JP2004190763A - Rotary supporting device for pulley - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To materialize long life by standing high vibrations and high load derived from the high velocity revolution while achieving remarkable miniaturization by reducing width dimensions of a bearing without reducing the diameter of a spherical rolling element. <P>SOLUTION: An inner ring raceway 11a and an outer ring raceway 12a on one row, and an inner ring raceway 11b and an outer ring raceway 12b on the other row, are formed to be contacted with each other in the center part so that a spherical rolling element 13a on one row is inserted in a rolling space for a spherical rolling element 13b on the other row. The spherical rolling element 13a on one row and the spherical rolling element 13b on the other row are mutually overlapped when being seen from the radial direction of the bearing 15. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention provides, for example, a rotary support for a pulley, which is used to rotatably support a driven pulley for rotationally driving the compressor on a fixed portion such as a housing constituting a compressor for an air conditioner for an automobile. Equipment related.
[0002]
[Prior art]
There are various types of auxiliary equipment driven by engines in automobiles.One of them is a compressor of an air conditioner. An endless belt is hung between a driven pulley provided at the end of the rotating shaft and a driving pulley of the engine to make the compressor. Is working.
[0003]
FIG. 3 is a cross-sectional view of a rotation supporting portion of a compressor for an air conditioner of an automobile, showing a first conventional example of the structure. FIG. 4 is a sectional view of only a bearing used for a rotation supporting portion of the compressor shown in FIG.
[0004]
In the illustrated conventional example, a driven pulley 4 having a U-shaped cross section is supported via a bearing 14 on the outer periphery of a support shaft 7 (mounting bracket) protruding from an end casing 2 of the compressor. A solenoid 6 fixed to the end casing 2 side is disposed in the space having the U-shaped cross section, and a magnetic material is disposed at a position opposed to the solenoid 6 with the annular wall 5 of the driven pulley 4 interposed therebetween. An annular plate 16 is disposed.
[0005]
As the bearing 14 for a vehicle compressor pulley, a bearing having an outer diameter of 65 mm or less is generally used, and a sealed bearing that seals grease is used.
[0006]
The end casing 2 is made of an aluminum alloy to reduce the weight. Therefore, the support shaft 7 (mounting bracket) on which the inner ring of the bearing 14 is fitted is made of an aluminum alloy.
[0007]
In the electromagnetic clutch shown in FIG. 3, when the solenoid 6 is not energized, the annular plate 16 is separated from the annular wall 5 of the driven pulley 4 as shown, and the driven pulley 4 is rotated by an endless belt. If so, the annular plate 16 will not rotate, and thus the compressor will not operate.
[0008]
On the other hand, when the solenoid 6 is energized, the annular plate 16 made of a magnetic material is attracted by its magnetic force and pressed against the annular wall 5 of the driven pulley 4. As a result, the electromagnetic clutch is brought into the coupled state, and when the driven pulley 4 rotates, the annular plate 16 also rotates integrally, so that the rotational force can be freely transmitted to the leaf spring 8, the mounting bracket 7, and the rotating shaft 1. That is, the solenoid 6, the annular plate 16, and the leaf spring 8 constitute an electromagnetic clutch for engaging and disengaging the driven pulley 4 and the rotary shaft 1.
[0009]
In the case of the rotation supporting device of the driven pulley 4 for the compressor as described above, the arrangement of the constituent members is limited because the device is required to be installed in a limited space. Therefore, the center position in the width direction of the portion of the outer peripheral surface of the driven pulley 4 which contacts the endless belt is positioned with respect to the center position in the width direction of the inner raceway and the outer raceway constituting the double row angular contact ball bearing 14. 4 (offset) in the axial direction. When the center positions in both width directions are displaced in this way, a moment load proportional to the length (offset amount) between the center positions in both width directions is applied to the double-row angular contact from the endless belt via the driven pulley 4. Joins the ball bearing 14. For this reason, the center axis of the outer ring constituting the double row angular contact ball bearing 14 is inclined with respect to the center axis of the inner ring, and the rotation center of the driven pulley 4 is easily inclined.
