JP2002327761A - Rolling bearing with enclosing plate and transmission integrated with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a rolling bearing with an enclosing plate provided with a synthetic resin-made enclosing plate capable of engaging with the race in an appropriate press-in strength. SOLUTION: Engaging grooves 34, 34 are formed over the whole periphery at both axial end faces of the external ring 14a in a state that these grooves become hollow in the substantially axial direction, and these respective engaging grooves 34, 34 are tilted in the direction toward the radial inside as they go to the depth and the engaging projections 37 formed at the outer peripheral edges of the plastic enclosing plates 33, 33 are axially pressed in these engaging grooves 34, 34. As a result, the contact area of the engaging groove 34 and the engaging projection 37 is made securable and hence, the above subject is solved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission for a vehicle or a special vehicle such as a tractor or a forklift (including a transaxle. The same applies to the entire specification). The present invention relates to an improvement of a rolling bearing with a sealing plate incorporated in various types of machinery including the above. The transmission to which the present invention is applied includes automatic transmissions having various structures such as a planetary gear type, a belt type, and a toroidal type, in addition to the manual transmission.

[0002]

2. Description of the Related Art U.S. Pat. No. 4,309,916 discloses a structure as shown in FIG. 7 as an automobile transmission incorporating a rolling bearing with a sealing plate. The manual transmission schematically shown in FIG.
And lubrication oil (mission oil) 2
In the casing 1, an input shaft 3 and an output shaft 4 are arranged concentrically with each other and relatively rotatable. A transmission shaft 5 is provided in the casing 1, and the input shaft 3 and the output shaft 4
Are arranged in parallel to. And these input shafts 3,
The output shaft 4 and the transmission shaft 5 are rotatably supported by rolling bearings 6 with a sealing plate, respectively.

The input shaft 3 supports a drive gear 7 as a drive power transmission member. The output shaft 4 supports driven gears 8a to 8d, each of which is a driven power transmission member, via a synchromesh mechanism (not shown). During operation, only one of the driven gears 8a to 8d rotates together with the output shaft 4, and the other driven gear rotates with respect to the output shaft 4. Further, transmission gears 9a to 9e are rotatably supported together with the transmission shaft 5 at portions of the transmission shaft 5 facing the drive side gear 7 and the driven side gears 8a to 8d, respectively. . The transmission gears 9a to 9e are meshed with the driving gear 7 and the driven gears 8a to 8d directly or via a reversing idle gear 10.

As described above, a transmission for an automobile incorporates a plurality of rotating shafts and many gears. These rotating shafts and gears are rotatably supported with respect to the housing and the support shaft by rolling bearings such as ball bearings and cylindrical roller bearings. Inside such a transmission, grinding debris or an abrasive that remains attached to the gears or the housing or the like during the processing of the gears or the housing, or abrasion powder generated at the meshing portion of the gears during operation. Many foreign substances exist. When such foreign matter enters the rolling bearing, an indentation is formed on the surface of the rolling contact portion by the foreign matter, and the surface is easily fatigued and peeled (flaked) based on the indentation, resulting in breakage. Become.
For this reason, a rolling bearing 6 with a sealing plate as shown in FIG. 8 has been conventionally used as a rolling bearing for use in an environment where a large amount of such metallic foreign matter is present.

[0005] The rolling bearing 6 with a sealing plate is provided with a deep groove type inner ring raceway 11 at an axially intermediate portion (left and right direction in FIG. 8) of the outer peripheral surface.
And an outer raceway 13 having a deep groove type outer raceway 13 at the axially intermediate portion of the inner peripheral surface, and an outer raceway 14 arranged concentrically with the inner raceway 12, and rolling between the inner raceway race 11 and the outer raceway raceway 13. A plurality of balls 1 movably provided, each of which is a rolling element.
5 is provided. The plurality of balls 15 are rollably held one by one in a plurality of pockets 17 provided in a holder 16. The rolling element is the ball 15 in the illustrated example.
Alternatively, a cylindrical roller or a tapered roller may be used.

The outer peripheral edges of the sealing plates 19 and 19 are respectively engaged with engaging grooves 18 provided on the inner peripheral surfaces of both ends of the outer ring 14 over the entire periphery. Each of these sealing plates 19 is formed in a ring shape by reinforcing a resilient material 21 such as an elastomer such as rubber with a metal core 20 formed of a metal plate such as a steel plate in a ring shape. Consisting of The outer peripheral edge of the elastic member 21 projects outward in the diametrical direction (up and down direction in FIG. 8) slightly more than the outer peripheral edge of the cored bar 20.
8. On the other hand, the inner peripheral edge of the elastic member 21 is sufficiently projected inward in the diametrical direction from the inner peripheral edge of the cored bar 20, and the projected portion makes the seal lip 2.
2. The distal end edge of the seal lip 22 is brought into sliding contact with the inner wall surfaces 24 of the seal grooves 23 formed on the outer peripheral surfaces of both ends of the inner ring 12. still,
The tip edge of the seal lip 22 is bifurcated in the axial direction. Even when the inner ring 12 or the outer ring 14 is displaced in the axial direction, the tip edge of the seal lip 22 is located inside the seal groove 23. Wall 24 and outer wall 2
5 is always slidable on at least one of them.

