JP5268580B2 - Conical roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing preventing heat generation and abrasion by sliding and improving transmission efficiency. <P>SOLUTION: The tapered roller bearing includes an inner ring 10 defining a central axis L and having a first outer peripheral surface 11 of a conical shape, an outer ring 20 arranged coaxially with the inner ring and having a first inner peripheral surface 21 of a conical shape, a plurality of tapered rollers 30 having first conical parts 31 arrayed to have rotation axes S in a virtual conical surface having an apex O on the central axis, externally contacting the first outer peripheral surface and internally contacting the first inner peripheral surface, and a cage 40 holding the plurality of tapered rollers while arraying them in a circumferential direction. The tapered roller 30 has a second conical part 32 tapered oppositely to the first conical part 31 and the outer ring 20 has a second inter peripheral surface 22 for internal contact with the second conical parts. With this, heat generation, abrasion or the like caused during sliding can be prevented while simplifying the construction, smooth bearing operation is obtained, the life can be extended, and the transmission efficiency of turning force can be improved. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a conical roller bearing in which a plurality of conical rollers are rotatably provided between an inner ring and an outer ring, and more particularly to a conical roller bearing having a structure for receiving a pulling force of a conical roller.

As shown in FIG. 12, the conventional conical roller bearing has an outer ring 1 having a conical raceway surface 1a, a conical raceway surface 2a, a large diameter surface 2b on the large diameter side of the raceway surface 2a, and a small diameter side. A plurality of conical rollers 3 arranged in a freely rollable manner between an inner ring 2 having a small collar surface 2c (or only a large collar surface on the large diameter side) and a raceway surface 1a of the outer ring 1 and a raceway surface 2a of the inner ring 2. And a cage 4 that holds the conical roller 3 in a circumferential direction so as to roll freely at a predetermined interval (for example, refer to Patent Document 1, Patent Document 2, Patent Document 3, etc.). .
In this conical roller bearing, when the inner ring 2 rotates around the central axis L, the plurality of conical rollers 3 rotate around their respective rotational axes S or roll (revolve) along the raceway surfaces 1a and 2a. The inner ring 2 is rotatably supported by the outer ring 1.

In this conical roller bearing, as shown in FIG. 12, when a thrust load F is applied in the direction of the central axis L, the normal load N exerted by the raceway surface 1a and the raceway surface 2a exert on the conical roller 3. As a resultant force of the normal load N, an extruding load (a withdrawal force) f that tries to push the conical roller 3 in the direction of the rotation axis S is generated. It is received by contacting the large collar surface 2b.
Here, since the end surface 3a of the conical roller 3 is slidably in contact with the large collar surface 2b, heat generation or wear due to sliding friction occurs when the pushing load f increases, and sliding friction occurs. There is a problem that the transmission efficiency is low due to a large loss due to.
Further, since the end surface 3a of the conical roller 3 slides with respect to the large collar surface 2b, the rotational axis S of the conical roller 3 is twisted with respect to the central axis L due to the sliding resistance as shown in FIG. Thus, there is a problem in that the outer edge portions near both ends of the conical roller 3 come into contact with the inner edge portion of the rectangular opening 4a of the cage 4 to cause wear of the conical roller 3 and shorten the life of the conical roller bearing.

JP 2000-170774 A JP 2003-343552 A JP 2007-40520 A

  The present invention has been made in view of the circumstances of the above-mentioned conventional conical roller bearings. The object of the present invention is to prevent heat generation or wear due to sliding while simplifying the structure. It is an object of the present invention to provide a conical roller bearing that can reduce transmission loss due to movement, extend the life, and improve transmission efficiency.

