JP2020172952A - Rolling bearing device - Google Patents

Abstract

To provide a rolling bearing device which enables an oil supply amount to be increased when a lubrication oil is decreased in a bearing part without having a sensor.SOLUTION: A rolling bearing device 10 includes: a bearing part 20 having an inner ring 21, an outer ring 22, balls 23, and a retainer 14 which retains the balls 23; and an oil supply unit 40 having a pump 42 which discharges a lubrication oil to the bearing part 20 and a tank 43 which retains the lubrication oil to be discharged from the pump 42, the oil supply unit 40 provided adjacent to the bearing part 20 in an axial direction. The outer ring 22 and the tank 43 directly contact with each other and a contact portion in the tank 43, contacting with the outer ring 22, is made of a metal.SELECTED DRAWING: Figure 1

Description

The present invention relates to a rolling bearing device including a lubrication unit that supplies lubricating oil to a bearing portion.

In recent years, in various machine tools, high speed of the spindle is required in order to improve processing efficiency and production efficiency. When the spindle rotates at high speed, lubricity becomes a problem especially in the bearing portion that supports the spindle. Therefore, a rolling bearing device in which a lubrication unit is provided next to the bearing portion has been proposed (see Patent Document 1). The refueling unit has a pump that discharges lubricating oil to the bearing portion and a tank that holds the lubricating oil discharged by the pump.

Japanese Unexamined Patent Publication No. 2017-180819

The refueling unit disclosed in Patent Document 1 has, in addition to the pump and the tank, a sensor for detecting vibration of the bearing portion and a determination circuit for inputting a sensor signal. When the amount of lubricating oil decreases in the bearing portion, the vibration increases. Therefore, the refueling unit is configured so that the pump operates when vibration exceeding the threshold value is detected by the sensor. By executing feedback control based on the sensor signal, it is possible to maintain the lubrication state of the bearing portion normally.

The refueling unit as described above is provided in a spacer adjacent to the bearing portion in the axial direction. Therefore, it is not possible to increase the size of the tank due to dimensional restrictions. That is, there is a limit to the capacity of the tank. Therefore, for example, in a machine tool, it is preferable that the consumption of lubricating oil is minimized in order to make maintenance free or to reduce the maintenance frequency as much as possible. Therefore, when the amount of lubricating oil decreases in the bearing portion, it is preferable to increase the amount of lubrication at that timing, and in order to realize this, a sensor and a determination circuit that inputs a sensor signal as in Patent Document 1 are required. Become. If the sensor is not required, the determination circuit as described above is also unnecessary, and the cost can be reduced.

Therefore, the present invention provides a rolling bearing device capable of increasing the amount of lubrication when the amount of lubricating oil decreases in the bearing portion even without a sensor.

The rolling bearing device of the present disclosure includes an inner ring, an outer ring, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage for holding the plurality of rolling elements, and the inner ring and the said. It has a bearing portion in which one of the outer rings is a rotating wheel and the other is a fixed ring, a pump that discharges lubricating oil to the bearing portion, and a tank that holds the lubricating oil discharged from the pump. A lubrication unit provided next to the bearing portion in the axial direction is provided, and the fixed wheel and the tank are in direct contact with each other, and the portion of the tank in contact with the fixed wheel is made of metal. Is.

According to the rolling bearing device, when the lubricating oil decreases in the bearing portion and the temperature of the fixed wheel rises, the heat is transferred to the tank. Then, the temperature of the lubricating oil held in the tank rises, and the viscosity of the lubricating oil decreases. As a result, the amount of lubricating oil discharged from the pump increases. As described above, even if there is no sensor, if the lubricating oil decreases in the bearing portion, the amount of lubrication can be increased. The pump may be set to discharge the lubricating oil at predetermined time intervals, and feedback control based on the sensor signal as in the conventional case is unnecessary. From the above, it is possible to configure a rolling bearing device at a lower cost than before.

Also, preferably, the tank has a heat sink as a portion in contact with the fixed ring. According to this configuration, the temperature of the fixed wheel is efficiently transmitted to the lubricating oil of the tank. It is possible to shorten the reaction time from the temperature rise of the bearing portion (fixed wheel) to the increase of the discharge amount of the lubricating oil.

