WO2017086135A1 - 真空ポンプ - Google Patents
真空ポンプ Download PDFInfo
- Publication number
- WO2017086135A1 WO2017086135A1 PCT/JP2016/082213 JP2016082213W WO2017086135A1 WO 2017086135 A1 WO2017086135 A1 WO 2017086135A1 JP 2016082213 W JP2016082213 W JP 2016082213W WO 2017086135 A1 WO2017086135 A1 WO 2017086135A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- stator
- rotor
- spacer
- vacuum pump
- base
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5853—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps heat insulation or conduction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
- F04D19/042—Turbomolecular vacuum pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
- F04D19/044—Holweck-type pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/02—Multi-stage pumps
- F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
- F04D19/046—Combinations of two or more different types of pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/006—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by influencing fluid temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
- F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
Definitions
- the present invention relates to a vacuum pump, and more particularly to a vacuum pump that can be used in a pressure range from low vacuum to ultrahigh vacuum.
- a vacuum pump such as a composite pump in which a turbo molecular pump and a thread groove pump are combined is used for the exhaust inside.
- a vacuum pump for example, a cylindrical casing, a cylindrical stator that is nest-fixed in the casing and provided with a thread groove, and a rotor that is supported so as to be capable of high-speed rotation in the stator,
- the gas is transported while being compressed in a thread pump comprising a rotor and a stator.
- a vacuum pump that suppresses the generation of products that includes a heat insulating space provided around the stator, a heat insulating spacer that supports the stator, and a heater embedded in the stator.
- the heater heats the stator so that the gas in the gas flow path is transferred without solidification.
- the electrical components provided in the vacuum pump and the motor that rotates the rotor do not perform the desired function when the temperature rises, and the rotor blades and stationary blades break down during operation due to their strength decreasing as the temperature rises. There was a risk of doing. For this reason, if the stator is heated to a high temperature, the heat release from the stator increases, which may adversely affect the operation of the vacuum pump.
- the present invention is proposed to achieve the above object, and the invention according to claim 1 has a base and a rotor cylindrical portion accommodated in the base, and is rotatably supported by the base.
- Rotor a substantially cylindrical stator disposed between the base and the rotor cylindrical portion, and a thread groove portion carved on either the outer peripheral surface of the rotor cylindrical portion or the inner peripheral surface of the stator
- a heat insulating means for insulating the stator from a fixed part excluding the stator, and a heating means for heating the stator, and an intake port for the rotor cylindrical portion and the stator
- the vacuum pump is provided such that the separation distance on the side is set to be equal to or greater than the separation distance on the exhaust port side between the rotor cylindrical portion and the stator.
- the separation distance between the rotor and the stator on the intake port side is set to be equal to or greater than the separation distance between the rotor and the stator on the exhaust port side, so that the rotor generates centrifugal force during operation of the vacuum pump. Even if it is deformed by receiving or the rotor is thermally expanded by receiving radiant heat from the stator, the separation distance between the rotor and the stator is kept substantially equal from the intake side to the exhaust side, It can suppress that the flow path of gas becomes narrow too much.
- the heat insulating means is in contact with the stator in the axial direction of the rotor and is disposed on the base, and the base, there is provided a vacuum pump that is a spacer that contacts the axial direction of the rotor and has a cylindrical cylindrical portion provided on an inner peripheral edge of the flange portion and accommodates the heating means in the flange.
- the spacer is interposed between the stator and the base, and by supporting the stator in the axial direction of the rotor, the spacer insulates the stator from the other fixed parts, thereby suppressing gas solidification.
- normal operation of the pump can be realized.
- the stator is provided with a vacuum pump in which deformation of at least a portion in the rotor radial direction is restrained by the spacer during thermal expansion. To do.
- the spacer prevents the stator from being deformed by receiving the kinetic energy of the rotor. Energy transfer can be reduced.
- the spacer in addition to the configuration of the vacuum pump according to the second or third aspect, provides a vacuum pump that is a member having a lower linear expansion coefficient than the stator.
- the amount of deformation due to the thermal expansion of the spacer is smaller than the amount of deformation due to the thermal expansion of the stator, so that the spacer disposed on the outer peripheral side in the rotor radial direction of the stator can regulate the deformation of the stator. it can.
