JP2003202029A - Rolling bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing device which extends a life by reducing foreign matter invading into a rolling bearing device. <P>SOLUTION: This rolling bearing device comprises a housing 11b, a shaft 11a inserted into the housing 11b, and rolling bearings 14 and 15 installed between the housing 11b and the shaft 11a to support the housing and the shaft rotatably relative to each other. The rotating member 12 of a compressor part of impeller type, scroll type, screw type, and swash plate type is fitted to the end part of the housing 11b or the shaft 11a, and a seal structure 1 is fitted to rolling bearings 14 and 15 at least on the rotating member 12 side. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing device having a rolling bearing for supporting a rotary shaft to which a compressor part such as an impeller type, a scroll type, a screw type and a swash plate type is fixed, and particularly steam used in a fuel cell. The present invention relates to a rolling bearing device suitable for a pump, a compressor device and the like.

[0002]

2. Description of the Related Art For example, a fuel cell is classified into a solid polymer type, a solid electrolyte type, a phosphoric acid type, a molten carbonate type, and an alkaline type according to the electrolyte used. In both types of fuel cells, both sides of an electrolyte plate or an electrolyte membrane are sandwiched between cathode (oxygen electrode) and anode (fuel electrode) electrodes, and oxygen (O 2
₂ ) is supplied and hydrogen (H ₂ ) as a fuel gas is supplied to the anode side as one cell, and each cell via a separator is laminated in multiple layers to form a stack. .

As a conventional air supply device for supplying air by pressure to the cathode side of the fuel cell, a turbocharger system in which an exhaust gas turbine drives a compressor, and a motor drives a compressor. There is a motor drive system. Also, when supplying oxygen and hydrogen to the fuel cell, for example, solid polymer type,
Depending on the type of fuel cell, it is necessary to add water vapor to react, and when gasoline is used as fuel, for example, very high temperature water vapor is required, and a vapor pressure pump is required to increase energy efficiency. There is a case.

FIG. 21 shows an example of a steam pump. Figure 2
In the steam pump 350 of No. 1, an impeller 352 is attached to a rotary shaft 351a, and the rotary shaft 351a is supported by rolling bearings 354 and 355. Rotating shaft 3
The impeller 352 rotates at high speed with the high speed rotation of 51a, and the water vapor sucked from the water vapor suction port 353 is
It is pressurized by the centrifugal force of the impeller 352 and passes through a pressure volute 356c formed by the impeller housing 356a and the back plate 356b to discharge water vapor (not shown).
Sent by pressure.

Rolling bearing 35 for supporting the rotary shaft 351a
Oil lubrication or grease lubrication is adopted as the lubrication method for 4,355. In the case of oil lubrication, a system for supplying lubricating oil is required. However, for example, as a fuel cell system for automobiles, weight reduction and simplification of the system are required, and therefore oil lubrication is not suitable. Further, since there is a problem that the lubricating oil of the bearing is mixed with compressed air and water vapor, the lubricating method of the impeller supporting rolling bearing of the steam pump and the compressor used in the automobile fuel cell system is preferably grease lubrication.

[0006]

However, in the water vapor pump 350, the back space 3 of the impeller 352 is used.
When the pressure of 59 is changed from negative pressure to positive pressure, the water vapor is rolled and the bearing 3
There is a possibility that it will enter the inside of 54,355. Bearing ring (outer ring,
Between the inner ring) and the rolling elements, rolling and sliding motion is performed via the EHL oil film (elastohydrodynamic oil film), but if water vapor enters the grease under the above-mentioned conditions, the oil film will be very difficult to form. . When metal is used for the bearing ring material and rolling element material, the oil film becomes thinner due to heat generation due to sliding friction during high-speed rotation, and wear is likely to occur due to metal contact, causing seizure. To be done.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a rolling bearing device and a compressor device for a fuel cell, which can reduce foreign matter entering the inside of the rolling bearing device.

[0008]

The object of the present invention is achieved by the following constitution. (1) A rolling bearing including a housing, a shaft fitted in the housing, and a rolling bearing interposed between the housing and the shaft to rotatably support the housing and the shaft. In the device, a rotary member of a compressor component such as an impeller type, a scroll type, a screw type, a swash plate type is attached to an end of the housing or the shaft, and a seal structure is provided at least on the rotary member side of the rolling bearing. A rolling bearing device characterized by the above. (2) The rolling bearing device according to (1), wherein the seal structure has a bearing seal member extending between the bearing rings of the rolling bearing. (3) The above-mentioned (1), wherein the seal structure has a bearing device seal member extending between the housing and the shaft.
Alternatively, the rolling bearing device according to (2). (4) The bearing device seal member is configured such that when the relative rotation speed of the housing and the shaft exceeds a predetermined value, the bearing device seal member is deformed by centrifugal force and does not come into contact with other members. Rolling bearing device. (5) The bearing device sealing member includes an elastic portion that extends in a direction inclined with respect to the radial direction of the shaft and is in contact with another member to seal between the housing and the shaft,
The rolling bearing device according to (3), wherein when the relative rotational speed of the housing and the shaft exceeds a predetermined value, the elastic portion is elastically deformed by centrifugal force and does not come into contact with other members. (6) The rolling bearing device according to any one of (1) to (5), which is used as a compressor device for a fuel cell.