[0010]
When the rotation center of the driven pulley 4 is inclined in this manner, the endless belt wrapped around the outer peripheral surface of the driven pulley 4 is unevenly worn, and the durability of the endless belt is reduced. In addition, when the driven pulley 4 is inclined, it is not possible to regulate a dimension relating to a gap between the annular plate 16 and the driven pulley 4 to a desired value. In many cases, the rotation support portion of the driven pulley 4 must be installed in a limited space, and the magnetic force of the solenoid 6 is also limited. Therefore, it is difficult to set the dimension related to the gap large. For this reason, even when the center axis of the inner ring is slightly inclined with respect to the center axis of the outer ring, the annular plate 16 and the driven pulley 4 may rub against each other. When these members rub against each other in this manner, it is not preferable because these members cause abnormal wear and generation of abnormal noise.
[0011]
FIG. 5 is a partial cross-sectional view of a rotary support of an air conditioner compressor of an automobile, showing a second conventional example of the structure.
[0012]
Although the specific structure of the compressor is not shown in FIG. 5, the compressor is generally known as a continuously variable displacement type, and the stroke of the reciprocating piston is changed by changing the inclination angle of the swash plate of the piston drive mechanism. The compressor displacement is continuously varied between 0% and 100%. By using such a continuously variable displacement type compressor, there is no need to equip the compressor with an electromagnetic clutch for interrupting the transmission of power. An overload torque limiter mechanism having a torque fluctuation absorbing function is provided between the pulley and the rotary shaft of the compressor.
[0013]
Also in such a clutchless type, similarly to the above-mentioned electromagnetic clutch type, due to restrictions on the arrangement of the constituent members, etc., the widthwise center position of the endless belt to be wound around the outer peripheral surface of the driven pulley 4, An offset may occur between the inner raceway 11 and the center position in the width direction of the outer raceway 12 of the single-row radial ball bearing 19 for the compressor pulley, and the moment load proportional to the amount of the offset may be reduced by the single-row for the compressor pulley. In addition to the radial ball bearing 19, the center axis of the outer ring constituting the single row radial ball bearing for the compressor pulley is inclined with respect to the center axis of the inner ring, so that the rotation center of the driven pulley 4 is easily inclined. When the rotation center of the driven pulley 4 is inclined in this manner, the endless belt wrapped around the outer peripheral surface of the driven pulley 4 is unevenly worn, making it difficult to maintain the durability of the endless belt. In addition, since the rotation supporting portion of the driven pulley 4 is set in a limited space, the gap between each member is set small, and there is a possibility that the driven pulley 4 and another member may rub against each other. As described above, such rubbing is not preferable because it causes abnormal wear and abnormal noise.
[0014]
As described above, in the rotary support device for pulleys, since the moment load from the pulley acts on the bearing in addition to the radial load, the bearing may be inclined. In one conventional example, a double-row angular contact ball bearing 14 is used to prevent the bearing 14 from tilting.
[0015]
In recent years, as automobiles have become smaller and lighter, engine supplements have been required to be smaller and lighter and have higher performance and higher output. Therefore, for example, there is an increasing demand for increasing the tension of a belt that is wound around a pulley fixed to the tip of a rotating shaft 1 of a compressor, and rotating the rotating shaft at a higher speed. When the rotary shaft 1 is rotated under such conditions, the double-row angular contact ball bearing 14 supporting the rotary shaft receives high vibration and high load due to high speed rotation via the belt simultaneously with the operation of the engine. Act.
[0016]
In addition, due to the structure of engine accessories such as a compressor, the size and weight of the engine accessories such as a compressor are required to be reduced in size. However, simply reducing the size of the bearing reduces the rated load of the bearing. Therefore, when high vibration and a high load are applied, the life of the bearing is quickly reached.
[0017]
As described above, when the moment load from the pulley acts on the bearing in addition to the radial load, it is possible to sufficiently prevent the bearing from tilting when the bearing may be tilted. There is a demand to extend the life so as to withstand the high vibration and the high load accompanying the vibration.
