JP2003336596A - Dry turbo vacuum pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the number of part items, to reduce a cost by forming a dry turbo vacuum pump in a compact manner and facilitating manufacture and management, and besides to suppress unevenness in performance owing to factors in terms of manufacture to a low value. <P>SOLUTION: At least a first stage impeller of a peripheral flow pump 4b and a centrifugal pump 4a is integrally formed, ribs are formed on a stator 2 and a motor casing 10, and communicating passages 22, 22a, 25, 26a, 26b, 27a and 27b for lubrication and cooling oil are formed in the rib. Further, the surface facing the impeller of an interstage wall of the stator 2 is formed in the shape of a plate and manufacture through ordinary casting is practicable. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dry turbo vacuum pump whose exhaust port has a pressure of atmospheric pressure, and is particularly suitable for use in a manufacturing apparatus for semiconductors, foods, chemicals, etc., and is suitable for producing a clean vacuum. The present invention relates to a dry turbo vacuum pump.

[0002]

2. Description of the Related Art In a conventional dry turbo vacuum pump in which the pressure of the exhaust port is atmospheric pressure, as described in Japanese Patent Publication No. 3-7039, it is difficult to machine a circumferential flow pump stage. The impeller stage was constructed by precision casting the circumferential flow pump stage and fastening it with a machined centrifugal pump stage using screws. Further, the production of the impeller by precision casting is described in detail in JP-A-63-61798. Further, as described in JP-A-62-258186, the stator of the vacuum pump has a shape in which a recess is formed in a portion of the stator interstage wall facing the impeller.

[Patent Document 1] Japanese Patent Publication No. 3-7039

[Patent Document 2] Japanese Patent Laid-Open No. 63-61798

[Patent Document 3] Japanese Patent Laid-Open No. 62-258186

[0003]

The prior art Japanese Patent Publication No. 3-7039 requires the work of attaching the centrifugal pump stage to the circumferential flow pump stage, and the concentricity of the impeller at the time of assembly. Assembling was not good because work such as securing the degree and preventing contact was required. As a result of combining a plurality of parts, the dimensional tolerance of each part is accumulated, it is difficult to control and secure the size of the slit between the impeller and the stator, and it is difficult to secure the performance required for the vacuum pump.

Further, the method described in Japanese Patent Laid-Open No. 63-61798 has a problem in that the dimensional accuracy is poor and the product performance varies because the impeller is manufactured by the casting method. Further, it is difficult to completely eliminate internal defects, and defects are exposed during processing after the casting work, and the components must be scrapped, resulting in a poor yield as a component. Furthermore, in order to form the impeller shape described in JP-A-62-258186 by casting, there is no choice but to use a casting method using lost wax, which causes a problem that the cost at the material stage is high.

It is an object of the present invention to provide a dry turbo vacuum pump which has a small number of parts, is compact, and is easy to manufacture and manage. Another object of the present invention is to provide a dry turbo vacuum pump in which variations in performance due to various manufacturing factors are reduced.

[0006]

In order to achieve the above object, a housing having an intake port and an exhaust port, a rotary shaft rotatably supported in the housing, and a multi-stage circumference supported by the rotary shaft. A flow impeller and a stator forming a multi-stage circumferential flow pump together with the circumferential flow impeller in the housing, and a centrifugal pump is disposed on the intake port side of the circumferential flow pump. In a dry turbo vacuum pump that exhausts gas sucked from its mouth to the atmosphere from an exhaust port, the inner diameters of at least two adjacent stator portions of the multistage circumferential flow pump stage are substantially the same, and the stator is provided in this stator. The portion of the inter-stage wall that separates each of the stages is opposed to the impeller and is flat.

