JP4670854B2 - Shaft seal structure in vacuum pump - Google Patents

Description

  The present invention relates to a shaft seal structure in a vacuum pump that moves a gas transfer body in a pump chamber based on rotation of a rotary shaft and transfers gas by the operation of the gas transfer body to provide a suction action.

  In the vacuum pumps disclosed in Patent Document 1, Patent Document 2, and Patent Document 3, two rotors that are adjacent to each other 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 a driving force from the motor, and the other rotating shaft obtains a driving force from the one rotating shaft via a gear mechanism.

Lubricating oil is stored in the housing that houses the gear mechanism, and this stored oil lubricates the gear mechanism. In order to prevent this lubricating oil from leaking into the pump chamber, in the apparatus of Patent Document 1, a rotating shaft that penetrates a partition wall that separates the transmission chamber that houses the gear mechanism and the working chamber (the pump chamber in the present application); A labyrinth seal is provided between the through hole. In the apparatus of Patent Document 2, an intermediate chamber is interposed between the bearing chamber and the evacuation chamber, and a non-contact seal (labyrinth) is provided between the rotating shaft that penetrates the partition wall that separates the bearing chamber and the intermediate chamber and the through hole. A seal) is provided. In the apparatus of Patent Document 3, a lip seal and a labyrinth seal are provided between a rotating shaft that passes through a housing wall that separates a timing gear housing chamber and a pump chamber and a through hole thereof.
JP-A-60-145475 Japanese Patent Laid-Open No. 3-89080 Japanese Patent Laid-Open No. 6-101684

  In a shaft seal structure with a labyrinth seal configured by arranging a plurality of annular grooves, the sealing function of the labyrinth seal does not deteriorate over time. Improvement of the sealing function in the labyrinth seal can be dealt with by increasing the volume of the annular groove. However, it is difficult to increase the volume of the annular groove in the labyrinth seal between the peripheral surface of the rotating shaft and the through hole.

  An object of this invention is to improve the sealing function of the labyrinth seal for preventing the oil leak to the pump chamber in a vacuum pump.

Therefore, according to the first aspect of the present invention, in the vacuum pump that moves the gas transfer body in the pump chamber based on the rotation of the plurality of rotating shafts and transfers the gas by the operation of the gas transfer body to provide a suction action, the pump chamber An oil housing that forms an oil existing area so as to be adjacent to each other, and a protruding portion of each of the plurality of rotating shafts that penetrates the oil housing and protrudes into the oil existing area can be rotated integrally with the rotating shaft. An annular shaft seal provided on the oil housing and the oil housing as many as the number of the rotation shafts so that each of the rotation shafts individually penetrates and each of the shaft seals is individually fitted. a plurality of fitting holes that are recessed with respect to the opposing surfaces of the shaft sealing ring member and the insertion hole, a pair of seal provided so as to have a radial direction component of the shaft sealing ring member And the pair of sealing facing surfaces includes a bottom forming surface of the fitting hole and an end face of the shaft seal ring fitted into the fitting hole, and the pair of sealing facing surfaces In the meantime, a shaft seal structure in a vacuum pump provided with a labyrinth seal was formed.

According to a second aspect of the present invention, in a vacuum pump that moves the gas transfer body in the pump chamber based on the rotation of the rotary shaft and transfers gas by the operation of the gas transfer body to bring about a suction action, the vacuum pump is adjacent to the pump chamber. An oil housing that forms an oil existing area, and an annular shaft that is rotatably provided integrally with the rotating shaft with respect to a protruding portion of the rotating shaft that penetrates the oil housing and protrudes into the oil existing area A sealing body, a fitting hole that is recessed in the oil housing so as to fit the shaft sealing body and through which the rotating shaft passes, and a facing surface between the shaft sealing body and the fitting hole, A pair of sealing facing surfaces provided to have a radial direction component of the shaft seal ring, and the pair of sealing facing surfaces are fitted into the bottom forming surface of the fitting hole and the fitting hole. The shaft seal A labyrinth seal is provided between the pair of sealing facing surfaces, and the circumferential surface of the insertion hole and the outer circumferential surface of the shaft seal ring are provided with a gap therebetween. with opposite, the the outer circumferential surface of the shaft sealing ring body, pumping means for urging into the oil existing region side oil in the gap from the pump chamber side with rotation of the rotary shaft is formed A shaft seal structure in a vacuum pump was constructed.

  The labyrinth seal has a setting region on a plane perpendicular to the rotation axis or a conical surface having a central axis on the rotation axis. The sealing function of the labyrinth seal having the setting area on such a surface is improved as compared with the labyrinth seal having the setting area on the peripheral surface of the rotating shaft. If the gap between the insertion hole and the shaft seal is reduced, the oil on the oil housing side will not easily enter the gap between the insertion hole and the shaft seal, and the sealing function of the labyrinth seal will be improved. To do. Furthermore, it is easy to expand the set area of the labyrinth seal in the radial direction between the end face of the shaft seal ring and the oil housing. The bottom forming surface of the insertion hole is suitable as a setting region for the labyrinth seal.

  According to a third aspect of the present invention, in the first or second aspect, the shaft seal is fitted and fixed to the rotary shaft, and a seal is provided between the shaft seal and the rotary shaft. A ring is interposed, and the seal ring prevents oil leakage along the peripheral surface of the rotating shaft from the oil existing region side to the pump chamber side. The configuration in which the shaft seal body and the rotation shaft are separated is advantageous in that the end face of the shaft seal body is used as the set region of the labyrinth seal.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the oil presence region is a region that accommodates a bearing for rotatably supporting the rotating shaft. The bearing is lubricated by oil in the oil existing area.