According to the rolling bearing device having the above structure, the seal structure can remarkably prevent foreign matter such as water from entering the inside of the rolling bearing and the inside of the rolling bearing device. In this way, the formation of the oil film is not hindered, wear and the like can be prevented, and the life of the rolling bearing device can be extended.

When the rolling bearing device having the above-mentioned structure is used in the compressor device, the seal structure reliably prevents foreign matter such as moisture from entering the inside of the rolling bearing and the compressor device. Therefore, the formation of the oil film is not obstructed, and wear and the like are prevented, so that the life of the compressor device is extended. Therefore, the rolling bearing device described above is suitable for a compressor device, particularly for a fuel cell compressor device.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 shows a water vapor pump to which the rolling bearing device according to the first embodiment of the present invention is applied.
The steam pump includes a housing 11b and a housing 11b.
Rolling having a rotary shaft 11a fitted in b and two rolling bearings (angular ball bearings) 14 and 15 arranged between the housing 11b and the rotary shaft 11a at a predetermined interval in the axial direction. The bearing device 10 is built in.

An inner ring spacer 11c is mounted between the inner rings of the two angular ball bearings 14 and 15, and an outer ring spacer 11d is mounted between the outer rings. That is, by applying a preload, the positioning in the axial direction is made accurate, the swing of the rotary shaft 11a is suppressed, and the slip of the balls is suppressed. The bearings 14 and 15 are backside combined.

One end of the rotating shaft 11a has one bearing 14
The impeller 12 is attached to the tip side of the impeller 12. The other end of the rotating shaft 11a has the other bearing 1
5, and has a structure driven by an electric motor (not shown). A mechanical seal 9 is provided on the electric motor side of the bearing 15 (right side in the figure). The mechanical seal 9 is a contact type sealing device, and completely seals between the rotary shaft 11a and the housing 11b here.

The impeller 1 of the bearing 14 on the impeller 12 side
The bearing seal member 1 is provided at the axial end on the second side. The bearing seal member 1 is composed of a seal main portion (core bar portion) and a seal lip portion, and the seal main portion is mounted and fixed to the outer ring. The seal lip is made of elastic material (rubber material: nitrile rubber, polyacrylic rubber, silicone rubber,
It is made of fluororubber or the like) and forms a labyrinth with a seal groove formed at an axial end portion of the inner ring. That is, the bearing seal member 1 is a non-contact type seal member.

In the bearings 14 and 15, the outer ring, inner ring and balls may be made of any material such as SUS440C, stainless steel, bearing steel such as SUJ2, heat resistant steel such as M50, carburized steel and ceramics material. Further, the surface may be subjected to surface modification by nitriding treatment, ceramic spraying, DLC or the like. The cages of the bearings 14 and 15 are PI (polyimide), PEEK (polyether ether ketone), PP.
Any material such as S (polyphenylene sulfide), PA (polyamide), PAI (polyamide imide), PES (polyether sulfone), PEI (polyether imide), brass and iron may be used. As the cage guide type, any type of outer ring guide, inner ring guide, and ball guide may be adopted.

In this steam pump, the impeller 12 rotates at high speed as the rotary shaft 11a rotates at high speed, and the steam sucked from the steam suction port 13 is pressurized by the impeller 12 and the impeller housing 16a and the back plate 16b. It is pressure-fed from a water vapor discharge port (not shown) through the pressure volute 16c formed in 1. In the present embodiment, the bearing seal member 1 can remarkably prevent water vapor from entering the rolling bearing 14 and the rolling bearing device 10 when the back space 19 of the impeller 12 changes from negative pressure to positive pressure. In this way, the formation of an oil film is not hindered even when exposed to a steam environment, wear and the like can be prevented, and the life of the rolling bearing device 10 can be extended.

FIG. 2 shows a water vapor pump to which the rolling bearing device 20 of the second embodiment of the present invention is applied. In the embodiments described below, members having the same configurations and functions as those already described in the first embodiment will be denoted by the same reference numerals in the drawings and will not be described.

As shown in FIG. 2, in this embodiment, a non-contact type bearing seal member 1 is provided at the end of the bearing 14 on the impeller 12 side on the impeller 12 side, and the bearing 15 on the opposite impeller side is provided. A non-contact type bearing seal member 1 is provided at the axial end on the side opposite to the impeller. In this embodiment, the bearing seal member 1 allows the water vapor to roll on both the impeller 12 side and the opposite impeller side.
It is possible to remarkably prevent the intrusion into the inside of the rolling bearing 5 and the inside of the rolling bearing device 10. Since the structure prevents the entry of water vapor from the side opposite to the impeller, the life of the rolling bearing device 20 can be extended even when the side opposite the impeller is in a water vapor environment.

FIG. 3 shows a water vapor pump to which the rolling bearing device 30 of the third embodiment of the present invention is applied. As shown in FIG. 3, in the present embodiment, the bearing 14 on the impeller 12 side
A contact type bearing seal member 2 is provided at the axial end portion of the impeller 12 side. The bearing seal member 2 is composed of a seal main portion (core bar portion) and a seal lip portion, and the seal main portion is mounted and fixed to the outer ring. The seal lip is made of an elastic material (rubber material: nitrile rubber, polyacrylic rubber, silicon rubber, fluororubber, etc.), and its tip contacts the side surface of the seal groove formed at the axial end of the inner ring. ing.