[0007] The rolling bearing 6 with a sealing plate constructed as described above.
Allows relative rotation between a member to which the inner race 12 is externally fixed and the member to which the outer race 14 is internally fixed based on the rolling of the balls 15. In addition, a pair of sealing plates 19, 19 having their outer peripheral edges locked to the inner peripheral surfaces of both ends of the outer ring 14, respectively.
The grease sealed in the space 26 in which the balls 15 are installed is prevented from leaking to the outside, and foreign substances such as dust, oil, and water, which float outside, are in the space 26 in which the balls 15 are installed. Prevent intrusion into.

A sealing plate 19 composed of the above-described core 20 and an elastic material 21 such as an elastomer such as rubber.
In this case, it is difficult to reduce the weight and reuse (recycle) as well as increase the cost. That is, the weight of the sealing plate 19 is increased by the amount that the elastic material 21 is reinforced by the core metal 20.
In addition, since the elastic member 21 is attached to the metal core 20, the manufacturing cost increases and it is difficult to reuse the elastic member 21. If only the manufacturing cost is to be reduced, a cheap nitrile rubber (NBR) may be used as the elastic member 21. However, NBR is liable to deteriorate due to hardening when used in an automotive transmission, particularly at high temperatures and in an environment where oil constantly falls, and it is impossible to ensure the sealing performance for a long period of time. there is a possibility. On the other hand, when using acrylic rubber or fluorine rubber which is relatively hard to be cured and deteriorated even in a high temperature environment, the cost and weight increase as described above, and it is difficult to reuse the rubber and the environment. Is not preferred. On the other hand, when the sealing plate is made of a synthetic resin, it is easy to reduce the weight and reuse, and it is also possible to reduce the manufacturing cost by facilitating mass production using a mold.

On the other hand, when the sealing plate is made of a synthetic resin as described above, it is difficult to ensure the sealing performance of the sealing plate. That is, a sealing plate having the shape shown in FIG. 8 is made of synthetic resin so that the leading edge of the seal lip constituting the inner peripheral edge of the sealing plate always makes sliding contact with the inner wall surface 24 or the outer wall surface 25 of the sealing groove 23. However, since the synthetic resin is less likely to be elastically deformed than rubber or the like, it is difficult to lock the sealing plate to the outer ring 14 with the seal lip entering the inside of the seal groove 23. Further, in a state where an elastic force is applied to the tip edge of the seal lip, that is, the tip edge of the seal lip is
When the sliding contact is made with an axial interference, the resistance (load torque) of the sealing plate tends to increase because the synthetic resin is less likely to be elastically deformed than the rubber or the like.

[0010]

DESCRIPTION OF THE PRESENT INVENTION FIG. 9 shows a rolling bearing 6a with a sealing plate invented by the present inventors in view of such circumstances (Japanese Patent Application No. 2001-007574). The rolling bearing 6a with a sealing plate according to the preceding invention has sealing grooves 19a, 19a formed by forming synthetic resin into a whole ring shape in locking grooves 18, 18 provided on the inner peripheral surfaces of both ends of the outer ring 14, respectively.
Is locked at the outer periphery. Each of these sealing plates 19a, 1
An elastic deformation portion 27 having an elastic force directed outward in the diametrical direction is formed on the entire outer periphery of the outer peripheral edge portion 9a. The elastic deformation portion 27 is formed in an eave-like shape on the outer peripheral edge of the sealing plate 19a, and by applying a diametrically inward force,
It is elastically deformable in the direction of reducing the outer diameter.

On the other hand, the inner peripheral edges of the sealing plates 19a, 19a are constituted by a pair of sealing lips 28, 29, respectively. The first seal lip 28, which is located on the outside in the axial direction, has its front end edge formed at the inner wall surface 2 of the seal grooves 23 formed on the outer peripheral surfaces of both ends of the inner ring 12.
In FIG. 4, it is closely opposed to the entire circumference. That is, the inner wall surface 2 of the seal groove 23 is provided on the inner peripheral edge of the sealing plate 19a.
First sealing lip 2 projecting inward in the axial direction toward
8 is formed over the entire circumference. A labyrinth seal is constituted by the tip edge of the first seal lip 28 and the inner wall surface 24 of the seal groove 23.

