JP2003120791A - Rotation support structure for pulley - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve durability by reducing differential temperature between an inner and an outer rings 16 and 15 composing a deep groove type radial ball bearing 14 of a three-point or four-point contact type to reduce reduction quantity of an inner gap due to this differential temperature. SOLUTION: In an outer circumferential surface of a support cylinder part 23 provided on an outer surface of an end part of a casing 2, at two positions apart from each other on both sides in an axial direction of the inner ring 16 composing the radial ball bearing 14, a first and a second heat transmission rings 26 and 27 are engaged and fixed. The first and the second heat transmission rings 26 and 27 are formed of material having a high heat transmission ratio. Parts by the heat transmission rings 26 and 27 close to the outer diameter are set to face a circular member 24 for containing and fixing the outer ring 15 for composing the radial ball bearing 14 and also to face the outer ring 15 closely to them through micro-gaps, respectively.

Description

Description: BACKGROUND OF THE INVENTION [0001] 1. Field of the Invention
The supporting device is, for example, a tie used for an automobile engine.
For adjusting the tension of endless belts such as
Pulley for tensioner or air conditioner for automobile
Driven pulley for driving auxiliary equipment such as a compressor
And these pulleys are fixed
Used to rotatably support minutes. 2. Description of the Related Art Conventionally, it has been used in automobile engines.
Adjust the tension of the endless belt such as the
Use an auto tensioner to
Is used to drive compressors and other auxiliary equipment.
I have. And the pulley used for the above auto tensioner
And rotation support of driven pulleys etc. for driving the above auxiliary equipment
Use rolling bearings on the
It is supported rotatably. [0003] Used in such a pulley rotation support device
Rolling bearings have sufficient durability such as seizure resistance
To the pulley at the same time
A large eccentric load is applied to this pulley from the endless belt
The center of the inner and outer rings that make up the rolling bearing
Prevents shafts from inclining and uneven wear of the endless belt
It is necessary to secure high moment rigidity in order to suppress
It is said. And ensure especially high moment rigidity
The above-mentioned rolling
Use double row ball bearings as bearings, or 3 or 4 points
The use of contact ball bearings has traditionally been
You. For example, FIG. 5 shows an air conditioner for an automobile.
Rotary support of compressor to incorporate and compress refrigerant
Shows a first example of a conventional structure using double-row ball bearings in the section
ing. The rotary shaft 1 of the compressor is provided with a rotary shaft (not shown).
It is rotatably supported in the casing 2 by the ball bearing.
I have. And, provided on the outer surface of the end of the casing 2,
Around the support cylinder 3 corresponding to the support portion described in the claims
The driven pulley 4 is rotated by a double row radial ball bearing 5.
It is freely supported. This driven pulley 4 has a U-shaped cross section.
, And the end of the casing 2
The solenoid 6 fixed to the surface is connected to the inside of the driven pulley 4.
Placed in space. On the other hand, the end of the rotating shaft 1
A mounting bracket 7 is provided on a portion protruding from the casing 2.
Fixed around the mounting bracket 7 made of magnetic material
Is supported via a leaf spring 9. This ring
When the solenoid 6 is not energized, the plate 8
As shown in FIG. 5, the driven pulley 4
But when the solenoid 6 is energized,
The driven pulley 4 is attracted to the driven pulley 4
The transmission of the rotational force from the motor to the rotating shaft 1 is free. Immediately
The solenoid 6, the annular plate 8, the leaf spring 9,
As a result, the driven pulley 4 and the rotary shaft 1 are disengaged.
Of the electromagnetic clutch 10 for the purpose. [0005] With the double-row radial ball bearing 5 as described above,
In the case of a structure in which the driven pulley 4 is rotatably supported,
The endless belt 11 stretched over the driven pulley 4
Even if a slight eccentric load is applied to the dynamic pulley 4,
Center axis and inner ring of outer ring 12 constituting row radial ball bearing 5
It is almost impossible for the central axis of 13 to be misaligned (inclined).
