inner rings 116. ) Is arranged. Next, the first inner ring 126 is moved to one side (upper side in the figure) of the inner peripheral surface 118 of the outer ring 114, and between the other side (lower side in the figure) of the outer ring 114 and the first inner ring 126. The resulting crescent-shaped gap 166 is filled with two rows of balls. The two rows of balls include a plurality of (here, eight) balls 148 which are ball rows 160 as shown in FIG. 2A, and a plurality of (here, eight) balls 150 which are ball rows 162. There are 16 balls in total. In FIG. 3A, eight balls 148 are shown on the back side and eight balls 150 are shown on the front side.

Subsequently, as shown in FIG. 3B, the first inner ring 126 is brought to the center with respect to the inner peripheral surface 118 of the outer ring 114 while dispersing the balls 148 and 150 for two rows. As a result, the eight balls 148 are arranged in the raceway groove 132 of the first inner ring 126 shown in FIG. 3C to form a ball row 160, and the remaining eight balls 150 are arranged in the raceway groove 134 to form a ball row. It becomes 162.

Further, as shown in FIG. 3 (c), the cage 154 is fitted from one side (right side in the figure) into the ball row 160 including the ball 148, and the other side (the other side (from the ball row 162 including the ball 150). Insert the cage 156 from the left side in the figure). In this way, the Conrad type first inner ring 126 can be assembled to the integrated outer ring 114, and the two rows of ball rows 160 and 162 can be arranged in the two rows of raceway grooves. Hereinafter, a procedure for arranging the third row of ball rows 164 (see FIG. 2A) from this state will be shown below.

As shown in FIG. 3 (d) following from FIG. 3 (c), one row of raceway grooves 138 (FIG. 2 (c)) of the split type inner ring 116 is formed on the inner peripheral surface 118 of the integrated outer ring 114. The first inner ring 128 having (see) is arranged. Next, the first inner ring 128 is moved to one side of the inner peripheral surface 118 of the outer ring 114, and one row is provided in the crescent-shaped gap 168 generated between the other side of the outer ring 114 and the first inner ring 128. Fill the balls. The balls for one row are a plurality of (here, eight) balls 152 that form the ball row 164 shown in FIG. 2A.

Next, as shown in FIG. 3 (e), the first inner ring 128 is brought to the center with respect to the inner peripheral surface 118 of the outer ring 114 while dispersing the balls 152 for one row. As a result, the eight balls 152 are arranged in the raceway groove 138 of the first inner ring 128 shown in FIG. 3 (f) to form a ball row 164. Further, as shown in FIG. 3 (f), the cage 158 is fitted into the ball row 164 including the ball 152 from one side (left side in the figure).

In this way, two Conrad type first inner rings 126 and 128 can be assembled to the integrated outer ring 114, and three rows of ball rows 160, 162 and 164 can be arranged in the three rows of raceway grooves. .. Further, the double row ball bearing 100 can be assembled by inserting the pinion shaft 144 connected to the carrier 146 shown in FIG. 2A into the inner peripheral surfaces 140 and 142 of the assembled first inner rings 126 and 128. ..

FIG. 4 is a diagram showing the inside of the double row ball bearings 100A and 100B in the modified example of the present invention. The pinion shaft 144 and the carrier 146 are not shown.

The modified double-row ball bearing 100A shown in FIG. 4A is different from the above-mentioned three-row double-row ball bearing 100 in that the double-row ball bearing 100A has four rows. As shown in the figure, four rows of raceway grooves are formed on the inner peripheral surface of the integrated outer ring 114A. The split type inner ring 116A has, in addition to the above two first inner rings 126 and 128, another Conrad type first inner ring 128A. A row of raceway grooves 170 is formed on the outer peripheral surface of the first inner ring 128A.

In the double row ball bearing 100A, two Conrad type first inner rings 126 and 128 are assembled to the integrated outer ring 114A, and three rows of ball rows 160, 162 and 164 are arranged in the three rows of raceway grooves. Then, the first inner ring 128A is further assembled to the outer ring 114A.

Therefore, in the double row ball bearing 100A, the four rows of ball rows 160, 162, 164, and 172 can be arranged in the four rows of raceway grooves by combining the integrated outer ring 114A and the split type inner ring 116A. The ball row 172 includes eight balls 174 arranged in the raceway groove 170 of the first inner ring 128A, and the cage 176 is fitted from the left side in the drawing.