Further, preferably, the pump and the fixed ring are arranged between each other via a heat transfer material. According to this configuration, when the lubricating oil decreases in the bearing portion and the temperature of the fixed wheel rises, the heat is transferred to the pump through the heat transfer material. Therefore, the amount of lubricating oil discharged from the pump increases. Even when an axial load (preload) acts on the rolling bearing device including the bearing portion, the heat transfer material between the pump and the fixed wheel functions as a cushioning material, and the load affects the pump. It becomes difficult.

According to the present invention, even without a sensor, it is possible to increase the amount of lubrication when the lubricating oil decreases in the bearing portion. As a result, it is possible to eliminate the shortage of lubricating oil in the bearing portion.

It is sectional drawing which shows an example of the rolling bearing apparatus. It is the figure which looked at the refueling unit from the axial direction. It is sectional drawing for demonstrating the schematic structure of a pump. It is sectional drawing for demonstrating the deformation example of a metal wall. 1 is an enlarged cross-sectional view showing a portion indicated by an arrow A in each of the forms of FIGS. 1 and 4. It is sectional drawing on the pump side in the rolling bearing apparatus.

[Overall configuration]
FIG. 1 is a cross-sectional view showing an example of a rolling bearing device. Although not shown, the rolling bearing device 10 (hereinafter referred to as “bearing device 10”) shown in FIG. 1 rotatably supports the spindle (shaft) of the spindle device of the machine tool, and is a spindle device. It is housed in the bearing housing. The bearing device 10 can be applied to other than machine tools.

The bearing device 10 includes a bearing portion 20 and a refueling unit 40. The bearing portion 20 has an inner ring 21, an outer ring 22, a plurality of balls (rolling elements) 23, and a cage 24 for holding the plurality of balls 23, and constitutes a ball bearing (rolling bearing). .. In the present disclosure, the inner ring 21 is a rotating wheel that rotates integrally with the main shaft. The outer ring 22 is a fixed ring attached to the bearing housing. The bearing device 10 further includes a cylindrical outer ring spacer 18.

The direction along the center line C of the bearing portion 20 (inner ring 21) is defined as the "axial direction" of the bearing device 10, and here, the direction parallel to the center line C is also included in the "axial direction". Further, in FIG. 1, the left side is one side in the axial direction of the bearing device 10, which is referred to as "one side in the axial direction", and the right side is the other side in the axial direction of the bearing device 10. It is called "the other side in the axial direction".

The refueling unit 40 has an annular shape as a whole, and is provided on the inner peripheral side of the outer ring spacer 18. The refueling unit 40 is provided next to one side of the bearing portion 20 in the axial direction. The refueling unit 40 has a pump 42 that discharges lubricating oil to the bearing portion 20 (see FIGS. 2 and 6) and a tank 43 that holds the lubricating oil discharged from the pump 42 (see FIGS. 1 and 2). The configuration of the refueling unit 40 will be described later.

The inner ring 21 is a cylindrical member that fits outside the main shaft, and a track 25 (inner ring track 25) is formed on the outer circumference thereof. The outer ring 22 is a cylindrical member attached to the inner peripheral surface of the bearing housing, and a track 26 (outer ring track 26) is formed on the inner circumference thereof. Although the outer ring 22 and the outer ring spacer 18 are separate members, they may be made of the same member. The ball 23 is interposed between the inner ring 21 and the outer ring 22. When the inner ring 21 rotates, the ball 23 rolls on the inner ring track 25 and the outer ring track 26. The cage 24 has an annular shape, and a plurality of pockets 27 for accommodating the balls 23 are formed along the circumferential direction. The ball 23 and the cage 24 are provided in an annular space 11 formed between the inner ring 21 and the outer ring 22. The bearing portion 20 is lubricated by the lubricating oil (oil) supplied by the lubrication unit 40.

FIG. 2 is a view of the refueling unit 40 as viewed from the axial direction. The refueling unit 40 includes a main body 41, a pump 42, and a tank 43. The main body 41 is an annular member. A hollow space is formed in the main body 41, and the pump 42 and the tank 43 are provided in this hollow space. As a result, the refueling unit 40 including the main body 41, the tank 43, and the pump 42 is integrally configured. The main body 41 is attached to the inner peripheral side of the outer ring spacer 18, and has a function as a frame for holding the pump 42 and the like.