The conical roller bearing of the present invention includes an inner ring that defines a predetermined center axis and has a conical first outer peripheral surface, an outer ring that is disposed coaxially with the inner ring and has a conical first inner peripheral surface, A plurality of conical rollers arranged in a virtual conical surface having an apex on the axis and having a first conical portion circumscribing the first outer peripheral surface and inscribed in the first inner peripheral surface; A conical roller bearing comprising a cage for holding conical rollers arranged in the circumferential direction, wherein the conical roller is a second conical portion formed in a conical shape that tapers in a direction opposite to the first conical portion. It has a outer ring or inner ring, the second inner peripheral surface or the second conical portion is inscribed a second conical portion have a second outer peripheral surface for bounding, with the generatrix of the central axis line and the first outer peripheral surface the angle theta _1, with respect to the central axis and angle theta ₂ between the generatrix of the first inner peripheral _surface, the generatrix of the first inner circumferential surface or the first outer peripheral surface The inclination angle of the generatrix of 2 conical portion when the _{β, β> (θ 2 -θ} 1), satisfies the second conical portion, an intermediate contact width between the second outer peripheral surface or the second inner peripheral surface In the region, the first conical portion is formed at a position where the extended line of the bus line intersects .
According to this configuration, the inner ring is rotatably supported by the outer ring via the plurality of conical rollers, or the outer ring is rotatably supported by the inner ring via the plurality of conical rollers, and the inner ring is supported in the direction of the central axis ( When a thrust load pressing in the thrust direction occurs, the conical roller has an extrusion load that pushes the conical roller in the direction of the rotation axis as a resultant force of the normal load received from the first outer peripheral surface and the first inner peripheral surface. (Release force) acts. The pushing load is received when the second conical portion of the conical roller rolls (or rolls and spins) the second inner peripheral surface of the outer ring or the second outer peripheral surface of the inner ring.
Thus, the pushing load for pushing out the conical roller is not received when the end surface of the conical roller abuts against the receiving portion and slides, but the second conical portion provided integrally with the conical roller is not provided. Since it can be received by rolling on the second inner peripheral surface or the second outer peripheral surface, heat generation or wear caused by sliding can be prevented while achieving a simplified structure, and a smooth bearing operation can be obtained. Thus, the service life can be extended and the transmission efficiency of the rotational force can be improved.
Here, the angle between the central axis and the first outer peripheral surface is θ ₁ , the angle between the central axis and the first inner peripheral surface is θ ₂ , and the first inner surface or the first outer peripheral surface When the inclination angle of the generatrix of the two conical parts is β, β> (θ ₂ −θ ₁ ) is satisfied, so that the pushing load (disengagement force) acting in the pushing direction is the second cone. It can be efficiently received by the rolling of the part (or rolling and spinning), and the conical roller can be reliably prevented from falling off between the inner and outer rings.
Further, since the second conical portion is formed at a position where the extension of the generatrix of the first conical portion intersects in the intermediate region of the contact width with the second outer peripheral surface or the second inner peripheral surface, When the portion comes into contact with the second inner peripheral surface or the second outer peripheral surface, it is possible to cancel the spin component that tends to twist the rotation axis of the conical roller with respect to the central axis. Contact can be reliably prevented.

In the above configuration, the surface pressure received by the second conical portion by contact with the second inner peripheral surface is formed to be substantially the same as the surface pressure received by the first conical portion by contact with the first inner peripheral surface. The configuration can be adopted.
According to this configuration, local wear and the like of the conical roller can be prevented, and the life of the conical roller and further the life of the conical roller bearing can be extended.

  According to the conical roller bearing configured as described above, the structure can be simplified, heat generation or wear due to conventional sliding can be prevented, transmission loss due to sliding can be reduced, life can be extended, and transmission efficiency can be increased. A conical roller bearing capable of improving the above is obtained.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings.
FIG. 1 and FIG. 2 show an embodiment of a conical roller bearing according to the present invention, FIG. 1 is a configuration diagram showing the configuration of the conical roller bearing, and FIG. 2 shows a force relationship acting on the conical roller bearing. It is a schematic diagram.
As shown in FIGS. 1 and 2, the conical roller bearing is arranged on an inner ring 10 that is rotatable around a predetermined center axis L and on the same axis L as the inner ring 10 (or is arranged so as to be rotatable). The outer ring 20, the plurality of conical rollers 30 that are interposed between the inner ring 20 and the outer ring 30 and have the first conical portion 31 and the second conical portion 32 integrally, and the plurality of conical rollers 30 are arranged and held in the circumferential direction. A cage 40 and the like are provided.

