WO2009101699A1 - ターボ分子ポンプ - Google Patents
ターボ分子ポンプ Download PDFInfo
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- WO2009101699A1 WO2009101699A1 PCT/JP2008/052540 JP2008052540W WO2009101699A1 WO 2009101699 A1 WO2009101699 A1 WO 2009101699A1 JP 2008052540 W JP2008052540 W JP 2008052540W WO 2009101699 A1 WO2009101699 A1 WO 2009101699A1
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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
- F04D19/042—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
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors
- F04D29/324—Blades
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
- F04D29/327—Rotors specially for elastic fluids for axial flow pumps for axial flow fans with non identical blades
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/70—Shape
Definitions
- the present invention relates to a turbo molecular pump.
- the turbo molecular pump performs vacuum evacuation by the operation of a turbine blade composed of a combination of a rotor blade and a fixed blade.
- the turbine blades are formed radially about the axis of rotation, and the peripheral speeds of the blade root portion and the blade tip portion are different. Therefore, the optimum design is performed so that the performance based on the blade angle and the blade interval at the intermediate point between the blade root and the blade tip becomes the target performance.
- the increase in the aperture ratio is larger than the increase in the peripheral speed on the outer periphery side than the intermediate point, and the influence of the backflow is larger than that in the intermediate point. It will be out of the optimal design.
- the aperture ratio when the turbine blade is viewed from the axial direction, the ratio of the portion that can be seen through from the opposite side is referred to as the aperture ratio.
- a rotor blade has been proposed that employs a torsion blade in which the blade angle of the turbine blade is gradually decreased from the blade root to the blade outer periphery to suppress an increase in the opening ratio of the outer peripheral portion.
- a torsion blade in which the blade angle of the turbine blade is gradually decreased from the blade root to the blade outer periphery to suppress an increase in the opening ratio of the outer peripheral portion.
- the blade angle is set so as to be optimal from the blade middle portion to the blade outer peripheral portion.
- the blade angle at the blade root portion having a low peripheral speed becomes too large, and the influence of the backflow on the exhaust performance becomes large.
- the exhaust performance is significantly reduced due to the reverse flow.
- a turbomolecular pump includes a plurality of rotating blades having a plurality of blades radially formed from a rotating body and a plurality of stationary blades having a plurality of blades arranged radially with respect to a rotating shaft of the rotating body.
- a blade provided on at least one of the rotor blade and the stationary blade is provided as a torsional blade in which the blade angle of the blade is set by an equation having a radial distance from the rotation axis as a variable, and the blade angle formula is: The first formula that gives the optimum blade angle on the outer peripheral side from the predetermined radial direction distance of the blade and the second formula that gives the blade angle that suppresses the backflow of gas molecules on the inner peripheral side from the predetermined radial direction distance.
- the blade angle at a predetermined radial distance is ⁇ b
- the blade angle at the innermost periphery of the blade is ⁇ in
- the blade angle at the outermost periphery of the blade is ⁇ out
- the blade angle ⁇ in the first equation Satisfies the condition “ ⁇ out ⁇ ⁇ ⁇ ⁇ b”
- the blade angle ⁇ in the second equation satisfies the condition “ ⁇ b ⁇ ⁇ ⁇ in”.
- at least one of the first and second expressions can be configured by a plurality of expressions.
- the blade angle at a predetermined radial distance is ⁇ b
- the blade angle at the innermost periphery of the blade is ⁇ in
- the blade angle at the outermost periphery of the blade is ⁇ out
- the distance from the outermost periphery of the blade is D
- the length of the blade is G
- a rotating blade having a plurality of blades radially formed from a rotating body, and a fixed blade having a plurality of blades arranged radially with respect to the rotating shaft of the rotating body,
- the blades satisfy the condition “ ⁇ out ⁇ ⁇ ⁇ ⁇ b” when the blade angle ⁇ is outside the predetermined radial distance and the condition “ ⁇ b ⁇ ⁇ ⁇ ⁇ in” when the blade is outside the predetermined radial distance. It is a torsion wing that satisfies the above.