- a separation distance from the heating unit to a contact portion between the stator and the flange portion is the heating unit.
- the vacuum pump is shorter than the distance between the base and the contact portion of the spacer cylindrical portion.
- the spacer cylindrical portion enables positioning in the rotor axial direction and elastically deforms in the rotor radial direction.
- a vacuum pump is provided that is formed as thin as possible.
- the spacer cylindrical portion is elastically deformed in accordance with the deformation of the stator, so that the stator and the spacer are excessively brought into contact with each other, so that the stator and the spacer are not in contact with each other. Since the contact heat resistance is prevented from significantly decreasing and heat release from the spacer to the base is suppressed, normal operation of the pump can be realized while suppressing solidification of the gas.
- the spacer is provided with a vacuum pump that is attached in an inlay structure in the radial direction of the stator and the rotor. To do.
- the stator presses the spacer in the rotor radial direction even when the stator is thermally expanded.
- An excessive increase in the contact area due to excessive contact with the spacer and such an increase in contact area prevent the contact thermal resistance between the base and the spacer from being significantly reduced, and from the spacer to the base. Therefore, normal operation of the pump can be realized while suppressing solidification of the gas.
- the spacer is provided with a vacuum pump that is attached in an inlay structure in the radial direction of the base and the rotor. To do.
- the vacuum pump according to the present invention suppresses heat from escaping from the stator, it is possible to realize normal operation of the pump while suppressing gas solidification.
- the separation distance between the rotor and the stator on the intake port side is set to be equal to or greater than the separation distance between the rotor and the stator on the exhaust port side, so that the rotor generates centrifugal force during operation of the vacuum pump. Even when the rotor is deformed or the rotor is thermally expanded by receiving radiant heat from the stator, the separation distance between the rotor and the stator extends from the intake side to the exhaust side at a predetermined separation distance or substantially Since the same degree of change is maintained, problems such as an excessively narrow gas flow path can be suppressed.
- FIG. drawing which shows the vacuum pump which concerns on one Example of this invention.
- the principal part enlarged view of FIG. Sectional drawing which shows a rotor cylindrical part and a stator. It is a schematic diagram explaining the effect
- the present invention has a base and a rotor cylindrically housed in the base and rotatably supported by the base And a substantially cylindrical stator disposed between the base and the rotor cylindrical portion, and a screw groove portion carved on either the outer peripheral surface of the rotor cylindrical portion or the inner peripheral surface of the stator.
- a pump comprising: a heat insulating means for insulating the stator from fixed parts excluding the stator; and a heating means for heating the stator, and the separation distance on the intake port side between the rotor cylindrical portion and the stator is such that the rotor cylindrical portion and the stator This is realized by setting it to be equal to or longer than the separation distance on the exhaust port side.
- a vacuum pump 1 according to an embodiment of the present invention will be described with reference to the drawings.
- the terms “upper” and “lower” correspond to the upper side and the lower side, respectively, on the intake port side and the exhaust port side in the rotor axial direction.
- FIG. 1 is a longitudinal sectional view showing a vacuum pump 1.
- the vacuum pump 1 is a composite pump including a turbo molecular pump mechanism PA and a thread groove pump mechanism PB housed in a substantially cylindrical casing 10.
- the vacuum pump 1 includes a casing 10, a rotor 20 having a rotor shaft 21 rotatably supported in the casing 10, a drive motor 30 that rotates the rotor shaft 21, a part of the rotor shaft 21, and the drive motor 30. And a stator column 40 to be accommodated.
- the casing 10 is formed in a bottomed cylindrical shape.
- the casing 10 has a base 11 with a gas exhaust port 11a formed on the lower side, and a cylinder fixed with bolts 13 in a state where the gas intake port 12a is formed on the upper side and placed on the base 11.
- symbol 14 in FIG. 1 is a back cover.
- the base 11 includes a base 11A and a base spacer 11B.
- the base 11A and the base spacer 11B are fixed via a bolt (not shown).
- a water-cooled tube 11b is embedded in the base spacer 11B. By passing cooling water through the water cooling pipe 11b, the base spacer 11B is maintained at a predetermined temperature (for example, 80 ° C.).