  According to a fifth aspect of the present invention, in the vacuum pump according to any one of the first to fourth aspects, the plurality of rotation shafts are arranged in parallel, and a rotor is arranged on each of the rotation shafts to be adjacent to each other. A plurality of pump chambers that mesh a rotor on a rotating shaft with each other and accommodate a plurality of rotors that are meshed with each other, or a roots pump that includes a single pump chamber. The oil-existing region is a region that accommodates the gear mechanism. The gear mechanism is lubricated by oil in the oil existing area.

  As described above, in the invention of each claim, since the labyrinth seal is provided on the seal facing surface constituted by the bottom forming surface of the fitting hole and the end surface of the shaft seal ring, oil leaks to the pump chamber in the vacuum pump. The labyrinth seal for preventing the above has an excellent effect of improving the sealing function.

Hereinafter, a first embodiment in which the present invention is embodied in a Roots pump will be described with reference to FIGS.
As shown in FIG. 1A, the front housing 13 is joined to the front end of the rotor housing 12 of the multistage roots pump 11, and the sealing 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. 1A, 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 as follows. These are pump chambers 39, 40, 41, 42, 43, respectively.

  A pair of rotary shafts 19, 20 are rotatably supported by the front housing 13 and the rear housing 14 via radial bearings 21, 37, 22, 38. Both rotating shafts 19 and 20 are arranged in parallel to each other. The rotary shafts 19 and 20 are passed through the chamber forming wall 16. The radial bearings 37 and 38 are supported by bearing holders 45 and 46. The bearing holders 45 and 46 are fitted and fixed in fitting holes 47 and 48 that are recessed in the end surface of the rear housing 14.

  A plurality of rotors 23, 24, 25, 26, and 27 are integrally formed on the rotating shaft 19, and the same number of rotors 28, 29, 30, 31, and 32 are integrally formed on the rotating shaft 20. The rotors 23 to 32 have the same shape and the same size when viewed in the directions of the axis lines 191 and 201 of the rotary shafts 19 and 20. The thicknesses of the rotors 23, 24, 25, 26, and 27 are made smaller in this order, and the thicknesses of the rotors 28, 29, 30, 31, and 32 are made smaller in this order. The rotors 23 and 28 are accommodated in the pump chamber 39 in mesh with each other, and the rotors 24 and 29 are accommodated in the pump chamber 40 in mesh with each other. The rotors 25 and 30 are accommodated in the pump chamber 41 in mesh with each other, and the rotors 26 and 31 are accommodated in the pump chamber 42 in mesh with each other. The rotors 27 and 32 are accommodated in the pump chamber 43 while being engaged with each other. The pump chambers 39 to 43 are not lubricated. For this reason, the rotors 23 to 32 do not slide in contact with the cylinder block 15, the chamber forming wall 16, the front housing 13 and the rear housing 14. Moreover, it is made not to slidably contact between the rotors which mesh.

  As shown in FIG. 2A, the rotors 23 and 28 define a suction region 391 and a pressure region 392 having a higher pressure than the suction region 391 in the pump chamber 39. Similarly, the rotors 24 and 29 are in the pump chamber 40, the rotors 25 and 30 are in the pump chamber 41, and the rotors 26 and 31 are in the pump chamber 42, respectively, and a suction region similar to the suction region 391 and the pressure region 392. A pressure region is defined. As shown in FIG. 3A, the rotors 27 and 32 define a suction region 431 and a pressure region 432 similar to the suction region 391 and the pressure region 392 in the pump chamber 43.

  As shown in FIG. 1A, a gear housing 33 is assembled to the rear housing 14. The rotary shafts 19 and 20 protrude into the gear housing 33 through the through holes 141 and 142 and the fitting holes 47 and 48 in the rear housing 14. Gears 34 and 35 are fixed to the projecting portions 193 and 203 of the rotary shafts 19 and 20 in a state where they are engaged with each other. An electric motor M is assembled to the gear housing 33. The driving force of the electric motor M is transmitted to the rotary shaft 19 via the shaft joint 44, and the rotary shaft 19 is transmitted by the electric motor M in FIGS. 2 (a) and 2 (b) and FIGS. 3 (a) and 3 (b). It is rotated in the direction of arrow R1. The rotation of the rotary shaft 19 is transmitted to the rotary shaft 20 through gears 34 and 35, and the rotary shaft 20 is indicated by an arrow R2 in FIGS. 2 (a) and 2 (b) and FIGS. 3 (a) and 3 (b). The rotating shaft 19 rotates in the opposite direction. That is, the rotating shafts 19 and 20 are rotated synchronously using the gears 34 and 35.