Further, a housing having an intake port and an exhaust port, a rotary shaft rotatably supported in the housing,
It has a multi-stage circumferential flow impeller supported on a rotating shaft and a stator that forms a multi-stage circumferential flow pump together with the circumferential flow impeller in the housing, and on the intake side of this circumferential flow pump. In a dry turbo vacuum pump in which a centrifugal pump is provided and which exhausts the gas sucked from the intake port to the atmosphere from the exhaust port, at least one stage of the multistage circumferential flow pump and the centrifugal pump is integrally formed. . ◆ And, preferably, the circumferential flow impeller comprises a core plate and a plurality of blades arranged at intervals in the core plate, and the radial cross-sectional shape of the groove bottom surface between the blades is stepwise or intermittent. It is formed by a group of straight lines.

Further, a housing having an intake port and an exhaust port, a rotary shaft rotatably supported in the housing, a multistage circumferential flow impeller supported by the rotary shaft, and a circumferential flow in the housing. A centrifugal pump is provided on the suction port side of the circumferential flow pump together with a stator that forms a multi-stage circumferential flow pump together with an impeller, and the gas sucked from the suction port is exhausted to the atmosphere from the exhaust port. In a dry turbo vacuum pump, the stator has a half-split structure, each half-split part is provided with a cooling jacket part, and a communication passage communicating between the jacket parts of each half-split part is formed in each half-split part. .

A housing having an intake port and an exhaust port, a rotary shaft rotatably supported in the housing, a multi-stage circumferential flow impeller supported by the rotary shaft, and a circumferential flow vane in the housing. A dry turbo vacuum pump including a stator that forms a multi-stage circumferential flow pump together with a vehicle, a motor having a motor rotor and a motor stator that drive the multi-stage circumferential flow pump, and a motor casing that houses the motor stator. In the motor casing, an oil sump portion is provided, a cooling jacket is provided on an outer peripheral side of the stator, and a motor cooling jacket is provided on an outer peripheral side of the motor casing. The oil sump portion, the motor cooling jacket, and the cooling jacket are provided. Are sequentially connected to form a cooling oil circulation path. ◆ Preferably, in any of the dry turbo vacuum pumps described above, the portion of the interstage wall of the stator that faces the impeller is formed into a flat plate shape so that it can be manufactured by ordinary casting. ◆ Also, preferably, an oil sump portion is provided in the motor casing, and the oil sump portion and the cooling jacket portion of the casing are provided in the communication passage formed in the rib provided in the outer peripheral portion of the motor casing and in the outer peripheral portion of the stator. And a communication path formed in the rib.

Further, a housing having an intake port and an exhaust port, a rotary shaft rotatably supported in the housing, a multi-stage circumferential flow impeller supported by the rotary shaft, and a circumferential flow in the housing. A centrifugal pump is provided on the suction port side of the circumferential flow pump together with a stator that forms a multi-stage circumferential flow pump together with an impeller, and the gas sucked from the suction port is exhausted to the atmosphere from the exhaust port. In the dry turbo vacuum pump, at least one stage of the multi-stage circumferential flow pump and the centrifugal pump is integrally formed, and a spacer is provided between a holder that holds an upper bearing in a bearing that supports the rotating shaft and the stator. It is a thing.

Machining at least one stage of a circumferential flow pump and a centrifugal pump integrally by forming a circumferential flow impeller, which was conventionally precision casting, into a shape that can be machined using a multi-axis numerical control processing machine. Is possible. As a result, the process of assembling the circumferential flow pump and the centrifugal pump can be reduced and workability is improved. In addition, since it is possible to perform the integral processing, it is possible to improve the processing accuracy, it becomes easy to manage the gap size between the impeller and the stator, and it is possible to provide a pump with a small variation in performance. ◆ Furthermore, since the shape of the part of the interstage wall of the stator facing the impeller is made flat, it is easy to remove the mold and it can be manufactured by ordinary casting. This allows
The material cost can be reduced to about 1/10 compared to the conventional precision casting method using lost wax. ◆ Also, by providing a cooling jacket to the motor casing and the stator, and providing a cooling flow path for oil supply and drainage from the jacket in the motor casing and the stator, cooling oil piping is not required, External piping work can be significantly reduced, workability is improved, and maintenance and inspection after installation is facilitated.

