JP2010096218A - Bearing sealing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing sealing device for reducing the influences of heating following friction sliding between a sub seal lip and an inner ring side slinger, resulting in contribution to improving the life of the sub seal lip and securing sealing performance. <P>SOLUTION: A heat dissipation promoting uneven portion 70 is formed in the axil outer face of the inner ring side slinger 10 to enlarge a heat dissipation area. This promotes the dissipation of the sliding heat of the sub seal lip 94 from the outer face of the inner ring side slinger 10, suppresses the friction temperature rise of the inner ring side slinger 10 and the sub seal lip 94, effectively suppresses the wear and deterioration of the sub seal lip 94, and improves a sealing life. This also suppresses the heat hardening at the front end of the sub seal lip 94 formed of a rubber to maintain good sealing performance between the sub seal lip 94 and the inner ring side slinger 10. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a bearing seal device.

JP 2003-194077 A JP 2005-282669 A

  Due to demands for smaller and lighter automobiles and further expansion of living space, the engine room space has been inevitably reduced, and electrical components and engine accessories have been further reduced in size and weight. Electromagnetic clutches and compressors for car air conditioners The idler pulley is no exception. However, a reduction in output is unavoidable due to downsizing, and an electromagnetic clutch compensates for the reduction in output by increasing the speed, and accordingly, the idler pulley is also increased in speed. Furthermore, since the engine room is being sealed due to a demand for improvement in quietness, and the high temperature in the engine room is promoted, these parts are also required to withstand high temperatures. In addition, since these parts are often attached to the lower part of the engine room, they are likely to be exposed to rain water, muddy water, etc. during traveling, and high sealing performance is required for the rolling bearings for these parts.

  Roller bearings for idler pulleys are used in such a manner that the inner ring is on the non-rotating side and the outer ring on which the pulley is fixed is on the rotating side. In such a rolling bearing seal device, the outer peripheral edge of the radial direction is fitted to the inner peripheral side of the axial end of the outer ring so as not to be relatively rotatable, and the main seal lip made of rubber formed on the inner peripheral side of the radial direction And a rubber sliding seal portion that is in sliding contact with the outer peripheral side of the axial end portion of the inner ring. In Patent Document 1, an inner ring side slinger (dust cover) fitted to a non-rotating inner ring is arranged oppositely on the outer side in the axial direction of such a sliding seal portion to suppress intrusion of dust or the like into the bearing. ing.

  In recent years, the conditions of use of automobiles have become more severe, and there are cases in which further increase in the amount of water is expected, such as when splashed muddy water or car wash water is jetted at a strong pressure, and flooding seen in RV cars, etc. Considering use in a submerged state or a submerged state, the bearing seal device is required to have higher waterproofness. In Patent Document 2, a secondary seal lip (axial lip) that protrudes toward the inner ring side slinger and slides against the inner surface of the slinger is formed on the outer surface in the axial direction of the sliding seal portion to further improve the sealing performance.

  However, in the configuration of Patent Document 2, the frictional heat between the secondary seal lip and the inner ring side slinger increases the frictional heat of the seal generated during high-speed rotation, and the rubber secondary seal lip wears and deteriorates significantly. There's a problem. In addition, the frictional heat causes the sliding side tip of the rubber sub-seal lip to harden, resulting in a loss of flexibility unique to rubber, and the sealing property of the sub-seal lip is likely to be impaired.

  An object of the present invention is to provide a bearing seal device that reduces the influence of heat generation due to frictional sliding between the sub seal lip and the inner ring side slinger, and thus contributes to the improvement of the life of the sub seal lip and the securing of hermeticity. is there.