  As shown in FIGS. 4A and 4B, the lubricating oil Y is stored in the gear housing chamber 331 in the gear housing 33, and the lubricating oil Y lubricates the gears 34 and 35. The gear housing chamber 331 of the gear housing 33 that houses the gears 34 and 35 constituting the gear mechanism is an oil existing region that is sealed so as not to communicate with the outside of the main body of the multistage roots pump 11. The gear housing 33 and the rear housing 14 constitute an oil housing that forms an oil existing region so as to be adjacent to the pump chamber 43. The stored oil in the gear housing chamber 331 is pumped up by the rotating operation of the gears 34 and 35. The lubricating oil Y pumped up by the rotation of the gears 34 and 35 lubricates the radial bearings 37 and 38 that are bearings. The lubricating oil Y that has lubricated the radial bearings 37 and 38 enters the fitting holes 47 and 48 via the ring gaps 371 and 381 of the radial bearings 37 and 38. The insertion holes 47 and 48 that communicate with the gear housing chamber 331 via the ring gaps 371 and 381 are also oil-existing regions.

  As shown in FIG. 2B, a passage 163 is formed in the chamber forming wall 16. An inlet 164 and an outlet 165 of the passage 163 are formed in the chamber forming wall 16. Adjacent pump chambers 39, 40, 41, 42 and 43 communicate with each other via a passage 163.

  As shown in FIG. 2A, an introduction port 181 is formed in the block piece 18 so as to communicate with the suction region 391 of the pump chamber 39. As shown in FIG. 3A, a discharge port 171 is formed in the block piece 17 so as to communicate with the pressure region 432 of the pump chamber 43. The gas introduced from the inlet 181 into the suction region 391 of the pump chamber 39 moves to the pressure region 392 as the rotors 23 and 28 rotate. The gas transferred to the pressure region 392 is compressed and increased in pressure compared to the state in the suction region 391. The gas in the pressure region 392 is transferred from the inlet 164 of the chamber forming wall 16 through the passage 163 to the suction region of the adjacent pump chamber 40 from the outlet 165. Hereinafter, similarly, the gas is transferred in the order of decreasing volume of the pump chamber, that is, in the order of the pump chambers 40, 41, 42, and 43. The gas transferred to the suction region 431 of the pump chamber 43 moves to the pressure region 432 by the rotation of the rotors 27 and 32 and is then discharged to the outside from the discharge port 171. The rotors 23 to 32 are gas transfer bodies that transfer gas.

  The discharge port 171 is a discharge passage for discharging the gas to the outside of the housing of the main body of the vacuum pump. The pump chamber 43 is a final pump chamber connected to the discharge port 171 that is a discharge passage, and a pressure region 432 in the final pump chamber 43 is a maximum pressure region that has a maximum pressure in the pump chambers 39 to 43. . The discharge port 171 communicates with a maximum pressure region 432 defined in the pump chamber 43 by the rotors 27 and 32.

  As shown in FIG. 1A, annular shaft seals 49 and 50 are fitted and fixed to the rotary shafts 19 and 20 in the fitting holes 47 and 48, respectively. Seal rings 51 and 52 are interposed between the inner peripheral surfaces of the shaft seal rings 49 and 50 and the peripheral surfaces 192 and 202 of the rotary shafts 19 and 20. The seal rings 51 and 52 interposed between the shaft seal members 49 and 50 and the rotary shafts 19 and 20 have the lubricating oil Y inserted into the insertion holes 47 and 48 along the peripheral surfaces 192 and 202 of the rotary shafts 19 and 20. Is prevented from leaking to the pump chamber 43 side.

  As shown in FIGS. 4B and 5B, between the outer peripheral surfaces 491 and 501 of the maximum diameter portion of the shaft seal rings 49 and 50 and the peripheral surfaces 471 and 481 of the fitting holes 47 and 48, respectively. There is a gap, and there is a gap between the end surfaces 492, 502 of the shaft seals 49, 50 and the bottom forming surfaces 472, 482 of the fitting holes 47, 48. Therefore, the shaft seal members 49 and 50 can rotate integrally with the rotary shafts 19 and 20.

  A plurality of annular protrusions 53 and 54 are concentrically formed on the bottom forming surfaces 472 and 482 of the fitting holes 47 and 48. A plurality of annular grooves 55 and 56 are formed concentrically on the end surfaces 492 and 502 of the shaft seal rings 49 and 50 facing the bottom forming surfaces 472 and 482. The annular ridges 53 and 54 enter so as to face the annular grooves 55 and 56. The tips of the annular ridges 53, 54 entering the annular grooves 55, 56 are close to the bottom surfaces of the annular grooves 55, 56. The annular groove 55 is partitioned into labyrinth chambers 551 and 552 by an annular protrusion 53, and the annular groove 56 is partitioned into labyrinth chambers 561 and 562 by an annular protrusion 54. The annular protrusion 53 and the annular groove 55 constitute a labyrinth seal 57 on the rotating shaft 19 side, and the annular protrusion 54 and the annular groove 56 constitute a labyrinth seal 58 on the rotating shaft 20 side. The end faces 492 and 502 of the shaft seals 49 and 50 become seal facing surfaces on the shaft seals 49 and 50 side, and the bottom forming surfaces 472 and 482 of the fitting holes 47 and 48 are for sealing on the rear housing 14 side. It becomes the opposite surface. In the present embodiment, the end surfaces 492 and 502 and the bottom forming surfaces 472 and 482 are planes orthogonal to the axis lines 191 and 201 of the rotation shafts 19 and 20. That is, the end surfaces 492 and 502 and the bottom forming surfaces 472 and 482 that are the opposing surfaces for sealing have only the radial direction component of the shaft seal rings 49 and 50.