[0012]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a view showing a first embodiment of the present invention, in which the intermediate portion and the lower end portion of a shaft 3 axially arranged in the vertical direction are supported by rolling bearings 7a and 7b, and a high frequency motor rotor 8a is provided between the bearings. Has been press-fitted. A pump rotor (hereinafter simply referred to as a rotor) 1 in which at least one stage of a circumferential flow pump 4b including a multi-stage circumferential flow impeller and a centrifugal pump 4a including a centrifugal flow impeller is integrated on the upper side of the shaft 3 is provided. Press in and fasten. A pump stator (hereinafter simply referred to as “stator”) 2 is disposed facing the rotor 1 and coaxially with the rotor 1 with a gap.
A suction casing 5 in which an intake port 6 of the pump is formed is attached to the upper part of the with a seal. And
A cooling jacket 9 for removing heat generated by the pumping action is formed at a position corresponding to a portion of the outer circumferential portion of the stator 2 on the outer circumferential side of the impeller that performs the vacuum pumping action.

On the other hand, a motor stator 8b arranged on the outer diameter side of the motor rotor 8a so as to face the motor rotor is held by the motor casing 10. A cooling passage for cooling the motor, that is, a cooling jacket 11 is formed in a portion of the motor casing 10 located on the outer diameter side of the portion where the motor stator 8b and the motor rotor 8a face each other. In FIG. 1, the circumferential section position is changed between the motor section and the pump section.

Next, the operation of the embodiment of the present invention thus constructed will be described. ◆ When a motor composed of a high-frequency motor rotor 8a and a high-frequency motor stator 8b drives the shaft 3 and the rotor 1 at high speed based on a command from a control device (not shown), the gas sucked from the intake port 6 becomes
It is sequentially compressed as it passes through the centrifugal pump stage 4a and the circumferential flow pump stage 4b, and is exhausted from the exhaust port 12. FIG. 2 is a cross-sectional view of a circumferential flow pump stage. In each stage of the vortex flow pump, gas flows in through a suction port 13 provided in each stage, and a circumferential flow impeller 14 that rotates at a high speed causes the gas to flow in the circumferential direction. The velocity component of is added. Then, it is discharged radially from the circumferential flow impeller 14 by the centrifugal force, is decelerated in the ventilation passage 15 to recover the pressure, and again flows into the circumferential flow impeller 14. Gas is a ventilation path 1
While passing through 5, the above action is repeated, energy is obtained from the circumferential flow impeller 14, spirally flows in the ventilation passage 15, and flows into the next stage from the discharge port 16. By performing this action in multiple stages, a high compression ratio can be obtained, and as a result, the gas can be directly exhausted to the atmosphere.

3 to 6 show an embodiment of the circumferential flow impeller used in the above embodiment. In the circumferential flow impeller, a plurality of blades are radially arranged on the outer diameter side of the core plate, and a groove portion is formed between the blades. The blade thickness is almost uniform. As shown in FIGS. 3 and 4, the radial shape of the groove bottom surface between the blades of the circumferential flow impeller is an intermittent straight line group or step shape. Then, as shown in FIG. 5, the circumferential shape of the groove bottom surface between the blades of the circumferential flow impeller is formed by a plurality of arcs. Further, as shown in FIG. 6, the inner diameter portion of the blade of the circumferential flow impeller on the core plate side is formed in an arc shape. By configuring the shape of the circumferential flow impeller in this way, it becomes possible to process the circumferential flow impeller by using the numerical control processing machine.

As a result, the dimensional accuracy of the circumferential flow impeller is improved and the variation in performance is reduced. Further, since the circumferential flow pump and the centrifugal pump can be integrated, workability of assembly is also improved. In addition, compared to casting, the rotor manufactured by machining has less unbalance due to casting defects, etc.
There is also an advantage that the balance adjustment work can be shortened. Further, as shown in FIG. 5, the blade end portion of the circumferential flow impeller on the side opposite to the eccentric plate is inclined in the rotation direction (indicated by an arrow) so that the compression ratio is 10
% To 30% can be improved.