On the other hand, a second seal lip 29 located axially inward of the first seal lip 28 and diametrically outward of the first seal lip 28 has a distal end edge portion which is connected to the inner ring. A cylindrical surface portion 30 formed on a part of the outer peripheral surface of the inner ring 12 and parallel to the central axis of the inner ring 12 is slidably contacted over the entire circumference. That is, on the inner peripheral edge of the sealing plate 19a,
Each ball 1 which is a rolling element on the outer peripheral surface of the inner ring 12
A second seal lip 29 projecting toward the outer peripheral surface of the shoulder portion 31 for sandwiching 5 from both sides is formed over the entire circumference. Then, the tip edge of the second seal lip 29 is attached to the outer peripheral surface of the shoulder 31 which is the cylindrical surface 30,
Sliding contact is made over the entire circumference. As described above, since the distal end portion of the second seal lip 29 is slidably contacted with the cylindrical surface portion 30 parallel to the central axis of the inner ring 12,
Alternatively, even if the outer ring 14 is displaced in the axial direction, the distal end edge of the second seal lip 29 and the cylindrical surface 30
Can always be kept in sliding contact. Further, the cross-sectional shape (in an imaginary plane including the central axis of the inner ring 12) of the tip end edge of the second seal lip 29 in the axial direction is
It is formed in a substantially V-shape protruding toward the cylindrical surface portion 30, and the top of the tip edge portion is slidably contacted with the cylindrical surface portion 30 over the entire circumference. Therefore, the resistance (load torque) of the sealing plate 19a does not increase.

The sealing plate 19a as described above elastically deforms the elastic deformation portion 27 in a direction to reduce its diameter,
The outer peripheral edge of the sealing plate 19 a is engaged with the locking groove 18 by being pushed into the locking groove 18. In this way,
In a state where the sealing plate 19a is engaged with the locking groove 18, the outer peripheral edge of the elastic deformation portion 27 is provided on the inner peripheral surface of the locking groove 18, and the outer peripheral edge is formed on the inner side surface of the sealing plate 19a in the axial direction. The deviated portion is in close contact with the inner surface of the locking groove 18 over the entire circumference. Also, in this state, the leading edge of the first seal lip 28 is
The second seal lip 29 is in sliding contact with the outer peripheral surface of the shoulder portion 31 which is the cylindrical surface portion 30 over the entire circumference. In addition, as described above, the sealing plate 1
When the engagement 9a is engaged with the locking groove 18, the first seal lip 28 formed on the inner peripheral edge of the sealing plate 19a is positioned outside the projection 32 forming the outer wall surface 25 of the seal groove 23. This first seal lip 29 is used so as not to interfere with the peripheral edge.
Regulates the inside diameter of

In the rolling bearing 6a with the sealing plate of the prior invention having the above-described structure, the sealing plate 19a is made of synthetic resin.
It is easy to reduce the weight and reuse, and furthermore, it is easy to mass-produce with a mold, so that the manufacturing cost can be reduced. Further, even when the inner ring 12 or the outer ring 14 is displaced in the axial direction, the distal end edge of the second seal lip 29 and the cylindrical surface 30 can be always slidably contacted over the entire circumference. A sufficient sealing property can be secured. That is,
The second seal lip 29 of the first and second seal lips 28 and 29 provided on the inner peripheral edge of the sealing plate 19a.
Is projected from the outer peripheral surface of the inner ring 12 toward a cylindrical surface 30 parallel to the center axis of the inner ring 12, and the leading edge of the second seal lip 29 extends over the entire circumference of the cylindrical surface 30. Sliding contact. For this reason, even if the inner ring 12 or the outer ring 14 is displaced in the axial direction, the tip edge of the second seal lip 29 can be kept in sliding contact with the cylindrical surface 30. As a result, foreign substances such as dust are less likely to enter the rolling bearing, and the surface of the rolling contact portion can be prevented from being fatigued, peeled (flaking) and easily damaged. In addition, even when the synthetic resin is incorporated in a transmission, the synthetic resin does not easily deteriorate with respect to the transmission oil, so that the sealing property can be secured for a long period of time.

[0015]

In the case of the rolling bearing 6a with the sealing plate of the prior invention which is constructed and operates as described above, there is room for further improvement. That is, as shown in FIG. 9 described above, the sealing plate 19a constituting the rolling bearing 6a with the sealing plate of the prior invention is provided.
Is premised on locking in a locking groove 18 having the same shape as the conventional rolling bearing 6 with a sealing plate as shown in FIG. In other words, the outer peripheral edge of the sealing plate 19a made of synthetic resin is bonded to the elastic material 21 such as an elastomer such as rubber and the core metal 2.
0 (hereinafter referred to as a sealing plate 1 made of an elastic material).
9) is intended to be locked as it is in the locking groove 18 for locking.