- the cylindrical portion 12 is attached to a vacuum container such as a chamber (not shown) via a flange 12b.
- the gas inlet 12a is connected to communicate with the vacuum vessel, and the gas outlet 11a is connected to communicate with an auxiliary pump (not shown).
- the rotor 20 includes a rotor shaft 21 and rotating blades 22 that are fixed to the upper portion of the rotor shaft 21 and are arranged concentrically with the axis of the rotor shaft 21.
- the rotor shaft 21 is supported in a non-contact manner by a magnetic bearing 50.
- the magnetic bearing 50 includes a radial electromagnet 51 and an axial electromagnet 52.
- the radial electromagnet 51 and the axial electromagnet 52 are connected to a control unit (not shown).
- the control unit controls the excitation current of the radial electromagnet 51 and the axial electromagnet 52 based on the detection values of the radial direction displacement sensor 51a and the axial direction displacement sensor 52a, so that the rotor shaft 21 floats at a predetermined position. It has come to be supported.
- the upper and lower portions of the rotor shaft 21 are inserted into the touchdown bearing 23.
- the rotor shaft 21 becomes uncontrollable, the rotor shaft 21 rotating at high speed comes into contact with the touchdown bearing 23 to prevent the vacuum pump 1 from being damaged.
- the rotor blade 22 is integrally attached to the rotor shaft 21 by inserting the bolt 25 into the rotor flange 26 and screwing the bolt 25 into the shaft flange 27 while the upper portion of the rotor shaft 21 is inserted into the boss hole 24.
- the axial direction of the rotor shaft 21 is referred to as “rotor axial direction A”
- the radial direction of the rotor shaft 21 is referred to as “rotor radial direction R”.
- the drive motor 30 includes a rotor 31 attached to the outer periphery of the rotor shaft 21 and a stator 32 arranged so as to surround the rotor 31.
- the stator 31 is connected to the control unit (not shown) described above, and the rotation of the rotor shaft 21 is controlled by the control unit.
- the stator column 40 is fixed on the base 11 via a bolt (not shown) at the lower end while being placed on the base 11.
- the turbo molecular pump mechanism PA is composed of a rotor blade 22 of the rotor 20 and a fixed blade 60 disposed with a gap between the rotor blades 22.
- the rotor blades 22 and the stationary blades 60 are arranged alternately and in multiple stages along the rotor axial direction A.
- the rotor blades 22 are arranged in 11 stages and the stationary blades 60 are arranged in 10 stages. .
- the rotor blade 22 is composed of a blade inclined at a predetermined angle, and is integrally formed on the upper outer peripheral surface of the rotor 20.
- a plurality of rotor blades 22 are provided radially around the axis of the rotor 20.
- the fixed blade 60 is composed of a blade inclined in the opposite direction to the rotary blade 22 and is positioned by being sandwiched in the rotor axial direction A by a spacer 61 installed in a stacked manner on the inner wall surface of the cylindrical portion 12.
- a plurality of fixed blades 60 are also provided radially around the axis of the rotor 20.
- the gap between the rotor blade 22 and the fixed blade 60 is set so as to gradually narrow from the upper side to the lower side in the rotor axial direction A.
- the lengths of the rotary blade 22 and the fixed blade 60 are set so as to gradually shorten from the upper side to the lower side in the rotor axial direction A.
- the turbo molecular pump mechanism PA as described above is configured to transfer the gas sucked from the gas inlet 12a from the upper side to the lower side in the rotor axial direction A by the rotation of the rotor blades 22.
- the thread groove pump mechanism PB is provided at a lower portion of the rotor 20 and extends along the rotor axial direction A, and a substantially cylindrical stator 70 disposed so as to surround the outer peripheral surface 28a of the rotor cylindrical portion 28. And.
- the stator 70 is placed on the base 11 via a spacer 80 described later.
- the stator 70 includes a thread groove portion 71 formed on the inner peripheral surface 70a.