FIG. 4 shows a water vapor pump to which the rolling bearing device 40 of the fourth embodiment of the present invention is applied. As shown in FIG. 4, in the present embodiment, the bearing 14 on the impeller 12 side
The contact type bearing seal member 2 is provided at the axial end portion of the impeller 12 side, and the contact type bearing seal member 2 is provided at the anti impeller side axial end portion of the anti-impeller side bearing 15. There is.

FIG. 5 shows a water vapor pump to which the rolling bearing device 50 of the fifth embodiment of the present invention is applied. As shown in FIG. 5, in the present embodiment, the bearing 14 on the impeller 12 side
The bearing device seal member 3 is provided on the impeller side of the. In the present embodiment, the bearing device seal member 3 includes a first portion 3a arranged on the inner peripheral side and a second portion 3b arranged on the outer peripheral side. The first portion 3a rotates integrally with the rotating shaft 11a. The first portion 3a includes a tubular portion that is fitted onto the rotating shaft 11a, and a shield plate that projects radially outward from the outer peripheral surface of the tubular portion in a ring shape. A lip-shaped elastic portion 3c extending in a direction inclined to the impeller side with respect to the radial direction is provided on the tip end side of the shield plate. The second portion 3b includes a tubular portion that is fitted into the housing 11b, and a shield plate that protrudes radially inward from the inner peripheral surface of the tubular portion in a ring shape. The shield plate of the second portion 3b is arranged adjacent to the shield plate of the first portion 3a on the side opposite to the impeller with a minute gap. This second part 3b
The elastic portion 3c of the first portion 3a is in contact with the side surface of the shield plate.

When the rotation speed of the rotating shaft 11a exceeds a predetermined value, the elastic portion 3 extending in the direction inclined with respect to the radial direction.
The c is pulled by the centrifugal force so as to be parallel to the radial direction and does not come into contact with the second portion 3b. That is, the first portion 3a and the second portion 3b are in a non-contact state. As the elastic portion 3c, one made of a rubber material (nitrile rubber, polyacrylic rubber, silicon rubber, fluororubber, etc.) can be adopted.

FIG. 6 shows a water vapor pump to which the rolling bearing device 60 of the sixth embodiment of the present invention is applied. In this embodiment, the form of the bearing device seal member 4 provided on the impeller side of the bearing 14 on the impeller 12 side is different from that of the fifth embodiment. In the present embodiment, the bearing device seal member 4 includes the first portion 4a arranged on the inner peripheral side and the second portion 4b arranged on the outer peripheral side. First part 4a
Rotates integrally with the rotating shaft 11a. First part 4a
Includes a tubular portion fitted onto the rotating shaft 11a, and a shield plate having an L-shaped cross section, which is provided in a ring-like shape so as to project radially outward from the outer peripheral surface of the tubular portion. The tip side of the shield plate extends to the anti-impeller side substantially parallel to the axial direction, and the tip end thereof has a lip-shaped elastic portion 4c extending in a direction inclined toward the inner peripheral side.
Is provided. The second portion 4b is the housing 11b.
And a shield plate having an L-shaped cross section, which is provided in a ring shape so as to project radially inward from the inner peripheral surface of the cylinder portion. The tip side of the shield plate extends to the impeller side substantially parallel to the axial direction, and the elastic portion 4c of the first portion 4a is in contact with the outer peripheral surface thereof.

When the rotation speed of the rotating shaft 11a exceeds a predetermined value, the tip of the elastic portion 4c is pulled by the centrifugal force and does not come into contact with the second portion 4b. That is, the first portion 4a and the second portion 4b are brought into a non-contact state.

FIG. 7 shows a steam pump to which the rolling bearing device 70 of the seventh embodiment of the present invention is applied. The present embodiment has a configuration in which the first embodiment and the fifth embodiment are combined. That is, the rolling bearing device 70
The non-contact bearing seal member 1 is provided at the end of the bearing 14 on the impeller 12 side in the impeller 12 side, and the bearing device seal member 3 is provided on the impeller side of the bearing 14.

FIG. 8 shows a water vapor pump to which the rolling bearing device 80 of the eighth embodiment of the present invention is applied. The present embodiment has a configuration in which the second embodiment and the fifth embodiment are combined. That is, the rolling bearing device 80
The non-contact type bearing seal member 1 is provided at the impeller 12 side axial end of the bearing 14 on the impeller 12 side, the bearing device seal member 3 is provided on the impeller side of the bearing 14, and the non-impeller side A non-contact bearing seal member 1 is provided at the end of the bearing 15 in the axial direction opposite to the impeller.

FIG. 9 shows a water vapor pump to which the rolling bearing device 90 of the ninth embodiment of the present invention is applied. This embodiment has a configuration in which the third embodiment and the fifth embodiment are combined. That is, the rolling bearing device 90
The contact-type bearing seal member 2 is provided at the end of the bearing 14 on the impeller 12 side in the impeller 12 side.
A bearing device seal member 3 is provided on the impeller side of No. 4.