No. Therefore, the durability of the double row radial ball bearing 5 is sufficiently improved.
And the rotation center of the driven pulley 4 is tilted.
To prevent uneven wear of the endless belt 11
it can. However, use of the double row radial ball bearings 5
Accordingly, it is inevitable that the axial dimension increases. Driven
The rotary support of the tool 4 must be installed in a limited space.
It is often necessary to increase the axial dimension
Absent. Moreover, as the axial dimension increases, each component
Cost increases. [0006] Rolling shaft for supporting the driven pulley 4
In place of the double row radial ball bearing 5 as described above,
The axial dimension can be reduced by using a row deep groove type radial ball bearing.
It is easier to install in a limited space by shortening. However,
For general, simple single row deep groove radial ball bearings
When the driven pulley 4 receives a moment load
The proof stress in the direction for preventing the inclination of the driven pulley 4, that is,
Low rigidity and constitutes the above radial ball bearing
The degree to which the center axis of the outer ring and the center axis of the
It becomes difficult. As a result, the durability of the above radial ball bearings is
Not only will it be sufficient, but it will be
The endless belt 11 is apt to undergo significant uneven wear. In view of such circumstances, the driven pulley is supported.
Use single row, four point contact type radial ball bearings.
For example, Japanese Unexamined Patent Publication No. 9-119510, 11
As described in JP-A-333695,
It is considered. FIGS. 6 and 7 show Japanese Patent Application Laid-Open No. 9-1.
19 shows a second example of the conventional structure described in Japanese Patent Publication No. 19510.
are doing. In the second example of this conventional structure, a metal plate
Driven pulley 4a formed by bending such as
By a single row, four-point contact type radial ball bearing 14
It is rotatably supported around a support portion not shown. This
Radial ball bearings 14 are outer rings supported concentrically with each other.
15 and inner ring 16, and a plurality of balls 17, 17
You. Outer ring raceway 18 is provided on the inner peripheral surface of outer ring 15,
An inner raceway 19 is provided on the outer peripheral surface of the inner race 16 on the entire circumference.
It is formed over. Cross section of each of these tracks 18 and 19
The shape of each ball is smaller than 1/2 of the diameter of each ball 17, 17
Arcs with large radii of curvature intersect at the middle
It is a so-called Gothic arch. Therefore, each of the above trajectories
18, 19 and the rolling surfaces of the balls 17, 17 are respectively
2 points each, each ball 17, 17 for a total of 4 points
Contact. Such a four-point contact type radial ball bearing 14
Is more compact than common single row deep groove radial ball bearings.
High rigidity against load
Even in the case of radiating, between the center axis of the outer ring 15 and the inner ring 16
The center axis is hardly displaced. For this reason, as shown in FIG.
A common single-row deep-groove radial on the support of the moving pulley 4a
When the ball bearing 14a is used, the driven pulley 4a
The driven pulley 4a tilts under a moment load.
Can be suppressed. Therefore, a general single row deep groove type
Rotary support for compressor pulleys using dial ball bearings
Hooking on the driven pulley 4a compared to the case where a holding device is configured.
The uneven wear generated in the passed endless belt 11 can be reduced.
The general single row deep groove type radial ball bearing shown in FIG.
14a is a roll of each ball 17, 17 on the inner peripheral surface of the outer ring 15a.
An arc-shaped section with a single curvature that contacts the moving surface at one point
The outer raceway 18a of each of the above-mentioned balls is attached to the outer peripheral surface of the inner race 16a.
Single point of contact with the rolling surface of 17, 17 at one point, single curvature
And forming the arc-shaped inner raceway 19a having
I have. Also, JP-A-11-33695 discloses that
The above-mentioned rotation support part of the driven pulley for driving the compressor
Such as a four-point contact type radial ball bearing
An electromagnetic clutch is placed between the driven pulley and the rotary shaft of the compressor.