As shown in FIGS. 1 and 2, the inner ring 10 includes a conical first outer peripheral surface 11 and a cylindrical through hole 12 centering on the central axis L.
The first outer peripheral surface 11, as shown in FIG. 1, a region where the first conical portion 31 of the conical roller 30 rolls circumscribe the central axis and the generatrix M1 and the central axis line L is at an angle theta ₁ It is formed as a part of a conical surface having a vertex O on L.
The through-hole 12 is formed so that a predetermined rotation shaft or the like is fitted and rotates integrally.

As shown in FIGS. 1 and 2, the outer ring 20 includes a conical first inner peripheral surface 21 and a conical second inner peripheral surface 22.
The first inner peripheral surface 21, as shown in FIG. 1, a region where the first conical portion 31 of the conical roller 30 rolls inscribed, with its generatrix M2 and the central axis line L forms an angle theta ₂ center It is formed as a part of a conical surface having a vertex O on the axis L.
As shown in FIG. 1, the second inner peripheral surface 22 is a region where the second conical portion 32 of the conical roller 30 is inscribed and rolls (or rolls and spins), and the first inner peripheral surface 21 and The first conical portion 31 is formed so as to form an inclination angle β with respect to the bus M2 of the first conical portion 31.

As shown in FIGS. 1 and 2, the conical roller 30 is formed integrally and continuously with the first conical portion 31 and the first conical portion 31 having a central angle α between the two buses M <b> 1 and M <b> 2. In a virtual conical surface having a second conical portion 32 tapering in the opposite direction and having a vertex O on the central axis L, the second conical portion 32 is arranged to have a rotation axis S that forms an angle θ ₀ with the central axis L.
The first conical portion 31 is formed so as to circumscribe the first outer peripheral surface 11 and in contact with the first inner peripheral surface 21.
As shown in FIGS. 1 and 2, the second conical portion 32 has a conical shape that tapers in the opposite direction to the first conical portion 31 (having a vertex on the rotation axis S opposite to the vertex O). And is inscribed in the second inner peripheral surface 22.
Here, the bus M3 of the second conical portion 32 and the second inner peripheral surface 22 is formed so as to form an inclination angle β with respect to the bus M2 of the first inner peripheral surface 21 (and the first conical portion 31). Yes.

  As shown in FIGS. 1 and 2, the retainer 40 rotatably arranges a plurality of conical rollers 30 by arranging them at equal intervals in the circumferential direction within a virtual conical surface having a vertex O on the central axis L. A rectangular opening 40a is provided, and the conical rollers 30 are arranged and held in each rectangular opening 40a.

Next, the operation of this conical roller bearing will be described with reference to FIG.
First, as shown in FIG. 2, when a thrust load F is applied to the inner ring 10 in the direction of the central axis L, the normal load N exerted by the first outer peripheral surface 11 and the first inner load are applied to the conical roller 30. As a resultant force of the normal load N exerted by the peripheral surface 21, an extrusion load (extraction force) f that tries to push the conical roller 30 in the direction of the rotation axis S is generated.