FIG. 10 shows a water vapor pump to which the rolling bearing device 100 according to the tenth embodiment of the present invention is applied. This embodiment has a configuration in which the fourth embodiment and the fifth embodiment are combined. That is, in the rolling bearing device 100, the contact type bearing seal member 2 is provided at the impeller 12 side axial end of the impeller 12 side bearing 14.
The bearing device seal member 3 is provided on the impeller side of the bearing 14, and the contact type bearing seal member 2 is provided on the anti-impeller side axial end of the bearing 15 on the opposite impeller side.

FIG. 11 shows a water vapor pump to which the rolling bearing device 110 of the eleventh embodiment of the present invention is applied. The present embodiment has a configuration in which the first embodiment and the sixth embodiment are combined. That is, the non-contact type bearing seal member 1 is provided at the impeller 12 side axial end of the bearing 14 on the impeller 12 side of the rolling bearing device 110, and the bearing device seal member 4 is provided on the impeller side of the bearing 14. Has been.

FIG. 12 shows a steam pump to which the rolling bearing device 120 of the twelfth embodiment of the present invention is applied. This embodiment has a configuration in which the second embodiment and the sixth embodiment are combined. That is, the non-contact type bearing seal member 1 is provided at the impeller 12 side axial end of the bearing 14 on the impeller 12 side of the rolling bearing device 120, and the bearing device seal member 4 is provided on the impeller side of the bearing 14. The non-contact type bearing seal member 1 is provided at the end of the bearing 15 on the side opposite to the impeller in the axial direction on the side opposite to the impeller.

FIG. 13 shows a water vapor pump to which the rolling bearing device 130 of the thirteenth embodiment of the present invention is applied. This embodiment has a configuration in which the third embodiment and the sixth embodiment are combined. That is, the contact type bearing seal member 2 is provided at the impeller 12 side axial end of the impeller 12 side bearing 14 of the rolling bearing device 130.
The bearing device seal member 4 is provided on the impeller side of the bearing 14.

FIG. 14 shows a water vapor pump to which the rolling bearing device 140 of the fourteenth embodiment of the present invention is applied. The present embodiment has a configuration in which the fourth embodiment and the sixth embodiment are combined. That is, the contact-type bearing seal member 2 is provided at the impeller 12 side axial end of the impeller 12 side bearing 14 of the rolling bearing device 140.
The bearing device seal member 4 is provided on the impeller side of the bearing 14, and the contact type bearing seal member 2 is provided on the anti-impeller side axial end of the bearing 15 on the opposite impeller side.

The present invention is not limited to the above-described embodiment, but can be appropriately modified and improved.
As a preloading method, a fixed position preload is suitable for applications requiring rigidity, and a constant pressure preload using a spring or the like is suitable for high speed applications. Further, as the direction of preload, the rotating shaft 11a
The back combination, which has a large action point distance and excellent load capacity for moment load, is more suitable, but a front combination may be adopted. The materials of the inner races, outer races, balls, and cages of the bearings 14 and 15 are not limited to those described above. Further, the bearings 14 and 15 may be deep groove ball bearings instead of the angular ball bearings. As a method of lubricating the bearings 14 and 15, grease lubrication is preferable because, for example, in a fuel cell system mounted on an automobile, weight reduction and system simplification are required. Grease lubrication is desirable for equipment that needs to minimize the mixing of the bearing lubricant from the impeller-side bearing 14 into the pumping medium. Oil-air lubrication, trace oil supply lubrication, or forced oil lubrication may be used when the bearing lubricant is allowed to be mixed in the pumping medium to some extent, or when grease lubrication may cause insufficient lubrication. In the above-described embodiment, the electric motor is used as the driving method, and the coupling is used for the connection. When it does not matter that the atmosphere penetrates into the pumping chamber with the impeller through the rolling bearing device, for example, when steam or air containing oxygen is pumped, a labyrinth seal is placed between the rotary shaft and the electric motor. The coupling may be adopted. However, in the case of pressure-feeding of water vapor containing hydrogen, a magnetic coupling can be adopted as the coupling to completely seal the rolling bearing device and prevent the invasion of the atmosphere.

FIG. 15 is a sectional view showing a schematic structure of a scroll type compressor device according to a fifteenth embodiment of the present invention.

Referring to FIG. 15, the scroll compressor device 200 includes a compression mechanism portion 210 for compressing a fluid such as air sent to an electrode of a fuel cell (not shown) by the fixed scroll 211 and the orbiting scroll 212, and a compression mechanism portion 210. A drive motor unit 220 having a drive motor 221 for driving the motor, and a crank mechanism unit 230 housed in the motor housing 201 together with the drive motor unit 220 and transmitting the rotation of the motor main shaft 222 of the drive motor unit 220 to the orbiting scroll 212. With.

In the drive motor unit 220, the drive motor 221 has the motor main shaft 2 inside the motor housing 201.
A rotor 223 fitted into the rotor 22 and a stator 22 provided around the rotor 223 and wound with a coil 224.
5 and.

The motor main shaft 222 has a crank pin 222.
The a side is rotatably supported by the motor housing 201 via an angular ball bearing 202, and the right end portion in FIG.
It is rotatably supported by 04.