- the blades of the rotor blades can be formed so as to satisfy the expression “ ⁇ Sx ⁇ (H / tan ⁇ x) ⁇ / 2 ⁇ ⁇ Sy ⁇ (H / tan ⁇ y) ⁇ / 2”.
- Sx and ⁇ x are the distance and blade angle between the blades at an arbitrary distance from the outermost periphery of the blade
- Sy and ⁇ y are the distance and blade angle between the blades at a distance on the inner peripheral side from the arbitrary distance of the blade
- H is The axial height of the blade.
- S is the distance between the blades at an arbitrary distance from the outermost periphery of the blade
- Sout is the distance between the blades at the outermost periphery of the blade
- Sin is the distance between the blades at the innermost periphery of the blade.
- S is the distance between the blades at an arbitrary distance from the outermost periphery of the blade
- Sout is the distance between the blades at the outermost periphery of the blade
- Sin is the distance between the blades at the innermost periphery of the blade
- Sb is the blade at a predetermined radial distance Is the distance between.
- the present invention in the torsional blade, it is possible to improve the effect of suppressing the backflow of gas molecules on the blade inner peripheral side while optimizing the blade angle on the blade outer peripheral side.
- FIG. 1 is a cross-sectional view showing an embodiment of a turbo molecular pump according to the present invention. It is a figure explaining a rotary blade, (a) is a top view, (b) is a perspective view. It is a perspective view which shows a rotary blade. It is a figure which shows an example of the conventional torsion wing
- FIG. 4 is a diagram showing a relationship between a radius Rt and a blade angle ⁇ , where (a) shows linearly changing lines L1 to L4, and (b) shows a curvedly changing line L6. It is sectional drawing which cut
- FIG. 1 is a view showing a turbo molecular pump according to a first embodiment of the present invention, and is a cross-sectional view of a turbo molecular pump main body.
- the turbo molecular pump includes a pump main body 1 shown in FIG. 1 and a controller (not shown) that supplies power to the pump main body 1 to control rotational driving.
- a rotor 4 having a plurality of stages of rotating blades 4B and a rotating cylindrical portion 4D is provided.
- a plurality of blades 40 are formed radially on the rotor 4, and one stage of rotating blades 4 ⁇ / b> B is configured by the blades 40 formed over one circumference of the rotor outer periphery.
- the rotor 4 is bolted to the shaft 3.
- the shaft 3 to which the rotor 4 is fixed is supported in a non-contact manner by a pair of upper and lower radial magnetic bearings 7 and a thrust magnetic bearing 8 and is driven to rotate by a motor M.
- the rotor 4 is made of a metal material such as an aluminum alloy so that it can withstand high-speed rotation.
- FIG. 3 is a perspective view showing the fixed wing 2B.
- the fixed wing 2B includes a semi-ring outer frame 20 and an inner frame 22 and a plurality of blades 21 formed therebetween.
- a plurality of stages of rotating blades 4B and a plurality of stages of fixed blades 2B arranged alternately in the axial direction constitute a turbine blade blade part.
- the plurality of fixed blades 2B are held at predetermined positions in the casing 2 by sandwiching the outer frame 20 from above and below with spacers 2S.
- a molecular drag pump unit is constituted by the rotating cylindrical part 4D and the fixed cylindrical part 9D arranged on the downstream side of the turbine blade blade part.
- the rotating cylindrical portion 4D is provided close to the inner peripheral surface of the fixed cylindrical portion 9D, and a spiral groove is formed on the inner peripheral surface of the fixed cylindrical portion 9D.
- an exhaust action is generated by the spiral groove of the fixed cylindrical part 9D and the rotating cylindrical part 4D rotating at high speed.
- the turbo molecular pump in which the turbine blade blade part and the molecular drag pump part shown in FIG. 1 are combined is called a wide area turbo molecular pump.
- the gas molecules flowing in from the intake port 5 are knocked down by the turbine blade blade and are compressed and exhausted toward the downstream side.
- the compressed gas molecules are further compressed by the molecular drag pump unit and discharged from the exhaust port 6.
- torsional blades which will be described later, are employed for the rotor blades 4B and stationary blades 2B up to the fourth stage counted from the intake port side.