However, as described above, the sealing plate 1 made of synthetic resin is used.
When the 9a is locked in the locking groove 18 for locking the sealing plate 19 made of the elastic material, the synthetic resin is less likely to be elastically deformed (has a lower elastic modulus) than the elastic material. It is difficult to lock the elastic deformation portion 27 constituting the outer peripheral edge of the sealing plate 19a made of the synthetic resin in the locking groove 18 with appropriate press-fitting strength (in a state where the elastic deformation portion is preferably elastically deformed). When it is not possible to lock with an appropriate press-fitting strength, the elastic deformation portion 27 is likely to rattle (slip) in the locking groove 18, and the sealing plate 19 a may be inclined from an optimal mounting state. There is. As a result, the sliding contact position between the tip edge of the second seal lip 29 provided on the inner peripheral edge of the sealing plate 19a and the shoulder 31 of the outer ring 14 is shifted, and
There is a possibility that the sealing property of a may decrease. In addition, if the rattling becomes remarkable, the elastic deformation portion 27 may be worn out due to the rattling, and the sealing plate 19a may fall out of the locking groove 18 (fall off). In order to prevent such inconvenience, it is conceivable to maintain the dimensional accuracy of the elastically deformable portion 27 at a high level. It is not preferable because it is troublesome and the processing time is long.

A mechanical device which undergoes a large temperature change during use;
For example, when the rolling bearing 6a with a sealing plate of the above-mentioned invention is incorporated into a transmission, the sealing plate 19a made of synthetic resin may greatly change its dimensions due to expansion and contraction due to a temperature change. For this reason, from this aspect,
The sealing plate 19a made of synthetic resin is inserted into the locking groove 18 as described above.
It is difficult to lock with appropriate press-fit strength. In view of such circumstances, the present invention has been made to realize a structure that can easily lock a sealing plate made of synthetic resin with an appropriate press-fitting strength.

[0018]

The rolling bearing with a sealing plate according to the present invention has the same structure as the above-mentioned conventional rolling bearing with a sealing plate.
An inner ring having an inner ring raceway at an axially intermediate portion of the outer peripheral surface, an outer ring having an outer ring raceway at an axially intermediate portion of the inner peripheral surface, and a plurality of rollingly provided between the inner raceway and the outer raceway And one of the peripheral parts is locked to a part of one of the raceways of the inner ring and the outer ring, and the other peripheral part is connected to one of the raceways of the other of the inner and outer races. In particular, in the rolling bearing with a sealing plate of the present invention, the sealing plate is made of a synthetic resin, and is connected to an axial end surface of the one race. The locking recess is provided in a state of being substantially recessed in the axial direction of the bearing ring (at a plurality of positions in the circumferential direction or over the entire circumference), and at least one of one peripheral edge of the sealing plate is provided in the locking recess. Part is locked.

The transmission of the present invention also has a casing in which lubricating oil is stored and an input shaft rotatably supported by rolling bearings in the casing, similarly to the above-described conventionally known transmission. A drive-side power transmission member that is supported by the input shaft and rotates together with the input shaft, and that is supported by the output shaft and engages with the drive force transmission member to transmit power. And a driven power transmission member that rotates with the output shaft as the input shaft rotates. In particular, in the transmission of the present invention, each of the rolling bearings is a rolling bearing with a sealing plate of the present invention as described above.

[0020]

In the case of the rolling bearing with a sealing plate of the present invention constructed as described above, one peripheral edge of the sealing plate can be locked to one of the races with an appropriate press-fit strength, so that the sealing performance can be maintained for a long period of time. Can be secured. That is, a locking recess for locking the peripheral edge of the sealing plate is provided in the axial end surface of the one raceway in a state substantially recessed in the axial direction of the raceway, so that the sealing plate is provided. The peripheral portion is easily locked along the inner surface of the locking recess. Therefore, a sufficient contact area between the locking recesses and the peripheral edge of the sealing plate can be secured. In other words, even if this sealing plate is made of a synthetic resin that is less likely to be elastically deformed than an elastic material such as an elastomer such as rubber, the frictional force between the contact portions between these locking recesses and the peripheral portion of the sealing plate can be sufficiently increased. As a result, sufficient press-fit strength can be obtained. As a result, the sealing plate is less likely to be tilted from the optimal mounting state, and the sliding wear between the outer peripheral edge portion of the sealing plate and the locking recess can be prevented, and the sealing performance can be ensured for a long period of time.

It is to be noted that at least one of the locking recesses is formed.
If a radial interference is provided between the inner wall surface of the sealing plate and a part of the peripheral portion of the sealing plate, the optimum shape of the peripheral portion of the sealing plate can be obtained without complicating the shape of the peripheral portion of the sealing plate as in the above-described invention. It becomes easy to obtain press-fit strength. Moreover, by giving a closing margin like this,
Even when the sealing plate is thermally expanded, it is possible to suppress the dimensional change of the sealing plate while sufficiently securing the press-fitting strength.
In addition, if a gap is provided between at least one inner wall surface of the locking recess and a part of the peripheral edge of the sealing plate, even if the sealing plate greatly expands, the size due to the thermal expansion is increased. Can absorb changes. Therefore, even when used in a mechanical device having a large temperature change during use, for example, a transmission, etc., the dimensional change accompanying the temperature change can be absorbed, and the sealing plate can be more reliably prevented from falling off.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIGS.
5 shows a first example of an embodiment of the present invention corresponding to FIG. The feature of the present invention is that the shape and structure of the locking groove 34 and the sealing plate 33 provided in the outer ring 14a are devised so that the sealing plate 33 made of synthetic resin can be easily locked to the outer ring 14a with an appropriate press-fitting strength. It is in. Since the basic configuration itself of the rolling bearing with a sealing plate is the same as that of the conventional structure shown in FIG. 8 and the structure of the prior invention shown in FIG. 9, the same parts are denoted by the same reference numerals and redundant description is omitted. Or, for simplicity, the following mainly describes the features of the present invention.