The tank 43 can store lubricating oil and is connected to the pump 42 through a pipe 46. Lubricating oil is supplied to the pump 42 from the tank 43. The pump 42 has a function of discharging lubricating oil at predetermined time intervals. For this purpose, the pump 42 has a control unit 44. The control unit 44 sends an electric signal for operating the piezo element 53 (described later) of the pump 42 to the piezo element 53 at predetermined time intervals. Then, the lubricating oil is discharged from the pump 42 as oil droplets. The discharge frequency of the lubricating oil (oil droplets) from the pump 42 is constant.

[About pump 42]
The configuration of the pump 42 will be described. FIG. 3 is a cross-sectional view for explaining a schematic configuration of the pump 42. The pump 42 has a pump body 52 and a piezo element (piezoelectric element) 53. The pump 42 is a piezo pump. A pressure chamber (internal space) 51 is formed in the pump body 52. The operation of the piezo element 53 changes the volume of the pressure chamber 51, whereby the pump 42 ejects the lubricating oil of the pressure chamber 51 from the discharge hole 50. The discharge hole 50 is connected to the pressure chamber 51 and opens toward the bearing portion 20. The discharge hole 50 is composed of linear minute through holes formed in the wall portion 52a of the pump main body 52. When the piezo element 53 operates, the lubricating oil becomes oil droplets from the discharge hole 50 and is discharged with an initial velocity. That is, for example, the oil droplets fly from the discharge hole 50 of the pump 42 so that the ink is discharged from the discharge hole formed in the head of the inkjet device used in the printing technique. The type of lubricating oil is a general hydraulic oil.

The operation of the pump 42 will be further described. An electric signal is intermittently output from the control unit 44 to the piezo element 53. This electric signal is a drive voltage that deforms the piezo element 53. A drive voltage is applied to the piezo element 53 for a short time. This drive voltage is supplied from a power supply unit (not shown). The refueling unit 40 includes a power supply unit. When a voltage (driving voltage) is applied to the piezo element 53, the piezo element 53 is deformed. When the voltage is released, the deformation is restored.

When a voltage (driving voltage) is applied to the piezo element 53, the elastic film 54 forming a part of the wall surface 51a of the pressure chamber 51 is elastically deformed due to the deformation, and the volume of the pressure chamber 51 is expanded. When the voltage is released, the volume of the pressure chamber 51 is reduced by the elastic restoring force of the elastic film 54. As a result, the lubricating oil in the pressure chamber 51 is discharged from the discharge hole 50 to the outside. By expanding the volume of the pressure chamber 51, lubricating oil is replenished from the tank 43 side to the pressure chamber 51. When the electric signal is output to the piezo element 53 in this way, the internal pressure of the pressure chamber 51 rises and the lubricating oil is discharged. When no electric signal is output to the piezo element 53, the internal pressure of the pressure chamber 51 does not change (it remains low) and the lubricating oil is not discharged.

From the above, the pump 42 has the characteristics described below. As the temperature of the lubricating oil rises, the viscosity of the lubricating oil decreases. In this case, the amount of lubricating oil (amount of oil droplets) discharged from the pump 42 increases. That is, the pump 42 has a characteristic that the amount of the lubricating oil (the amount of oil droplets) discharged by one discharge operation increases as the temperature of the lubricating oil rises. On the other hand, when the temperature of the lubricating oil decreases, the viscosity of the lubricating oil increases. In this case, the amount of lubricating oil (amount of oil droplets) discharged from the pump 42 decreases. That is, the pump 42 has a characteristic that when the temperature of the lubricating oil becomes low, the amount of the lubricating oil (the amount of oil droplets) discharged by one discharge operation decreases.

[About tank 43]
As shown in FIG. 2, the tank 43 is provided in the annular main body 41 along the circumferential direction. The tank 43 may be formed by a part of the hollow space of the main body 41. The main body 41 of the present disclosure is made of resin. In this case, as shown in FIGS. 1 and 2, the tank 43 has resin walls 47 on one side in the axial direction, the outer side in the radial direction, and the inner side in the radial direction. Further, the tank 43 (see FIG. 1) has a metal wall 48 on the other side in the axial direction. The space surrounded by the walls 47 on one side in the axial direction, the outer side in the radial direction, and the inner side in the radial direction, and the metal wall 48 on the other side in the axial direction is a region where lubricating oil is stored.