A structure provided with a switch is described. [0010] Further, as shown in FIG.
The ball bearing 14b is also a common single row deep groove type radial ball shaft.
Rigidity against moment load is greater than
The center axis of the outer ring 15 and the inner ring 1
6a is less likely to deviate from the central axis. This three-point contact ball
A bearing 14b is provided on the outer peripheral surface of the inner ring 16a.
A circular arc having a single curvature in cross section that contacts the rolling surface at one point
The inner raceway 19a is formed on the inner peripheral surface of the outer race 15 as described above.
Same as the four-point contact type radial ball bearing 14 shown in FIGS.
As described above, the ball 17 comes into contact with the rolling surface of each ball 17 at two points.
Arch-shaped outer raceways 18 are formed respectively.
Pulleys using such three-point contact type ball bearings 14b
Even in the case of a rotary support device, a common single row deep groove type
Compared to the case of pulley rotation support device using ball bearings
Endless belt 11 (see FIG. 5)
(See Ref.) Can be alleviated. Described in FIG.
Contrary to the structure, the rolling surface of each ball and the outer ring raceway are one point each
And the inner ring raceway has 2 points each
The same applies to the case of a contact type ball bearing. [0011] The driven pulley as described above.
Radial ball bearings 5, 1 used to support the ribs 4a
4, 14b (especially three- or four-point contact type ball bearings 14, 1
4b) is the size of the internal gap (effective gap) during use
However, the calorific value of the ball bearings 5, 14, and 14b,
Ball bearings 5, 14, and 14b for durability such as seizure resistance
It has a significant effect. The ball bearings 5, 14, 1
4b, the size of the internal gap when using this ball bearing 5,
Inner rings 13, 16, 16 a and outer which constitute 14, 14 b
Fitting and use of the rings 12, 15 with other members
Ambient temperature (ambient temperature) at the time of use and
Between the inner rings 13, 16, 16a and the outer rings 12, 15
Significantly affected by temperature differences. The main items affected by the internal clearance are as follows.
The inner rings 13, 16, 16a and the outer rings 12, 15
For the fitting and ambient temperature during use, see above
Even before the assembly to the driven pulley 4a,
It is easy to predict the value in the state. For this reason, the stage before this assembly
Due to the influence of the above fitting and ambient temperature from the floor,
By designing in consideration of the amount of change in the gap between parts,
It is relatively difficult to make the size of the internal gap close to the desired value.
Not easy. However, the main items affected by this internal clearance
Of the inner rings 13, 16, 16 in actual use
to accurately predict the temperature difference between a and the outer rings 12 and 15
Is difficult, so the internal gap changes due to this temperature difference
It is difficult to design for quantity. For this reason,
The size of the internal gap above is a matter that is difficult to predict.
The inner and outer wheels 13, 16, 16 in this use state.
a, due to the effect of the temperature difference between
It easily shifts with respect to the value. In particular, the pulley rotation support section as described above
When using the ball bearings 5, 14, 14b, the ball bearings
Inner rings 13, 16, 16b constituting 5, 14, 14b;
Of the outer rings 12, 15, the inner rings 13, 16, 16b are:
Heat such as cylinder block of engine and casing of auxiliary equipment
It is fixed on the side of the fixed part that is the source. On the contrary,
The outer rings 12 and 15 are formed of the inner rings 13, 16 and 16 b.
It is supported around a plurality of balls 17, 17. This
Therefore, during use, the temperature of the inner rings 13, 16, 16b
Is likely to be higher than the temperature of the outer rings 12 and 15,
These inner and outer wheels 13, 16, 16b, 12, 15
The temperature difference between them tends to be large. Therefore, in use condition
The internal clearances of the ball bearings 5, 14, and 14b correspond to the temperature difference.
, It tends to be smaller than the desired value. Like this
If the internal clearance becomes smaller, the ball bearings 5, 1
The calorific value of 4, 14b increases, and this ball axis
There is a possibility that seizure may occur on the receivers 5, 14, 14b early.
is there. [0014] In view of such circumstances, the inventor of the present invention.