The modified double-row ball bearing 100B shown in FIG. 4B is different from the double-row ball bearing 100 in that it has five rows of double rows. As shown in the figure, five rows of raceway grooves are formed on the inner peripheral surface of the integrated outer ring 114B. The split type inner ring 116B has one Conrad type first inner ring 128B in addition to the two Conrad type first inner rings 126, 128, 128A (see FIG. 4A). A row of raceway grooves 178 is formed on the outer peripheral surface of the first inner ring 128B.

In the double row ball bearing 100B, three Conrad type first inner rings 126, 128, 128A are assembled to the integrated outer ring 114B, and four rows of ball rows 160, 162, 164, 172 are assembled in the four rows of raceway grooves. After arranging, the first inner ring 128B is further assembled to the outer ring 114B.

Therefore, in the double row ball bearing 100B, by combining the integrated outer ring 114B and the split type inner ring 116B, five rows of ball rows 160, 162, 164, 172, and 180 can be arranged in the five rows of raceway grooves. can. The ball row 180 includes eight balls 182 arranged in the raceway groove 178 of the first inner ring 128B, and the cage 184 is fitted from the left side in the drawing.

As described above, according to the double row ball bearings 100, 100A and 100B, the integrated outer ring and the conrad type can be obtained by combining the integrated outer ring and the split type inner ring having a plurality of Conrad type first inner rings. Three or more rows of raceway grooves can be reliably formed between the plurality of first inner rings, and the same number of raceway grooves, that is, three or more rows of ball rows can be arranged. Therefore, with the double row ball bearings 100, 100A, and 100B, the load capacity can be improved.

When a Conrad type split type inner ring is used, theoretically, an infinite number of double row ball bearings can be used. However, although ball bearings have less friction than roller bearings, the friction increases as the number of stages increases, so if the number of stages is too large, the advantage of ball bearings is lost. Therefore, there is an optimum range for the number of stages in terms of the balance between load capacity and frictional resistance, but the frictional resistance varies depending on the material of the bearing and ball, the number of contact points, the viscosity and material of the lubricant, etc. It is not possible to unconditionally discuss the optimum number of stages.

FIG. 5 is a diagram showing a double row ball bearing 200 and a procedure for assembling the double row ball bearing 200 in another embodiment of the present invention. As shown in FIG. 5A, the double row ball bearing 200 has an integrated outer ring 204 and a split inner ring 206 (see FIG. 5B).

On the inner peripheral surface 208 of the outer ring 204, there are two rows of raceway grooves 210 and 212, and counterbore-shaped raceway grooves 214 and 216 located on both ends of the two rows of raceway grooves 210 and 212 and having their shoulders dropped. Have. Further, two rows of ball rows 218 and 220 are arranged on the outer ring 204. The two rows of ball rows 218 and 220 include a plurality of balls 222 and 224 arranged in the raceway grooves 210 and 212 of the outer ring 204, respectively, and the cages 226 and 228 are fitted and combined to form an outer ring unit. There is.

The split type inner ring 206 has two counterbore type second inner rings 230 and 232. A row of raceway grooves 236 and a counterbore-shaped raceway groove 238 located on one end side of the raceway groove 236 are formed on the outer peripheral surface 234 of the second inner ring 230. Further, one row of ball rows 240 is arranged on the second inner ring 230. The ball row 240 in one row includes a plurality of balls arranged in the raceway groove 236 of the second inner ring 230, and the cage 242 is fitted to form the inner ring unit.

A row of raceway grooves 246 and a counterbore-shaped raceway groove 248 located on one end side of the raceway groove 246 are formed on the outer peripheral surface 244 of the second inner ring 232. Further, one row of ball rows 250 is arranged on the second inner ring 232. The ball row 250 in one row includes a plurality of balls arranged in the raceway groove 246 of the second inner ring 232, and the cage 252 is fitted to form the inner ring unit.

Next, a procedure for combining the integrated outer ring 204 and the split inner ring 206 will be described. First, the second inner rings 230 and 232 of the split type inner ring 206 are brought closer to the outer ring 204 from both sides of the outer ring 204 shown in FIG. 5 (a). Next, the second inner ring 230 and 232 are arranged so that the outer peripheral surfaces 234 and 244 of the second inner ring 230 and 232 face the inner peripheral surface 208 of the outer ring 204, respectively.