In the case of this embodiment, locking grooves 34, 34 corresponding to the locking recesses described in the claims are formed on both axial end surfaces (both right and left end surfaces in FIG. 1) of the outer race 14a. It is provided over the entire circumference in a state of being substantially recessed in the axial direction. Each of the locking grooves 34 has a pair of inner wall surfaces 35 facing each other in the radial direction of the outer ring 14a. Then, these inner wall surfaces 35 and 36 are connected to the outer ring 1.
The outer ring 14a is inclined in a direction approaching the central axis of the outer ring 14a toward the inside in the axial direction. That is, each of the locking grooves 3
4, 34 are inclined in a direction toward a radially inward toward the back. And in each of these locking grooves 34, 34,
Locking ridges 37 formed on the outer peripheral edges of the synthetic resin sealing plates 33, 33 are locked. This locking ridge 37
The sealing plates 33, 33 protrude inward from the outer peripheral edge of the axially inner side surface (the surface facing the ball 15) over the entire circumference or intermittently in the circumferential direction. As it approaches the leading edge, it is inclined in a direction inward in the radial direction.

In addition, a radial interference between the inner diameter side inner wall surface 35 of the inner wall surfaces 35 and 36 and the inner diameter surface of the locking ridge 37 aligned with the inner diameter side inner wall surface 35. Have. That is, as shown in FIGS.
7 is elastically deformed from a free state shown by a dashed line to a state shown by a solid line in a state locked in the locking groove 34, and a tightening margin is provided by a difference α between the free state and the locked state. I have. On the other hand, between the outer diameter side inner wall surface 36 of the inner wall surfaces 35 and 36 and the outer diameter surface of the locking ridge 37 aligned with the outer diameter side inner wall surface 36, at least Article 37
Is in a free state (a state before elastic deformation), so that a radial gap exists. That is, the radial gap is provided between the outer diameter surface of the locking ridge 37 shown by a chain line in FIGS. 1 and 2 and the outer diameter side inner wall surface 36.
In the state where the locking ridge 37 is locked in the locking groove 34, it is not always necessary to provide a gap between the outer diameter surface of the locking ridge 37 and the outer diameter side inner wall surface 36. However, in order to ensure the absorption of the thermal expansion, the gap is provided even in the locked state. In short, the gap is regulated in accordance with the amount of deformation of the locking ridge 37 due to a temperature change during use.

A sealing lip 38 is formed on the inner peripheral edge of each of the sealing plates 33, 33 over the entire circumference. This seal lip 38 has a short cylindrical shape like the second seal lip 29 formed on the inner peripheral edge of the sealing plate 19a according to the prior invention shown in FIG. A ridge 39 having a substantially V-shaped cross-sectional shape projecting inward in the radial direction is formed over the entire circumference.

Each of the sealing plates 33 having such a shape,
Reference numeral 33 denotes the locking ridge 3 formed on each outer peripheral edge.
7 are provided on both end surfaces of the outer ring 14a.
By press-fitting the outer rings 14 and 34 in the axial direction, their outer peripheral edges are locked to both end surfaces of the outer ring 14a. In this state, the protrusion 39 formed on the inner peripheral surface of the distal end edge of the seal lip 38 is attached to the cylindrical surface portion 3 which is the outer peripheral surface of the shoulder portions 31 a provided on both ends of the outer peripheral surface of the inner ring 12.
0 and 30 are elastically slidably contacted over the entire circumference. Therefore, even in the case of the present embodiment, even when the inner ring 12 or the outer ring 14a is displaced in the axial direction, the ridge 39 and the cylindrical surface portion 30 can always be kept in sliding contact with each other.

When the structure of this embodiment is implemented, the interference between the ridge 39 and the cylindrical surface 30 in the radial direction (the difference between the outer diameter of the cylindrical surface 30 and the inner diameter of the ridge 39 in the free state). 1
/ 2) within the range of 0.01 to 0.4 mm. Preferably, the interference is set within the range of 0.01 to 0.2 mm, and more preferably within the range of 0.01 to 0.08 mm.
If the interference is less than 0.01 mm, the protrusion 39
It becomes difficult to secure the sealing performance due to the above. On the other hand, if the interference is too large, the frictional resistance of the sliding contact portion increases, and the rotational resistance of the rolling bearing with the sealing plate increases. For example, the transmission efficiency of the transmission incorporating the rolling bearing with the sealing plate decreases. . Therefore, the upper limit of the interference is set to 0.4 mm, preferably 0.2 mm, and more preferably 0.08 mm. In addition, the value of the above-mentioned interference (absolute value)
Shows the case of a rolling bearing with a sealing plate in which the outer diameter of the cylindrical surface portion 30 is generally about 40 mm for transmission. In terms of the ratio to the outer diameter of the cylindrical surface portion 30, the interference is 0.00025 to
0.01, preferably 0.00025 to 0.005, and more preferably 0.00025 to 0.002. or,
The roundness of the sealing plate 33 is preferably suppressed to 0.3 or less, more preferably 0.1 or less.

