Turbo vacuum pump

Abstract: A compact, easy-to-handle turbo vacuum pump includes a housing (11) having an inlet port (11A) and an outlet port (11B); a cylindrical rotor (30) disposed in the housing (11) and having a stepped peripheral surface and a plurality of blades (35) secured to protruding corners of the steps; and a pumping mechanism portion in which a pumping stage is formed by a stator (31) which faces the blades (35) of the rotor (30) across a narrow gap, and in which peripheral pump flow paths are provided in step-like recessions inside the stator (31). The turbo vacuum pump further includes a rotating shaft (13) which is connected to the rotor (30) and is rotatably supported by radial gas bearing (33) and a thrust gas bearing (34); and a motor portion (16) for operating the rotor (30). Gas sucked in through the inlet port (11A) can be discharged into the atmosphere through the outlet port (11B).

Description: The present invention relates to a turbo vacuum pump comprising a housing having an inlet port and an outlet port, a cylindrical rotor disposed in the housing and having a stepped peripheral surface and a plurality of blades secured to protruding corners of the steps, a pumping mechanism portion in which a pumping stage is formed by a stator which faces the blades of said rotor across a narrow gap, and in which peripheral pump flow paths are provided in step-like recessions inside the stator, a rotating shaft connected to said rotor and rotatably supported by bearings, and a motor portion for operating said rotor whereby gas drawn in through the inlet port can be discharged into the atmosphere through the outlet port. This generic turbo vacuum pump as described in DE-A-3 932 228 is arranged to have an outlet port at an atmospheric pressure and support the rotating shaft of the pump rotor by ball bearings disposed at two positions and lubricated with oil and thus makes it necessary to provide sealing means between the pump part and the driving part so as not to contaminate the vacuum system. As sealing means a screw seal of the non-contact type or an oil seal of the non-contact type for purging the compressed gas is employed. JP-A-2-16389 describes a turbo molecular drag pump which is arranged to dispose a radial hydrodynamic type gas bearing and a thrust hydrodynamic type gas bearing at the lower end of the rotary shaft and form a gas seal above the hydrodynamic type gas bearings to seal the driving part. The turbo molecular drag pump cannot perform exhaust function, unless the discharge pressure falls within a pressure range less than 10⁻² Torr so that the interior of the pump is kept at a pressure less than the atmospheric pressure (e.g. 10⁻² Torr). Accordingly, the turbo molecular drag pump as employing gas bearings requires a non-contact seal, since the gas bearings cannot serve satisfactorily in this case. In a turbo vacuum pump disclosed in JP-A-1-187396, a centrifugal pump stage and a peripheral pump stage constitute a pumping mechanism portion, and a hydrodynamic type gas bearing supports a rotating shaft. A conventional turbo vacuum pump according to JP-A-62-2581186 is equipped with a housing having an inlet port and an outlet port, the housing extending between the inlet port and the outlet port, a rotating shaft rotatably supported with the aid of a bearing in the housing, a centrifugal pump stage and a peripheral pump stage. The pump stages of the above two types are disposed one after another in the housing. In this turbo vacuum pump an impeller, a stator plate, another impeller and another stator plate are alternately arranged in the axial direction of the pump. Both of these plates must be divided in half to insert them. Such a structure is complicated, and there is a limit to how small the structure can be made. The pump has a vertical axis structure in which lubricating oil is drawn in from an oil tank at the lower end of the pump so as to lubricate the bearing. Owing to this structure, the number of possible directions from which the pump can be installed is limited. Also, because of the use of the oil-lubricating ball bearing, the oil contaminates the inside of a passage in the pump during long-time use thereof, even though this contamination is negligible. With a turbo vacuum pump as disclosed in JP-A-1-267392 pressure in an outlet port thereof is made equal to the atmospheric pressure so as to discharge gas, and a magnetic bearing, requiring no lubricating oil, is used as the bearing of the pump. Thus no contamination caused by oil occurs since lubricating oil is not used. The magnetic bearing, however, requires a large number of very expensive parts, including a control unit. Because the pump has a complicated structure, it is difficult to reduce the size thereof. It is the object of the