JP2002115668A - Rotary shaft support structure in fluid machinery - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prolong service life of a lip seal provided in parallel with a bearing without shortening service life of the bearing in fluid machinery. SOLUTION: Lip seals 45, 46 are arranged in protruding end parts 192, 202 of rotary shafts 19, 20 protruding in a gear storage chamber 331 by passing through a rear housing 14. The radial bearing 37 is attached to the protruding end part 192 through a serial base 47. The radial bearing 38 is attached to the protruding end part 202 through a serial base 48. Flanges 471, 481 are formed on the serial bases 47, 48. An inner ring 371 of the radial bearing 37 is brought into contact with the flange 471, and an inner ring 381 of the radial bearing 38 is brought into contact with the flange 481.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotating shaft support structure for a fluid machine which moves a fluid transfer member in a pump chamber based on rotation of a rotation shaft and transfers a fluid by the operation of the fluid transfer member.

[0002]

2. Description of the Related Art In a vacuum pump disclosed in Japanese Patent Application Laid-Open No. 2-157490, two adjacent rotors are rotated in a meshed state. The rotating operation of the two rotors rotating while meshing transfers gas. One of the rotating shafts of the rotor obtains driving force from a motor, and the other rotating shaft obtains driving force from the one rotating shaft via a gear mechanism.

[0003] Lubricating oil is stored in a housing for accommodating the gear mechanism, and the lubricating oil lubricates the gear mechanism. In order to prevent the lubricating oil from leaking into the pump chamber, in the device disclosed in Japanese Patent Application Laid-Open No. 2-157490, an end plate that separates the inside of the housing accommodating the gear mechanism and the compression chamber (pump chamber in the present application) is used. A lip seal is provided between a penetrating portion of the rotating shaft and the end plate. The lip seal prevents the lubricating oil in the housing from entering the compression chamber along the peripheral surface of the rotating shaft.

[0004]

When the lip seal deteriorates, the sealing function of the lip seal deteriorates. Lubrication of the lip seal with lubricating oil is necessary to suppress the deterioration of the lip seal.However, to extend the life of the lip seal, reduce the diameter of the rotating shaft and reduce the peripheral speed of the rotating shaft that is in sliding contact with the lip seal. Countermeasures to slow down are also effective.

[0005] However, the rotating shaft is supported by a bearing in a housing for accommodating the gear mechanism, and the diameter of the portion of the rotating shaft in the housing determines the diameter of the bearing. If the diameter of the rotating shaft is reduced to extend the life of the lip seal, a bearing having a rated diameter required for supporting the rotating shaft may not be used in some cases. If a bearing smaller than the required rated diameter is used, the bearing is rendered useless early.

SUMMARY OF THE INVENTION It is an object of the present invention to extend the life of a lip seal juxtaposed with a bearing without shortening the life of the bearing in a fluid machine.

[0007]

SUMMARY OF THE INVENTION The present invention is directed to a fluid machine that moves a fluid transfer member in a pump chamber based on rotation of a rotating shaft and transfers a fluid by the operation of the fluid transfer member. In one aspect of the present invention, the oil-existing region and the pump chamber are adjacent to each other, and the partition wall that penetrates the rotary shaft, and the position of the projecting portion of the rotary shaft that penetrates the partition wall and projects into the oil-existing region Bearing means for rotatably supporting a rotating shaft; contact-type sealing means for a shaft seal disposed so as to slide on a peripheral surface of a protruding portion of the rotating shaft between the partition wall and the bearing means; A diameter increasing table fitted to both the rotating shaft and the bearing means, and first position regulating means for regulating the position of the diameter increasing table with respect to the rotating shaft so as not to move in the axial direction of the rotating shaft; Moving in the axial direction of the rotating shaft. A second position restricting unit that restricts the position of the bearing unit with respect to the diameter increasing table; and a third position that restricts the position of the bearing unit with respect to the partition wall so that the bearing unit cannot move in the axial direction of the rotating shaft. A rotation shaft support structure including a regulating means is configured.