- the number of stages of the rotary blade 4B and the fixed blade 2B to which the torsional blade is applied is determined as appropriate in consideration of the balance with the exhaust performance.
- FIG. 4 shows an example of a conventional rotary blade 400 having a twisted blade, where (a) is a plan view and (b) is a perspective view.
- a plurality of blades 401 constituting one stage of the rotary blade 400 are formed radially about the axis J of the rotor 4.
- an interval S between the blades 400 (hereinafter referred to as an inter-blade distance) S becomes smaller toward the inner peripheral side.
- the exhaust performance is optimal in the range A1 on the outer peripheral side (Rout ⁇ R ⁇ R1) from the radius R1 where the peripheral speed is relatively large and the exhaust performance is easy to set high. Wing design is adopted.
- the blade angle ⁇ out at the outermost periphery (blade tip) is set to be smaller than the blade angle ⁇ in at the innermost periphery (blade root).
- one machining formula using the blade angle ⁇ and the inter-blade distance S as parameters is used.
- machining is generally performed using a machining formula in which the inter-blade distance S and the blade angle ⁇ change with respect to the radius R.
- the blade angle ⁇ is increased from the blade tip toward the blade root. It is set to gradually increase.
- a rotor blade 400 shown in FIG. 4 is a rotor blade processed under such conditions.
- the relationship between the radius Rt and the blade angle ⁇ in the conventional case is shown as a line L1 in FIG.
- the blade angle ⁇ increases at a constant rate with respect to the radius R.
- the inclination angle of the line L1 is set so that the exhaust performance is optimal in the range A1 from the tip to the middle vicinity.
- the blade angle ⁇ is also increased in the range A2 at the same rate as in the range A1, there is a problem that the blade angle ⁇ becomes too large when the influence of gas backflow is considered.
- the blade angle ⁇ in the range A2 inside the radius R1 is changed according to the lines L2 to L4 different from the line L1.
- the lines L2 to L4 shown in FIG. 5A are expressed by equations, the following equations (1) and (2) are obtained.
- (Range A1): ⁇ ⁇ out + ( ⁇ b ⁇ out) ⁇ (D / Gbout) (1)
- (Range A2): ⁇ ⁇ in + ( ⁇ b ⁇ in) ⁇ (GD) / Gbin (2)
- FIG. 6 is a cross-sectional view of a part of the rotor blade 4B cut in a direction perpendicular to the axis. This sectional view has the same shape as the shape of the upper end surface of the blade 40 shown in FIG. 2, and the contour line of the section represents the locus of the machining tool.
- G is the length of the blade 40
- Gbout is the blade length from the outermost circumference (tip) of the blade 40 to the radius R1
- Gbin is from the innermost circumference (root) of the blade 40 to the radius R1.
- the blade length. D represents the distance from the outermost periphery.
- the line L2 has a smaller inclination (absolute value) than the line L1, and the blade angle ⁇ is constant in the line L3. Further, in the case of the line L4, the blade angle ⁇ is set to be smaller as it approaches the blade root (radius Rin).
- the exhaust performance is optimal in the range A1 on the outer peripheral side (Rout ⁇ R ⁇ R1) from the radius R1 where the peripheral speed is relatively large and the exhaust performance can be easily set high as in the conventional case.
- the range A2 (R1 ⁇ R) where the peripheral speed is relatively small it is possible to set the emphasis on backflow suppression of gas molecules as compared with the conventional case.
- the lines L1 to L4 in which the blade angle ⁇ changes linearly with respect to the radius R are employed.
- a line in which the blade angle ⁇ monotonously increases or decreases may be employed.
- the blade angle ⁇ may be changed like a single line L5 (parabola) having a peak at the radius R1.
- L5 parabola
- FIG. 2 is a case where the blade 40 is processed as shown by a line L4 in FIG. 5A, (a) is a plan view, and (b) is a perspective view.
- the blade shape is the same because both the rotor blade 4B of FIG. 2 and the rotor blade 400 of FIG. 4 are processed by the processing formula of the line L1.
- the aperture ratio is smaller than that of the conventional rotor blade 400.