The angular contact ball bearing 202 has a non-contact type bearing seal member 1 similar to that of the first embodiment, or a contact type similar to that of the second embodiment, to the left end face (end face on the compression mechanism 210 side) in FIG. The bearing seal member 2 is provided. The bearing seal member 1 or the bearing seal member 2 prevents foreign matter such as water vapor from entering the inside of the bearing 202 from the compression mechanism portion 210 side, thereby achieving a longer life.

That is, in the case of the bearing seal member 1, it is composed of a seal main portion (core bar portion) and a seal lip portion, and the seal main portion is mounted and fixed to the outer ring. The seal lip is made of an elastic material (rubber material: nitrile rubber, polyacrylic rubber, silicon rubber, fluororubber, etc.) and forms a labyrinth with the seal groove formed at the axial end of the inner ring. There is. Further, in the case of the bearing seal member 2, it is composed of a seal main portion (core metal portion) and a seal lip portion, and the seal main portion is mounted and fixed to the outer ring.
The seal lip is made of an elastic material (rubber material: nitrile rubber,
It is made of polyacrylic rubber, silicon rubber, fluororubber or the like), and its tip is in contact with the side surface of the seal groove formed at the axial end portion of the inner ring.

On the crankpin 222a side of the ball bearing 202, the motor main shaft 222 has an oil seal 206 between it and the motor housing 201, and at the right end in FIG. A seal 207 is interposed.

A balance weight 222b is provided on the motor main shaft 222, and the balance weight 222b is provided.
As a result, the moment of inertia generated when the orbiting scroll 212 turns is canceled out, and vibration is reduced.

In the compression mechanism section 210, the fixed scroll 211 is a spiral scroll in which a fixed spiral portion 211c is erected from the fixed base 211a in a front housing 213 composed of a disk-shaped fixed base 211a and an outer peripheral wall 211b. It is formed in. A discharge port 214 for air compressed between the fixed scroll 211 and the orbiting scroll 212 is provided in the fixed base 211a at approximately the center in the vertical direction in FIG. The discharge port 214 communicates with the electrode of the fuel cell.

In the orbiting scroll 212, the orbiting spiral portion 212a is formed in a spiral shape by being erected from a disk-shaped orbiting base 212b. Swivel base 212b
A concave holding portion 212c formed in a cylindrical shape having a bottom is provided substantially at the center on the rear side of the.

The crank mechanism section 230 is a drive crank mechanism 231 that causes the orbiting scroll 212 to perform an orbiting motion.
And a rotation prevention mechanism 232 for preventing rotation of the orbiting scroll 212. The crank mechanism portion 231 orbits the orbiting scroll 212 by transmitting the driving force of the drive motor 221 to the orbiting scroll 212 of the compression mechanism portion 210 via a crank pin 222a eccentrically provided with respect to the motor main shaft 222. Let

That is, the drive crank mechanism 230 includes a concave holding portion 212c provided on the orbiting scroll 212,
It has a clamp pin 222a of the motor main shaft 222 and a pair of left and right needle roller bearings 233 in FIG. 5 that allow the crank pin 222a to rotate with respect to the orbiting scroll 212. The rotation prevention mechanism 232 is used for the orbiting scroll 21.
2 and the motor housing 201.

The outer ring 233a of the needle roller bearing 233 or the inner ring (not shown) has, for example, JIS steel types SUS304, S.
Austenitic stainless steel such as US316 and JI
A soft corrosion-resistant steel such as a ferritic stainless steel such as S steel type SUS410 or SUS430 can be preferably used as a material. In this case, it is preferable to carry out carburizing treatment or nitriding treatment in order to improve wear resistance and durability. 50 for carburizing and nitriding
Bionite and NV super-nitriding treatment (both trade names of Air Water Co., Ltd.), which can be treated at a relatively low temperature of 0 ° C. or less, are suitable. If it can be processed at a low temperature, the deformation at the time of carburizing or nitriding can be small, and it can be processed with the cage and the rolling element incorporated in the outer ring, and the increase in manufacturing cost can be suppressed.

As the rotation preventing mechanism 232, an Oldham coupling (not shown) or a pin & ring coupling is preferably used in addition to the ball coupling 234 described above.

The operation of this embodiment will be described. In the scroll type compressor device 200, the drive motor 221
When electric power is supplied to the motor main shaft 222, the motor main shaft 222 rotates, and the rotation is transmitted to the orbiting scroll 212 via the drive crank mechanism 230. The orbiting scroll 212 orbits while meshing with the fixed scroll 211 as the motor main shaft 222 rotates, sucks air or the like from the suction port (not shown) to the fixed scroll 211, and compresses with the fixed scroll 211. Let Then, compressed air or the like is discharged from the discharge port 214 to the electrode side of the fuel cell.

At this time, the angular contact ball bearing 202 of FIG.
The bearing seal member 1 or the bearing seal member 2 provided on the middle left end face (the end face on the compression mechanism 210 side) prevents foreign matter such as water vapor from entering the bearing 202 from the compression mechanism 210 side. As a result, the angular contact ball bearing 202
Longer life is achieved.

FIG. 16 is a sectional view showing a schematic structure of a scroll type compressor device according to a sixteenth embodiment of the present invention. Referring to FIG. 16, in the scroll compressor device 240, the crank mechanism unit 250 includes a drive crank mechanism 2 that causes the orbiting scroll 212 to perform an orbiting motion.
51 and a driven crank mechanism 252 that prevents the orbiting scroll 212 from rotating.