The diameter increasing table satisfies both the reduction of the diameter of the portion of the rotary shaft corresponding to the contact-type sealing means and the securing of the required diameter of the bearing means. The position of the diameter increasing stand is regulated by the first position regulating means so as to be immovable in the axial direction of the rotating shaft with respect to the rotating shaft. The position of the bearing means is restricted by the second position restricting means with respect to the diameter increasing table so as not to move in the axial direction of the rotating shaft. Further, the position of the bearing means is regulated with respect to the partition wall by the third position regulating means so as not to move in the axial direction of the rotating shaft. Therefore, the position of the rotating shaft is regulated with respect to the partition wall so as not to move in the axial direction.

According to the second aspect of the present invention, in the first aspect,
The contact-type sealing means is a lip seal that prevents oil in the oil-existing region from leaking to the pump chamber side along the peripheral surface of the rotating shaft.

[0010] The life of the lip seal is extended by the presence of the diameter increasing table. In the invention of claim 3, in claim 2, the lip seal is made of rubber. A rubber lip seal is a contact-type sealing means having high sealing performance.

According to a fourth aspect of the present invention, in any one of the first to third aspects, the bearing means is a radial bearing, and the diameter increasing base is a flange abutting on an end surface of an inner race of the radial bearing. And the flange is a part of the second position regulating means.

If a plurality of diameter increasing tables having different flange thicknesses are prepared, the position of the rotary shaft with respect to the partition wall in the axial direction of the rotary shaft can be adjusted by selecting one of the plurality of diameter increasing tables.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment in which the present invention is embodied in a roots pump will be described below with reference to FIGS.

As shown in FIG. 1, the multi-stage roots pump 11
The front housing 13 is joined to the front end of the rotor housing 12 of the first embodiment, and the closing body 36 is joined to the front housing 13. A rear housing 14 is joined to the rear end of the rotor housing 12. The rotor housing 12 includes a cylinder block 15 and a plurality of chamber forming walls 16. As shown in FIG. 2B, the cylinder block 15 includes a pair of block pieces 17 and 18, and the chamber forming wall 16 includes a pair of wall pieces 161 and 162. As shown in FIG. 1, the space between the front housing 13 and the chamber forming wall 16, the space between the adjacent chamber forming walls 16, and the space between the rear housing 14 and the chamber forming wall 16 are each a pump. Rooms 39, 40, 41, 42, 43
It has become.

A pair of rotating shafts 19 and 20 are rotatably supported by the front housing 13 and the rear housing 14 via radial bearings 21, 37, 22 and 38. Both rotating shafts 19 and 20 are arranged parallel to each other. The rotation shafts 19 and 20 are passed through the chamber forming wall 16. Radial bearings 21 and 22 including inner rings 211 and 221, outer rings 212 and 222 and balls 213 and 223.
2 are accommodation holes 131, 132 of the front housing 13.
It is fitted and accommodated. The radial bearings 37 and 38 including the inner races 371 and 381, the outer races 372 and 382, and the balls 373 and 383 are accommodated by being fitted into the support holes 141 and 142 of the rear housing 14.

A plurality of rotors 23, 24,
25, 26, 27 are integrally formed, and the same number of rotors 28, 29, 30, 31, 32 are integrally formed on the rotating shaft 20. The rotors 23 to 32 are
Are the same shape and the same size when viewed in the directions of the axes 191 and 201 of the first embodiment. The thickness of the rotors 23, 24, 25, 26, 27 is reduced in this order.
The thicknesses of 8, 29, 30, 31, 32 are designed to decrease in this order. The rotors 23 and 28 are housed in a pump chamber 39 in a state of being meshed with each other.
The pumps 4 and 29 are housed in the pump chamber 40 in a state of being engaged with each other. The rotors 25 and 30 are housed in the pump chamber 41 in a state of meshing with each other, and the rotors 26 and 31 are housed in the pump chamber 42 in a state of meshing with each other. The rotors 27 and 32 are housed in the pump chamber 43 in a state of being meshed with each other.