  As shown in FIG. 4B, the resin layer 59 is fixed to the end surface 492 of the shaft seal ring 49. As shown in FIG. 5B, the resin layer 60 is fixed to the end face 502 of the shaft seal ring 50. The gaps g1, g2 between the resin layers 59, 60 and the bottom forming surfaces 472, 482 are made smaller than the gaps G1, G2 between the tips of the annular ridges 53, 54 and the bottom surfaces of the annular grooves 55, 56. It is. The gaps G1 and G2 are approximately the same size as the gap between the outer peripheral surfaces 491 and 501 of the shaft seal rings 49 and 50 and the circumferential surfaces 471 and 481 of the fitting holes 47 and 48. The gap g1 is a minimal gap between the shaft seal ring 49 that is a part of the rotary shaft 19 and the rear housing 14, and the gap g2 is a shaft seal ring 50 that is a part of the rotary shaft 20 and the rear housing 14. A minimal gap between the two. In the present invention, the minimal gap refers to a gap for enhancing the sealing performance of the labyrinth chamber.

  As shown in FIGS. 1B, 4 </ b> B, and 6, a spiral groove 61 is formed on the outer peripheral surface 491 of the maximum diameter portion of the shaft seal ring 49. As shown in FIGS. 1C, 5 B and 7, a spiral groove 62 is formed on the outer peripheral surface 501 of the maximum diameter portion of the shaft seal ring 50. The spiral direction of the spiral groove 61 is a direction that shifts from the gear housing chamber 331 side to the pump chamber 43 side as it follows the rotational direction R1 of the rotating shaft 19. The spiral direction of the spiral groove 62 is a direction that shifts from the gear housing chamber 331 side to the pump chamber 43 side as it follows the rotational direction R2 of the rotary shaft 20. Accordingly, the spiral grooves 61 and 62 provide a pumping action for transferring fluid from the pump chamber 43 side to the gear housing chamber 331 side as the rotary shafts 19 and 20 rotate. That is, the spiral grooves 61 and 62 allow oil between the outer circumferential surfaces 491 and 501 of the shaft seal rings 49 and 50 and the circumferential surfaces 471 and 481 of the fitting holes 47 and 48 to be from the pump chamber 43 side to the oil existing region side. A pumping means for biasing is configured. The circumferential surfaces 471 and 481 of the fitting holes 47 and 48 serve as seal surfaces, and the outer peripheral surfaces 491 and 501 facing the circumferential surfaces 471 and 481 serve as surfaces facing the seal surface.

  As shown in FIG. 3 (b), exhaust pressure spreading grooves 63 and 64 are formed on the chamber forming wall surface 143 of the rear housing 14 that forms the final pump chamber 43. As shown in FIG. 4A, the exhaust pressure spreading groove 63 communicates with a maximum pressure region 432 whose volume changes as the rotors 27 and 32 rotate. Further, the exhaust pressure spreading groove 63 communicates with the through hole 141. As shown in FIG. 5A, the exhaust pressure spreading groove 64 communicates with the maximum pressure region 432 and communicates with the through hole 142.

  As shown in FIGS. 1 (a), 4 (a) and 5 (a), an annular cooling chamber 65 is formed in the rear housing 14 so as to surround the shaft seals 49 and 50. Cooling water is supplied to the cooling chamber 65 so that it can be recirculated. The cooling water supplied to the cooling chamber 65 cools the lubricating oil Y in the insertion holes 47 and 48.

The following effects can be obtained in the first embodiment.
(1-1) The diameters of the end faces 492 and 502 of the shaft seal rings 49 and 50 fitted to the rotary shafts 19 and 20 are larger than the diameters of the peripheral surfaces 192 and 202 of the rotary shafts 19 and 20. Therefore, the diameters of the labyrinth seals 57 and 58 between the end surfaces 492 and 502 of the shaft seal members 49 and 50 and the bottom forming surfaces 472 and 482 of the fitting holes 47 and 48 are set to the peripheral surfaces 192 and 192 of the rotary shafts 19 and 20. The diameter of the labyrinth seal provided between 202 and the rear housing 14 is larger. As the diameters of the labyrinth seals 57 and 58 are increased, the volumes of the labyrinth chambers 551, 552, 561, and 562 for suppressing the pressure fluctuation are increased, and the sealing function of the labyrinth seals 57 and 58 is improved. That is, the volume of the labyrinth chambers 551, 552, 561, 562 is increased between the end surfaces 492, 502 of the shaft seals 49, 50 and the bottom forming surfaces 472, 482 of the fitting holes 47, 48 to improve the sealing function. Therefore, it is suitable as a setting area for the labyrinth seals 57 and 58.

  (1-2) The smaller the gap between the fitting holes 47 and 48 and the shaft sealing bodies 49 and 50, the more the lubricating oil Y enters the gap between the fitting holes 47 and 48 and the shaft sealing bodies 49 and 50. It becomes difficult to enter. The bottom forming surfaces 472 and 482 of the fitting holes 47 and 48 having the circumferential surfaces 471 and 481 and the end surfaces 492 and 502 of the shaft seal rings 49 and 50 are easily brought close to each other evenly. Therefore, it is easy to make the minimal gaps g1 and g2 as small as possible. As the minimum gaps g1 and g2 are smaller, the sealing function of the labyrinth seals 57 and 58 is improved. That is, the bottom forming surfaces 472 and 482 of the fitting holes 47 and 48 are suitable as setting regions for the labyrinth seals 57 and 58.