Means for Solving the Problems and Effects of the Invention

The present invention is a bearing seal device used for a radial bearing used in inner ring non-rotation and outer ring rotation, in order to solve the above problems,
Metal inner ring side that is arranged in such a way as to block the annular opening of the rolling element arrangement space formed between the inner and outer rings in the axial direction, and the inner peripheral edge of the radial direction is fitted to the axial end of the inner ring so as not to be relatively rotatable With slinger,
The inner ring side slinger is placed facing the inner ring in the axial direction to form an axial seal gap. The outer peripheral edge of the radial direction is fitted to the axial end of the outer ring in a relatively non-rotatable manner, and the inner ring is positioned on the inner peripheral side of the radial direction. A main seal lip made of rubber that is in sliding contact with the outer end of the axial direction is formed, and the surface facing the inner ring side slinger is used as an axial base surface, and the axial base surface is crossed through the axial seal gap to face outward in the radial direction. A sliding seal part formed with a rubber secondary seal lip that is slidably contacted with the inner ring side slinger in the axial direction inner surface with a predetermined axial tightening allowance, and having an inner ring side slinger A heat-dissipating concavo-convex part for expanding the heat-dissipating area of the outer surface is formed on the outer surface in the axial direction. To.

  According to the above configuration, the heat radiation accelerating projections and depressions are formed on the outer surface in the axial direction of the inner ring side slinger, and the heat radiation area is expanded, so the heat release of the sliding heat of the secondary seal lip is promoted on the outer surface of the inner ring side slinger. The frictional temperature rise of the slinger and the secondary seal lip is suppressed, and the wear and deterioration of the secondary seal lip can be effectively suppressed, and the seal life can be improved. Moreover, since the thermosetting of the tip of the rubber secondary seal lip is suppressed, the sealing property between the secondary seal lip and the inner ring side slinger can be kept good. Furthermore, even when water droplets adhere to the heat radiation promoting uneven portion, the adhesion area expands, and the water droplets or the like toward the gap formed between the outer peripheral edge of the inner ring side slinger and the axial edge of the inner ring Is prevented from moving, so that the entry of the water droplets or the like into the bearing can be suppressed.

  The rubber material that forms the secondary seal lip is preferably an acrylic rubber from the viewpoint of excellent grease resistance, heat resistance, and weather resistance, but the temperature reached by the inner ring side slinger is increased by forming heat-promoting irregularities. Can be further reduced, it is also possible to employ a cheaper nitrile rubber as the rubber material forming the secondary seal lip.

  The sliding contact surface of the inner ring side slinger with the secondary seal lip on the inner surface in the axial direction is preferably formed on a flat surface in order to improve the sealing performance with the secondary seal lip.

  Next, the heat radiation promoting uneven portion can be a processed uneven pattern integrally formed on the outer surface of the inner ring side slinger by plastic working. The heat radiation promoting uneven portion can be efficiently formed as a processed uneven pattern by plastic working. In particular, it is more efficient to form the processed uneven pattern at the same time during the press molding of the inner ring side slinger. As such a processed uneven pattern, for example, a plurality of recesses can be dispersedly formed on the outer surface of the inner ring side slinger. Thereby, the heat radiation area of the outer surface of the inner ring side slinger can be increased more effectively, and the effect of suppressing the temperature increase of the inner ring side slinger and, in turn, the auxiliary seal lip can be enhanced.

  Moreover, the heat radiation promoting uneven portion can be a plurality of heat radiating ridges arranged in a predetermined direction along the outer surface of the inner ring side slinger. In such a heat radiating ridge, the flow of airflow on the surface when the inner ring side slinger rotates is smooth, and the heat radiation efficiency is further enhanced. In particular, the effect can be further enhanced by forming the radiating ridges in the circumferential direction of the slinger. In this case, the radiating ridges may be formed in a ring shape or a spiral shape. In addition, when such heat radiating ridges are arranged in the radial direction of the inner ring side slinger, grooves (concave portions) formed between adjacent radiating ridges are arranged in the radial direction and attached. The effect of suppressing water droplets and the like from moving in the radial direction toward the gap is further enhanced.

  Further, the heat radiation promoting uneven portion can be a rough surface uneven portion formed by dispersion on the outer surface of the inner ring side slinger by surface roughing. Such a roughened uneven portion has an advantage that it can be easily formed by shot blasting or the like.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing an embodiment of a bearing to which the bearing sealing device of the present invention is applied. The bearing 1 is for rotating and supporting an automobile idler pulley, and is configured as a double row deep groove ball bearing (radial bearing) used so that the inner ring 3 is non-rotating and the outer ring 4 is rotating. Yes. The balls 5 and 5 forming the rolling elements are arranged in the rolling element arrangement space 10 formed between the inner ring 3 and the outer ring 4 while the circumferential arrangement interval is restricted by the cages 6 and 6 in each row. Yes. A pulley 20 is concentrically fitted on the outer peripheral surface of the outer ring 4.