The driven crank mechanism 252 includes a concave holding portion 212c provided on the orbiting scroll 212, a crank pin 253a of the driven crankshaft 253, and a radial ball bearing 254 that allows the crank pin 253a to rotate with respect to the orbiting scroll 212. Consists of. Driven crankshaft 2
53 is a double row ball bearing 2 on the side opposite to the crank pin 253a.
It is rotatably supported by the motor housing 201 via 55.

The left end surface of the angular ball bearing 202 in FIG. 16 (compression mechanism portion 210 side), the right end surface of the radial ball bearing 254 in FIG. 16 and the left end surface of the double row ball bearing 255 (compression mechanism portion 210) in FIG. The side) is provided with a non-contact type bearing seal member 1 similar to that of the first embodiment or a contact type bearing seal member 2 similar to that of the second embodiment. With the bearing seal member 1 or the bearing seal member 2,
Foreign matter such as water vapor is prevented from entering the inside of the bearing 202 from the compression mechanism 210 side, and a long life is achieved.

Further, the driven crankshaft 253 is provided with a balance weight 253b similarly to the motor main shaft 222, and the balance weight 253b cancels the moment of inertia generated when the orbiting scroll 212 orbits to reduce the vibration. ing. Other configurations and operations are similar to those of the fifteenth embodiment.

FIG. 17 is a sectional view showing the schematic arrangement of a swash plate compressor apparatus according to the seventeenth embodiment of the present invention.
Referring to FIG. 17, a swash plate type compressor device 260
Is a one-sided inclined plate 2 for supplying a fluid such as air to the fuel cell electrode.
The compression mechanism portion 270 that compresses by the reciprocating motion of the piston 272 accompanying the rotation of 71 and the motor spindle 28 of the drive motor 281
The rotation of 2 causes the compression mechanism 27 to pass through the drive shaft 273.
And a drive motor unit 280 for driving 0.

In the compression mechanism portion 270, the piston 27
2 is provided in the crank chamber 262 of the cylinder block 261 so as to be capable of reciprocating along the axial direction of the drive shaft 273, and is connected to the one-sided inclined plate 271 via the swing plate 274 and the rod 275. . The drive shaft 273 is attached to a support member 263 provided in the cylinder block 261,
It is rotatably supported via a radial bearing 276. The single-sided inclined plate 271 is attached to the outer peripheral surface of the drive shaft 273 so as to rotate integrally with the drive shaft 273. The single-sided inclined plate 271 can rotate relative to the support member 263 via a thrust bearing 277, and can rotate relative to the swing plate 274 via a thrust bearing 278.

Radial bearing 27 for supporting drive shaft 273
The non-contact type bearing seal member 1 similar to that of the first embodiment or the contact type bearing seal member 2 similar to that of the second embodiment is provided on the right end surface (piston side) in FIG. . The bearing seal member 1 or the bearing seal member 2 prevents foreign matter such as water vapor from entering the inside of the bearing 276 from the piston 272 side, thereby achieving a longer life.

In the drive motor section 280, the drive motor 281 has a rotor 283 fitted in the motor main shaft 282.
And a stator 285, which is provided on the outer peripheral side of the rotor 283 and around which a coil 284 is wound,
Prepare for 6

The operation of this embodiment will be described. In the one-sided swash plate compressor device 260, when electric power is supplied to the drive motor 281, the motor main shaft 282 rotates, and the rotation causes the one-sided inclined plate 272, the swing plate 274, and the rod 275.
Is transmitted to the piston 272 via. Piston 272
The crank chamber 262 as the motor main shaft 282 rotates.
It reciprocates in the axial direction inside, sucks and compresses air and the like and discharges it to the electrode side of the fuel cell.

At this time, the bearing seal member 1 or the bearing seal member 2 provided on the right end surface (piston 272 side) in FIG. 17 of the radial bearing 276 allows foreign matter such as water vapor to enter the bearing 276 from the piston 272 side. Is prevented. As a result, the life of the radial bearing 276 is increased.

FIG. 18 is a sectional view showing a schematic structure of a screw type compressor device according to an eighteenth embodiment of the present invention. Referring to FIG. 18, the screw compressor device 290 includes a compression mechanism unit 300 that compresses fluid such as air sent to the electrodes of the fuel cell by meshing rotation of the main rotor 301 and the auxiliary rotor 302, and a motor main shaft of the drive motor 281. And a drive motor unit 280 that drives the compression mechanism unit 300 by the rotation of 282. The drive motor unit 280
Are the same as those of the swash plate type compressor device 260 of the seventeenth embodiment described above, and are denoted by the same reference numerals, and description thereof will be omitted.

In the compression mechanism section 300, the main rotor 30
1 and the sub-rotor 302 are formed in a corresponding spiral shape and can mesh with each other to rotate, and
02a is rotatably supported by a housing 307 via ball bearings 303, 304, 305, and 306.