Here, as shown in FIG. 5B, in the second inner ring 230, the raceway groove 238 having a counterbore shape and the raceway groove 210 of the outer ring 204 face each other so that the ball train 218 is located in the raceway groove 210 and 238. Is placed in. Further, in the second inner ring 230, the raceway groove 236 and the counterbore-shaped raceway groove 214 of the outer ring 204 are opposed to each other, and the ball train 240 is arranged in the raceway groove 214, 236.

Further, in the second inner ring 232, as shown in FIG. 5B, the counterbore-shaped raceway groove 248 and the raceway groove 212 of the outer ring 204 face each other so that the ball train 220 is located in the raceway groove 212 and 248. Is placed in. Further, in the second inner ring 232, the raceway groove 246 and the counterbore-shaped raceway groove 216 of the outer ring 204 face each other, and the ball train 250 is arranged so as to be located in the raceway groove 216, 246.

In this way, in the double row ball bearing 200, the integrated outer ring 204 and the separate inner ring 206 having two counterbore type second inner rings 230 and 232 can be separably combined. In the double row ball bearing 200, four rows of raceway grooves are formed between the outer ring 204 and the two second inner rings 230 and 232, and the same number of four rows of ball rows 218, 220, 240 and 250 as the raceway grooves are formed. Can be placed.

In the counterbore type, the number of balls in the ball row can be increased as compared with the Conrad type. Therefore, in the double row ball bearing 200, by using two counterbore type second inner rings 230 and 232 as the split type inner ring 206, the ball densities of each of the four rows of ball rows 218, 220, 240 and 250 are used. Can be increased and the load capacity can be improved.

Further, as shown in FIG. 5B, in the double row ball bearing 200, the width dimension La of the integrated outer ring 204 is set smaller than the width dimension Lb of the separate inner ring 206. As a result, it is possible to prevent the outer ring 204 from rubbing against the carrier 256 while preloading the second inner ring 230 and 232 by the carrier 256 connected to the pinion shaft 254.

FIG. 6 is a diagram showing a double row ball bearing 200A and a procedure for assembling the double row ball bearing 200A in another modification of the present invention. The double row ball bearing 200A is different from the double row ball bearing 200 in that both the Conrad type and the counterbore type are used.

On the inner peripheral surface 208A of the integrated outer ring 204A, in addition to the above-mentioned two rows of raceway grooves 210 and 212 and counterbore-shaped raceway grooves 214 and 216, two rows of deep groove raceway grooves 260 and 262 are further provided in the center. It is formed.

The split type inner ring 206A has one conrad type first inner ring 264 in addition to the above-mentioned counterbore type two second inner rings 230 and 232. That is, in the double row ball bearing 200A, as the split type inner ring 206A, one Conrad type first inner ring 264 and two counterbore type second inner rings 230 and 232 are combined.

Two rows of raceway grooves 266 and 268 are formed on the outer peripheral surface of the first inner ring 264. In the first inner ring 264, the two rows of raceway grooves 266 and 268 and the two rows of raceway grooves 260 and 262 of the outer ring A face each other, and the ball train 270 is located in the raceway grooves 260 and 266, and the raceway grooves 262 and 268 are located. The ball row 272 is arranged so as to be located there. The cages 274 and 276 are fitted in the two rows of balls 270 and 272, respectively.

Further, in the double row ball bearing 200A, the second inner ring 230 and 232 of the split type inner ring 206A are brought closer to the outer ring 204A from both sides of the outer ring 204A shown in FIG. The second inner ring 230 and 232 are arranged so that the 234 and 244 face the inner peripheral surface 208A of the outer ring 204A, respectively.

As shown in FIG. 6B, in the second inner ring 230, the counterbore-shaped raceway groove 238 and the raceway groove 210 of the outer ring 204A are opposed to each other, and the ball train 218 is arranged in the raceway grooves 210 and 238. Will be done. Further, in the second inner ring 230, the raceway groove 236 and the counterbore-shaped raceway groove 214 of the outer ring 204A are opposed to each other, and the ball train 240 is arranged in the raceway grooves 214 and 236.