Is the size of the internal clearance of the ball bearing
The effect on the temperature was confirmed by experiments. Next, this experiment
Will be explained. In this experiment, the slave shown in FIGS.
Using the four-point contact type radial ball bearing 14 of the second example of the conventional structure.
And three types of internal clearance (-48 μm, -35 μm,-
5 μm) and 8000 Nm of momentum
While the outer ring is 10,000 min. ^-1 Rotated in
The bearing life was confirmed. FIG. 10 shows the results of this experiment.
Is shown. The vertical axis in FIG. 10 indicates that the internal gap is -3.
Radius of 5 μm (-indicates a negative gap)
Bearing of each ball bearing 14 against the bearing life of the ball bearing 14
It represents the life ratio (life ratio). Experiment shown in FIG.
As is clear from the results, the internal clearance of the radial ball bearing 14
Becomes smaller (the negative absolute value becomes larger), the bearing life
Are shorter and the radial ball bearings 5, 14, 14b (FIGS.
In order to ensure a sufficient bearing life in 7, 9),
Sufficiently suppress the internal clearance from becoming smaller than the desired value
Need to be However, as described above,
Partial clearances constitute the radial ball bearings 5, 14, and 14b.
And the temperature between the outer wheels 13, 16, 16a, 12, 15
Due to the influence of the difference, it tends to be smaller than the desired value.
Also, it is necessary to make the internal clearance too large before the temperature rise.
It is not preferable from the viewpoint of securing the required moment rigidity.
No. In view of such circumstances, the present invention has
By reducing the temperature difference between the wheel and outer ring,
During use, this temperature difference reduces the internal clearance of the rolling bearing
Invented to improve durability
is there. SUMMARY OF THE INVENTION A rotary support for a pulley according to the present invention.
The holding device is a pulley of a conventionally known pulley as described above.
As with the rotary support device, a fixed support section and this fixed
The rolling bearing supported by the supporting part and the rolling bearing
Endlessly supported rotatably around this support part
And a pulley for hanging the belt. In particular, in the pulley rotation supporting device of the present invention,
High heat conduction supported by a part of the support part
A heat transfer member made of a material having a high rate is provided. And this biography
A part of the heat member was fixedly fitted with the outer ring or the outer ring.
It is close to the member. Preferably, the rolling is
Contact the outer peripheral surface with the ball rolling surface at one or two points.
Inner ring with inner ring raceway of different shape and ball rolling surface on inner peripheral surface
Outer ring having an outer ring raceway of a shape that makes contact at one or two points with the outer ring
Between the inner raceway and the outer raceway
The inner ring raceway and the outer ring raceway
And the rolling surface of each of these balls
3 or 4 point contact type where each contacts at 2 points
Radial ball bearing. The rotation support of the pulley of the present invention constructed as described above.
In the case of equipment, the temperature difference between the inner and outer rings in use
Can be kept small, so the rolling bearing
Partial clearance (effective clearance) decreases due to this temperature difference
Can be suppressed. As a result, the calorific value of the rolling bearing
Increase of durability and improvement of durability such as seizure resistance
You. Also, this rolling bearing has a three-point or four-point contact type
When ball bearings are used,
It is possible to use a single row of rolling bearings while ensuring sufficient rigidity.
To reduce the size of the entire device and reduce costs
it can. 1 and 2 show an embodiment of the present invention.
1 shows a first example. Pulley rotation support device of this example
Drives rotary compressors for automotive air conditioners
Pulley 4b for rotating the casing 2
We support now. Also, in the case of this example, as shown in FIG.
Unlike the first example of the conventional structure,
I haven't. That is, in the case of this example, the inside of the casing 2
Side, the rotating shaft 20 is rotated by a rolling bearing (not shown).