In the above embodiment, the radial shape of the groove bottom surface between the blades is formed into a straight line group or step shape, the circumferential shape is formed into a plurality of arcs, and the inner diameter portion on the core plate side is formed into an arc shape. It is not necessary to satisfy all the requirements, and any configuration may be used as long as the shape allows machining.

Further, in the present embodiment, the processing using the end mill is premised, but the present invention is included if the same processing can be performed by a tool other than the end mill.

FIG. 7 shows an embodiment of the stator 2 shown in FIG. In the present embodiment, the circumferential flow pump stage consists of eight pumps, and the inner diameters of the first to sixth stages are the same,
The inner diameters of the 7th and 8th stages are the same. The portion of the inter-stage wall 18 formed between the stages of the stator that faces the impeller has a flat plate shape. By making the inter-stage wall 18 into a flat plate shape, the mold can be easily removed at the time of casting, and by changing the conventional precision casting method from the conventional precision casting method to the ordinary casting method, the material cost is reduced to about 1/10. It can be reduced. As shown in FIG. 8, a portion of the inter-stage wall 18 of the stator 2 has a blocking portion having a length equal to or greater than the circumferential vane pitch of the circumferential flow impeller, that is, a length that allows two or more vanes to enter. 17 is provided so that the gas compressed in each stage can flow into the next stage without recirculation in the pump or internal leakage. As shown in FIG. 7, the blocking portion 17 has a structure in which the circumferential position is sequentially shifted from the upstream side to the downstream side, whereby the circumferential distribution of the thrust force is made uniform and the axial dimension of the stator 2 is made. Can be reduced.

FIG. 9 shows an embodiment of the oil supply system of the present invention. In this embodiment, the lubricating oil has two functions of lubricating and cooling the bearing and cooling the pump body and the motor. Therefore, two flow passage systems are formed. First, the lubrication / cooling system for the bearing will be described.
The oil supplied to the motor casing 10 by the oil pump 20 is filtered by the oil filter 21 accommodated in the oil filter 21 accommodating portion provided on the side portion of the motor casing and branched in the motor casing, one of which is the motor casing 10. Through the communication passage 22 provided in the upper bearing 7
a is supplied to the lower bearing 7b through the communication passage 23 separately provided in the motor casing 10. Oilifis 22a and 23a are incorporated in the middle of the communication passages 22 and 23, respectively, and the amount of oil supplied to each bearing can be adjusted by this orifice. The oil that lubricates and cools each bearing descends in the space near the shaft in the motor casing and the space formed under the bearing, and returns to the oil tank portion 24 in the motor casing 10.

Next, the cooling system for the motor and pump body will be described. The oil supplied to the motor casing 10 by the oil pump 20 is the oil filter 21 this time.
Not through, but is supplied to the cooling jacket 11 for cooling the motor through the communication passage 25 provided in the motor casing, and after cooling the motor, is supplied to the cooling jacket 9 of the stator 2 through the communication passages 26a and 26b. To be done. The oil that has cooled the pump stage returns to the oil tank portion 24 in the motor casing through the communication passages 27a and 27b. The temperature of the oil returned to the oil tank is controlled by an oil cooler (not shown), and the oil is supplied again to the motor casing 10 by the oil pump 20. This circulation is repeated thereafter.