The gear housing 3 is mounted on the rear housing 14.
3 are assembled. The rotating shafts 19 and 20 penetrate the rear housing 14 and protrude into the gear housing 33, and projecting end portions 192 and 202 of the respective rotating shafts 19 and 20.
, Gears 34 and 35 are fixedly engaged with each other. An electric motor M is mounted on the gear housing 33. The driving force of the electric motor M is transmitted to the rotating shaft 19 via the shaft joint 44, and the rotating shaft 19 is rotated by the electric motor M in the direction of arrow R1 in FIGS. 2 (a), 2 (b) and 2 (c). Is done. The rotating shaft 20 obtains a driving force from the electric motor M via the gears 34 and 35, and the rotating shaft 20 is rotated by the rotating shaft 19 as shown by an arrow R2 in FIGS. 2 (a), 2 (b) and 2 (c). And rotate in the opposite direction.

As shown in FIG. 4, a lubricating oil Y is provided in a gear housing chamber 331 for housing a gear mechanism including gears 34 and 35.
Is stored. Gear storage chamber 331 which is an oil existing area
The lubricating oil Y inside is swept up by the rotating operation of the gears 34 and 35. The lubricating oil Y lubricates the gears 34, 35 and the radial bearings 37, 38.

As shown in FIGS. 1 and 2B, a passage 163 is formed in the chamber forming wall 16. FIG. 2 (b)
As shown in FIG.
4 and an outlet 165 are formed. Adjacent pump room 3
9, 40, 41, 42, and 43 communicate with each other via a passage 163.

As shown in FIG. 2A, the block piece 18
Is formed such that an inlet 181 communicates with the pump chamber 39. As shown in FIG.
Is formed so that a discharge port 171 communicates with the pump chamber 43. The gas introduced into the pump chamber 39 from the inlet 181 is rotated by the rotation of the rotors 23 and 28 to form the chamber forming wall 1.
6 from the inlet 164 via the passage 163 to the adjacent pump chamber 40 from the outlet 165. Hereinafter, similarly, the gas flows in the order of decreasing the volume of the pump chamber, that is, the pump chamber 4
They are transferred in the order of 0, 41, 42, 43. Pump room 43
The gas transferred to the discharge port is discharged from the discharge port 171 to the outside. The rotors 23 to 32 are fluid transfer bodies that transfer fluid.

As shown in FIG. 1, the radial bearing 2
The outer ring 212 of the radial bearing 22 is slidable with respect to the peripheral surface of the housing hole 131.
22 is slidable with respect to the peripheral surface of the accommodation hole 132. Rotary shaft 1 on front housing 13 side
Holding screws 55 and 56 are screwed to end surfaces of the holding members 9 and 20, and the position regulating bodies 57 and 58 are held by the holding screws 55 and 56. The position regulating bodies 57 and 58 abut on the inner rings 211 and 221 of the radial bearings 21 and 22. A circlip 5 is provided on the peripheral surfaces of the receiving holes 131 and 132.
3, 54 are attached. Radial bearing 2
The end faces of the outer races 212 and 222 of the first and second 22 contact the circlips 53 and 54.

As shown in FIG. 3, cylindrical protrusions 47, 48 are provided at the protruding ends 192, 202 of the rotating shafts 19, 20.
Are fitted. The inner ring 371 of the radial bearing 37 is fitted to the diameter increasing table 47, and the inner ring 381 of the radial bearing 38 is fitted to the diameter increasing table 48.
Flanges 471 and 481 are formed on the diameter increasing tables 47 and 48. Protruding ends 192, 202 of rotating shafts 19, 20
Are attached with circlips 49 and 50. The circlips 49 and 50 abut against end faces of the diameter increasing tables 47 and 48, and the positions of the diameter increasing tables 47 and 48 in the direction of the axes 191 and 201 of the rotating shafts 19 and 20 are regulated by the circlips 49 and 50. Protruding ends 19 of rotating shafts 19, 20
Nuts 51 and 52 are screwed into the nuts 2 and 202. The nut 51 contacts the end surface of the inner ring 371 of the radial bearing 37, and the nut 52 contacts the end surface of the inner ring 381 of the radial bearing 38.