This pushing load f is received by the second conical portion 32 of the conical roller 30 coming into contact with the second inner peripheral surface 22 of the outer ring 20, and in this contact region, as shown in FIG. A normal load H that pushes the second inner peripheral surface 22 is generated by the pulling force f).
Most of the normal load H is converted into rolling power while the second conical portion 32 is inscribed in the second inner peripheral surface 22 and slightly spins.
As described above, the pushing load f for pushing out the conical roller 30 is not received by sliding the end surface of the conical roller 30 in contact with the receiving portion as in the prior art, but the second load provided integrally with the conical roller 30. Since the conical portion 32 is rolled and received while partially spinning on the second inner peripheral surface 22, heat generation or wear or the like generated in the case of conventional sliding is achieved while achieving a simplified structure. It can be prevented, a smooth bearing action can be obtained, the life can be extended, and the transmission efficiency of the rotational force can be improved.
FIG. 3 shows the transmission efficiency of the input torque. While the transmission efficiency of the conventional conical roller bearing is about 93%, the transmission efficiency of the conical roller bearing of the present invention is improved to about 97%. It is understood that.
In the transmission efficiency evaluation test shown in FIG. 3, the conical roller bearing is applied to the conical roller bearing under the condition that the input torque Tin (Nm) and the thrust load F (N) are related as shown in FIG. 4. An evaluation test was performed by applying the thrust load F (N) shown in FIG.

5 and 6 show another embodiment of the conical roller bearing according to the present invention. FIG. 5 is a structural view showing the structure of the conical roller bearing, and FIG. 6 is a partially enlarged view of the conical roller bearing. . In this embodiment, the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
As shown in FIG. 5, the conical roller bearing includes an inner ring 10, an outer ring 20 ′, a plurality of conical rollers 30, and a cage 40.
As shown in FIG. 6, the first conical portion 31 is formed so as to contact the first outer peripheral surface 11 of the inner ring 10 with a contact width W <b> 1.
As shown in FIG. 6, the first inner peripheral surface 21 ′ of the outer ring 20 is formed so as to contact the first conical portion 31 with a contact width W <b> 2.
As shown in FIG. 6, the second inner peripheral surface 22 of the outer ring 20 is formed so as to contact the second conical portion 32 with a contact width W <b> 3.

The angle theta ₁ formed by the generatrix M1 of the central axis L and the first outer peripheral surface _11, the central axis L and the angle theta ₂ which forms the generatrix M2 of the first inner peripheral surface 21 _', the inner first peripheral surface 21' The relationship of the inclination angle β of the bus M3 of the second conical portion 32 with respect to the bus M2 is expressed by conditional expression (1).
(1) β> (θ ₂ −θ ₁ )
It is formed to satisfy.
That is, by satisfying conditional expression (1), the extrusion load (disengagement force) f acting in the pushing direction can be efficiently received by the rolling (and spin) of the second conical portion 32, and the conical roller 30. Can be reliably prevented from falling off between the inner ring 10 and the outer ring 20 '.

In particular, conditional expression (2)
(2) β = (3/2) · (θ ₂ −θ ₁ )
It may be formed so as to satisfy
In this case, the inner ring 10 is pushed in the direction of the central axis L, the first conical portion 31 receives the normal load N1 from the first outer peripheral surface 11, and the first inner peripheral surface is opposed to the normal load N1. The first conical portion 31 receives the normal load N2 from 21 'and the second conical portion 32 receives the normal load N3 from the second inner peripheral surface 22.
At this time, if it is formed so as to satisfy the conditional expression (2), the normal load N2 that the first conical portion 31 receives from the first inner peripheral surface 21 'and the second conical portion 32 are the second inner peripheral surface. The normal load N3 received from 22 can be made the same. As a result, the conical roller 30 can be interposed between the inner ring 10 and the outer ring 20 'in a stable state.

Further, the surface pressure that the second conical portion 32 receives by contact with the second inner peripheral surface 22 is substantially the same as the surface pressure that the first conical portion 31 receives by contact with the first inner peripheral surface 21 ′. It may be formed.
In this case, local wear of the conical roller 30 can be prevented, and the life of the conical roller 30 and further the life of the conical roller bearing can be extended.