Further, in the case of this embodiment, the sealing plate 33 is made of a polyamide resin reinforced with glass fibers covered with a modified high-density polyethylene. That is, if a synthetic resin containing a reinforcing fiber such as glass fiber is used as the synthetic resin constituting the sealing plate, the linear expansion coefficient of the sealing plate can be reduced, and the sealing plate can be hardly deformed even at a high temperature. However, if a sealing plate made of a synthetic resin containing such reinforcing fibers is used as it is, the reinforcing fibers among them may directly contact the cylindrical surface portion 30 and the cylindrical surface portion 30 may be easily worn. On the other hand, in the case of this example, since the reinforcing fibers are covered with the modified high-density polyethylene which is a modified synthetic resin, the reinforcing fibers such as glass fibers do not directly slide on the cylindrical surface portion 30. Moreover, the use of a modified synthetic resin in which the properties of the synthetic resin are changed by a modifying agent, particularly a modified high-density synthetic resin in which the strength and wear resistance are improved by increasing the density, makes it difficult to expose the reinforcing fibers. it can. FIG. 3 shows a case where a sealing plate made of a synthetic resin containing glass fibers (conventional product) is used, and a case where the sealing plate of the present example in which glass fibers are covered with modified high-density polyethylene (product of the present invention) is used. The wear amount (wear depth) of the cylindrical surface portion 30 is shown. As is clear from this figure, according to the product of the present invention, the reinforcing fiber can be prevented from directly slidingly contacting the cylindrical surface portion 30, and the cylindrical surface portion 30 can be hardly worn.
In this manner, the technique of covering the reinforcing fibers with the modified synthetic resin is not only effective when combined with the present invention, but also includes the synthetic resin sealing plate of the previous invention shown in FIG. The above operation and effect can also be obtained when the present invention is implemented with the above structure.

In the case of the rolling bearing with a sealing plate of the present invention configured as described above, the outer peripheral edge of the sealing plate 33 is
Can be locked with an appropriate press-fitting strength, so that sealing performance can be ensured for a long period of time. That is, the locking groove 34 for locking the outer peripheral edge of the sealing plate 33 is provided in the axial end surface of the outer ring 14a in a state substantially recessed in the axial direction of the outer ring 14a. The outer peripheral edge of the locking groove 34
It is easy to lock along the inner surface of. Therefore, a sufficient contact area between the locking grooves 34 and the locking ridges 37 provided on the outer peripheral edge of the sealing plate 33 can be secured. In other words,
Even when the sealing plate 33 is made of a synthetic resin that is less likely to be elastically deformed than an elastic material such as an elastomer such as rubber, the frictional force between the contact portions between the locking grooves 34 and the locking ridges 37 is sufficiently ensured. And sufficient press-fit strength can be obtained. As a result, the sealing plate 33 is less likely to be tilted from the optimal mounting state, and the sliding wear of the locking portion between the locking ridge 37 and the locking groove 34 can be prevented, and the sealing performance can be ensured for a long period of time. .

Since there is a radial interference between the inner wall surface 35 of the inner diameter side of the locking groove 34 and the inner surface of the locking ridge 37, the above-described prior invention is not provided. Sealing plate 1
9 does not complicate the shape of the outer peripheral edge, and it is easy to obtain the optimum press-fit strength. Moreover, by providing the interference in this manner, even when the sealing plate 33 expands, it is possible to suppress a dimensional change of the sealing plate 33 while sufficiently securing the press-fitting strength. Further, the locking ridge 37 is connected to the locking groove 34.
If a gap is provided between the outer diameter side inner wall surface 36 constituting the locking groove 34 and the outer diameter surface of the locking ridge 37 in a state where the locking ridge 37 is In this case, the dimensional change due to the thermal expansion can be absorbed. For this reason, even when used in a mechanical device having a large temperature change during use, for example, a transmission, etc., it is possible to absorb a dimensional change due to a temperature change, and to prevent excessive compressive stress from being applied to the locking ridge 37. Settling of the locking ridge 37 can be prevented, and the sealing plate 33 can be more reliably prevented from falling off.