When the nut 51 is tightened, the radial bearing 37 and the diameter increasing table 47 are sandwiched and held between the circlip 49 and the nut 51. In a state where the nut 52 is tightened, the radial bearing 38 and the diameter increasing table 48 are sandwiched and held between the circlip 50 and the nut 52. Also, the inner ring 37 of the radial bearing 37
1 is sandwiched and held between the nut 51 and the flange 471, and the inner ring 381 of the radial bearing 38 is sandwiched and held between the nut 52 and the flange 481.

The radial bearing 37 is held by the nut 51 and the circlip 49 so that the rotating shaft 19
Is determined in the direction of the axis 191. The circlip 49 and the nut 51 constitute first position restricting means for restricting the position of the diameter increasing table 47 so as not to move in the direction of the axis 191 with respect to the rotation shaft 19. The flange 471, the circlip 49, and the nut 51 of the diameter increasing table 47 constitute second position regulating means for regulating the position of the radial bearing 37 so as not to move in the direction of the axis 191 with respect to the diameter increasing table 47.

The radial bearing 38 is held by the nut 52 and the circlip 50,
, The position in the direction of the axis 201 is determined. The circlip 50 and the nut 52 cannot move in the direction of the axis 201 with respect to the rotary shaft 20 so that the radial bearing 38 cannot move.
Constitutes a first position restricting means for restricting the position. The flange 481, the circlip 50, and the nut 52 of the diameter increasing table 48 constitute second position regulating means for regulating the position of the radial bearing 38 so as not to move in the direction of the axis 201 with respect to the diameter increasing table 48.

The end surface of the outer ring 372 of the radial bearing 37 is in contact with the position regulating wall 143 at the bottom of the support hole 141. This contact is brought about by tightening the cap screw 55 so as to join the position regulating body 57 to the end face of the inner ring 211 of the radial bearing 21. The position restricting body 57, the holding screw 55, the nut 51, and the position restricting wall 143 serve as third position restricting means for restricting the position of the radial bearing 37 with respect to the rear housing 14 so as not to move in the direction of the axis 191 of the rotating shaft 19. Constitute.

The end surface of the outer ring 382 of the radial bearing 38 is in contact with the position regulating wall 144 at the bottom of the support hole 142. This contact is provided by tightening the cap screw 56 so as to join the position regulating body 58 to the end surface of the inner ring 221 of the radial bearing 22. The position restricting body 58, the holding screw 56, the nut 52, and the position restricting wall 144 form third position restricting means for restricting the position of the radial bearing 38 with respect to the rear housing 14 so as not to move in the direction of the axis 201 of the rotating shaft 20. Constitute.

The state in which the end surface of the outer ring 372 of the radial bearing 37 is in contact with the position regulating wall 143 is in the pump chamber 43.
The clearance between the end surface 145 of the rear housing 14 that forms the wall of the rotor and the rotor 27, the clearance between the end surface 133 of the front housing 13 that forms the wall of the pump chamber 39 and the rotor 23, and the rotors 23 to 27 The clearance between the adjacent wall of the chamber forming wall 16 is determined. The state in which the end surface of the outer ring 382 of the radial bearing 38 is in contact with the position regulating wall 144 is the rear housing 1
4, the clearance between the end surface 145 of the front housing 13 and the rotor 32, the clearance between the end surface 133 of the front housing 13 and the rotor 28, and the clearance between each of the rotors 28 to 32 and the wall surface of the adjacent chamber forming wall 16. I do.