  (1-3) In the state in which the Roots pump 11 is assembled, the resin layers 59 and 60 fixed to the shaft seal members 49 and 50 that rotate integrally with the rotary shafts 19 and 20 are the bottoms of the fitting holes 47 and 48. It is assumed that they are in contact with the formation surfaces 472 and 482. With the operation of the roots pump 11, the resin layers 59 and 60 are merely worn by sliding contact with the bottom forming surfaces 472 and 482 on the metal rear housing 14 side. That is, the contact between the resin layers 59 and 60 and the bottom forming surfaces 472 and 482 of the insertion holes 47 and 48 does not hinder the rotation of the rotary shafts 19 and 20. Therefore, the sum (F1 + d1) of the depth F1 of the annular groove 55 (shown in FIG. 4B) and the thickness d1 of the resin layer 59 (shown in FIG. 4B) is the height H1 of the annular ridge 53 [ Even if the shaft seal ring 49 is assembled to the rotary shaft 19 so that the resin layer 59 and the bottom forming surface 472 are brought into contact with each other, the rotation of the rotary shaft 19 is slightly exceeded. Will not cause any problems. Similarly, the sum (F2 + d2) of the depth F2 of the annular groove 56 (shown in FIG. 5B) and the thickness d2 of the resin layer 60 [shown in FIG. 5B] is the height H2 of the annular protrusion 54. Even if the shaft seal ring 50 is assembled to the rotary shaft 20 so that the resin layer 60 and the bottom forming surface 482 are brought into contact with each other. There is no hindrance to rotation. Therefore, the minimum gaps g1 and g2 between the shaft seals 49 and 50, which are a part of the rotary shafts 19 and 20, and the rear housing 14 can be reduced by the resin layers 59 and 60 interposed therebetween. The sealing properties of the labyrinth chambers 551, 552, 561, and 562 enhance the sealing function of the labyrinth seals 57 and 58, but the sealing properties of the labyrinth chambers 551, 552, 561, and 562 are reduced by reducing the minimum gaps g1 and g2. Rise. Shortening the minimal gaps g1 and g2 in the labyrinth seals 57 and 58 enhances the sealing function of the labyrinth seals 57 and 58. That is, the presence of the resin layers 59 and 60 contributes to the improvement of the sealing function in the labyrinth seals 57 and 58.

  (1-4) Even if the resin layers 59, 60 provided on the end surfaces 492, 502 of the shaft seal rings 49, 50 are brought into contact with the bottom forming surfaces 472, 482 of the fitting holes 47, 48, the rotation shafts 19, 20 There is no hindrance to rotation. Therefore, the space between the bottom forming surfaces 472 and 482 of the fitting holes 47 and 48 and the end surfaces 492 and 502 of the shaft seal rings 49 and 50 is suitable as a location for the labyrinth seal in order to narrow the minimum gap of the labyrinth seal. is there.

  (1-5) The labyrinth seals 57 and 58 have a sealing property against gas. At the start of operation of the multi-stage Roots pump 11, the inside of the pump chambers 39 to 43 becomes higher than the atmospheric pressure. The labyrinth seals 57 and 58 prevent exhaust gas leakage along the surfaces of the shaft seal rings 49 and 50 from the pump chamber 43 to the gear housing chamber 331 side. The labyrinth seals 57 and 58 that prevent both oil leakage and exhaust gas leakage are optimal as non-contact type sealing means.

  (1-6) The spiral groove 61 provided in the shaft seal body 49 sweeps the circumferential surface 471 of the insertion hole 47 as the rotary shaft 19 rotates. The lubricating oil Y in the sweep region of the spiral groove 61 is swept from the pump chamber 43 side to the gear housing chamber 331 side. Further, the spiral groove 62 provided in the shaft seal 50 sweeps the circumferential surface 481 of the insertion hole 48 as the rotary shaft 20 rotates. Lubricating oil Y in the sweep region of the spiral groove 62 is swept from the pump chamber 43 side to the gear housing chamber 331 side. That is, the shaft seal rings 49 and 50 provided with the spiral grooves 61 and 62 which are pumping means exhibit high sealing performance against the lubricating oil Y.

  (1-7) The outer peripheral surfaces 491 and 501 provided with the spiral grooves 61 and 62 are the outer peripheral surfaces of the maximum diameter portions of the shaft seal bodies 49 and 50, and the peripheral speeds of the shaft seal members 49 and 50 are maximum. It is a place. Gas between the outer peripheral surfaces 491 and 501 of the shaft seals 49 and 50 and the circumferential surfaces 471 and 481 of the fitting holes 47 and 48 is geared from the pump chamber 43 side by the spiral grooves 61 and 62 that circulate at high speed. It is urged efficiently toward the storage chamber 331 side. Lubricating oil Y between the outer peripheral surfaces 491 and 501 of the shaft seal rings 49 and 50 and the circumferential surfaces 471 and 481 of the fitting holes 47 and 48 is efficiently applied from the pump chamber 43 side to the gear housing chamber 331 side. Follow the gas that is being forced. The outer peripheral surfaces 491 and 501 of the shaft seal members 49 and 50 prevent oil leakage from the fitting holes 47 and 48 passing through between the outer peripheral surfaces 491 and 501 and the circumferential surfaces 471 and 481 to the pump chamber 43 side. In order to improve the performance to be performed, that is, the sealing performance of the shaft seal members 49 and 50 with respect to the lubricating oil Y, it is suitable as a set location of the spiral grooves 61 and 62.