- the thread groove pump mechanism PB as described above compresses the gas transferred from the gas inlet 12a downward in the rotor axial direction A by the drag effect due to the high-speed rotation of the rotor cylindrical portion 28, and moves toward the gas outlet 11a. Transport. Specifically, after the gas is transferred to the gap between the rotor cylindrical portion 28 and the stator 70, the gas is compressed in the screw groove portion 71 and transferred to the gas exhaust port 11a. Generally, since the drag effect in the thread groove pump mechanism PB is affected by the gap (separation distance) between the rotor cylindrical portion 28 and the stator 70, the thread groove pump mechanism PB exhibits sufficient exhaust performance. The gap needs to be set to a predetermined dimension.
- FIG. 2 is an enlarged cross-sectional view of a main part of FIG.
- the heating structure H includes a spacer 80 as heat insulating means and a cartridge heater 90 as heating means.
- the spacer 80 is formed in a cylindrical shape with an L-shaped cross section.
- the spacer 80 includes a flange portion 81 and a spacer cylindrical portion 82.
- the spacer 80 is interposed between the base 11 and the stator 70.
- the flange portion 81 supports the stator 70 in the rotor axial direction A.
- the spacer cylindrical portion 82 is in contact with the base 11 in the rotor axial direction A.
- the spacer 80 is preferably attached to the base 11 in an inlay structure in the rotor radial direction R.
- the spacer 80 is attached in a non-contact state with the stator 70 except for a minimum contact point for determining the center position in the rotor radial direction R as in the case of an inlay structure. Thereby, the heat in the spacer 80 is easily transmitted to the stator 70, and the heat transfer to fixed parts other than the stator 70 is suppressed as described later.
- the flange portion 81 includes a stator receiving portion 81a that protrudes slightly inward in the rotor radial direction R. When the pump is stopped, the stator 70 and the stator receiving portion 81a face each other with a slight gap. ing.
- the flange portion 81 is disposed on the base 11 via an O-ring 83.
- the flange portion 81 is positioned at a predetermined position without directly contacting the base 11. Further, even when the stator 70 is heated to a predetermined temperature (for example, 150 ° C.), it is possible to prevent heat from being transferred from the stator 70 to the base 11 by interposing an O-ring between the base 11 and the flange portion 80. it can.
- the flange portion 81 is integrally connected via the stator 70 and the bolt 84.
- the bolts 84 and the bolts used in the vacuum pump are preferably made of stainless steel from the viewpoint of corrosion resistance to corrosive gas and structural strength.
- the spacer cylindrical portion 82 extends from the inner peripheral edge of the flange portion 81 downward in the rotor axial direction A.
- the spacer cylindrical portion 82 is formed thinner than the flange portion 81 in order to suppress an increase in contact thermal resistance, which will be described later, while ensuring the strength necessary for positioning the stator 70 in the rotor axial direction A. ing.
- the spacer cylindrical portion 82 is formed with a thickness of about 1 to 5 mm, for example.
- the cartridge heater 90 is accommodated in the heater accommodating portion 81 b of the flange portion 81.
- the cartridge heater 90 is connected to a heater control device (not shown), and the heater control device controls the temperature of the cartridge heater 90.
- the cartridge heater 90 is appropriately adjusted so as to maintain the temperature of the stator 70 at a predetermined value.
- the separation distance L1 from the cartridge heater 90 to the contact portion between the stator 70 and the flange portion 81 is set shorter than the separation distance L2 from the cartridge heater 90 to the contact portion between the base 11 and the spacer cylindrical portion 82.
- FIG. 3 is a cross-sectional view showing the rotor cylindrical portion 28 and the stator 70.
- hatching is omitted for convenience of explanation.
- the outer peripheral surface 28a of the rotor cylindrical portion 28 and the inner peripheral surface 70a of the stator 70 are opposed to each other.
- a distance L3 above (intake port side) between the rotor cylindrical portion 28 and the stator 70 is set to be equal to or greater than a distance L4 below (exhaust port side) between the rotor cylindrical portion 28 and the stator 70. .
- the rotor cylindrical portion 28 is deformed outward in the rotor radial direction R by centrifugal force during the pump operation.
- the deformation caused by the centrifugal force increases from the upper side to the lower side of the rotor cylindrical portion 28 due to structural characteristics.