Further, the contact width where the first conical portion 31 contacts the first outer peripheral surface 11 is W1, the contact width where the first conical portion 31 contacts the first inner peripheral surface 21 'is W2, and the second conical portion 32 is the second. When the contact width in contact with the inner peripheral surface 22 is W3, the conditional expression (3) is satisfied under the condition that satisfies the conditional expression (2).
(3) W3 = W2 = W1 / 4
It may be formed so as to satisfy
According to this, local wear and the like of the conical roller 30 can be prevented, the life of the conical roller bearing can be extended, and the conical roller 30 can be miniaturized and further the conical roller bearing can be miniaturized. Can do.

7 to 9 show still another embodiment of the conical roller bearing according to the present invention. FIG. 7 is a configuration diagram showing the configuration of the conical roller bearing, and FIGS. 8 and 9 are parts of the conical roller bearing. It is an enlarged view. In this embodiment, the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
As shown in FIG. 7, the conical roller bearing includes an inner ring 10 ′, an outer ring 20 ″, a plurality of conical rollers 30 ′, and a cage 40.

As shown in FIGS. 7 and 8, the inner ring 10 ′ includes a conical first outer peripheral surface 11 ′ and a cylindrical through hole 12 centering on the central axis L.
As shown in FIGS. 7 and 8, the outer ring 20 ″ has a first inner peripheral surface 21 ″ that contacts the first conical portion 31 ′ with a contact width W 2, and a second conical portion 32 ′ and a contact width W 3. 2nd inner peripheral surface 22 '' which contacts.

As shown in FIGS. 7 and 8, the conical roller 30 ′ is formed integrally with the first conical portion 31 ′ and the first conical portion 31 ′ having a central angle α between the two buses M <b> 1 and M <b> 2. In a virtual conical surface having a second conical portion 32 ′ that tapers in the opposite direction and having a vertex O on the central axis L, the second conical portion 32 ′ is arranged to have a rotation axis S that forms an angle θ ₀ with the central axis L. .
The first conical portion 31 ′ is formed so as to circumscribe the first outer peripheral surface 11 ′ and in contact with the first inner peripheral surface 21 ″.
As shown in FIG. 8, the second conical portion 32 ′ has a conical shape that tapers in a direction opposite to the first conical portion 31 ′ (having a vertex on the rotation axis S opposite to the vertex O). It is formed so as to be inscribed in the second inner peripheral surface 22 ″, and in the middle region (point C) of the contact width W3 of the outer peripheral surface so that the extension line of the bus M2 of the first conical portion 31 ′ intersects Is formed.

  According to this embodiment, as shown in FIG. 9, no spin is generated on the contact line CL passing through the point C between the second conical portion 32 ′ and the second inner peripheral surface 22 ″, and the conical roller 30 ′. The spin component that tends to twist the rotation axis S of the rotation axis S with respect to the center axis L can be canceled, and the contact between the cage 40 and the conical roller 30 ′ can be reliably prevented.

FIG. 10 is a sectional view showing still another embodiment of the conical roller bearing according to the present invention. In this embodiment, the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
As shown in FIG. 10, the conical roller bearing includes an inner ring 110, an outer ring 120, a plurality of conical rollers 30, and a cage 40.

As shown in FIG. 10, the inner ring 110 includes a conical first outer peripheral surface 111, a cylindrical through hole 112 centered on the central axis L, and a conical second outer peripheral surface 113.
The first outer peripheral surface 111 is formed so as to circumscribe the first conical portion 31 in the same manner as the first outer peripheral surface 11 described above.
The second outer peripheral surface 113 is formed so as to circumscribe the second conical portion 32.
As shown in FIG. 10, the outer ring 120 includes a first inner peripheral surface 121 that inscribes the first conical portion 31.
The first inner peripheral surface 121 is formed so as to inscribe the first conical portion 31 in the same manner as the first inner peripheral surface 21 described above.