invention to provide a turbo vacuum pump of the generic kind that is compact in structure and easy to handle. This object is achieved with the turbo vacuum pump of the generic kind in that its bearings consist of a radial gas bearing and a grease-lubricating ball bearing. In the turbo vacuum pump of the present invention the rotating shaft of the pump rotor is supported by a radial gas bearing and a grease-lubricating ball bearing. More specifically, the load in the radial direction is supported by the radial gas bearing and the grease-lubricating ball bearing and the load in the thrust direction is supported by the grease-lubricating ball bearing. The pressure within the pump housing and at the outlet port is the atmospheric pressure so that the gas bearing acts satisfactorily. In addition, lubricating oil is not used for the driving part at all so that no special seal is necessary. Advantageously, the radial gas bearing is a hydrodynamic type gas bearing. Conveniently, a means for cooling air is provided in the motor portion. Preferably, a spiral grooved pump stage is disposed on the side of an inhaling opening of a peripheral pump stage. Embodiments of the invention are described referring to the drawings in which Fig. 1 is a vertical cross-sectional view showing a first embodiment of a turbo vacuum pump, Fig. 2a is an enlarged vertical cross-sectional view showing a portion around the blades of a peripheral pump impeller illustrated in Fig. 1, Fig. 2b is an enlarged horizontal cross-sectional view taken along line A-A of Fig. 2a, Fig. 3 is a vertical cross-sectional view showing a second embodiment of a turbo vacuum pump, and Fig. 4 is a vertical cross-sectional view showing a third embodiment of a turbo vacuum pump. The turbo vacuum pump shown in Fig. 1 is equipped with a pumping mechanism portion and an operating portion. The pumping mechanism portion is composed of a peripheral pump impeller 30, a stator 31 and a lid 32. The operating portion is composed of a rotating shaft 13 and a high-frequency motor 16 provided around the rotating shaft 13. The rotating shaft 13 is rotatably supported by a hydrodynamic type radial gas bearing 33 and a grease lubricating ball bearing 38, both bearings being accommodated in a housing 11. The peripheral pump impeller 30 is shaped as a cylinder having steps. A plurality of blades 35 are secured to protruding corners of the steps. As shown in Figs. 2a and 2b, the stator 31 faces the impeller 30 across a narrow gap therebetween. Around each corner a partition 37 is provided in a portion of a circumferential direction of a gas passage 36 so as to surround the blades 35 of the impeller 30. An inhaling opening 36A is formed at the forward side of each partition 37, and a discharge opening 36B is formed at the rear side of each partition 37, where the peripheral pump impeller 30 rotates. The position of the inhaling opening 36A of a given stage deviates from that of another inhaling opening 36A of the next stage; likewise, the position of the discharge opening 36B of a given stage deviates from that of another discharge opening 36B of the next stage. The inhaling opening 36A of a given stage is connected in series to the discharge opening 36B of the preceding stage. In this way, because the peripheral pump impeller 30 faces the stator 31 at each stage, these components can be integrally formed with each other. The hydrodynamic type radial gas bearing 33 has grooves (not shown) formed on the surface thereof; The hydrodynamic type radial gas bearing 33 supports, in a non-contact manner, the vibrations and load of the rotating shaft 13 in the radial direction of the shaft 13. The grease lubricating ball bearing 38 supports the vibrations and load of the rotating shaft 13 in the thrust direction of the shaft 13. Because of the integral formation of the peripheral pump impeller 30 and the stator 31, it is possible to improve the accuracy with which these two components are machined. The use of the hydrodynamic type radial gas bearing 33 increases the diameter and hence the stiffness of the rotating shaft 13, thus resulting in an improvement in vibration characteristics. The high-frequency motor 16, integrally formed with the rotating shaft 13, is capable of operating the peripheral pump impeller 30 at a high speed. Since the peripheral pump impeller 30 operates at a high speed, gas sucked in through an inlet port 11A flows into the gas passage 36 through the inhaling opening 36A of the first stage. When the gas flows to the blades 35 of the impeller 30, the blades 35 rotating at a high speed provide the gas with speed in the circumferential direction of the impeller 30. A centrifugal force discharges the gas between the blades 35 in the radial direction of the impeller 30. After the speed of the gas