(1-8) The sealing performance of the spiral grooves 61 and 62 is improved as the number of times the shaft seal rings 49 and 50 are rotated once is increased. Such spiral grooves 61 and 62 are suitable as pumping means.
(1-9) When the shaft seal bodies 49, 50 and the rotary shafts 19, 20 are integrated, the maximum diameter portion of the shaft seal bodies 49, 50 needs to be matched with the diameter of the through holes 141, 142. Occurs. Such a restriction reduces the degree of freedom in selecting the shape of the shaft seals 49 and 50. As in the present embodiment, the configuration in which the shaft seals 49 and 50 and the rotary shafts 19 and 20 are separated from each other is advantageous in that the shape of the shaft seals 49 and 50 is advantageous in enhancing the pumping action of the pumping means. Increase the degree of freedom of selection.

  (1-10) There is a slight gap between the peripheral surface 192 of the rotating shaft 19 and the through hole 141, and there is a slight gap between the rotors 27 and 32 and the chamber forming wall surface 143 of the rear housing 14. . Therefore, the pressure of the final pump chamber 43 is applied to the labyrinth seal 57 through the slight gap. Similarly, since there is a slight gap between the peripheral surface 202 of the rotating shaft 20 and the through hole 142, the final pressure in the pump chamber 43 is applied to the labyrinth seal 58.

  In the absence of the exhaust pressure spreading grooves 63, 64, the pressure in the suction region 431 and the pressure in the maximum pressure region 432 are spread to the labyrinth seals 57, 58 to the same extent. Assuming that the pressure in the suction region 431 of the final pump chamber 43 is P1 and the pressure in the maximum pressure region 432 is P2 (> P1), the labyrinth seals 57 and 58 are intermediate between the pressures P1 and P2 (P2 + P1) from the pump chamber 43 side. ) / 2 pressure. On the other hand, the pressure in the insertion holes 47 and 48 communicating with the gear housing chamber 331 is a region corresponding to atmospheric pressure (about 1000 Torr) that does not cause a pressure fluctuation by the operation of the rotors 23 to 32. The pumping action of the spiral grooves 61 and 62 is such that the pressure in the gap between the shaft seals 49 and 50 and the fitting holes 47 and 48 between the spiral grooves 61 and 62 and the labyrinth seals 57 and 58 is lower than that corresponding to atmospheric pressure. Reduce to pressure P3.

  The exhaust pressure spreading grooves 63 and 64 in the present embodiment enhance the effect of the pressure in the maximum pressure region 432 on the labyrinth seals 57 and 58. That is, the ripple effect of the pressure in the maximum pressure region 432 via the exhaust pressure ripple grooves 63 and 64 greatly exceeds the ripple effect of the pressure in the suction region 431. Therefore, the pressure exerted on the labyrinth seals 57 and 58 greatly exceeds the above-described (P2 + P1) / 2, and the pressure difference before and after the labyrinth seals 57 and 58 is [P3− (P2 + P1) / 2] Torr. It is far below. As a result, the effect of preventing oil leakage in the labyrinth seals 57 and 58 is enhanced.

  (1-11) The ripple effect of the pressure in the maximum pressure region 432 on the labyrinth seals 57, 58 via the exhaust pressure spreading grooves 63, 64 depends on the size of the passage cross-sectional area in the exhaust pressure spreading grooves 63, 64. . It is easy to form the exhaust pressure spreading grooves 63 and 64 having a desired cross-sectional area, and the exhaust pressure spreading grooves 63 and 64 are optimal as an exhaust pressure spreading passage for spreading the pressure in the maximum pressure region 432.

  (1-12) The exhaust pressure spreading grooves 63 and 64 are provided on the chamber forming wall surface 143 of the rear housing 14 constituting a part of the forming wall surface of the pump chamber 43. The through holes 141 and 142 for passing the rotary shafts 19 and 20 through the rear housing 14 pass through the chamber forming wall surface 143, and the maximum pressure region 432 which is a part of the pump chamber 43 faces the chamber forming wall surface 143. Yes. Therefore, it is easy to form the exhaust pressure spreading passage on the chamber forming wall surface 143 so as to communicate with the maximum pressure region 432 and so as to communicate with the through holes 141 and 142. In other words, the chamber forming wall surface 143 is optimal as a location for forming an exhaust pressure spreading passage that connects the through holes 141 and 142 and the maximum pressure region 432.

  (1-13) In the dry pump type roots pump 11, the lubricating oil Y is not used in the pump chambers 39 to 43. The roots pump 11 that does not want the lubricant oil Y to be present in the pump chambers 39 to 43 is suitable as an application target of the present invention.

  In the present invention, the second to eighth embodiments shown in FIGS. 8 to 14 are also possible. In the second to seventh embodiments, only the labyrinth seal on the rotating shaft 19 side will be described, but the labyrinth seal on the rotating shaft 20 side has the same configuration.

  In the second embodiment of FIG. 8, the annular ridge 66 formed on the end surface 492 of the shaft seal ring 49 and the annular ridge 53 formed on the bottom forming surface 472 of the fitting hole 47 are opposed to each other. . A resin layer 67 is provided at the tip of the annular protrusion 66. The plurality of annular ridges 66 and the plurality of annular ridges 53 constitute a labyrinth seal.