  The bearing 1 is provided with bearing seal devices 7 and 7 in annular openings 15 a and 15 a that respectively appear at both ends in the axial direction of the rolling element arrangement space 15. The bearing sealing devices 7 and 7 on either side have exactly the same configuration, and the main part thereof is composed of an inner ring side slinger 10 and a sliding seal portion 8.

  FIG. 2 is an enlarged cross-sectional view showing the details of one of the bearing seal devices 7, and the inner ring side slinger 10 is made of metal, for example, stainless steel (in particular, austenitic stainless steel such as SUS304, or ferrite such as SUS430. (Stainless steel). The inner ring side slinger 10 is arranged in such a manner as to block the annular opening 15a of the rolling element arrangement space 15 formed between the inner and outer rings 3 and 4 in the axial direction, and the inner peripheral edge in the radial direction is the axial end of the inner ring 3. Fitted to the part so as not to be relatively rotatable. Specifically, the inner ring side slinger 10 has an annular main body plate 10m disposed concentrically with the inner ring 3 so that the plate thickness direction coincides with the axial direction, and the inner ring side slinger 10 extends in the axial direction from the inner periphery of the opening of the main body plate 10m. And a cylindrical portion 10f integrally formed so as to protrude in the direction. A midway section portion in the radial direction of the main body plate 10m bulges inward in the axial direction with respect to both end section portions, and is an annular reinforcing bulging portion 10d having a flattened inner surface 10a. Further, the outer peripheral edge of the axial end face of the inner ring 3 is notched in a stepped shape in the circumferential direction, and an annular inner ring side notch 42 is formed. The cylindrical portion 10 f of the inner ring side slinger 10 is press-fitted and fitted to the inner peripheral surface 42 a of the inner ring side cutout portion 42.

  Further, on the outer surface in the axial direction of the main body plate 10m of the inner ring side slinger 10 is formed a heat radiation promoting uneven portion 70 for expanding the heat radiation area of the outer surface. The heat radiation promoting uneven portion 70 is a processed uneven pattern formed on the outer surface of the main body plate 10m at the time of the aforementioned press working (plastic working). For example, as shown in FIG. 3, a plurality of recessed portions 70 (dimples) are formed on the inner ring. It is formed in a distributed manner on the outer surface of the side slinger 10 (the peripheral portion of the concave portion 70 is identified as a convex portion). On the other hand, the sliding contact surface 10s with the sub seal lip 94 on the inner surface in the axial direction of the main body plate 10m is formed as a flat surface.

  Next, the sliding seal portion 8 is disposed opposite to the inner ring side slinger 10 so as to form an axial seal gap 17 on the inner side in the axial direction. The outer peripheral edge in the radial direction is fitted to the axial end of the outer ring 4 so as not to rotate relative thereto, and a rubber main seal lip 9 is formed on the inner peripheral edge of the radial ring in sliding contact with the outer end of the inner ring 3 in the axial direction. ing. Further, a surface facing the inner ring side slinger 10 is an axial base surface 8b, and a rubber secondary seal lip 94 is formed so as to rise obliquely outward in the radial direction while traversing the axial seal gap 17 from the axial base surface 8b. The tip end portion of the sub seal lip 94 is in sliding contact with the axial inner surface 10a of the inner ring side slinger 10 (which forms the inner surface of the above-described reinforcing bulging portion 10d).

  Specifically, the sliding seal portion 8 includes an outer ring-side slinger 81 that forms a seal core disposed so that the plate thickness direction coincides with the axial direction, and a plate surface on the outer side in the axial direction of the outer ring-side slinger 81. And a rubber seal body 8M. The main seal lip 9 is integrally formed with the seal body 8M so as to extend inward in the radial direction from the radially inner peripheral edge of the outer ring side slinger 81. The sub seal lip 94 is integrally formed with the seal body 8M in such a manner that the outer surface in the axial direction of the seal body 8M is an axial base surface 8b.