That is, the main rotor 301 is rotatably supported by the housing 307 via a pair of ball bearings 303 that are adjacent to each other in the left side rotary shaft 301a in FIG. Further, the main rotor 301 is rotatably supported by a housing on a rotation shaft 301a on the right side in FIG. 18 via a ball bearing 304. The sub-rotor 302 is rotatably supported by the housing 307 via a pair of ball bearings 305 whose left-side rotary shafts 302a in FIG. 18 are axially adjacent to each other. In addition, the sub rotor 302 includes a rotary shaft 302a on the right side in FIG.
It is rotatably supported by 7. An oil seal 308 is interposed between the main rotor 301 and the housing 307 axially inward of the ball bearings 303 and 304. Further, on the rotary shaft 302a of the auxiliary rotor 302, the housing 3 is provided inside the ball bearings 305 and 306 in the axial direction.
An oil seal 309 is interposed between the oil seal 309 and the oil seal 07.

The main rotor 301 and the sub-rotor 302 are interlocked with each other via connecting gears 310 provided on the rotary shafts 301a and 302a on the left side in FIG. Main rotor 3
The driven gear 311 is provided at the left end of the rotary shaft 301a on the left side of FIG.
Is meshed with the drive gear 289 of the drive shaft 288 fitted to the motor main shaft 282 of the drive motor 281. Therefore, the main rotor 301 controls the rotation of the motor main shaft 282 so that the drive shaft 288, the drive gear 289 and the driven gear 31 rotate.
1 is transmitted. The rotation of the main rotor 301 is transmitted to the sub rotor 302 via the connecting gear 310. The drive shaft 288 is a pair of ball bearings 312 that are adjacent to each other in the axial direction.
It is rotatably supported by the housing 313 via. The drive shaft 288 is provided with an oil seal 314 interposed between the drive shaft 288 and the housing 313 near the left end in FIG.

The right end surface of the ball bearing 303 and the ball bearing 305 in FIG. 18 and the ball bearing 304 and the ball bearing 306 in FIG.
A non-contact type bearing seal member 1 similar to that of the first embodiment or a contact type bearing seal member 2 similar to that of the second embodiment is provided on each of the middle left end faces. The bearing seal member 1 or the bearing seal member 2 prevents foreign matter such as water vapor from entering the inside of the bearings 303, 304, 305, and 306 from the compression mechanism portion 300 side, thereby achieving a long life.

The operation of this embodiment will be described. In the screw type compressor device 290, the drive motor 281
When electric power is supplied to the motor main shaft 282, this rotation causes the drive shaft 288, the drive gear 289, and the driven gear 3 to rotate.
It is transmitted to the rotating shaft 301 a of the main rotor 301 via 11. Then, the rotation of the rotating shaft 301a causes the connecting gear 31 to rotate.
It is transmitted to the rotating shaft 302a of the auxiliary rotor 302 via 0. The main rotor 301 and the sub-rotor 302 rotate in mesh with each other to suck and compress air or the like and discharge it to the electrode side of the fuel cell.

The compression mechanism 3 of the ball bearings 303, 304, 305, 306 for supporting the rotary shafts 301a, 302a of the main rotor 301 and the auxiliary rotor 302 on the housing 307.
The bearing seal member 1 or the bearing seal member 2 provided on the end face on the 00 side allows the bearings 303, 304, 305, to the bearings 303, 304, 305, from the main rotor 301 and the auxiliary rotor 302 sides of the compression mechanism unit 300.
Foreign matter such as water vapor is prevented from entering the inside of 306. As a result, the life of each ball bearing 303, 304, 305, 306 is extended.

FIG. 19 is a sectional view showing an impeller type compressor device to which the rolling bearing device of the nineteenth embodiment is applied. Referring to FIG. 19, the impeller-type compressor device 310 includes an impeller 32 in the impeller housing 322, which is generated when an electric motor (not shown) rotates a rotary shaft 321 at a high speed by supplying fluid such as air to the electrodes of the fuel cell.
19 that rotatably supports the compression mechanism unit 320 that compresses by the rotation of 3 and the rotation shaft 321 in the housing 311.
A pair of middle left and right angular ball bearings 330 and 331 are provided.

A contact type bearing seal member 2 similar to that of the second embodiment is provided on the left end face (end face on the impeller 323 side) of the angular ball bearing 330 in FIG. The bearing seal member 2 prevents water vapor or the like from entering the angular contact ball bearing 330 from the impeller 323 side. Further, the respective angular ball bearings 330 and 331 are combined in the back surface, and the inner ring spacer 332 and the outer ring spacer 333 are interposed between the inner and outer rings 330a, 331a, 330b and 331b of the angular ball bearings 330 and 331, respectively. Has been done. As a result, the angular contact ball bearings 330, 331
A preload is applied to the shaft to secure axial positioning, thereby suppressing vibration of the rotary shaft 321 and suppressing ball slippage.

The operation of this embodiment will be described. In the impeller-type compressor device 310, when the impeller 323 rotates at high speed as the rotary shaft 321 rotates, the suction port 3
The water vapor sucked from 12 is accelerated by the impeller 323, pressurized by the pressure volute 314 formed by the impeller housing 322 and the back plate 313, and discharged from the discharge port (not shown). At this time, even if the pressure in the back space 315 of the impeller 323 changes from a negative pressure to a positive pressure, intrusion of water vapor and the like into the angular ball bearing 330 is prevented by the bearing seal member 2. Therefore, the formation of an oil film in a water vapor environment is not hindered, and wear and the like can be prevented and the life can be extended.