As shown in FIG. 1, the metal wall 48 is in contact with the outer ring 22 in the axial direction. The outer ring 22 is made of metal (for example, made of steel such as bearing steel). In the present disclosure, the metal wall 48 is made of copper, which has particularly high thermal conductivity. The wall 48 may be made of metal or any other material. Since the outer ring 22 and the metal wall 48 are in direct contact with each other, heat is easily transferred from the outer ring 22 to the wall 48.

The surface 49 on the other side in the axial direction of the metal wall 48 and the side surface 28 on the one side in the axial direction of the outer ring 22 are in surface contact with each other. The wall 48 and the outer ring 22 are in continuous contact with each other along the circumferential direction. The wall 48 and the outer ring 22 are preferably in contact with each other over the entire length in the circumferential direction of the tank 43. As described above, in the form shown in FIG. 1, the outer ring 22 and the tank 43 are in direct contact with each other, and the portion (wall 48) of the tank 43 in contact with the outer ring 22 is made of metal. In the form shown in FIG. 1, the metal wall 48 is made of a flat plate.

FIG. 4 is a cross-sectional view for explaining a modified example of the metal wall 48. The wall 48 shown in FIG. 4 is made of metal (made of copper), and is composed of a heat sink 60 in order to increase the contact area with the lubricating oil in the tank 43. More specifically, the metal wall 48 has a flat base portion 61 and fin portions 62 protruding from the base portion 61 in one axial direction. The space surrounded by the walls 47 on one side in the axial direction, the outer side in the radial direction, and the inner side in the radial direction, and the base portion 61 on the other side in the axial direction is the area where the lubricating oil is stored. As described above, the tank 43 shown in FIG. 4 has a heat sink 60 as a portion in contact with the outer ring 22.

The mounting structure of the metal wall 48 (heat sink 60) will be described. The bearing device 10 is attached to a bearing housing of a machine tool or the like in a state where a preload in the axial direction is applied. An axial load acts on the bearing device 10 due to the preload. Then, the refueling unit 40 on the inner peripheral side of the outer ring spacer 18 and the outer ring 22 are pressed against each other in the axial direction. The outer ring 22, the wall 48 (heat sink 60), and the outer ring spacer 18 are made of metal. On the other hand, the axial one side, the radial outer side, and the radial inner wall 47 of the tank 43 are made of resin.

FIG. 5 is an enlarged cross-sectional view showing a portion indicated by an arrow A in each of the forms of FIGS. 1 and 4. An annular groove 65 is formed on the inner peripheral side of the outer ring spacer 18 in the other axial direction. Due to the groove 65, the end of the outer ring spacer 18 on the other side in the axial direction has a stepped shape. The outer peripheral edge portion 48a of the metal wall 48 comes into contact with the annular surface 66 facing the other side in the axial direction of the groove 65. In this contact state, the surface 49 on the other side in the axial direction of the metal wall 48 is located further on the other side in the axial direction than the end surface 19 on the other side in the axial direction of the outer ring spacer 18.

Therefore, when an axial load (preload) acts on the bearing device 10 and the lubrication unit 40 on the inner peripheral side of the outer ring spacer 18 and the outer ring 22 are pressed against each other in the axial direction, as shown in FIG. In addition, the side surface 28 of the outer ring 22 and the end surface 19 of the outer ring spacer 18 are in a non-contact state, and the outer ring 22 and the metal wall 48 are in contact with each other. Therefore, the load from the outer ring 22 in one axial direction is transmitted to the outer ring spacer 18 made of metal through the metal wall 48. As a result, the load is not transmitted to the wall 47 made of resin, the deformation of the wall 47 is prevented, and the wall 47 is not damaged.

[About the structure on the pump 42 side]
As shown in FIG. 2, the pump 42 is attached to a part of the annular main body 41 in the circumferential direction. FIG. 6 is a cross-sectional view of the bearing device 10 on the pump 42 side. The pump 42 has a pump body 52 as described above. The pump body 52 serves as a housing (exterior member) of the pump 42. As shown in FIG. 6, the pump main body 52 and the outer ring 22 are not in direct contact with each other, and the heat transfer material 70 is interposed between them. Specific examples of the heat transfer material 70 are a resin material containing a heat conductive filler or a heat transfer paste. The heat transfer material 70 is deformable when a load is applied.