The projecting ends 192, 20 of the rotating shafts 19, 20
2 are provided with lip seals 45 and 46 made of rubber. The lip seal 45 is a rear housing 1 which is a partition.
4 and the radial bearing 37, the lip seal 46 is provided between the rear housing 14 and the radial bearing 3.
Between 8. The lip seals 45, 46
Sliding contact is made with the peripheral surfaces of the protruding end portions 192 and 202 which serve as the protruding portions of the components 9 and 20, thereby providing a sealing effect. Lip seal 45
Prevents the lubricating oil Y in the gear housing chamber 331 from entering the pump chamber 43 along the peripheral surface of the protruding end 192 of the rotating shaft 19. The lip seal 46 is provided in the gear housing 331.
The lubricating oil Y inside is prevented from entering the pump chamber 43 along the peripheral surface of the protruding end 202 of the rotating shaft 20.

In the first embodiment, the following effects can be obtained. (1-1) The radial bearings 37 and 38 are
The diameters of 71 and 381 are the rated diameter Do (shown in FIG. 3). The protruding ends 192 of the rotating shafts 19, 20
The diameter D1 (shown in FIG. 3) of 202 is smaller than the rated diameter Do. The diameter increasing tables 47 and 48 compensate for the difference between the rated diameter Do of the radial bearings 37 and 38 and the diameter D1 of the protruding ends 192 and 202. The diameter increasing tables 47 and 48 are provided at the positions of the rotating shafts 19 and 20 corresponding to the lip seals 45 and 46 as the contact-type sealing means, that is, the projecting ends 192 and 20.
2 and the required diameters of the radial bearings 37 and 38 as bearing means are both satisfied. Therefore, the life of the lip seals 45, 46 juxtaposed with the radial bearings 37, 38 can be extended without shortening the life of the radial bearings 37, 38.

(1-2) A plurality of diameter increasing tables 47 having different thicknesses d (shown in FIG. 3) of the flange 471 are prepared, and if the thickness d of the flange 471 is changed, the radial bearing 37 with respect to the rotating shaft 19 can be changed. The position can be changed.
If the position of the radial bearing 37 with respect to the rotating shaft 19 is changed, the position of the rotating shaft 19 with respect to the rotor housing 12 in the direction of the axis 191 of the rotating shaft 19 is changed. Changing the position of the rotary shaft 19 with respect to the rotor housing 12 can be performed by changing the clearance between the end surface 145 of the rear housing 14 and the rotor 27, the end surface 1 of the front housing 13.
This results in a change in the clearance between the rotor 33 and the rotor 23 and the clearance between each rotor 23 to 27 and the wall surface of the adjacent chamber forming wall 16. Similarly, if a plurality of diameter increasing tables 48 having different thicknesses d of the flange 481 are prepared and the thickness d of the flange 481 is changed, the position of the radial bearing 38 with respect to the rotating shaft 20 can be changed.
If the position of the radial bearing 38 with respect to the rotating shaft 20 is changed, the position of the rotating shaft 20 with respect to the rear housing 14 and the rotor housing 12 in the direction of the axis 201 of the rotating shaft 20 is changed. Changing the position of the rotary shaft 20 with respect to the rotor housing 12 is performed by changing the clearance between the end surface 145 of the rear housing 14 and the rotor 32, the clearance between the end surface 133 of the front housing 13 and the rotor 28, and adjacent to each of the rotors 28 to 32. This causes a change in the clearance between the chamber forming wall 16 and the wall.

Such adjustment of the clearance is performed by appropriately selecting from a plurality of diameter increasing tables having different thicknesses d of the flanges 471 and 481. The structure in which the flanges 471 and 481 for clearance adjustment are provided on the diameter increasing tables 47 and 48 eliminates the need for a spacer dedicated to clearance adjustment. That is, flanges 471 and 48 for clearance adjustment.
The diameter increasing tables 47 and 48 provided with 1 reduce the number of parts.