In order to explain the cooling state with the lubricating oil in more detail, FIGS. 10 and 11 show one embodiment of the cooling jacket 9 formed on the stator 2. The stator 2 is formed in a substantially rectangular shape in the cooling jacket portion, and the cooling jacket 9 is configured by utilizing the corner portion of the rectangular shape and the portion formed by the stator wall surface having a slightly outer diameter than the stator interstage wall. The jacket covers 28a and 28b are screwed to the outlet portion 28 of this space via packing or the like. The stator 2 has a half-split structure, and holes 29 are formed in both jackets (half-split portions) so as to communicate with each other.
As a result, the oil supplied from the communication passage 26b to one jacket can flow into the other jacket. The communication passages 26 b and 27 a are provided in ribs provided on the outer circumference of the stator 2. This makes it possible to omit external piping, improve workability, and prevent defective piping during transportation and operation. ◆ In Fig. 12 and Fig. 13,
An example of the cooling jacket 11 of the motor casing and each communication passage is shown. Ribs 41, 42, 43 are formed on the outer peripheral side of the motor casing for communication passages, and communication passages 22, 26b, 27b are formed inside the ribs 41, 42, 43.
As in the case of the stator, the cooling jacket of the motor casing can also omit external piping, and the workability is improved.

FIG. 14 shows another embodiment of the present invention. The outer case 30 has a cylindrical shape that covers the outer circumferences of the stator 2 and the suction casing 5, and is arranged on the outer circumference of the stator.
The upper portion is supported by the ring 31, the lower end side is bent into a flange shape, and the bent portion is fixed with bolts. With this structure, the outer case 30 can be attached and detached, and workability is improved. Also, the bearing holder 32 and the half-split holder spacer 3
3 is a separate part. As a result, the rotor 1 and the stator 2
In the adjustment of the length of the collar 34 necessary for the gap adjustment work of the
No need to remove from. Further, the gap adjustment only needs to adjust the thickness of the holder spacer 33, disassembling and reassembling the rotor 1 and the shaft 3 is not necessary, and the assembly time per pump can be shortened by about 6 hours.

FIG. 15 shows an embodiment of the apparatus equipped with the dry vacuum pump of the present invention. The pump main body 35, the pump control device 36 and other auxiliary equipments are attached to the pedestal 37, and the cover 38 covers the package. It has been transformed. By packaging, the user does not have to perform wiring work between the pump main body 35 and the pump control device 36. Also,
Simply connect the power supply, water supply and drainage, and shaft sealing gas utilities to start the pump immediately.

16 and 17 show a modified example of the dry vacuum pump of the present invention, in which the exhaust chamber is changed. When reducing the exhaust capacity, remove the centrifugal pump stage added to the upper part of the integrally formed centrifugal pump stage and the circumferential flow pump stage, and further increase the exhaust capacity to the upper part of the integrally formed centrifugal pump stage. A removable centrifugal pump stage is added, and the suction casing 5 is attached to the stator of the centrifugal pump stage or the upper part of the stator. As a result, the exhaust capacity can be changed from 1000 l / min to 9000 l / min without changing the other parts, only by increasing or decreasing the number of centrifugal pump stages, making it possible to standardize parts, material costs, and assembly. Cost can be reduced.

According to this embodiment, since at least one of the circumferential flow pump stage and the centrifugal pump stage is integrated, dimensional control is facilitated, and variations in performance and performance can be improved. ◆ In addition, the time required for assembly can be reduced to about half that of the conventional product because the external piping has been significantly reduced, and the reliability of the piping system during transport operation can be improved. By changing the conventional precision casting method from the conventional precision casting method to the stator manufacturing method, the stator manufacturing cost can be greatly reduced to about 1/10 of the conventional cost.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of an embodiment of the present invention.

2 is a cross-sectional view of the embodiment shown in FIG.

FIG. 3 is a detailed vertical cross-sectional view of a circumferential flow impeller according to an embodiment of the present invention.

FIG. 4 is a detailed vertical sectional view of a circumferential flow impeller according to an embodiment of the present invention.

5 is a view from the outer periphery of the embodiment shown in FIGS. 3 and 4. FIG.

FIG. 6 is a front view of a circumferential flow impeller.

FIG. 7 is a front view of the stator according to the embodiment of the present invention.