- the blade angle of the blade 20 of the fixed blade 2B shown in FIG. 2 is also set in the same manner as the blade 40 of the rotary blade 4B.
- the processing formula is switched only before and after the radius R1, but if the conditions of the formulas (3) and (4) are satisfied, a plurality of processing formulas are further included in the range A1 or the range A2.
- a processing formula may be used.
- the size of the radius R1 that divides the ranges A1 and A2 is not uniquely determined, and differs depending on which item of the exhaust performance such as the compression ratio and the exhaust speed is important.
- the backflow of gas molecules on the inner peripheral side is suppressed by switching the tendency of the change in the blade angle ⁇ before and after the radius R1, as shown in FIG. ing.
- the blade angle ⁇ decreases as in the lines L4 and L5 in FIG. 5
- the degree of decrease is too large, when the blade 40 is viewed from the outer peripheral side, the inner peripheral side where the processing tool is to be inserted is inserted.
- the gap between the blades may be hidden behind the outer peripheral blade portion. In such a case, since processing from the outer diameter direction is impossible, the rotor blade 4B must be processed from the axial direction.
- the gap between the upper and lower blades is slightly larger than the size of one stage of the fixed blade. Therefore, it is very difficult to process the rotary blade 4B from the axial direction. Therefore, in the second embodiment, a blade shape that can process the rotor blade from the outer peripheral side while satisfying the conditions of the first embodiment will be described. Since the fixed blade 2B shown in FIG. 3 can be processed step by step, the processing from the axial direction is easier than the rotating blade 4B.
- the inter-blade distance S of the blade 40 is set so as to satisfy the following expression (5).
- the inter-blade distance at the distance Dx where Dx ⁇ Dy is Sx, and the inter-blade distance at the distance Dy is Sy.
- H is the height of the blade 40 in the axial direction.
- FIG. 7 is a diagram for explaining the equation (5), and shows the trajectories Tx and Ty of the machining tool at the distances Dx and Dy viewed from the outer peripheral side. Since the blade 40 is machined from the outer peripheral side, in FIG. 7, the inner tool locus Tx needs to be inside the outer tool locus Ty.
- the blade angle ⁇ the relationship as shown in FIG. 7 is satisfied by setting the inter-blade distance S as shown in Expression (5), and the blade 40 can be machined from the outer peripheral side. .
- the blade angle ⁇ may be set as shown in equations (1) and (2) and equations (3) and (4).
- the inter-blade distance S of the blade 40 at the distance D is set so as to satisfy the following expression (6).
- Expression (6) is an expression related to the inter-blade distance S, and the blade angle ⁇ may be set as in Expressions (1) and (2), and Expressions (3) and (4).
- S Sout ⁇ (Sout ⁇ Sin) ⁇ (D / G) (6)
- the inter-blade distance S of the blade 40 at the distance D is set so as to satisfy the following expressions (7) and (8).
- Sb is the distance between the blades at the radius R1, and is set larger than the distance between the blades Sc at the innermost circumference (blade root).
- (Range A1): S Sout ⁇ (Sout ⁇ Sb) ⁇ (D / Gbout) (7)
- (Range A2): S Sout ⁇ (Sb ⁇ Sin) ⁇ (D ⁇ Gbout) / Gbin (8)
- the influence of the backflow of gas molecules is set while setting the optimum blade angle from the blade outer periphery dominant in the exhaust performance to the blade middle portion (range A1).
- the backflow can be suppressed in the blade inner periphery (range A2).
- the exhaust performance of the turbo molecular pump can be improved.
- the inter-blade distance S as in the second embodiment, processing of the torsional wing becomes easy.