(1-3) The radial bearings 3 are attached to the rotating shafts 19 and 20 by tightening the nuts 51 and 52.
The structure for positioning and holding the positions 7, 38 is simple.
(1-4) The rubber lip seals 45 and 46 are
The seals 9 and 20 have excellent close contact with the peripheral surface (that is, sealing performance), but have low wear resistance to sliding contact. Rotating shafts 19 and 2 slidingly contacting lip seals 45 and 46
The configuration in which the diameter of the protruding end portions 192 and 202 is reduced to reduce the peripheral speed improves the durability of the rubber lip seals 45 and 46 having excellent sealing performance.

Next, a second embodiment shown in FIG. 5 will be described. The same components as those in the first embodiment are denoted by the same reference numerals. Screws are formed on the outer peripheral surfaces of the cylindrical diameter increasing tables 59 and 60. A pair of nuts 61 and 62 are provided on the diameter increasing table 59.
Are screwed together, and a pair of nuts 63,
64 is screwed. One of the nuts 61 and 63 abuts one end surface of the inner rings 371 and 381 of the radial bearings 37 and 38, and the other nuts 62 and 64 abuts the other end surfaces of the inner rings 371 and 381 of the radial bearings 37 and 38. Touch The position of the radial bearing 37 with respect to the diameter increasing table 59 in the direction of the axis 191 of the rotating shaft 19 is changed by changing the screwing position of the nuts 61 and 62 with respect to the diameter increasing table 59. That is, the position of the rotating shaft 19 with respect to the rear housing 14 as a partition can be changed by changing the screwing position of the nuts 61 and 62 with the diameter increasing base 59. The position of the radial bearing 38 with respect to the diameter increasing table 60 in the direction of the axis 201 of the rotating shaft 20 is changed by changing the screwing positions of the nuts 63 and 64 with respect to the diameter increasing table 60. That is, the position of the rotating shaft 20 with respect to the rear housing 14 can be changed by changing the screwing positions of the nuts 63 and 64 with respect to the diameter increasing base 60.

The circlip 49 and the nut 51 are immovable with respect to the rotating shaft 19 in the direction of the axis 191.
The first position restricting means for restricting the position 9 is constituted. The pair of nuts 61, 62 are connected to the axis
A second position restricting means for restricting the position of the radial bearing 37 so as not to move in the direction of 1 is constituted. The circlip 50 and the nut 52 are aligned with the axis 201 with respect to the rotation shaft 20.
The first position restricting means for restricting the position of the diameter increasing table 60 so as not to be able to move in the direction of. The pair of nuts 63, 64
A second position restricting means for restricting the position of the radial bearing 38 so as not to move in the direction of the axis 201 with respect to the diameter increasing table 60 is configured.

In the present invention, the following embodiments are also possible. (1) The present invention is applied to a vacuum pump other than a roots pump. (2) The present invention is applied to a fluid machine other than a vacuum pump in which a lip seal for preventing fluid leakage and a bearing means are juxtaposed. (3) The material of the lip seal is made of resin.

The inventions other than those described in the claims which can be grasped from the above embodiment will be described below. (1) In the fluid machine according to any one of claims 1 to 4, the plurality of rotating shafts are arranged in parallel, a rotor is arranged on each of the rotating shafts, and the rotors on adjacent rotating shafts are engaged with each other. A rotary shaft support structure in a fluid machine that is a vacuum pump having a plurality of pump chambers that accommodate a plurality of rotors that are engaged with each other as a set or a single pump chamber.