FIG. 20 is a sectional view showing an impeller type compressor device to which the rolling bearing device of the twentieth embodiment is applied. Referring to FIG. 20, in the impeller-type compressor device 340, FIG.
A non-contact type bearing seal member 1 similar to that of the first embodiment is provided on the 0 middle left end face (end face on the impeller 323 side). Other configurations and operations are the same as those in the nineteenth embodiment.

[0071]

As described above, according to the present invention,
(EN) Provided are a rolling bearing device and a compressor device for a fuel cell, which can reduce the amount of foreign matter entering the inside and can extend the life.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a steam pump to which a rolling bearing device according to a first embodiment is applied.

FIG. 2 is a sectional view showing a water vapor pump to which the rolling bearing device of the second embodiment is applied.

FIG. 3 is a cross-sectional view showing a steam pump to which the rolling bearing device of the third embodiment is applied.

FIG. 4 is a cross-sectional view showing a steam pump to which a rolling bearing device of a fourth embodiment is applied.

FIG. 5 is a sectional view showing a water vapor pump to which the rolling bearing device of the fifth embodiment is applied.

FIG. 6 is a cross-sectional view showing a steam pump to which the rolling bearing device of the sixth embodiment is applied.

FIG. 7 is a cross-sectional view showing a water vapor pump to which the rolling bearing device of the seventh embodiment is applied.

FIG. 8 is a sectional view showing a water vapor pump to which the rolling bearing device of the eighth embodiment is applied.

FIG. 9 is a cross-sectional view showing a water vapor pump to which the rolling bearing device of the ninth embodiment is applied.

FIG. 10 is a cross-sectional view showing a steam pump to which the rolling bearing device of the tenth embodiment is applied.

FIG. 11 is a cross-sectional view showing a steam pump to which the rolling bearing device of the eleventh embodiment is applied.

FIG. 12 is a cross-sectional view showing a water vapor pump to which the rolling bearing device of the twelfth embodiment is applied.

FIG. 13 is a sectional view showing a water vapor pump to which the rolling bearing device of the thirteenth embodiment is applied.

FIG. 14 is a cross-sectional view showing a steam pump to which the rolling bearing device of the fourteenth embodiment is applied.

FIG. 15 is a sectional view showing a scroll type compressor device to which the rolling bearing device of the fifteenth embodiment is applied.

FIG. 16 is a sectional view showing a scroll type compressor device to which the rolling bearing device of the sixteenth embodiment is applied.

FIG. 17 is a sectional view showing a swash plate type compressor device to which the rolling bearing device of the seventeenth embodiment is applied.

FIG. 18 is a sectional view showing a screw type compressor device to which the rolling bearing device of the eighteenth embodiment is applied.

FIG. 19 is a sectional view showing an impeller-type compressor device to which the rolling bearing device of the nineteenth embodiment is applied.

FIG. 20 is a sectional view showing an impeller-type compressor device to which the rolling bearing device of the twentieth embodiment is applied.

FIG. 21 is a cross-sectional view showing a schematic configuration of a conventional water vapor pressure feeder.

[Explanation of symbols]

1, 2 bearing seal member 3,4 Bearing device seal member 10 Rolling bearing device 11a rotating shaft (axis) 11b housing 12 Impeller (rotating member) 14,15 Rolling shaft

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F16C 33/76 H01M 8/06 R 5H027 // H01M 8/06 F04B 27/08 N (72) Inventor Aramaki Hirotoshi Kanagawa Prefecture, Fujisawa-shi, Kugenuma 1-5-50, Niseko Co., Ltd. F-term (reference) 3H003 AA03 AB06 AC01 BC00 BC01 CA02 3H022 AA02 BA06 CA27 CA33 CA51 CA54 CA58 DA04 DA13 3H029 AA02 AA03 AB01 BB16 BB44 CC17 CC20 3H00 BB10 BB26 CC07 CC20 CC36 3J016 AA02 BB03 CA03 CA08 5H027 AA02 BA00

Claims (6)

[Claims] 1. A housing, a shaft fitted into the housing, and a rolling bearing interposed between the housing and the shaft to support the housing and the shaft so as to be rotatable relative to each other. In a rolling bearing device, a rotary member of a compressor component such as an impeller type, a scroll type, a screw type, or a swash plate type is attached to an end of the housing or the shaft, and a seal structure is provided at least on the rotary member side of the rolling bearing. Rolling bearing device characterized by the above. 2. The rolling bearing device according to claim 1, wherein the seal structure has a bearing seal member extending between the bearing rings of the rolling bearing. 3. The rolling bearing device according to claim 1, wherein the seal structure includes a bearing device seal member extending between the housing and the shaft. 4. The bearing device seal member according to claim 3, wherein when the relative rotation speed of the housing and the shaft exceeds a predetermined value, the bearing device seal member is deformed by centrifugal force and does not come into contact with other members. Rolling bearing device. 5. The bearing device seal member includes an elastic portion that extends in a direction inclined with respect to a radial direction of the shaft and is in contact with another member to seal between the housing and the shaft. The rolling bearing device according to claim 3, wherein when the relative rotation speed of the housing and the shaft exceeds a predetermined value, the housing is elastically deformed by a centrifugal force and does not come into contact with other members. 6. The rolling bearing device according to any one of claims 1 to 5, which is used as a compressor device for a fuel cell.