decreases at the gas passage 36 and pressure is recovered, the gas flows again between the blades 35 while forming a vortex. The gas undergoes the above procedure as many times as the number of stages while it is flowing through the gas passage 36 from the inhaling opening 36A to the discharge opening 36B of each stage. The gas flows helically through the gas passage 36 while fully gaining energy from the peripheral pump impeller 30. It is then discharged into the atmosphere through an outlet port 11B connected to the discharge opening 36B of the last stage. As described above, the peripheral pump impeller 30 gains a high compression ratio in such a manner that it provides the gas with kinetic energy, which is converted into static pressure. Therefore, if it is possible to rotate the peripheral pump impeller 30 at a high speed, it is also possible to improve the performance of the pump. The shaft power of the turbo vacuum pump is proportional to the third power of the rotating speed and the fifth power of the diameter of the impeller. Thus when the peripheral pump impeller is made compact to rotate at a higher speed, the shaft power can be reduced without modifying the performance of the turbo vacuum pump; the size of the turbo vacuum pump can be reduced; and the high-frequency motor 16 having a smaller capacity can be employed. With the embodiment shown in Fig. 3 a spiral grooved pump stage 41 is provided in addition to a peripheral pump stage 40, composed of the peripheral pump impeller 30 and the stator 31, shown in Fig. 1. As described already, the peripheral pump stage 40 provides gas with speed energy to convert it into pressure. A high compression ratio is thereby obtainable. Thus, the performance of the pump can increase in the pressure zone of a viscous flow, but decreases in the pressure zones of intermediate and molecular flows. The ultimate pressure of the vacuum pump is limited to a low vacuum zone. In the embodiment shown in Fig. 3, to obtain the ultimate pressure even in the pressure zone of the molecular flow, the spiral grooves pump stage 41, which operates effectively with the intermediate and molecular flows, is installed on the low pressure side of the peripheral pump stage 40. A centrifugal pump stage, an axial pump stage or the like is used as a pump stage operating effectively with the intermediate and molecular flows. However, these stages must have a structure in which a stator is divided in half to insert it, so that it is difficult to maintain the accuracy with which the stages are machined. Thus the stages are not suitable for a smaller pump operating at a higher speed. In this embodiment, because of the peripheral pump stage 40 and the spiral grooved pump stage 41, the ultimate pressure of the turbo vacuum pump can be made higher. With the embodiment shown in Fig.4 a fan 39 is provided in a housing 11 in which a hydrodynamic type radial gas bearing 33 and a grease-lubricating ball bearing 38 are accommodated. This embodiment can effectively remove the heat generated by a high-frequency motor 16 and the grease-lubricating ball bearing 38. It is thus possible to decrease the deterioration of the grease and to increase the life of the bearings.

Claims: A turbo vacuum pump comprising a housing (11) having an inlet port (11A) and an outlet port (11B), a cylindrical rotor (30) disposed in the housing (11) and having a stepped peripheral surface and a plurality of blades (35) secured to protruding corners of the steps, a pumping mechanism portion in which a pumping stage is formed by a stator (31) which faces the blades (35) of said rotor (30) across a narrow gap, and in which peripheral pump flow paths are provided in step-like recessions inside the stator (31), a rotary shaft (13) connected to said rotor (30) and rotatably supported by bearings (33, 38) and a motor portion (16) for operating said rotor (30), whereby gas drawn in through the inlet port (11A) can be discharged into the atmosphere through the outlet port (11B), characterized in that said bearings consist of a radial gas bearing (33) and a grease-lubricating ball bearing (38). A turbo vacuum pump according to Claim 1, wherein the radial gas bearing (33) is a hydrodynamic type gas bearing. A turbo vacuum pump according to Claim 1 or 2 wherein a means (39) for cooling air is provided in the motor portion (16). A turbo vacuum pump according to one of the Claims 1 to 3, wherein a spiral grooved pump stage (41) is disposed on the side of an inhaling opening (36A) of a peripheral pump stage (40).

Inventors: MASE MASAHIRO, NAGAOKA TAKASHI, SAKAGAMI SEIJI, UEDA SHINJIRO, MASE, MASAHIRO, NAGAOKA, TAKASHI, SAKAGAMI, SEIJI, UEDA, SHINJIRO
Applicants: HITACHI LTD, HITACHI, LTD.
Application year: 1991
Main classification: F04D19
IPC codes: F04D29, F04D19