[0018]
In Patent Literature 1, a normal double row angular contact ball bearing is used as a countermeasure in a case where a bearing is inclined by a moment load from a pulley in addition to a radial load.
[0019]
Further, in Patent Document 2, in addition to coping with the case where the bearing is inclined due to the moment load from the pulley acting in addition to the radial load, in order to reduce the size of the bearing, a three-point contact with a small axial displacement is used. Single row ball bearings are used.
[0020]
Further, in Patent Document 3, a single-row ball bearing of four-point contact is used for the same purpose.
[0021]
[Patent Document 1]
JP-A-9-42411 [Patent Document 2]
Japanese Patent Application Laid-Open No. 2000-120668 [Patent Document 3]
Japanese Patent Application Laid-Open No. H11-333695
[Problems to be solved by the invention]
However, in Patent Literature 1, a normal double-row angular contact ball bearing is used, but the dimension in the axial direction becomes large, and there is a problem that miniaturization cannot be achieved.
[0023]
According to Patent Document 2, a three-point contact single-row ball bearing is configured such that when a load is applied, the spherical rolling element revolves around an axis and rotates (spins) in a direction different from that of the axis. There is an inconvenience that the moving body causes a large slip with respect to the inner and outer wheel rolling surfaces.
[0024]
Further, in Patent Document 3, for the same purpose, a single-row ball bearing of four-point contact is used, but similarly, there is a disadvantage that a large slip occurs.
[0025]
SUMMARY OF THE INVENTION The present invention has been made in view of the above-described circumstances, and reduces the width of a bearing without reducing the diameter of a spherical rolling element. An object of the present invention is to provide a rotation support device for pulleys, which can achieve a long life so as to withstand high vibration and high load associated with the rotation.
[0026]
[Means for Solving the Problems]
In order to achieve the above object, the rotation support device for a pulley according to the present invention includes a fixed support portion,
An inner ring supported by the support portion and having two rows of deep groove inner ring raceways on the outer peripheral surface, an outer ring having two rows of deep groove type outer ring raceways on the inner peripheral surface, and these two rows of inner ring raceways and two rows of A double-row deep-groove angular ball bearing comprising two rows of a plurality of spherical rolling elements each rotatably interposed between the outer ring raceway;
A pulley rotatably supported by the double-row deep groove type angular contact ball bearing, and a pulley for hanging an endless belt;
The inner raceway and the outer raceway in one row and the inner raceway and the outer raceway in the other row are arranged such that, in a central portion thereof, the spherical rolling elements of one row are used for the spherical rolling elements of the other row. It is characterized by being formed in contact with each other so as to enter the movement space.
[0027]
As described above, according to the present invention, the inner raceway and the outer raceway in one row and the inner raceway and the outer raceway in the other row are formed such that the spherical rolling elements in one row are in the other row in the central portion thereof. Are formed in contact with each other so as to enter the rolling space for the spherical rolling element.
[0028]
That is, the spherical rolling elements in one row and the spherical rolling elements in the other row overlap each other when viewed from the radial direction of the bearing (see FIGS. 1 and 2). The width of the bearing can be reduced.
[0029]
Also, in this case, the diameter of the spherical rolling element is the same as the conventional one and is not reduced, so that the same rated load as the conventional bearing can be expected, and it can withstand high load etc. sufficiently. And durability can be remarkably improved.
[0030]
Therefore, according to the present invention, it is possible to reduce the width of the bearing without reducing the diameter of the spherical rolling element (without shortening the service life). It is also possible to extend the service life to withstand the high vibration and high load accompanying the above.
[0031]
In addition, since the bearing that rotatably supports the rotating shaft of the engine accessories on the housing is a double-row angular contact ball bearing, in addition to the radial load, the moment load from the pulley acts on the bearing to incline. Even when there is a fear, it is possible to sufficiently prevent the inclination of the bearing. That is, according to the present invention, it is possible to cope with the moment load from the pulley and to eliminate the possibility of the bearing being tilted, although the size is significantly reduced.
[0032]
As described above, the durability of the pulley rotation support device can be improved while the pulley rotation support device has a compact structure.
[0033]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a rotation support device for a pulley according to an embodiment of the present invention will be described with reference to the drawings.