A heat transfer material 70 is interposed between the side surface 28 on one side in the axial direction of the outer ring 22 and the surface 55 on the other side in the axial direction of the pump body 52. Therefore, the heat of the outer ring 22 is transferred to the pump 42 (pump main body 52) via the heat transfer material 70. Further, as described above, when an axial load (preload) is applied to the bearing device 10, the outer ring 22 presses the heat transfer material 70 to deform it. Therefore, it is possible to suppress the action of the axial load on the pump 42.

[About the bearing device 10 of each of the above forms]
As described above, the bearing device 10 of each of the above-described embodiments includes a bearing portion 20 having an inner ring 21, an outer ring 22, a plurality of balls 23, and a cage 24, and a refueling unit 40 provided next to the bearing portion 20 in the axial direction. To be equipped. The refueling unit 40 has a pump 42 and a tank 43. The pump 42 discharges lubricating oil to the bearing portion 20. The tank 43 holds the lubricating oil discharged from the pump 42. As shown in FIGS. 1 and 4, the outer ring 22 and the tank 43 are in direct contact with each other, and the portion (wall 48) of the tank 43 that comes into contact with the outer ring 22 is made of metal.

According to the bearing device 10, when the inner ring 21 continuously rotates and the lubricating oil is consumed and reduced in the bearing portion 20, the temperature of the bearing portion 20 eventually rises. Then, the temperature of the outer ring 22 also rises, and the heat is transferred to the tank 43. Then, the temperature of the lubricating oil held in the tank 43 rises, and the viscosity of the lubricating oil decreases. As described above, the pump 42 has a characteristic that when the temperature of the lubricating oil is high, the amount of the lubricating oil (the amount of oil droplets) discharged by one discharge operation increases. Therefore, when the lubricating oil decreases in the bearing portion 20 and the temperature of the bearing portion 20 rises, the amount of lubricating oil discharged from the pump 42 increases.

The bearing device 10 of each form does not include a conventional sensor, and refueling control (feedback control) based on the signal of the sensor is not performed. However, even without the sensor, it is possible to increase the amount of oil supplied to the bearing portion 20 when the lubricating oil decreases in the bearing portion 20 as described above. According to each of the above-described modes, a conventional sensor and a calculation unit for processing the signal of the sensor are unnecessary, and the bearing device 10 can be configured at low cost.

The pump 42 may be set to discharge the lubricating oil at predetermined time intervals, and feedback control based on the sensor signal as in the conventional case is unnecessary. In the bearing device 10 of each form, the amount of refueling can be adjusted (controlled) by a mechanical structure due to contact between the outer ring 22 and the tank 43 without using a sensor. Therefore, the adjustment (control) is not affected by electrical noise.

In the bearing device 10 provided with the oil supply unit 40 as described above, conventionally, the outer ring 22 of the bearing portion 20 and the tank 43 are not in contact with each other. This is because, as described above, the bearing device 10 including the bearing portion 20 may be preloaded in the axial direction. That is, since the tank 43 is made of resin, the outer ring 22 and the tank 43 are provided apart from each other in the prior art so that the load due to the preload in the axial direction does not act on the tank 43.

At least the wall 48 in the tank 43 in contact with the outer ring 22 may be made of metal, and all the walls of the tank 43 may be made of metal. If all the walls of the tank 43 are made of metal, the heat capacity of the tank 43 becomes large, and the reaction of raising the temperature of the lubricating oil in the tank 43 by transferring heat from the outer ring 22 may be delayed. is there. Therefore, as shown in FIGS. 1 and 4, it is preferable that only the wall 48 in the tank 43 in contact with the outer ring 22 is made of metal.

In each of the above embodiments, the cage 24 included in the bearing portion 20 is radially positioned by the outer ring 22. Specifically, when a part of the cage 24 slides into contact with a part of the inner peripheral surface of the outer ring 22, the cage 24 is positioned in the radial direction by the outer ring 22. That is, the cage 24 is a cage for outer ring guidance. In this case, the rotation of the bearing portion 20 causes the cage 24 and the outer ring 22 to slide, and when the amount of lubricating oil decreases at the sliding portion, the temperature rises at the sliding portion. Therefore, in the case of the outer ring guide cage 24, the temperature of the outer ring 22 tends to be higher than that of other parts. Therefore, when the amount of lubricating oil is reduced, the temperature of the lubricating oil in the tank 43 can be raised by the temperature of the outer ring 22.