We support now. The end of the rotating shaft 20 is
At the same time, fix the outer part of the racket 21
Of the bracket 21 closer to the outer diameter of the driven pulley 4b
Excessive torque was applied to one side (left side of FIGS. 1 and 2)
Only through a torque fuse that spins when
(Without going through the clutch). The driven pulley 4b is connected to the casing
Corresponding to the supporting portion described in the claims provided at the end of the bush 2
A single row deep groove type and a four-point contact type
It is rotatably supported by a radial ball bearing 14. Immediately
The radial ball bearing 14 is shown in FIGS.
Configuration similar to that incorporated in the second example of the conventional structure
Outer ring 15 having an outer ring raceway 18 formed on the inner peripheral surface.
An inner ring 16 having an inner ring track 19 formed on the outer peripheral surface;
Rollably installed between the inner raceway 19 and the outer raceway 18
A plurality of balls 17 are provided. And each of the above
The cross-sectional shapes of the orbits 18 and 19 are respectively set to the respective balls 17 and
Arc having a radius of curvature greater than half the diameter of 17
A so-called Gothic arch shape where they cross at the middle part
ing. Accordingly, each of the orbits 18 and 19 and each of the balls 1
The rolling surfaces 7 and 17 are two points each,
Contact is made at a total of four points every 17, 17. The inner peripheral surface of the driven pulley 4b is
The outer ring 15 is internally fitted to the inner peripheral surface of the fitted and fixed annular member 24.
While being fixed, one side portion of the outer peripheral surface of the support cylindrical portion 23
(The left part of FIGS. 1 and 2)
The ring 16 is externally fitted and fixed. The axial direction of the inner ring 16
The one end face (the right end face in FIGS. 1 and 2) is
Large-diameter portion 37 provided at the other end (right end in FIGS. 1 and 2) of the peripheral surface
Abuts on a step surface 38 which is a continuous portion of the
I am. In particular, in the case of the present invention, the radial ball
On both axial sides of the bearing 14, each is a heat transfer member,
A first heat transfer ring 26 and a second heat transfer ring 27 are provided.
You. Each of these heat transfer rings 26 and 27 is made of copper or a combination thereof.
Metal materials with high thermal conductivity, such as gold and aluminum alloys
Made from the material, the cross section is almost U-shaped and the whole is circular
Has formed. These first and second heat transfer rings 26, 2
7, the radial direction of the ring portions 28a and 28b provided at the radially intermediate portion.
The direction lengths are different from each other. And these second
The radial length of the first and second heat transfer rings 26 and 27 is
Of the first heat transfer ring 26 having a large circular portion 28a
The inner cylindrical portion 29 provided on the peripheral portion is attached to the outside of the support cylindrical portion 23.
A part of the inner ring 13a is a part of the small diameter portion 36 provided on the peripheral surface.
Side (left side in FIGS. 1 and 2).
You. Also, in order to prevent the axial displacement of the inner ring 13a,
Of the retaining ring 30 locked on a part of the outer peripheral surface of the small diameter portion 36
The first heat transfer ring 2 is provided on one side (the left side in FIGS. 1 and 2).
6, the axial end surface of the inner cylindrical portion 29 provided in
You. The first heat transfer ring 26 is provided on the outer peripheral edge.
The axial end face of the outer cylindrical portion 31 is
Direction one end face (left end face in FIGS. 1 and 2) through a small gap
They are close to each other. On the other hand, the first and second heat transfer rings 26,
27 has a ring portion 28b having a small radial length.
Inner cylindrical portion 3 provided on the inner peripheral edge of second heat transfer ring 27
3 is a large-diameter portion 37 provided on the outer peripheral surface of the support cylindrical portion 23.
Partially fixed to the portion adjacent to the step surface 38 by external fitting
I have. Then, one end surface in the axial direction of the outer ring 12a (FIG. 1,
2 at the outer peripheral edge of the second heat transfer ring 27.
The axial end surface of the outer cylindrical portion 35 is
This outer cylinder is attached to the inner peripheral surface of the other end in the axial direction (the right end in FIGS. 1 and 2).