[0034]
FIG. 1 is a sectional view of a pulley rotation support device according to an embodiment of the present invention. 2A is a cross-sectional view of a bearing used in the pulley rotation support device shown in FIG. 1, and FIG. 2B is an arrow view along line bb in FIG.
[0035]
As shown in FIG. 1, a driven pulley 4 having a U-shaped cross section is supported via a bearing 15 on the outer periphery of a support shaft 7 (mounting bracket) protruding from an end casing 2 of the compressor.
[0036]
A solenoid 6 fixed to the end casing 2 side is disposed in the space having the U-shaped cross section, and a magnetic material is disposed at a position opposed to the solenoid 6 with the annular wall 5 of the driven pulley 4 interposed therebetween. An annular plate 16 is disposed.
[0037]
When the solenoid 6 is not energized, the annular plate 16 is separated from the annular wall 5 of the driven pulley 4 as shown in the figure, and even if the driven pulley 4 is rotated by the endless belt, the annular plate 16 rotates. And the compressor does not work.
[0038]
On the other hand, when the solenoid 6 is energized, the annular plate 16 made of a magnetic material is attracted by its magnetic force and pressed against the annular wall 5 of the driven pulley 4. As a result, the electromagnetic clutch is brought into the coupled state, and when the driven pulley 4 rotates, the annular plate 16 also rotates integrally, so that the rotational force can be freely transmitted to the leaf spring 8, the mounting bracket 7, and the rotating shaft 1. That is, the solenoid 6, the annular plate 16, and the leaf spring 8 constitute an electromagnetic clutch for engaging and disengaging the driven pulley 4 and the rotary shaft 1.
[0039]
As shown in FIGS. 2A and 2B, the double row angular contact ball bearing 15 has an inner ring 9 having two rows of inner ring raceways 11a and 11b on the outer peripheral surface, and a deep groove type two outer ring raceway on the inner peripheral surface. And an outer ring 10 having 12a and 12b.
[0040]
Between two rows of inner raceways 11a and 11b and two rows of outer raceways 12a and 12b, two rows of a plurality of spherical rolling elements 13a and 13b, respectively, are rotatably interposed.
[0041]
Further, the plurality of rolling elements 13a, 13b are rotatably held at predetermined intervals in the circumferential direction by retainers 18a, 18b formed in an annular shape, respectively.
[0042]
In addition, the outer peripheral edge of an annular seal plate 17 is fixed to the peripheral edge of the opening at both ends of the inner ring 9 and the outer ring 10, and both ends of the space in which the plurality of spherical rolling elements 13a and 13b are installed. The department is closed.
[0043]
In the present embodiment, the inner raceway 11a and the outer raceway 12a in one row and the inner raceway 11b and the outer raceway 12b in the other row are arranged such that the spherical rolling elements 13a in one row are the other in the central portion thereof. They are formed in contact with each other so as to enter the rolling space for the row of spherical rolling elements 13b.
[0044]
That is, the spherical rolling elements 13a in one row and the spherical rolling elements 13b in the other row are configured to overlap each other when viewed from the radial direction of the bearing 15, so that the width of the bearing 15 Dimensions can be reduced.
[0045]
At this time, the diameters of the spherical rolling elements 13a and 13b are the same as the conventional ones and are not reduced, so that a rated load equivalent to that of a conventional bearing can be desired, and sufficient for high loads and the like. , And the durability can be significantly improved.
[0046]
Therefore, according to the present embodiment, the width of the bearing 15 can be reduced without reducing the diameter of the spherical rolling elements 13a and 13b (without shortening the service life), thereby significantly reducing the size. In addition, it is possible to achieve a long life so as to withstand high vibration and high load accompanying high-speed rotation.
[0047]
Further, since the bearing 15 that rotatably supports the rotating shaft of the engine accessories in the housing is a double-row angular ball bearing 15, a moment load from the driven pulley 4 acts in addition to the radial load. Even when the bearing 15 may be inclined, the inclination of the bearing 15 can be sufficiently prevented. That is, according to the present embodiment, it is possible to cope with the moment load from the driven pulley 4 and to eliminate the possibility of the bearing being tilted, although the size is significantly reduced.