- the rotor cylindrical portion 28 receives the radiant heat from the stator 70 and thermally expands outward in the rotor radial direction R from the upper side to the lower side almost uniformly. Therefore, the amount of deformation of the rotor cylindrical portion 28 considering the centrifugal force and thermal expansion during the pump operation increases from the upper side to the lower side.
- the total deformation amount due to the centrifugal force and thermal expansion of the rotor cylindrical part 28 that reached 150 ° C. during the pump operation is about 0.35 to 0.50 mm in the upper part, It is about 0.40 to 0.55 mm.
- stator 70 is restrained from displacement in the rotor radial direction R by bolts 84 and spacers 80 having a lower linear expansion coefficient and a higher elastic coefficient than the stator 70, the amount of deformation of the thermal expansion of the stator 70 is high. Is larger in the lower part than in the upper part. That is, since there is a difference between the elastic coefficient and the linear expansion coefficient between the members arranged inside and outside the rotor radial direction R, the amount of deformation of the stator 70 due to the thermal expansion during the pump operation increases from the upper side to the lower side. Become.
- the amount of deformation due to the thermal expansion of the stator 70 when there is no constraint by the spacer 80 is substantially uniform from the top to the bottom as in the case of the rotor cylindrical portion 28.
- the linear expansion is lower than that of the stator 70.
- the separation distance L3 on the intake port side between the rotor cylindrical portion 28 and the stator 70 is set to be equal to or greater than the separation distance L4 on the exhaust port side between the rotor cylindrical portion 28 and the stator 70.
- FIGS. 4 (a) and 4 (b) show a state before the stator 70 is thermally expanded
- FIG. 4B shows a state after the stator 70 is thermally expanded.
- the stator 70 is mainly supported by the upper end surface 81c and the side surface 81d of the flange portion 81.
- the heat of the cartridge heater 90 is transferred to the stator 70 through the spacer 80.
- the aluminum alloy stator 70 has a larger linear expansion coefficient than the stainless steel spacer 80, and therefore, as shown by a thin arrow in FIG.
- the stator 70 presses the stator receiving portion 81a or the side surface 81d toward the outside in the rotor radial direction R.
- the spacer cylindrical portion 82 moves following the thermal expansion of the stator 70 and is elastically deformed as indicated by the thick arrow in FIG. 4B. . Thereby, excessive contact between the stator 70 and the flange portion 81 is suppressed. In other words, even when the stator 70 is relatively large in thermal expansion with respect to the spacer 80, the contact thermal resistance between the stator 70 and the spacer 80 and the contact thermal resistance between the spacer 80 and the base 11 are excessively small. It is possible to suppress the heat release from the stator 70 to the base 11.
- the vacuum pump 1 operates abnormally due to heat escape from the stator 70 when the stator 70 is heated while being insulated from other fixed parts. And the strength fall of the rotary blade 22 or the fixed blade 60 is suppressed. The normal operation of the vacuum pump 1 can be realized while suppressing the solidification of the gas.
- the separation distance L3 on the intake port side between the rotor cylindrical portion 28 and the stator 70 is set to be equal to or greater than the separation distance L4 on the exhaust port side between the rotor cylindrical portion 28 and the stator 70, so that the vacuum Even when the rotor 20 is deformed by centrifugal force during operation of the pump 1 or the rotor 20 is thermally expanded by receiving radiant heat from the stator 70, the separation distance between the rotor cylindrical portion 28 and the stator 70.
- the predetermined separation distance and substantially the same degree of change are maintained from the intake side to the exhaust side, problems such as excessively narrow gas flow paths can be suppressed.
- the present invention is applicable as long as it has a thread groove pump mechanism, and may be applied to a thread groove type pump in addition to a composite pump.
- the heating means is not limited to the cartridge heater 90, and any heating means may be used as long as the stator 70 can be heated.
- SYMBOLS 1 Vacuum pump 10 ... Casing 11 ... Base 11A ... Base part 11B ... Base spacer 11a ... Gas exhaust port 11b ... Water cooling pipe 12 ... Cylindrical part 12a ... Gas inlet 12b ... Flange 13 ... Bolt 20 ... Rotor 21 ... Rotor shaft 22 ... Rotor 23 ... Touchdown bearing 28 ... Rotor cylindrical part 28a ... Outer peripheral surface DESCRIPTION OF SYMBOLS 30 ... Drive motor 31 ... Rotor 32 ... Stator 40 ... Stator column 50 ... Magnetic bearing 51 ... Radial electromagnet 52 ... Axial electromagnet 60 ...