In the third embodiment shown in FIG. 9, the annular protrusion 53 in the first embodiment is not formed on the bottom forming surface 472 of the insertion hole 47, and the annular groove 55 constitutes a labyrinth seal.
In the fourth embodiment of FIG. 10, the annular groove 55 in the first embodiment is not formed in the shaft seal ring body 49, and the annular protrusion 53 formed on the bottom forming surface 472 of the insertion hole 47. Constitutes a labyrinth seal. A resin layer 68 is provided at the tip of the annular ridge 53.

  In the fifth embodiment of FIG. 11, the annular protrusion 53 in the first embodiment is not formed on the bottom forming surface 472 of the insertion hole 47, and the annular groove 55 constitutes a labyrinth seal. A resin layer 69 is provided on the bottom forming surface 472.

  In the sixth embodiment shown in FIG. 12, the annular groove 55 in the first embodiment is not formed on the end surface 492 of the shaft seal ring 49, and the annular protrusion 53 constitutes a labyrinth seal. A resin layer 70 is provided on the end surface 492.

  In the seventh embodiment of FIG. 13, a shaft seal ring body 49 </ b> A is integrally formed on the end surfaces of the rotary shaft 19 and the rotor 27. The shaft seal member 49 </ b> A is fitted into a fitting hole 71 that is recessed in the end surface of the rear housing 14 on the side facing the rotor housing 12. A labyrinth seal 72 is provided between the end face of the shaft seal ring 49 </ b> A and the bottom forming face 711 of the fitting hole 71.

  In the eighth embodiment shown in FIG. 14, rubber sliding rings 73 and 74 are fitted and fixed to the outer peripheral surfaces of the shaft seal rings 49B and 50B. A plurality of leakage prevention ridges 731 and 741 are formed on the peripheral surfaces of the sliding contact rings 73 and 74. The leakage prevention ridge 731 is in sliding contact with the peripheral surface 471 of the insertion hole 47 as the rotary shaft 19 rotates, and the leakage prevention ridge 741 is slid onto the peripheral surface 481 of the insertion hole 48 as the rotation shaft 20 rotates. Touch. The plurality of leakage prevention ridges 731 are arranged around the axis 191 without making a round around the axis of the shaft seal ring 49B, that is, the axis 191 of the rotary shaft 19. The plurality of leakage prevention ridges 741 are arranged around the axis line 201 without making a round around the axis line of the shaft seal ring 50B, that is, the axis line 201 of the rotary shaft 20. The leakage prevention protrusion 731 moves from the gear housing chamber 331 side to the pump chamber 43 side as it follows the rotational direction R1 of the rotating shaft 19. The leakage prevention protrusion 741 moves from the gear housing chamber 331 side to the pump chamber 43 side as it follows the rotational direction R2 of the rotating shaft 20.

  The leakage prevention protrusion 731 causes the lubricating oil Y between the peripheral surface 192 of the rotary shaft 19 and the outer peripheral surface of the shaft seal body 49B to move from the pump chamber 43 side to the gear housing chamber 331 side as the rotary shaft 19 rotates. Energize. The leakage prevention protrusion 741 causes the lubricating oil Y between the peripheral surface 202 of the rotary shaft 20 and the outer peripheral surface of the shaft seal 50B to move from the pump chamber 43 side to the gear housing chamber 331 side as the rotary shaft 20 rotates. Energize.

  In order to make a single leakage prevention ridge around the axis 191, 201, it is necessary to increase the width of the sliding contact rings 73, 74 in the direction of the axis 191, 201. Increasing the width of the sliding rings 73 and 74 is not preferable because the sliding resistance increases. A configuration in which a plurality of leakage prevention protrusions 731 and 741 are provided around the axis lines 191 and 201 without making a round around the axis lines 191 and 201 does not require an increase in the width of the sliding contact rings 73 and 74.

In the present invention, the following embodiments are also possible.
(1) The bottom forming surfaces of the fitting holes 47 and 48 are tapered opposing surfaces for sealing, and the end faces of the shaft seal rings 49 and 50 are tapered sealing opposing surfaces, and between the opposing surfaces for both seals. Provide a labyrinth seal.

(2) In the first embodiment, a resin layer is also provided at the tips of the annular ridges 53 and 54.
(3) A resin plate is interposed between the bottom forming surfaces 472 and 482 of the fitting holes 47 and 48 and the end surfaces 492 and 502 of the shaft seal rings 49 and 50 to form a resin layer.

(4) The present invention is applied to vacuum pumps other than the roots pump.
Inventions other than the claims that can be grasped from the above-described embodiment will be described below.
[1] In a vacuum pump that moves a gas transfer body in a pump chamber based on the rotation of a rotary shaft, transfers gas by an operation of the gas transfer body, and brings a suction action,
An oil housing that forms an oil presence area adjacent to the pump chamber;
An annular shaft seal provided so as to be integrally rotatable with respect to a projecting portion of the rotating shaft that projects through the oil housing and projects into the oil existing region;
A shaft seal structure in a vacuum pump comprising a labyrinth seal provided between an end face of the shaft seal ring and the oil housing.