[0048]
As described above, the durability of the pulley rotation support device can be improved while the pulley rotation support device has a compact structure.
[0049]
Further, in the rolling bearing 15 for an engine accessory according to the present embodiment, a type in which the contact angles of both rows are open to the inner diameter side of the bearing 15 is used, but a type in which the contact angle is zero is used. You may.
[0050]
The present invention is not limited to the above-described embodiment, but can be variously modified.
[0051]
【The invention's effect】
As described above, according to the present invention, the inner raceway and the outer raceway in one row and the inner raceway and the outer raceway in the other row are arranged such that the spherical rolling elements in one row have Are formed adjacent to each other so as to enter the rolling space for the spherical rolling elements in the row.
[0052]
That is, the spherical rolling elements in one row and the spherical rolling elements in the other row overlap each other when viewed from the radial direction of the bearing (see FIGS. 1 and 2). The width of the bearing can be reduced.
[0053]
In this case, the diameter of the spherical rolling element is the same as that of the conventional one and is not reduced, so that the same rated load as that of the conventional bearing can be expected, and the bearing can sufficiently withstand a high load and the like. And durability can be remarkably improved.
[0054]
Therefore, according to the present invention, it is possible to reduce the width of the bearing without reducing the diameter of the spherical rolling element (without shortening the service life). It is also possible to extend the service life to withstand the high vibration and high load accompanying the above.
[0055]
In addition, since the bearing that rotatably supports the rotating shaft of the engine accessories in the housing is a double row angular contact ball bearing, in addition to the radial load, a moment load from the pulley acts in addition to the radial load, and the bearing is inclined. Even when there is a fear, it is possible to sufficiently prevent the inclination of the bearing. That is, according to the present invention, it is possible to cope with the moment load from the pulley and to eliminate the possibility of the bearing being tilted, although the size is significantly reduced.
[0056]
As described above, it is possible to improve the durability of the rotation support device for pulleys while making the rotation support device for pulleys compact.
[Brief description of the drawings]
FIG. 1 is a sectional view of a pulley rotation support device according to an embodiment of the present invention.
2A is a cross-sectional view of a bearing used in the pulley rotation support device shown in FIG. 1, and FIG. 2B is a view taken along line bb of FIG.
FIG. 3 is a sectional view of a rotation supporting portion of a compressor for an air conditioner of an automobile, showing a first conventional example of the structure.
FIG. 4 is a sectional view of only a bearing used for a rotation supporting portion of the compressor shown in FIG. 3;
FIG. 5 is a partial cross-sectional view of a rotary support of an air conditioner compressor of an automobile, showing a second conventional example of the structure.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Rotation shaft 2 Casing 3 Support cylinder part 4 Follower pulley 5 Annular wall part 6 Solenoid 7 Support shaft part (mounting bracket)
Reference Signs List 8 leaf spring 9 inner ring 10 outer ring 11a, 11b inner ring raceway 12a, 12b outer ring raceway 13a, 13b spherical rolling element 14 double row radial ball bearing (conventional)
15 Double-row radial ball bearing 16 Ring plate 17 Seal plates 18a, 18b Cage 19 Single-row radial ball bearing

Claims (1)

A fixed support,
An inner ring supported by the support portion and having two rows of deep groove inner ring raceways on the outer peripheral surface, an outer ring having two rows of deep groove type outer ring raceways on the inner peripheral surface, and these two rows of inner ring raceways and two rows of A double-row deep-groove angular ball bearing comprising two rows of a plurality of spherical rolling elements each rotatably interposed between the outer ring raceway;
A pulley rotatably supported by the double-row deep groove type angular contact ball bearing, and a pulley for hanging an endless belt;
The inner raceway and the outer raceway in one row and the inner raceway and the outer raceway in the other row are arranged such that, in a central portion thereof, the spherical rolling elements of one row are used for the spherical rolling elements of the other row. A rotation support device for a pulley, which is formed in contact with each other so as to enter a moving space.

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