Abstract
Description
本発明によるターボ分子ポンプにおいて、所定半径方向距離における翼角度をαb、ブレードの最内周における翼角度をαin、ブレードの最外周における翼角度をαoutとしたとき、第1の式における翼角度αは条件「αout≦α≦αb」を満たし、第2の式における翼角度αは条件「αb≧α≧αin」を満たすようにする。また、第1および第2の式の少なくとも一方を、複数の式で構成することもできる。
さらにまた、所定半径方向距離における翼角度をαb、ブレードの最内周における翼角度をαin、ブレードの最外周における翼角度をαout、ブレードの最外周からの距離をD、ブレードの長さをG、ブレードの最外周から所定半径方向距離までの長さをGbout、ブレードの最内周から所定半径方向距離までの長さをGbinとしたとき、翼角度αに関する第1の式を式「α=αout+(αb-αout)・(D/Gbout)」で設定し、第2の式を「α=αin+(αb-αin)・(G-D)/Gbin」で設定することもできる。
本発明によるターボ分子ポンプの他の態様では、回転体から放射状に形成された複数のブレードを有する回転翼と、回転体の回転軸に対して放射状に配置された複数のブレードを有する固定翼とを交互に複数段備え、ブレードは、その翼角度αが所定半径方向距離より外周側では条件「αout≦α≦αb」を満たし、所定半径方向距離より外周側では条件「αb≧α≧αin」を満たすねじり翼である。ただし、αbは所定半径方向距離における翼角度、αinはブレードの最内周における翼角度、αoutはブレードの最外周における翼角度である。
本発明によるターボ分子ポンプにおいて、回転翼のブレードを、式「{Sx-(H/tanαx)}/2≧{Sy-(H/tanαy)}/2」を満たすように形成することができる。ただし、Sxおよびαxはブレードの最外周から任意の距離におけるブレード間の距離および翼角度、Syおよびαyはブレードの任意の距離よりも内周側の距離におけるブレード間の距離および翼角度、Hはブレードの軸方向高さである。
また、回転翼のブレードを、式「S=Sout-(Sout-Sin)・(D/G)」を満たすように形成することもできる。ただし、Sはブレードの最外周から任意の距離におけるブレード間の距離、Soutはブレードの最外周におけるブレード間の距離、Sinはブレード最内周におけるブレード間の距離である。
さらにまた、回転翼のブレードのブレード間の距離Sを、所定半径方向距離より外周側においては式「S=Sout-(Sout-Sb)・(D/Gbout)」のように設定し、所定半径方向距離より内周側においては式「S=Sout-(Sb-Sin)・(D-Gbout)/Gbin」のように設定することができる。ただし、Sはブレードの最外周から任意の距離におけるブレード間の距離、Soutはブレードの最外周におけるブレード間の距離、Sinはブレード最内周におけるブレード間の距離、Sbは所定半径方向距離におけるブレード間の距離である。
-第1の実施の形態-
図1は本発明に係るターボ分子ンプの第1の実施の形態を示す図であり、ターボ分子ポンプ本体の断面図である。ターボ分子ポンプは、図1に示すポンプ本体1と、ポンプ本体1に電源を供給し回転駆動を制御するコントローラ(不図示)とから成る。
(範囲A1):α=αout+(αb-αout)・(D/Gbout) …(1)
(範囲A2):α=αin+(αb-αin)・(G-D)/Gbin …(2)
αout≦α≦αb (範囲A1)…(3)
αb≧α≧αin (範囲A2)…(4)
上述した第1の実施の形態では、翼角度αの変化の傾向を、図5に示すように半径R1の前後で切り替えることにより、内周側(範囲A2)における気体分子の逆流を抑えるようにしている。ところが、図5のラインL4やL5のように翼角度αが減少するものにおいては、減少の度合いが大きすぎると、ブレード40を外周側から見たときに、加工ツールを入れるべき内周側のブレード間の隙間が外周側のブレード部分に隠れてしまう場合がある。そのような場合、外径方向からの加工が不可能となるため、軸方向から回転翼4Bの加工を行わざるを得ない。
第1のブレード形状では、ブレード40の翼間距離Sを次式(5)を満たすように設定する。図6に示すブレード40の最外周からの距離Dに関して、Dx<Dyなる距離Dxにおける翼間距離をSxとし、距離Dyにおける翼間距離をSyとする。Hはブレード40の軸方向の高さである。
{Sx-(H/tanαx)}/2≧{Sy-(H/tanαy)}/2 …(5)
第2のブレード形状では、距離Dにおけるブレード40の翼間距離Sを次式(6)を満たすように設定する。この設定の場合、外周側から内周側にかけて一定の割合で翼間距離Sが減少しているので、ブレード40を外周側から加工することが可能となる。式(6)は翼間距離Sに関する式であり、翼角度αに関しては式(1)、(2)や、式(3)、(4)のように設定すれば良い。
S=Sout-(Sout-Sin)・(D/G) …(6)