The outer peripheral surface of the portion 35 is closely opposed to each other via a minute gap.
Let me. The rotating support of the pulley of the present embodiment configured as described above
In the case of a holding device, the radial ball bearings 14 are in a single row.
Therefore, the axial dimension is reduced, and the overall compressor size is reduced.
And cost reduction. Four-point contact with rolling bearing
Since the radial ball bearing 14 is used, the moment
Sufficient rigidity against load can be secured. Moreover, the present invention
In the case of the inner ring 1 constituting the radial ball bearing 14,
6 is a part of the outer peripheral surface of the support cylinder 23 to which the outer tube 6 is fixed.
In the vicinity of the inner ring 16, first and second heat transfer rings 26,
The inner cylindrical portions 29 and 33 provided on the inner peripheral edge of the outer tube 27 are externally fitted and fixed.
are doing. Furthermore, these first and second heat transfer rings 26,
The outer cylindrical portions 31 and 35 provided on the outer peripheral edge of the
A ring in which an outer ring 15 constituting a dial ball bearing 14 is fitted and fixed.
Through the minute member 24 and the outer ring 15
And close to each other. Therefore, when used, the inner ring
16 or from the supporting cylinder 23 to which the inner race 16 is fixed.
Outer tubular portion 3 provided on first and second heat transfer rings 26 and 27
The heat transmitted to the annular member 32 and the outer ring 1
5, which is quickly transmitted by radiation. Moreover, the present invention
In the case of the first and second heat transfer rings 26, 27
Is made of a material having high thermal conductivity. this
For this reason, the first and second rings are separated from the inner ring 16 and the support cylinder 23.
The heat is transmitted to the inner cylindrical portions 29, 33 of the heat transfer rings 26, 27.
The heat generated outside the first and second heat transfer rings 26 and 27
It is easy to transmit to the cylinder parts 31 and 35. In addition, these first and second
The heat transmitted to each heat transfer ring 26, 27
The air existing near each of the heat transfer rings 26 and 27 is heated.
The heat transmitted to each of these heat transfer rings 26 and 27
Is more efficiently transmitted to the inner ring 16 and the support cylinder 23.
Is reached. Therefore, the inner ring 16 and the outer ring in use are in use.
15 can be used to reduce the temperature difference between
Internal clearance (effective clearance) of the radial ball bearing 14 in the state
However, it is possible to suppress the decrease due to the effect of this temperature difference.
Wear. As a result, in the case of the present invention,
The size of the internal clearance is determined by fitting the inner ring 16 and the outer ring 15
And the amount that changes due to the influence of the ambient temperature during use
It is easy to regulate to the desired value only by designing with anticipation,
While securing rigidity against moment load,
The increase in the calorific value of the ball bearing 14 is suppressed, and the seizure resistance etc.
Can be improved in durability. FIG. 3 shows a second embodiment of the present invention.
An example is shown. In the case of this example, the case of the first example described above is used.
Unlike the case, the compressor has an electromagnetic clutch 39
By the operation / non-operation of the electromagnetic clutch 39, the rotation
The shaft 20 and the driven pulley 4c can be freely engaged and disengaged. This
For this reason, in the case of this example,
The part protruding from the sing 2 is close to the inner diameter of the bracket 40.
The small-diameter cylindrical portion 41 provided at the rim portion is externally fitted and fixed. Soshi
A large-diameter cylinder provided near the outer diameter of the bracket 40
The outer side of the portion 42 and one side in the axial direction (the right side in FIG. 4)
A cylindrical member 44 and an annular plate 45 made of a magnetic material via a material 43
Are combined. The casing 2 is provided on the outer surface at the end.
The outer peripheral surface of the support tube portion 23, which is a fixed support portion, is driven
The inside is fixed inside the pulley 4c, the cross section is U-shaped and the whole
Is provided at a portion near the inner diameter of the annular member 46 formed in an annular shape.