[0038]

As described in detail above, according to the present invention, both the bearing means for supporting the rotary shaft and the rotary shaft are provided in addition to the contact-type sealing means disposed on the peripheral surface of the projecting portion of the rotary shaft. The diameter table is fitted and the first position restricting means restricts the position of the diameter increasing table with respect to the rotary shaft so as not to move in the axial direction of the rotary shaft. The position of the bearing means is restricted with respect to the diameter increasing table so that the bearing means cannot be moved in the axial direction, and the position of the bearing means is restricted with respect to the partition wall such that the bearing means cannot be moved in the axial direction of the rotary shaft by a third position restricting means. Therefore, an excellent effect that the life of the lip seal juxtaposed with the bearing can be extended without shortening the life of the bearing in the fluid machine.

[Brief description of the drawings]

FIG. 1 shows a multi-stage roots pump 11 according to a first embodiment.
FIG.

FIG. 2A is a sectional view taken along line AA of FIG. (B) is FIG.
BB sectional drawing of FIG. (C) is a sectional view taken along line CC of FIG. 1.

FIG. 3 is an enlarged plan sectional view of a main part.

FIG. 4 is a sectional view taken along line DD of FIG. 1;

FIG. 5 is an enlarged plan sectional view of a main part showing a second embodiment.

[Explanation of symbols]

11 Multistage roots pump, which is a vacuum pump. 14 ... Rear housing to be a partition. 143, 144 ... Position regulating walls constituting third position regulating means. 19, 20 ... rotating shaft. 1
92, 202: Protruding end portions to be protruding portions. 23-32 ...
A rotor serving as a fluid transfer body. Reference numeral 331 denotes a gear storage chamber serving as an oil existing area. 37, 38 ... radial bearings as bearing means. 39-43 ... Pump room. 45, 46: Lip seals serving as contact-type sealing means. 47, 48, 59, 60
… A diameter increase stand. 471,481 ... Flanges constituting the second position regulating means. 49, 50... Circlips constituting the first position restricting means and the second position restricting means. 51, 52
... Nuts constituting the first position restricting means, the second position restricting means, and the third position restricting means. 55, 56 ... set screws constituting the third position regulating means. 57, 58 ... Position regulating bodies constituting third position regulating means.

Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat II (Reference) F04B 21/00 R (72) Inventor Mamoru Kuwahara 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (72) Inventor Hitoshi Masaji 2-1-1 Toyota-cho, Kariya-shi, Aichi F-term in Toyota Industries Corporation (reference) 3H029 AA06 AA09 AA16 AB06 BB16 BB44 CC16 CC17 CC20 CC38 3H071 AA06 BB02 BB12 CC26 CC28 DD53 3J006AE17 CA01 3J017 AA05 DA01 DB02

Claims (4)

[Claims] 1. A fluid machine for moving a fluid transfer body in a pump chamber based on rotation of a rotating shaft to transfer a fluid by an operation of the fluid transfer body, wherein an oil existing area is adjacent to the pump chamber, A partition that penetrates the rotating shaft, bearing means that rotatably supports the rotating shaft at a position of a protruding portion of the rotating shaft that protrudes into the oil presence area through the partition, and the partition and the bearing means. A contact-type sealing means for a shaft seal disposed so as to be in sliding contact with the peripheral surface of the projecting portion of the rotating shaft, a diameter increasing table fitted to both the rotating shaft and the bearing means, First position restricting means for restricting the position of the diameter increasing table with respect to the rotation axis so as not to move in the axial direction of the rotation shaft; and Positioning the bearing means And second position regulating means, the rotating shaft support structure in a fluid machine having a third position regulating means regulating the position of said bearing means relative to the axis immovably the partition wall in the direction of the rotation axis. 2. The fluid according to claim 1, wherein the contact-type sealing means is a lip seal for preventing oil in the oil existing area from leaking to the pump chamber side along a peripheral surface of the rotating shaft. Rotary shaft support structure in machinery. 3. The lip seal is made of rubber.
3. A rotating shaft support structure in the fluid machine according to 1. 4. The bearing means is a radial bearing, the diameter increasing base includes a flange abutting on an end face of an inner ring of the radial bearing, and the flange is a part of the second position regulating means. A rotating shaft support structure in the fluid machine according to any one of claims 1 to 3.