  The outer ring side slinger 81 is integrally formed with an annular main body plate 81m arranged so that the plate thickness direction coincides with the axial direction, and protruding inward in the axial direction from the outer peripheral edge of the main body plate 81m. It has a cylindrical wall portion 81a and a flange portion 81b extending radially outward from the axial end edge of the cylindrical wall portion 81a. The outer peripheral edge portion of the seal body 8M forms an annular fitting lip 8e having a rectangular cross section so as to surround the cylindrical wall portion 81a and the flange portion 81b. On the other hand, a reinforcing bent portion 81c is formed on the inner peripheral edge side of the outer ring side slinger 81 so as to be bent obliquely inward in the axial direction, and the seal body 8M wraps around the reinforcing bent portion 81c in the radial direction. A main seal lip 9 is formed extending inward.

  The inner peripheral edge portion of the end surface in the axial direction of the outer ring 4 is notched in a stepped shape in the circumferential direction, and an annular outer ring side notch portion 41 is formed. The fitting lip 8e is press-fitted and fitted so as to be in close contact with the bottom surface 41a and the inner peripheral surface 41b of the outer ring side cutout 41. In addition, a retaining rib 41r is formed to protrude in the circumferential direction at an end portion in the axial direction on the open side of the inner peripheral surface 41b of the outer ring side cutout portion 41, and the fitting lip 8e elastically moves the retaining rib 41r. It gets over and is fitted in the outer ring side cutout 41.

  The main seal lip 9 has a base 91 extending radially outward from the seal body 8 and an inner lip 92 extending axially inward from the base 91. The inner lip 92 extends from the base 91 on the radially inner side toward the bottom surface 42a of the inner ring side cutout portion 42 and slidably contacts the bottom surface 42a, and the base 91 on the radially outer side of the inner slidable lip 92a. The inner auxiliary lip 92b extends from the base 91 on the radially outer side of the inner auxiliary lip 92b to the inner side in the axial direction. The outer lip 93 has a first outer lip 93a extending outward in the axial direction at substantially the same position as the inner sliding lip 92a in the base 91, and a radial position of the inner auxiliary lip 92b in the base 91. A second outer lip 93b extending outward in the axial direction. In the present embodiment, the base portion 91 faces the side surface 10c on the inner side in the axial direction of the flange portion 10b at substantially the same position as the radial direction of the axial lip 92c. An outer slidable contact lip 93c that extends and slidably contacts the side surface 10c is provided.

  At the beginning of use, the inner lip 92 is configured such that only the inner sliding lip 92a is in sliding contact with the bottom surface 42a of the inner ring side cutout portion 42, and the inner auxiliary lip 92b is not in sliding contact with the bottom surface 42a of the inner ring side cutout portion 42. Yes. The inner auxiliary lip 92b comes into slidable contact with the bottom surface 42a of the inner ring side cutout portion 42 when the inner slidable contact lip 92a wears a certain amount after the bearing 1 is started. The axial lip 92 c forms a labyrinth seal with the outer peripheral surface 3 a of the inner ring 3. An annular space surrounded by the main seal lip 9, the sub seal lip 94, the inner ring 3 and the inner ring side slinger 10 is filled with grease for sliding lubrication of each seal lip. The grease may contain an amine-based additive.

  In the present embodiment, the seal body 8M is made of acrylic rubber together with the main seal lip 9 and the sub seal lip 94. Specifically, acrylic rubber is used, but ethylene acrylate rubber can also be used as other acrylic rubber. Acrylic rubber, together with nitrile rubber described later, has good resistance to grease containing the above amine-based additives.

  The lip tip portion 94t of the sub seal lip 94 has a shape that tapers at an acute angle in a cross section including the bearing rotation axis. By making the lip tip portion 94t have such a tapered shape, the tip end of the sub seal lip 94 becomes good and the adhesion to the inner ring side slinger 10 can be improved. Here, the entire sub seal lip 94 has a wedge shape that continuously reduces the lip thickness from the rising base end side to the sliding contact side tip from the axial base surface 8b in the cross section including the bearing rotation axis. ing. Since the lip thickness at the base end portion of the sub seal lip 94 is increased, it is possible to prevent a problem that the sub seal lip 94 is reversed in the radial direction at the time of assembly or the like, and the lip tip side is tapered. The effect of can be achieved at the same time.