  In this embodiment, the extrusion load f that pushes out the conical roller 30 is not received by sliding the end surface abutting against the receiving portion as in the prior art, but is provided integrally with the conical roller 30. Since the second conical portion 32 is received by rolling on the second outer peripheral surface 113, the structure can be simplified, and heat generated or worn in the case of sliding can be prevented, and a smooth bearing operation can be obtained. Thus, the service life can be extended and the transmission efficiency of the rotational force can be improved.

FIG. 11 is a cross-sectional view showing still another embodiment of the conical roller bearing according to the present invention. In this embodiment, the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
As shown in FIG. 11, the conical roller bearing includes an inner ring 110 ′, an outer ring 120 ′, a plurality of conical rollers 30 ′, and a cage 40.

As shown in FIG. 11, the inner ring 110 ′ includes a conical first outer peripheral surface 111 ′, a cylindrical through hole 112 centered on the central axis L, and a conical second outer peripheral surface 113 ′.
The first outer peripheral surface 111 ′ is formed so as to circumscribe the first conical portion 31 ′, similarly to the first outer peripheral surface 11 ′ described above.
As shown in FIG. 11, the second outer peripheral surface 113 ′ circumscribes the second conical portion 32 ′, and the bus M 3 is inclined with respect to the bus M 1 of the first conical portion 31 ′ (first outer peripheral surface 111 ′). It is formed so as to form β.
As shown in FIG. 11, the outer ring 120 ′ includes a first inner peripheral surface 121 ′ that inscribes the first conical portion 31 ′.
The first inner peripheral surface 121 ′ is formed so as to inscribe the first conical portion 31 ′, similarly to the first inner peripheral surface 21 ″ described above.
As shown in FIG. 11, the second conical portion 32 ′ of the conical roller 30 ′ is opposite to the first conical portion 31 ′ (having a vertex on the opposite side of the vertex O on the rotation axis S). It is formed in a tapered cone shape and circumscribes the second outer peripheral surface 113 ′, and an intermediate region (point C) of the contact width of the outer peripheral surface of the first conical portion 31 ′ (first outer peripheral surface 111 ′). It is formed so that the extended lines of the bus M1 intersect.

  Also in this embodiment, the pushing load f that pushes out the conical roller 30 'is not received by the end surface of the conical roller 30' coming into contact with the receiving portion and sliding, but is provided integrally with the conical roller 30 '. Since the second conical portion 32 ′ is received by rolling on the second outer peripheral surface 113 ′, it is possible to prevent the generation of heat or wear caused by sliding while achieving simplification of the structure, and smooth A bearing action can be obtained, the life can be extended, and the transmission efficiency of the rotational force can be improved.

In the above embodiment, the inner rings 10, 10 ′, 110, 110 ′ are rotatable around the central axis L, and the outer rings 20, 20 ′, 20 ″, 120, 120 ′ are rotated around the central axis L. Although the case where it is rotatable is shown, the present invention is not limited to this. In a configuration in which the outer ring is fixed and only the inner ring is rotatable, or in a configuration in which the inner ring is fixed and only the outer ring is rotatable. The configuration of the present invention may be adopted.
In the above embodiment, the second inner peripheral surface 22, 22 ″ is provided on the outer ring 20, 20 ′, 20 ″, 120, 120 ′ as a portion where the second conical portions 32, 32 ′ come into contact, or Although the case where the second outer peripheral surfaces 113 and 113 ′ are provided on the inner rings 110 and 110 ′ is shown, the present invention is not limited to this, and the second outer peripheral surface is provided on the inner ring as a portion where the second conical portion comes into contact. And you may employ | adopt the structure which provides a 2nd internal peripheral surface in an outer ring | wheel.

  As described above, the conical roller bearing of the present invention can prevent the heat generation or wear due to the conventional sliding, achieve the simplification of the structure, reduce the transmission loss due to the sliding, and extend the life. Since the transmission efficiency can be improved, it can be applied to a bearing region for supporting a rotating body, and is useful as a bearing mechanism between a propeller shaft of an automobile and a differential gear or a drive shaft of a wheel.