1 shows a first embodiment, (a) is a plan sectional view of the entire multi-stage Roots pump 11; FIG. 4B is an enlarged plan sectional view of a main part on the rotating shaft 19 side. (C) is a principal enlarged plan sectional view on the rotating shaft 20 side. (A) is the sectional view on the AA line of FIG. (B) is the BB sectional drawing of FIG. (A) is CC sectional view taken on the line of FIG. (B) is the DD sectional view taken on the line of FIG. (A) is the EE sectional view taken on the line of FIG.3 (b). (B) is a principal part expanded side sectional view. (A) is the FF sectional view taken on the line of FIG.3 (b). (B) is a principal part expanded side sectional view. FIG. FIG. The principal part expanded plane sectional view which shows 2nd Embodiment. The principal part expanded plane sectional view which shows 3rd Embodiment. The principal part expanded plane sectional view which shows 4th Embodiment. The principal part expanded plane sectional view which shows 5th Embodiment. The principal part expanded plane sectional view which shows 6th Embodiment. The principal part expanded plane sectional view which shows 7th Embodiment. The principal part expanded plane sectional view which shows 8th Embodiment.

Explanation of symbols

  11 ... Roots pump which is a vacuum pump. 14: A rear housing constituting an oil housing. 143 ... Room forming wall surface. 171: A discharge port serving as a discharge passage. 19, 20 ... rotating shaft. 193, 203 ... Projection site. 23, 24, 25, 26, 27, 28, 29, 30, 31, 32... Rotor serving as a gas transfer body. 33: A gear housing constituting the oil housing. 331: A gear housing chamber that serves as an oil existing area. 34, 35 ... Gears constituting the gear mechanism. 37, 38 ... Radial bearings that serve as bearings. 43 ... Pump room. 432 ... Maximum pressure region. 47, 48, 71 ... insertion holes. 472, 482, 711... Bottom forming surface which becomes a sealing opposing surface 49, 50, 49A, 49B, 50B ... Shaft seal. 492, 502... End faces that are opposed surfaces for sealing. 57, 58, 72 ... Labyrinth seals. 59, 60, 67, 68, 69, 70 ... resin layer. 61, 62 ... Spiral grooves serving as pumping means. 63, 64 ... Exhaust pressure spill grooves serving as exhaust pressure spill passages.

Claims (5)

In a vacuum pump that moves a gas transfer body in a pump chamber based on the rotation of a plurality of rotating shafts, transfers gas by the operation of the gas transfer body, and brings a suction action,
An oil housing that forms an oil presence area adjacent to the pump chamber;
An annular shaft seal provided so as to be rotatable integrally with the rotary shaft for each of the protruding portions of the plurality of rotary shafts that penetrate the oil housing and protrude into the oil existing region;
A plurality of insertion holes recessed in the oil housing by the same number as the number of the rotation shafts so that each of the rotation shafts individually penetrates and each of the shaft seals is individually inserted ;
A pair of opposed surfaces for sealing provided to have a radial direction component of the shaft seal against the opposed surfaces of the shaft seal and the fitting hole,
The pair of sealing opposing surfaces are composed of a bottom forming surface of the insertion hole and an end surface of the shaft seal ring inserted into the insertion hole,
A shaft seal structure in a vacuum pump in which a labyrinth seal is provided between the pair of opposing surfaces for sealing. In the vacuum pump that moves the gas transfer body in the pump chamber based on the rotation of the rotation shaft and transfers the gas by the operation of the gas transfer body to provide a suction action,
An oil housing that forms an oil presence area adjacent to the pump chamber;
An annular shaft seal provided so as to be rotatable integrally with the rotating shaft, with respect to the protruding portion of the rotating shaft that penetrates the oil housing and protrudes into the oil existing region;
A fitting hole which is recessed in the oil housing so as to fit the shaft seal ring and through which the rotary shaft passes;
A pair of opposed surfaces for sealing provided to have a radial direction component of the shaft seal against the opposed surfaces of the shaft seal and the fitting hole,
The pair of sealing opposing surfaces are composed of a bottom forming surface of the insertion hole and an end surface of the shaft seal ring inserted into the insertion hole,
A labyrinth seal is provided between the pair of seal facing surfaces,
The circumferential surface of the fitting hole and the outer peripheral surface of the shaft seal body are opposed to each other via a gap, and oil in the gap is caused to rotate on the outer peripheral surface of the shaft seal body as the rotary shaft rotates. A shaft seal structure in a vacuum pump in which pumping means for urging from the pump chamber side to the oil existing region side is formed .   The shaft seal is fitted and fixed to the rotating shaft, a seal ring is interposed between the shaft seal and the rotating shaft, and the seal ring is in the oil existing region. The shaft seal structure in the vacuum pump according to claim 1 or 2, wherein oil leakage along a peripheral surface of the rotary shaft from the side to the pump chamber side is prevented.   The shaft seal structure for a vacuum pump according to any one of claims 1 to 3, wherein the oil existence region is a region that accommodates a bearing for rotatably supporting the rotating shaft.   In the vacuum pump, a plurality of rotating shafts are arranged in parallel, a rotor is arranged on each rotating shaft, rotors on adjacent rotating shafts are engaged with each other, and a set of a plurality of rotors in a state of being engaged with each other A plurality of pump chambers, or a roots pump having a single pump chamber, wherein the plurality of rotating shafts are rotated synchronously using a gear mechanism, and the oil presence region includes the gear mechanism. The shaft seal structure for a vacuum pump according to any one of claims 1 to 4, wherein the shaft seal structure is a region to be accommodated.

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