  When the bearing 1 rotates, the inner ring side slinger 10 rises in temperature due to frictional heat generated as the sub seal lip 94 slides. When the rotation speed of the outer ring 4 increases and the temperature of the inner ring side slinger 10 exceeds 120 ° C. due to the frictional heat generation, for example, the wear and deterioration of the lip tip 94t become remarkable, and the life of the sub seal lip 94 is lost. Further, the lip end portion 94t of the rubber sub-seal lip 94 is hardened when the temperature rises due to frictional heat generation even if the wear does not progress, and there is a possibility that the inherent flexibility of the rubber is lost and the sealing performance is deteriorated.

  However, as shown in FIG. 2, in the present invention, since the heat radiation accelerating uneven portion 70 is formed on the outer surface in the axial direction of the inner ring side slinger 10 to expand the heat radiation area, the sliding heat of the sub seal lip 94 is increased on the inner ring side. Heat dissipation on the outer surface of the slinger 10 is promoted, and the frictional temperature rise of the inner ring side slinger 10 and the sub seal lip 94 is suppressed. As a result, wear and deterioration of the sub seal lip 94 can be effectively suppressed, and the seal life can be improved. Further, as a result of the temperature rise of the inner ring side slinger 10 and the sub seal lip 94 being suppressed, thermosetting of the lip tip 94t is suppressed, and therefore the sealing performance between the sub seal lip 94 and the inner ring side slinger 10 is good. Can be kept in. Further, when the water droplet WD adheres to the heat radiation promoting uneven portion 70, the adhesion area is enlarged, so that the clearance CL formed between the outer peripheral edge of the inner ring side slinger 10 and the axial edge of the inner ring 3 is formed. The water droplets or the like are prevented from moving toward the surface, and the water droplets or the like can be prevented from entering the bearing.

  In addition, by forming the heat radiation promoting uneven portion 70 as described above, the area of the outer surface of the inner ring side slinger 10 can be enlarged to about 1.1 to 2 times, for example. When the heat radiation accelerating uneven portion 70 is a recess as shown in FIG. 3, the opening size of the recess is, for example, a recess formation area ratio (defined as the sum of the recess opening area with respect to the entire area of the outer surface of the inner ring side slinger 10) When the area of the outer surface of the inner ring side slinger 10 is desired to be increased to about 1.3 times by about%, for example, it may be set to about 1.0 to 1.6 times the plate thickness of the main body plate 10m.

  By expanding the area of the outer surface of the inner ring side slinger 10 to, for example, about 1.2 times to 1.5 times, the maximum temperature reached by the inner ring side slinger 10 is compared with the case where the heat radiation promoting uneven portion 70 is not formed. It can reduce about 10-30 degreeC. From the viewpoint of suppressing heat curing, wear, and the like of the lip tip portion 94t, even a temperature drop of this level has a remarkable effect. Further, although the heat resistance is somewhat inferior due to the reduction of the temperature reached by the inner ring side slinger 10, the secondary seal lip 94 (and the main seal lip 9 and It is also possible to constitute the seal body 8M).

Hereinafter, various modifications of the present invention will be described.
As shown in FIG. 4, the heat radiation promoting concavo-convex portion can be a plurality of heat radiating ridges 71 arranged in a predetermined direction along the outer surface of the inner ring side slinger 10. Such a heat-radiating ridge 71 has a smooth airflow on the surface when the inner ring-side slinger 10 rotates, and the heat radiation efficiency is further enhanced. In particular, as shown on the right side of FIG. 4, the effect is further enhanced by forming the heat radiating protrusions 71 in the circumferential direction of the outer surface of the inner ring side slinger 10. In FIG. 4, the radiating ridge 71 is formed in a concentric ring shape, but may be formed in a spiral shape. Since the heat radiating ridges 71 are arranged in the radial direction of the inner ring side slinger 10, the groove portions 72 formed between the adjacent heat radiating ridges 71 are also arranged in the radial direction, and adhered water droplets or the like are formed. The effect of suppressing the movement in the radial direction toward the gap CL (FIG. 2) is further enhanced.

  In FIG. 4, the heat radiating ridges 71 are formed as having a rectangular cross section together with the adjacent groove portions 72 (in order to facilitate press working as one form of the rectangular cross section, the heat radiating ridges 71 are formed. It is also possible for the portion 71 to have a trapezoidal cross section and the groove 72 to have an inverted trapezoidal cross section). Moreover, what is necessary is just to set the groove width by the side of the opening of the groove part 72 to about 1.0 to 1.6 times the plate | board thickness of the main body board 10m, for example.