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Non-Positive Displacement Air Blowers (AREA)
Abstract
Description
ータシャフト21が制御不能になった場合には、高速で回転するロータシャフト21がタッチダウン軸受23に接触して真空ポンプ1の損傷を防止するようになっている。
これにより、真空ポンプ1に異常が発生して、ロータ円筒部28がステータ70に接触した場合、本発明のようにステータ70の変形量を上方から下方に向かって大きくする構造(特に、運動エネルギーが伝わり易い部分を拘束する構造)を採用することにより、ステータ70の変形を抑制し、ポンプ外部への運動エネルギーの伝達を低減することができる。
10・・・ ケーシング
11・・・ ベース
11A・・・基部
11B・・・ベーススペーサ
11a・・・ガス排気口
11b・・・水冷管
12・・・ 円筒部
12a・・・ガス吸気口
12b・・・フランジ
13・・・ ボルト
20・・・ ロータ
21・・・ ロータシャフト
22・・・ 回転翼
23・・・ タッチダウン軸受
28・・・ ロータ円筒部
28a・・・外周面
30・・・ 駆動モータ
31・・・ 回転子
32・・・ 固定子
40・・・ ステータコラム
50・・・ 磁気軸受
51・・・ ラジアル電磁石
52・・・ アキシャル電磁石
60・・・ 固定翼
61・・・ スペーサ
70・・・ ステータ
70a・・・(ステータの)内周面
71・・・ ネジ溝部
80・・・ スペーサ
81・・・ フランジ部
81a・・・ステータ受け部
81b・・・ヒータ収容部
81c・・・上端面
81d・・・側面
82・・・ スペーサ円筒部
83・・・ Oリング
84・・・ ボルト
90・・・ カートリッジヒータ
H ・・・ 加熱構造
A ・・・ ロータ軸方向
R ・・・ ロータ径方向
PA・・・ ターボ分子ポンプ機構
PB・・・ ネジ溝ポンプ機構
Claims (8)
- ベースと、該ベース内に収容されたロータ円筒部を有して前記ベースに回転可能に支持されたロータと、前記ベースと前記ロータ円筒部との間に配置された略円筒状のステータと、前記ロータ円筒部の外周面又は前記ステータの内周面の何れか一方に刻設されたネジ溝部と、を備えた真空ポンプであって、
前記ステータを除く固定部品から前記ステータを断熱する断熱手段と、
前記ステータを加熱する加熱手段と、
を備え、
前記ロータ円筒部と前記ステータとの吸気口側の離間距離は、前記ロータ円筒部と前記ステータとの排気口側の離間距離と同じかそれ以上となるように設定されていることを特徴とする真空ポンプ。 - 前記断熱手段は、前記ステータとロータ軸方向に接触すると共に前記ベースに配設されるフランジ部と、前記ベースとロータ軸方向に接触すると共に前記フランジ部の内周縁に設けられたスペーサ円筒部と、を有し、前記フランジ部に前記加熱手段を収容するスペーサであることを特徴とする請求項1記載の真空ポンプ。
- 前記ステータは、熱膨張時に少なくとも一部分のロータ径方向への変形を、前記スペーサに拘束されていることを特徴とする請求項2記載の真空ポンプ。
- 前記スペーサは、前記ステータよりも線膨張係数が低い部材であることを特徴とする請求項2又は3記載の真空ポンプ。
- 前記加熱手段から前記ステータと前記フランジ部の接触部分までの離間距離は、前記加熱手段から前記ベースと前記スペーサ円筒部の接触部分までの離間距離より短いことを特徴とする請求項2乃至4の何れか1項記載の真空ポンプ。
- 前記スペーサ円筒部は、ロータ軸方向の位置決めを可能にすると共にロータ径方向に弾性変形可能に薄く形成されていることを特徴とする請求項2乃至5の何れか1項記載の真空ポンプ。
- 前記スペーサは、前記ステータとロータ径方向にインロー構造で取り付けられていることを特徴とする請求項2乃至6の何れか1項記載の真空ポンプ。
- 前記スペーサは、前記ベースとロータ径方向にインロー構造で取り付けられていることを特徴とする請求項2乃至7の何れか1項記載の真空ポンプ。
Priority Applications (4)
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EP16866137.9A EP3379086A4 (en) | 2015-11-16 | 2016-10-31 | VACUUM PUMP |
US15/774,861 US10907653B2 (en) | 2015-11-16 | 2016-10-31 | Vacuum pump |
KR1020187007774A KR102620442B1 (ko) | 2015-11-16 | 2016-10-31 | 진공 펌프 |
CN201680063254.5A CN108350894B (zh) | 2015-11-16 | 2016-10-31 | 真空泵 |
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JP2015-224199 | 2015-11-16 | ||