The rolling bearing with a sealing plate of the present embodiment as described above,
For example, the transmission according to the present invention is configured by incorporating the transmission as shown in FIG. 7 described above or the rotary support portion of various conventionally known transmissions. In the case of this example, the locking recess for locking the sealing plate 33 is a locking groove 34 recessed over the entire circumference in the circumferential direction of the outer ring 14a. The locking recesses may be formed by providing recesses at locations (for example, several locations at equal intervals in the circumferential direction). Of course, in such a case, the locking ridge formed on the peripheral edge of the sealing plate is formed intermittently in accordance with the position where each of the concave portions is provided. With this configuration, the rotation of the sealing plate with respect to the outer ring 14a can be reliably prevented. Further, in the case of the present example, the inner wall surfaces 35 and 36 constituting the locking groove 34 are inclined in a direction approaching the central axis of the outer ring 14a, but conversely, in a direction away from the central axis. It may be inclined or parallel to the central axis, or only one of the inner walls 35 and 36 may be inclined. In such a case as well, the locking projection is formed in accordance with the inclination direction and the inclined wall surface of the locking recess, and the interference between the locking projection and the locking recess and the clearance are regulated. In the case of this example, the outer peripheral edge of the sealing plate 33 is locked in the locking groove 34 of the outer race 14a, and
The tip edge of the seal lip 38 formed on the inner peripheral edge of
The inner ring 12 is in sliding contact with the cylindrical surface portion 30. Conversely, the inner peripheral edge of the sealing plate is locked in the locking groove formed on the outer peripheral surface of the inner ring, and the leading edge of the seal lip formed on the outer peripheral edge of the sealing plate is connected to the inner ring of the outer ring. The peripheral surface may be slidably contacted with a cylindrical surface parallel to the center axis of the outer ring.

Next, FIGS. 4 and 5 show a second example of the embodiment of the present invention corresponding to claims 1 to 5. FIG. In the case of this example, the axially outer surfaces of the sealing plates 33a, 33a (FIG. 5)
A constricted portion 40 recessed inward from the side surface in the axial direction is provided over the entire periphery in the circumferential direction. By providing such a constricted portion 40, a sliding contact state between the distal end edges of the seal lips 38, 38 constituting the inner peripheral edge portions of the respective sealing plates 33a, 33a and the cylindrical surface portions 30, 30 of the inner ring 12 is provided. It is easy to maintain the proper state. That is, when the locking ridge 37 constituting the outer peripheral edge of the sealing plate 33a is press-fitted into the locking groove 34, if the interference between the locking ridge 37 and the locking groove 34 is too large, this engagement A large force is applied to the outer peripheral edge of the sealing plate 34a including the stop rib 37, and the outer peripheral edge may be deformed. If the constricted portion 40 is not provided, the deformation may extend to the inner peripheral edge of the sealing plate 34a, and the sealing plate 33 may be inclined as shown by a broken line in FIG. When the sealing plate 33 is inclined in this manner, the sealing lip 38
There is a possibility that a gap is formed between the leading edge of the cylindrical surface portion and the cylindrical surface portion 30, and the sealing property cannot be secured.

In order to prevent such an inclination of the sealing plate 33, it is conceivable to reduce the interference between the locking ridge 37 and the locking groove 34. The press fitting strength of the stop rib 37 cannot be secured, and the sealing plate 33
May be displaced in the rotational direction due to the inner ring 12. Such displacement of the sealing plate 33 wears the locking ridges 37 to further reduce the press-fitting strength, and at the same time, the leading edge of the sealing lip 38 and the cylindrical surface 30
It is not preferable because the sliding contact state cannot be properly maintained.
Therefore, in the case of this example, the constricted portion 4 is formed in the sealing plate 33a.
By providing 0, the rigidity of this portion is reduced, and even if a large force is applied to the outer peripheral edge of the sealing plate 33a due to the increased interference as described above, this force is released and the sealing plate 33a is released. The deformation of the outer peripheral edge of the inner peripheral edge does not reach the inner peripheral edge. For this reason, the sliding contact state between the distal end edge of the seal lip 38 and the cylindrical surface portion 30 can be appropriately maintained, and sufficient sealing performance can be ensured. Such a rolling bearing with a sealing plate of the present embodiment is also incorporated into, for example, a transmission as shown in FIG. 7 described above or a rotary support portion of various conventionally known transmissions to constitute a transmission of the present invention. Other configurations and operations are the same as those of the above-described first example, and thus redundant description will be omitted.

[0034]

Since the present invention is constructed and operates as described above, it is provided with a sealing plate made of synthetic resin which is mounted with an appropriate press-fitting strength, and with a sealing plate which can ensure the sealing performance for a long period of time. A rolling bearing can be realized. As a result, it is possible to contribute to the improvement of the reliability of a mechanical device incorporating a rolling bearing with a sealing plate such as a transmission. In addition, when foreign matter enters the rolling bearing, an indentation is formed on the surface of the rolling contact portion by the foreign matter, and the surface is fatigued based on the indentation, so that the surface is easily damaged and the life of the rolling bearing is shortened. .
On the other hand, in the case of the present invention, the tip edge of the seal lip remains in sliding contact with the cylindrical surface portion of the bearing ring over the entire circumference regardless of the displacement in the axial direction. And it is possible to exhibit sufficient sealing properties.
Further, the surface fatigue can be eliminated, and the life of the rolling bearing with a sealing plate can be extended.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view showing a first example of an embodiment of the present invention.