  In FIG. 5, the heat radiating ridge 71 'is formed to have an acute triangular cross section. Specifically, the surface 71b ′ located on the radially inner side of the two side surfaces of the heat radiating ridge 71 is more than the surface 71a ′ located on the outer side (the side where the gap CL (FIG. 2) is located). Is also formed so as to stand up (that is, the angle formed with the main surface of the main body plate 10m is large), and the entire plurality of radiating ridges 7 have a saw-tooth cross-sectional shape. Thereby, the effect which suppresses that the adhering water droplet etc. move to radial direction outward toward the clearance gap CL (FIG. 2) is further heightened.

  Further, as shown in FIG. 6, the heat radiation promoting uneven portion can be a rough surface uneven portion 75 that is dispersedly formed on the outer surface of the inner ring side slinger 10 by surface roughing. Such a roughened uneven portion 75 has an advantage that it can be easily formed by shot blasting or the like.

  Furthermore, as shown in FIG. 7, it is also possible to form the heat radiation promoting uneven portion by a net member 73 (which may be an expanded metal) joined to the outer surface of the main body plate 10m.

Sectional drawing which shows an example of the bearing for idler pulleys to which the sealing device for bearings of this invention is applied. Sectional drawing which expands and shows the seal apparatus part for bearings of FIG. The figure which shows the 1st form of formation of a heat dissipation promotion uneven | corrugated | grooved part. + The figure which shows the 2nd formation form of the heat radiation promotion uneven | corrugated | grooved part. The figure which shows the 3rd formation form of a heat dissipation promotion uneven | corrugated | grooved part. The figure which shows the 4th form of formation of a heat dissipation promotion uneven | corrugated | grooved part. + The figure which shows the 5th formation form of a heat-radiation promotion uneven | corrugated | grooved part.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Bearing 3 Inner ring 4 Outer ring 7 Bearing seal device 8 Sliding seal part 8b Axial base surface 9 Main seal lip 10 Inner ring side slinger 15 Rolling element arrangement space 15a Annular opening 17 Axial seal gap 70 Concave part (radiation promotion uneven part)
71, 71 ′ Radiation ridges for heat dissipation (radiation-promoting irregularities)
75 Surface roughening uneven part (heat dissipation promoting uneven part)
94 Sub seal lip 94a Radial inner surface 94t Lip tip

Claims (4)

A radial bearing seal device used for inner ring non-rotation and outer ring rotation,
It is made of a metal that is arranged in such a way as to block the annular opening of the rolling element arrangement space formed between the inner and outer rings in the axial direction, and the radially inner peripheral edge fits relative to the axial end of the inner ring in a relatively non-rotatable manner. Inner ring side slinger,
The inner ring side slinger is opposed to the inner ring side so as to form an axial seal gap, and the outer peripheral edge portion in the radial direction is fitted in the axial direction end portion of the outer ring so as not to rotate relative to the inner ring side. A rubber main seal lip is formed in sliding contact with the outer end of the inner ring in the axial direction, and the opposite surface to the inner ring side slinger is used as an axial base surface so as to cross the axial seal gap from the axial base surface. And a sliding seal portion formed with a rubber secondary seal lip formed so that the tip end portion of the lip is slidably contacted to the inner surface of the inner ring side slinger with a predetermined axial tightening margin. Prepared,
A bearing seal device, wherein a heat radiation accelerating uneven portion for expanding a heat radiation area of the outer surface is formed on an outer surface in the axial direction of the inner ring side slinger.   The bearing sealing device according to claim 1, wherein a sliding contact surface of the inner ring side slinger with the sub seal lip on the inner surface in the axial direction is formed as a flat surface.   3. The bearing seal device according to claim 1, wherein the heat radiation promoting uneven portion is a processed uneven pattern integrally formed by plastic working on the outer surface of the inner ring side slinger.   The bearing sealing device according to any one of claims 1 to 3, wherein a plurality of recesses forming the processed uneven pattern are formed in a distributed manner on the outer surface of the inner ring side slinger.

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