It is a block diagram which shows one Embodiment of the conical roller bearing which concerns on this invention. It is a schematic diagram of the conical roller bearing shown in FIG. It is a graph which shows the transmission efficiency of the conical roller bearing which concerns on this invention, and the conventional conical roller bearing. It is a graph which shows the relationship between the input torque and thrust load in an evaluation test. It is a block diagram which shows other embodiment of the conical roller bearing which concerns on this invention. It is the elements on larger scale of the conical roller bearing shown in FIG. It is a block diagram which shows other embodiment of the conical roller bearing which concerns on this invention. It is the elements on larger scale of the conical roller bearing shown in FIG. It is a figure which shows the spin component which acts on the conical roller of the conical roller bearing shown in FIG. It is a block diagram which shows other embodiment of the conical roller bearing which concerns on this invention. It is a block diagram which shows other embodiment of the conical roller bearing which concerns on this invention. It is a block diagram which shows the conventional conical roller bearing. FIG. 13 is a partial view showing a part of the conical roller bearing shown in FIG. 12.

Explanation of symbols

L Center axis S Rotation axis O Vertex 10, 10 ′, 110, 110 ′ Inner ring 11, 11 ′, 111, 111 ′ First outer peripheral surface 12, 112 Through hole 113, 113 ′ Second outer peripheral surface 20, 20 ′, 20 ″ ″, 120, 120 ′ Outer rings 21, 21 ′, 21 ″, 121, 121 ′ First inner peripheral surface 22, 22 ″ Second inner peripheral surface 30, 30 ′ Conical rollers 31, 31 ′ First conical portion 32, 32 'second conical portion 40 cage 40a rectangular opening M1 first outer peripheral surface and first conical portion bus M2 first inner peripheral surface and first conical portion bus M3 second conical portion, second inner peripheral surface , And an angle θ2 between the central axis θ1 of the second outer peripheral surface and the first outer peripheral surface θ2 an angle between the central axis and the first inner peripheral surface β of the second conical portion with respect to the first inner peripheral surface or the bus of the first outer peripheral surface Inclination angle W1 of busbar Contact width W2 at which the first conical portion contacts the first outer peripheral surface The first conical portion is the first inner peripheral surface Contact width contact width W3 second conical portion in contact is in contact with the second inner peripheral surface

Claims (2)

An inner ring that defines a predetermined center axis and has a conical first outer peripheral surface, an outer ring that is arranged coaxially with the inner ring and has a conical first inner peripheral surface, and has an apex on the central axis A plurality of conical rollers arranged in a virtual conical surface with a rotation axis and having a first conical portion circumscribing the first outer peripheral surface and inscribed in the first inner peripheral surface; A conical roller bearing comprising a cage arranged and held in a circumferential direction,
The conical roller has a second conical portion formed in a conical shape that tapers in a direction opposite to the first conical portion,
The outer ring or the inner ring is to have a second outer peripheral surface for circumscribing the second inner peripheral surface or the second conical portion is inscribed the second conical portion,
The angle between the central axis and the generatrix of the first outer peripheral surface is θ ₁ , the angle between the central axis and the generatrix of the first inner peripheral surface is θ ₂ , and the bus of the first inner peripheral surface or the first outer peripheral surface Satisfying β> (θ ₂ −θ ₁ ), where β is the inclination angle of the generatrix of the second conical section with respect to
The second conical portion is formed at a position where an extension line of a bus of the first conical portion intersects in an intermediate region of a contact width with the second outer peripheral surface or the second inner peripheral surface.
A conical roller bearing characterized by that. The surface pressure that the second conical portion receives by contact with the second inner peripheral surface is formed to be substantially the same as the surface pressure that the first conical portion receives by contact with the first inner peripheral surface. Yes,
The conical roller bearing according to claim 1 .

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