FIG. 2 is an enlarged view of a portion A in FIG.

FIG. 3 is a graph showing the amount of wear of a cylindrical surface portion of an inner ring that is in sliding contact with a leading edge of a sealing plate.

FIG. 4 is a partial sectional view showing a second example of the embodiment of the present invention.

FIG. 5 is an enlarged view of a portion B in FIG. 4;

FIG. 6 is a partial cross-sectional view for explaining the reason why a disadvantage occurs in the comparative example.

FIG. 7 is a schematic sectional view showing an example of a transmission.

FIG. 8 shows a conventionally known rolling bearing with a sealing plate.
Half sectional view showing an example.

FIG. 9 is a half sectional view showing a rolling bearing with a sealing plate according to the prior invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Casing 2 Lubricating oil 3 Input shaft 4 Output shaft 5 Transmission shaft 6, 6a Rolling bearing with a sealing plate 7 Drive side gear 8a-8d Driven side gear 9a-9e Transmission gear 10 Idle gear 11 Inner ring raceway 12 Inner ring 13 Outer ring raceway 14, 14a Outer ring 15 Ball 16 Cage 17 Pocket 18 Lock groove 19, 19a Sealing plate 20 Core 21 Elastic material 22 Seal lip 23 Seal groove 24 Inner wall surface 25 Outer wall surface 26 Space 27 Elastic deformation part 28 First seal lip 29 Second Seal lip 30 Cylindrical surface part 31, 31a Shoulder part 32 Protrusion part 33, 33a Sealing plate 34 Engagement groove 35 Inner wall side inner wall part 36 Outer diameter side inner wall part 37 Engagement ridge 38 Seal lip 39 Protrusion part 40 Constriction part

Continued on the front page F-term (reference) 3J016 AA02 BB03 CA01 CA02 CA03 3J063 AA02 AB02 AC03 BB11 CA01 CD03 3J101 AA02 AA32 AA42 AA52 AA62 BA53 BA54 BA56 BA73 CA11 EA32 EA36 EA63 EA76 FA13 FA32 FA35 GA01 GA11

Claims (6)

[Claims] 1. An inner race having an inner raceway at an axially intermediate portion of an outer peripheral surface, an outer race having an outer raceway at an axially intermediate portion of an inner peripheral surface, and rolling freely between the inner raceway and the outer raceway. A plurality of rolling elements provided, and one peripheral edge portion is locked to a part of one of the raceways of the inner ring and the outer ring,
In a rolling bearing with a sealing plate, comprising a sealing plate in which the other peripheral portion slides in contact with a part of the other raceway of the inner ring and the outer ring, the sealing plate is made of synthetic resin. There is a locking recess on the axial end face of the one race,
A rolling bearing with a sealing plate, wherein the bearing ring is provided so as to be substantially concave in the axial direction, and at least a part of one peripheral edge of the sealing plate is locked in the locking recess. 2. The locking recess has a pair of inner wall surfaces facing each other in the radial direction of the outer ring provided with the locking recess, and at least the inner wall surface on the inner diameter side of the pair of inner wall surfaces is formed. The inner ring is inclined in a direction approaching the center axis of the outer ring toward the inner side in the axial direction of the outer ring, and the inner wall surface on the inner diameter side and a part of the peripheral edge of the sealing plate aligned with the inner wall surface on the inner diameter side. A radial interference is provided therebetween, and at least when the sealing plate is in a free state, the inner wall surface on the outer diameter side of the pair of inner wall surfaces is aligned with the inner wall surface on the outer diameter side. The rolling bearing with a sealing plate according to claim 1, wherein a gap is provided between the sealing plate and a peripheral portion of the sealing plate. 3. The sealing plate according to claim 1, further comprising a constricted portion which is recessed inward in the axial direction from the side surface in a circumferential direction at a portion near one peripheral edge on the axially outer surface of the sealing plate. Rolling bearing with sealing plate described in crab. 4. The sealing plate is made of a synthetic resin containing reinforcing fibers covered with a modified synthetic resin.
The rolling bearing with a sealing plate described in any one of the above. 5. A cylindrical surface portion, which is a part of the peripheral surface of the other bearing ring and is parallel to the central axis of the bearing ring constituting the peripheral surface, at least one sealing lip constituting the other peripheral portion of the sealing plate. And a leading edge of the seal lip is slidably contacted with the cylindrical surface over the entire circumference.
5. The rolling bearing with a sealing plate according to any one of items 1 to 4. 6. A casing having lubricating oil stored therein,
An input shaft and an output shaft rotatably supported by rolling bearings in the casing, a drive-side power transmission member supported by the input shaft and rotating with the input shaft, and supported by the output shaft. In the transmission, the rolling bearing includes a driven-side power transmission member that engages with the driving force transmission member so as to transmit power, and rotates together with the output shaft with the rotation of the input shaft. A transmission characterized by the rolling bearing with a sealing plate described in any one of 1 to 5.