Further, in the second inner ring 232, as shown in FIG. 6B, the counterbore-shaped raceway groove 248 and the raceway groove 212 of the outer ring 204A face each other so that the ball train 220 is located in the raceway groove 212 and 248. Is placed in. Further, in the second inner ring 232, the raceway groove 246 and the counterbore-shaped raceway groove 216 of the outer ring 204A are opposed to each other, and the ball train 250 is arranged so as to be located in the raceway grooves 216 and 246.

In this way, in the double row ball bearing 200A, the integrated outer ring 204A and the split type inner ring 206A in which one Conrad type first inner ring 264 and two counterbore type second inner rings 230 and 232 are combined. Can be combined in a separable manner. As a result, in the double row ball bearing 200A, the raceway grooves formed between the outer ring 204A and the Conrad type first inner ring 264 are formed in two rows, and the outer ring 204A and the counterbore type two second inner rings 230 and 232 are formed. The track grooves can be arranged in 4 rows at both ends, for a total of 6 rows.

As described above, although the counterbore type alone has a maximum of four rows, the number of stages can be further increased by using the Conrad type together, and the load capacity can be arbitrarily improved. In the double row ball bearing 200A shown in FIG. 6, one Conrad type first inner ring is used, but a plurality of first inner rings may be used. In this way, in the double-row ball bearing 200A, the ball rows are made into double rows by making the raceway grooves infinite by the first inner ring of the Conrad type, and the ball density of each of the four rows at both ends is further increased by the counterbore type. The load capacity can be improved by increasing the height. In the double row ball bearing 200A, two counterbore type second inner rings are used, but only one second inner ring may be used. In this case, the counterbore method can increase the ball density for each of the two rows of balls at one end to improve the load capacity.

Although the preferred embodiments of the present invention have been described above with reference to the accompanying drawings, it goes without saying that the present invention is not limited to such examples. It is clear that a person skilled in the art can come up with various modifications or modifications within the scope of the claims, which naturally belong to the technical scope of the present invention. Understood.

INDUSTRIAL APPLICABILITY The present invention can be used as a double-row ball bearing in which a ball as a rolling element rolls between an outer ring and an inner ring.

100, 100A, 100B, 200, 200A ... Double row ball bearings, 102 ... Planetary gear mechanism, 104 ... Sun gear, 106 ... Ring gear, 107 ... Pinion gear, 108, 110, 112 ... Tooth surface, 114, 114A, 114B, 204, 204A ... Integrated outer ring, 116, 116A, 116B, 206, 206A ... Divided inner ring, 118, 208, 208A ... Inner peripheral surface of outer ring, 120, 122, 124, 210, 212, 214, 216, 260, 262 ... Outer ring raceway grooves, 126, 128, 128A, 128B, 264 ... First inner ring, 130, 136 ... Outer peripheral surface of the first inner ring, 132, 134, 138, 170, 178, 266, 268 ... First inner ring Track groove, 140, 142 ... Inner peripheral surface of the first inner ring, 144, 254 ... Pinion shaft, 146, 256 ... Carrier, 148, 150, 152, 174, 182, 222, 224 ... Ball, 154, 156, 158, 176, 184, 226, 228, 242, 252, 274, 276 ... Cages, 160, 162, 164, 172, 180, 218, 220, 240, 250, 270, 272 ... Balls, 166, 168 ... Gap, 230, 232 ... 2nd inner ring, 234, 244 ... outer peripheral surface of the 2nd inner ring, 236, 238, 246, 248 ... raceway groove of the 2nd inner ring

Claims (4)

In ball bearings
An integrated outer ring with three or more rows of raceway grooves formed on the inner peripheral surface,
A split type inner ring that is split in the axial direction,
The raceway groove formed on the outer peripheral surface of the inner ring and
With the same number of ball rows as the track groove,
A double row ball bearing characterized by being equipped with. The split type inner ring is
The duplex according to claim 1, wherein the plurality of Conrad type first inner rings having one row or two rows of raceway grooves is provided, and the raceway grooves of the plurality of first inner rings are three or more rows in total. Column ball bearing. The split type inner ring is
The double row ball bearing according to claim 1, further comprising two counterbore type second inner rings. The split type inner ring is
Conrad type first inner ring with one or more rows of raceway grooves,
One or two counterbore type second inner rings,
The double row ball bearing according to claim 1, wherein the bearing is provided with.

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