第3のブレード形状では、距離Dにおけるブレード40の翼間距離Sを次式(7),(8)を満たすように設定する。Sbは半径R1における翼間距離であり、最内周(翼根元)の翼間距離Scよりも大きく設定される。
(範囲A1):S=Sout-(Sout-Sb)・(D/Gbout) …(7)
(範囲A2):S=Sout-(Sb-Sin)・(D-Gbout)/Gbin …(8)
Claims (8)
- 回転体から放射状に形成された複数のブレードを有する回転翼と、前記回転体の回転軸に対して放射状に配置された複数のブレードを有する固定翼とを交互に複数段備え、
前記回転翼および固定翼の少なくとも一方に設けられた前記ブレードを、該ブレードの翼角度が前記回転軸からの半径方向距離を変数とする式により設定されるねじり翼とし、
前記翼角度の式を、前記ブレードの所定半径方向距離より外周側における最適翼角度を与える第1の式と、前記所定半径方向距離より内周側において気体分子の逆流を抑制する翼角度を与える第2の式とで構成したターボ分子ポンプ。 - 請求項1に記載のターボ分子ポンプにおいて、
前記所定半径方向距離における翼角度をαb、前記ブレードの最内周における翼角度をαin、前記ブレードの最外周における翼角度をαoutとしたとき、
前記第1の式における翼角度αは条件「αout≦α≦αb」を満たし、前記第2の式における翼角度αは条件「αb≧α≧αin」を満たすターボ分子ポンプ。 - 請求項1または2に記載のターボ分子ポンプにおいて、
前記第1および第2の式の少なくとも一方を、複数の式で構成したターボ分子ポンプ。 - 請求項1に記載のターボ分子ポンプにおいて、
翼角度αに関する前記第1の式を、式「α=αout+(αb-αout)・(D/Gbout)」で設定し、
翼角度αに関する前記第2の式を、式「α=αin+(αb-αin)・(G-D)/Gbin」で設定するターボ分子ポンプ。
ただし、前記所定半径方向距離における翼角度をαb、前記ブレードの最内周における翼角度をαin、前記ブレードの最外周における翼角度をαout、前記ブレードの最外周からの距離をD、前記ブレードの長さをG、前記ブレードの最外周から前記所定半径方向距離までの長さをGbout、前記ブレードの最内周から前記所定半径方向距離までの長さをGbinとする。 - 回転体から放射状に形成された複数のブレードを有する回転翼と、前記回転体の回転軸に対して放射状に配置された複数のブレードを有する固定翼とを交互に複数段備え、
前記ブレードは、その翼角度αが所定半径方向距離より外周側では条件「αout≦α≦αb」を満たし、前記所定半径方向距離より外周側では条件「αb≧α≧αin」を満たすねじり翼であるターボ分子ポンプ。ただし、αbは前記所定半径方向距離における翼角度、αinは前記ブレードの最内周における翼角度、αoutは前記ブレードの最外周における翼角度である。 - 請求項1~5のいずれか一項に記載のターボ分子ポンプにおいて、
前記回転翼のブレードを、式「{Sx-(H/tanαx)}/2≧{Sy-(H/tanαy)}/2」を満たすように形成したターボ分子ポンプ。
ただし、Sxおよびαxはブレードの最外周から任意の距離におけるブレード間の距離および翼角度、Syおよびαyはブレードの前記任意の距離よりも内周側の距離におけるブレード間の距離および翼角度、Hはブレードの軸方向高さである。 - 請求項4に記載のターボ分子ポンプにおいて、
前記回転翼のブレードを、式「S=Sout-(Sout-Sin)・(D/G)」を満たすように形成したターボ分子ポンプ。
ただし、Sは前記ブレードの最外周から任意の距離におけるブレード間の距離、Soutは前記ブレードの最外周におけるブレード間の距離、Sinはブレード最内周におけるブレード間の距離である。 - 請求項4に記載のターボ分子ポンプにおいて、
前記回転翼のブレードのブレード間の距離Sを、前記所定半径方向距離より外周側においては式「S=Sout-(Sout-Sb)・(D/Gbout)」のように設定し、前記所定半径方向距離より内周側においては式「S=Sout-(Sb-Sin)・(D-Gbout)/Gbin」のように設定するターボ分子ポンプ。
ただし、Sは前記ブレードの最外周から任意の距離におけるブレード間の距離、Soutは前記ブレードの最外周におけるブレード間の距離、Sinはブレード最内周におけるブレード間の距離、Sbは前記所定半径方向距離におけるブレード間の距離である。
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JP2009553317A JP5445143B2 (ja) | 2008-02-15 | 2008-02-15 | ターボ分子ポンプ |
PCT/JP2008/052540 WO2009101699A1 (ja) | 2008-02-15 | 2008-02-15 | ターボ分子ポンプ |
CN200880128619.3A CN102007298B (zh) | 2008-02-15 | 2008-02-15 | 涡轮分子泵 |