JP2015224199A JP6666696B2 (ja) | 2015-11-16 | 2015-11-16 | 真空ポンプ |
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WO2017086135A1 true WO2017086135A1 (ja) | 2017-05-26 |
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PCT/JP2016/082213 WO2017086135A1 (ja) | 2015-11-16 | 2016-10-31 | 真空ポンプ |
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US (1) | US10907653B2 (ja) |
EP (1) | EP3379086A4 (ja) |
JP (1) | JP6666696B2 (ja) |
KR (1) | KR102620442B1 (ja) |
CN (1) | CN108350894B (ja) |
WO (1) | WO2017086135A1 (ja) |
Cited By (3)
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WO2020241521A1 (ja) * | 2019-05-31 | 2020-12-03 | エドワーズ株式会社 | 真空ポンプ、および連結型ネジ溝スペーサ |
WO2022124240A1 (ja) * | 2020-12-11 | 2022-06-16 | エドワーズ株式会社 | 真空ポンプ |
WO2022124239A1 (ja) * | 2020-12-11 | 2022-06-16 | エドワーズ株式会社 | 真空ポンプ、真空ポンプの固定部品、及び真空ポンプの支持部品 |
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JP6077804B2 (ja) * | 2012-09-06 | 2017-02-08 | エドワーズ株式会社 | 固定側部材及び真空ポンプ |
JP7137923B2 (ja) * | 2017-11-16 | 2022-09-15 | エドワーズ株式会社 | 真空ポンプ |
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JP7164981B2 (ja) * | 2018-07-19 | 2022-11-02 | エドワーズ株式会社 | 真空ポンプ |
JP7382150B2 (ja) * | 2019-03-25 | 2023-11-16 | エドワーズ株式会社 | 真空ポンプ、及び、真空ポンプに用いられるシール部材 |
JP7306878B2 (ja) * | 2019-05-31 | 2023-07-11 | エドワーズ株式会社 | 真空ポンプ、及び、真空ポンプ構成部品 |
JP2021055673A (ja) * | 2019-09-30 | 2021-04-08 | エドワーズ株式会社 | 真空ポンプ |
JP7480604B2 (ja) | 2020-06-26 | 2024-05-10 | 株式会社島津製作所 | 真空ポンプ |
FR3118651B1 (fr) * | 2021-01-06 | 2023-03-31 | Pfeiffer Vacuum | Dispositif de chauffage et pompe à vide turbomoléculaire |
JP2023079565A (ja) * | 2021-11-29 | 2023-06-08 | エドワーズ株式会社 | 真空ポンプ、スペーサ部品、及びボルトの締結方法 |
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Also Published As
Publication number | Publication date |
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CN108350894A (zh) | 2018-07-31 |
KR102620442B1 (ko) | 2024-01-03 |
CN108350894B (zh) | 2021-02-12 |
EP3379086A4 (en) | 2019-06-26 |
JP6666696B2 (ja) | 2020-03-18 |
US20180335052A1 (en) | 2018-11-22 |
JP2017089582A (ja) | 2017-05-25 |
KR20180082423A (ko) | 2018-07-18 |
EP3379086A1 (en) | 2018-09-26 |
US10907653B2 (en) | 2021-02-02 |
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