Further, in the form shown in FIG. 4, the tank 43 has a heat sink 60 as a portion in contact with the outer ring 22. According to the tank 43 having the heat sink 60, the temperature of the outer ring 22 is efficiently transmitted to the lubricating oil of the tank 43. Therefore, it is possible to shorten the reaction time from the temperature rise of the bearing portion 20 (outer ring 22) to the increase of the discharge amount of the lubricating oil. The portion (metal portion) of the tank 43 that comes into contact with the outer ring 22 may be other than the heat sink 60. That is, the portion of the tank 43 that comes into contact with the outer ring 22 may have an uneven shape that is wider than the case where the contact area with the lubricating oil in the tank 43 is only a flat plate.

Further, in each of the above-described embodiments, as shown in FIG. 6, the pump 42 and the outer ring 22 are arranged between each other via a heat transfer material 70. According to the heat transfer material 70, when the lubricating oil decreases in the bearing portion 20 and the temperature of the outer ring 22 rises, the heat is transferred to the pump 42 through the heat transfer material 70. Therefore, the amount of lubricating oil discharged from the pump 42 increases. Further, in the pump 42, when the temperature of the lubricating oil drops, a part of the lubricating oil solidifies, which causes clogging of the pump 42. However, when the inner ring 21 continuously rotates, the heat of the outer ring 22 is transferred to the outer ring 22 through the heat transfer material 70, so that the temperature of the pump 42 can be raised. Therefore, it is possible to prevent the pump 42 from being clogged.

As described above (see FIG. 3), the pump 42 has a piezo element 53, a pressure chamber 51, a discharge hole 50 composed of minute through holes, and the like. If a large load (external force) such as the preload is applied to such a pump 42, a problem may occur. However, as shown in FIG. 6, the heat transfer material 70 between the pump 42 and the outer ring 22 functions as a cushion material. Therefore, the load applied for the preload is less likely to affect the pump 42. As a result, it is possible to prevent a problem from occurring in the discharge of the lubricating oil from the pump 42.

As described above, according to the bearing device 10 of each form, even if there is no sensor as in the conventional case, when the lubricating oil decreases in the bearing portion 20, the amount of oil supplied by the pump 42 can be increased at that timing. It becomes. As a result, it is possible to eliminate the shortage of lubricating oil in the bearing portion 20.

[About others]
In each of the above embodiments, the case where the bearing portion 20 is an angular contact ball bearing has been described, but the type of the bearing is not limited to this, and may be a deep groove ball bearing, a tapered roller bearing, or a cylindrical roller bearing. You can.

Further, in each of the above-described embodiments, the case where the outer ring 22 is a fixed ring has been described. However, the outer ring 22 may be a rotating wheel and the inner ring 21 may be a fixed ring. In this case, although not shown, the bearing device 10 has an inner ring spacer as a spacer, and the lubrication unit 40 is provided on the outer peripheral side of the inner ring spacer. The inner ring 21 and the tank 43 of the refueling unit 40 are in direct contact with each other, and the portion of the tank 43 that comes into contact with the inner ring 21 is made of metal. Further, the cage 24 is preferably an inner ring guide cage that is positioned in the radial direction by the inner ring 21.

The embodiments disclosed this time are exemplary in all respects and are not restrictive. The scope of rights of the present invention is not limited to the above-described embodiment, and includes all modifications within a range equivalent to the configuration described in the claims.

10: Rolling bearing device 20: Bearing part 21: Inner ring 22: Outer ring 23: Ball (rolling element) 24: Cage 40: Refueling unit 42: Pump 43: Tank 48: Wall (part in contact with fixed wheel) 60: Heat sink 70: Heat transfer material

Claims (3)

It has an inner ring, an outer ring, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage for holding the plurality of rolling elements, and one of the inner ring and the outer ring rotates. The bearing part, which is a ring and the other is a fixed ring,
A refueling unit having a pump for discharging lubricating oil to the bearing and a tank for holding the lubricating oil to be discharged from the pump, which is provided next to the bearing in the axial direction.
With
A rolling bearing device in which the fixed wheel and the tank are in direct contact with each other, and the portion of the tank in contact with the fixed wheel is made of metal. The rolling bearing device according to claim 1, wherein the tank has a heat sink as a portion in contact with the fixed wheel. The rolling bearing device according to claim 1 or 2, wherein the pump and the fixed ring are arranged between each other via a heat transfer material.

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