US12/867,232 US8668436B2 (en) | 2008-02-15 | 2008-02-15 | Turbomolecular pump |
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Cited By (2)
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JP2013092063A (ja) * | 2011-10-24 | 2013-05-16 | Shimadzu Corp | ターボ分子ポンプおよびターボ分子ポンプ用の翼構造 |
JP2020122429A (ja) * | 2019-01-30 | 2020-08-13 | 株式会社島津製作所 | ターボ分子ポンプ |
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CN102588320A (zh) * | 2012-03-09 | 2012-07-18 | 北京北仪创新真空技术有限责任公司 | 分子泵钣金定片 |
GB2552793A (en) | 2016-08-08 | 2018-02-14 | Edwards Ltd | Vacuum pump |
US10557471B2 (en) | 2017-11-16 | 2020-02-11 | L Dean Stansbury | Turbomolecular vacuum pump for ionized matter and plasma fields |
TWI678471B (zh) * | 2018-08-02 | 2019-12-01 | 宏碁股份有限公司 | 散熱風扇 |
GB2618348A (en) * | 2022-05-04 | 2023-11-08 | Edwards Ltd | Rotor blade for a turbomolecular vacuum pump |
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DE3891263T1 (de) * | 1988-02-26 | 1990-03-15 | Nikolaj Michailovic Novikov | Turbomolekular-vakuumpumpe |
JPH0261387A (ja) | 1988-08-24 | 1990-03-01 | Seiko Seiki Co Ltd | ターボ分子ポンプ |
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2008
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- 2008-02-15 WO PCT/JP2008/052540 patent/WO2009101699A1/ja active Application Filing
- 2008-02-15 CN CN200880128619.3A patent/CN102007298B/zh active Active
- 2008-02-15 JP JP2009553317A patent/JP5445143B2/ja active Active
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JPH1089284A (ja) * | 1996-09-12 | 1998-04-07 | Seiko Seiki Co Ltd | ターボ分子ポンプ |
JP2000110771A (ja) * | 1998-10-01 | 2000-04-18 | Mitsubishi Heavy Ind Ltd | ターボ分子ポンプ |
JP2000161285A (ja) * | 1998-11-24 | 2000-06-13 | Seiko Seiki Co Ltd | ターボ分子ポンプ及び真空装置 |
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JP2020122429A (ja) * | 2019-01-30 | 2020-08-13 | 株式会社島津製作所 | ターボ分子ポンプ |
JP7052752B2 (ja) | 2019-01-30 | 2022-04-12 | 株式会社島津製作所 | ターボ分子ポンプ |
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CN102007298A (zh) | 2011-04-06 |
US8668436B2 (en) | 2014-03-11 |
US20110064562A1 (en) | 2011-03-17 |
CN102007298B (zh) | 2014-04-30 |
JP5445143B2 (ja) | 2014-03-19 |
JPWO2009101699A1 (ja) | 2011-06-02 |
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