Between the inner peripheral surface of the inner diameter side cylindrical portion 47 and the first example described above.
Single-row, deep-groove, four-point-contact radial ball spindle
A receiver 14 is provided. And the end face of the casing 2
The solenoid 6 fixed to the annular member 46
It is located between them. On one side of the bracket 40 in the axial direction
The connected annular plate 45 does not communicate with the solenoid 6.
At the time of electrification, as shown in FIG.
At a distance from the annular member 46,
When power is supplied to the node 6, it is attracted toward the annular member 46.
And the rotational force from the driven pulley 4c to the rotary shaft 20
Transmission of information. That is, in the case of this example,
In the case of the solenoid 6, the annular member 46, the annular plate 45, and the elastic member 43,
In order to disengage the driven pulley 4c and the rotating shaft 20,
Of the electromagnetic clutch 39. In the case of this embodiment, the casing
2, a part of the outer peripheral surface of the support cylinder portion 23 provided on the outer surface of the end portion,
The axial direction of the inner ring 16 constituting the radial ball bearing 14
The first and second heat transfer rings 2 are located at two locations
Inner cylindrical portions 29 and 33 provided on the inner peripheral edges of 6, 27 are externally fitted.
It is fixed. In addition, outside of these heat transfer rings 26 and 27,
The axial end faces of the outer cylindrical portions 31 and 35 provided on the peripheral edge
Both ends in the axial direction of the outer ring 15 constituting the radial ball bearing 14
The surface is closely opposed via a minute gap. Furthermore, on
The outer peripheral surfaces of the outer cylindrical portions 31 and 35 are
inner diameter side cylindrical portion 47 provided on an annular member 46 internally fitted and fixed to
At two places on the inner peripheral surface of the outer ring 15 on both sides in the axial direction.
The position is closely opposed via a minute gap. In the case of this embodiment as well, the first example
As in the case of the above, the radial ball bearing 14
Temperature difference between the inner ring 16 and the outer ring 15 constituting
The internal clearance of this radial ball bearing 14
To prevent the distance from decreasing due to the effect of this temperature difference.
Performance can be improved. For other configurations and actions,
Since it is the same as the case of the first example described above,
The same reference numerals are given and duplicate descriptions are omitted. Next, FIG. 4 shows a third embodiment of the present invention.
An example is shown. In the case of this example, used in each of the above examples
Single-row deep groove radial ball bearings 14 (see FIGS.
), Instead of incorporating a double row radial ball bearing 5a
I have. This double row radial ball bearing 5a has a pair of inner circumferential surfaces.
Outer ring 12a having outer ring raceways 18a, 18a, and outer peripheral surface
Inner ring 13a having a pair of inner ring raceways 19a, 19a
And each of these inner raceways 19a, 19a and each of the above outer raceways
18a, 18a, each of which can roll freely
The ball 17 is provided. And each outer ring gauge
Roads 18a, 18a and each inner raceway 19a, 19a,
The rolling surfaces of the balls 17, 17 are in contact with each other at one point.
I try to touch it. In the case of this example, the ball 1
Since the rows 7 and 17 are arranged in multiple rows,
The overall axial dimension of the compressor is larger than in the case of
Higher moment stiffness than the first example
Can be For other configurations and operations, see FIG.
Since it is the same as the case of the first example shown in FIGS.
Are denoted by the same reference numerals, and overlapping description will be omitted. Next, in order to confirm the effects of the present invention,
An experiment performed by the inventor will be described. This experiment
The present invention has the structure of the first example shown in FIGS.
The first and second heat transfer rings with the light product and the structure of this first example
This was performed using a comparative example in which 26 and 27 were omitted. Soshi
To form the rotation support portion of the driven pulley for the compressor
The inner ring of the rolling bearing is heated to 160 ° C and
° C and the temperature around the rolling bearing (ambient).