FIG. 8 is a view from the outer periphery of the stator blocking portion according to the embodiment of the present invention.

FIG. 9 is a vertical sectional view showing a lubricating oil system according to an embodiment of the present invention.

FIG. 10 is a cross-sectional view of the stator according to the embodiment of the present invention.

FIG. 11 is a side view of the stator according to the embodiment of the present invention.

FIG. 12 is a cross-sectional view of the motor casing according to the embodiment of the present invention.

FIG. 13 is a cross-sectional view of the motor casing according to the embodiment of the present invention.

FIG. 14 is a vertical sectional view of another embodiment of the present invention.

FIG. 15 is a vertical cross-sectional view of a package type vacuum exhaust device equipped with a dry turbo vacuum pump according to an embodiment of the present invention.

FIG. 16 is a vertical sectional view of another embodiment of the present invention.

FIG. 17 is a vertical cross-sectional view of still another embodiment of the present invention.

[Explanation of symbols]

1 ... Rotor, 2 ... Stator, 3 ... Shaft, 4a ... Centrifugal pump, 4b ... Circular flow pump, 5 ... Suction casing,
6 ... Air supply port, 7a, 7b ... Bearing, 8a ... Motor rotor,
8b ... Motor stator, 9 ... Cooling jacket, 10 ... Motor casing, 11 ... Cooling jacket, 12 ... Exhaust port, 14 ... Circular flow impeller, 17 ... Dam section, 18 ... Interstage wall, 20 ... Oil pump, 21 ... Oil filter, 2
2, 23 ... Communication passage, 24 ... Oil tank part, 25 ... Communication passage, 26a, 26b, 27a, 27b ... Communication passage, 32 ...
Bearing holder, 33 ... Holder spacer, 35 ... Pump body.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Katsuaki Kikuchi             603 Jinmachi-cho, Tsuchiura-shi, Ibaraki Japan Co., Ltd.             Tachiura Tsuchiura Factory (72) Inventor Takashi Nagaoka             502 Kintatemachi, Tsuchiura City, Ibaraki Japan             Tate Seisakusho Mechanical Research Center F term (reference) 3H031 DA01 DA02 DA04 EA06 EA08                       FA01 FA02 FA03 FA31 FA36                       FA37 FA41

Claims (5)

[Claims] 1. A housing having an intake port and an exhaust port,
A rotary shaft rotatably supported in the housing, a multistage circumferential flow impeller supported by the rotary shaft, and a multistage circumferential flow pump together with the circumferential flow impeller in the housing. A dry turbo vacuum pump having a stator and a centrifugal pump disposed on the intake side of the circumferential flow pump, at least two adjacent to the multi-stage circumferential flow pump stages.
A dry turbo vacuum pump characterized in that the inner diameters of the stator portions of the stages are substantially the same, and the portion of the inter-stage wall that partitions each stage provided in this stator and that faces the impeller is flat. 2. The circumferential flow impeller includes a core plate and a plurality of blades, and a dam portion having a circumferential length equal to or greater than the pitch of the two blades is provided on an interstage wall of the stator. The dry turbo vacuum pump according to claim 1. 3. The dry turbo vacuum according to claim 7, wherein the damming portion provided on the interstage wall has its circumferential position sequentially changed from the upstream interstage wall to the downstream interstage wall. pump. 4. The circumferential flow impeller comprises a mandrel and a plurality of vanes arranged at intervals on the mandrel, and the radial cross section of the groove bottom surface between the vanes is stepwise or intermittent. The dry turbo vacuum pump according to claim 1, wherein the dry turbo vacuum pump is formed of a group of linear lines. 5. The circumferential flow impeller comprises a mandrel and a plurality of vanes arranged at intervals on the mandrel, and a groove bottom surface between the vanes has a plurality of arcs in a circumferential cross section. The dry turbo vacuum pump according to claim 1, wherein the dry turbo vacuum pump is formed.