Radial ball bearings with different ambient temperatures)
The temperature difference between the inner ring 16 and the outer ring 15 is measured.
Was. Tables 1 and 2 below show the results of experiments performed in this way.
Is shown. Table 1 shows the experimental results of the comparative examples.
Table 2 shows the experimental results of the product of the present invention. [Table 1] [Table 2] The experimental results shown in Tables 1 and 2 clearly show the results.
As in the case of the present invention, in the case of the present invention, the first and second heat transfer rings
In comparison with the comparative example in which 26 and 27 are not used,
Temperature difference between the inner ring 16 and the outer ring 15 in the state
Can be obtained. In each of the above examples, the radial ball bearing 1
4 or double row radial ball bearing 5a
The first and second heat transfer rings 26 and 2 are heat transfer members.
7 has been described. However, the present invention
The structure is not limited to the one shown in
A heat transfer member may be provided only on one side. However,
Temperature between the inner and outer wheels of a rolling bearing
From the viewpoint of minimizing the difference, the axial
It is preferable to provide a pair of heat transfer members on the side. Also,
The first and second examples shown in FIGS.
Although the case of the four-point contact type has been described, the present invention
When the rolling bearing is a three-point contact type radial ball bearing
Can also be implemented. The pulley rotation supporting device of the present invention
As described in the above section, the configuration
Structure that can ensure sufficient rigidity and rolling in use
The size of the internal clearance of the bearing can be easily regulated to a desired value,
Improve durability such as seizure resistance by suppressing the increase in heat
I can do it.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial sectional view showing a first example of an embodiment of the present invention. FIG. 2 is an enlarged sectional view of a portion A in FIG. FIG. 3 is a partial cross-sectional view showing a second example of the embodiment of the present invention. FIG. 4 is a partial sectional view showing a third example. FIG. 5 is a partial cross-sectional view showing a first example of a conventional structure for supporting a driven pulley for a compressor provided with an electromagnetic clutch. FIG. 6 is a cross-sectional view showing a second example of the conventional structure with a part thereof omitted. FIG. 7 is an enlarged half sectional view of FIG. 6 showing only a ball bearing. FIG. 8 is a cross-sectional view for explaining a problem that occurs when a general deep groove type structure is used for a ball bearing. FIG. 9 is a half sectional view showing a third example of the conventional structure. FIG. 10 is a diagram showing the results of an experiment performed to confirm the effect of the size of the internal gap on the bearing life. DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Casing 3 Supporting cylinder 4, 4a, 4b, 4c Followed pulley 5, 5a Double row radial ball bearing 6 Solenoid 7 Mounting bracket 8 Annular plate 9 Leaf spring 10 Electromagnetic clutch 11 Endless belt 12, 12a Outer ring 13, 13a Inner ring 14, 14a, 14b Radial ball bearing 15, 15a Outer ring 16, 16a Inner ring 17 Ball 18, 18a Outer ring raceway 19, 19a Inner ring raceway 20 Rotating shaft 21 Bracket 23 Supporting cylinder portion 24 Ring member 26 First transmission Heat ring 27 Second heat transfer rings 28a, 28b Circular ring part 29 Inner cylinder part 30 Retaining ring 31 Outer cylinder part 33 Inner cylinder part 35 Outer cylinder part 36 Small diameter part 37 Large diameter part 38 Step surface 39 Electromagnetic clutch 40 Bracket 41 Small diameter Tube portion 42 Large-diameter tube portion 43 Elastic material 44 Tube member 45 Ring plate 46 Ring member 47 Diameter side tube portion

Claims (1)

Claims 1. A fixed support portion, a rolling bearing supported by the fixed support portion, and an endless belt rotatably supported by the rolling bearing around the support portion. In a pulley rotation support device having a pulley for bridging, a heat transfer member made of a material having a high thermal conductivity supported by a part of the support portion is provided. A pulley rotating support device, wherein the portion is brought close to and opposed to the outer ring or a member to which the outer ring is fixed.