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WO1998012435A1 - Compresseur centrifuge et turbomachine frigorifique dans lequel il est utilise - Google Patents

Compresseur centrifuge et turbomachine frigorifique dans lequel il est utilise Download PDF

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Publication number
WO1998012435A1
WO1998012435A1 PCT/JP1996/002715 JP9602715W WO9812435A1 WO 1998012435 A1 WO1998012435 A1 WO 1998012435A1 JP 9602715 W JP9602715 W JP 9602715W WO 9812435 A1 WO9812435 A1 WO 9812435A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
flow
suction
centrifugal compressor
plate
Prior art date
Application number
PCT/JP1996/002715
Other languages
English (en)
Japanese (ja)
Inventor
Kouji Nakagawa
Yuuichi Keimi
Yasuo Uraki
Kenichi Kuwabara
Masatoshi Terasaki
Original Assignee
Hitachi, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi, Ltd. filed Critical Hitachi, Ltd.
Priority to PCT/JP1996/002715 priority Critical patent/WO1998012435A1/fr
Priority to JP51447598A priority patent/JP3735376B2/ja
Publication of WO1998012435A1 publication Critical patent/WO1998012435A1/fr

Links

Classifications

    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • 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
    • F04D27/02—Surge control
    • F04D27/0253—Surge control by throttling
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • 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
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • 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
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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
    • F05D2260/00—Function
    • F05D2260/14—Preswirling

Definitions

  • the present invention relates to a centrifugal compressor and a centrifugal chiller using the centrifugal compressor.
  • the present invention relates to a centrifugal compressor provided with a flow control device and a diffuser with blades in an impeller, and more particularly to a centrifugal compressor that controls a flow rate to an extremely small state to reduce power consumption during a small flow rate operation. It relates to a centrifugal chiller using a compressor.
  • a flow control device As a flow control device provided in an upstream flow passage of an impeller of a centrifugal compressor, a flow adjusting plate such as a suction damper or a suction vane is widely used.
  • the suction damper is, for example, as shown in Fig. 435 on Echart's "Axial Pentra Dial Complex Soren” 2nd Edition Springer, 1996
  • This is a throttle mechanism with a variable cross-sectional area provided in the flow path, which controls the flow rate by generating pressure loss and reducing the rise in pressure of the centrifugal compressor including the suction damper.
  • the suction vane is shown in Fig. 15.16, for example, by Ikui and Inoue, “Turbo Blower and Compressor” (First Edition Corona Publishing, August, 1963), p.
  • This is a mechanism in which the fluid flow is swirled in the same direction as the rotation direction of the impeller by a plurality of vanes provided in the flow path upstream of the impeller, and the power consumption and pressurizing action of the impeller are simultaneously reduced.
  • the flow rate is controlled by reducing the rise in pressure of the centrifugal compressor.
  • Most are composed of 4 to 5 or more movable vanes, have low energy loss, and have less impeller uniformity, noise, vibration, Desirable in both aspects of efficiency.
  • turbo blower and compressor shown in Fig. 676-1, Fig. 15.16 shows that the structure is complicated because many vanes are rotated in synchronization, and the use of small-capacity models is complicated. Is limited.
  • the aim of the present invention is to realize energy loss during low flow M operation, low noise and low vibration with a simple structure, and to expand the operation flow range on the low flow side.
  • An object of the present invention is to provide a centrifugal compressor which can be increased in size and a centrifugal chiller using the centrifugal compressor.
  • the above object is to provide a centrifugal compressor including a flow rate control device that controls a suction flow rate of a fluid in a suction flow path at an inlet of an impeller, and a bladed diffuser in which the blades arranged in the diffuser form a circular cascade.
  • the flow control device is rotatable from a direction perpendicular to the suction flow path to a direction parallel to the suction flow path and is divided into a flow control plate and a drive for rotating the flow control plate in directions opposite to each other. And the distance between the leading edge of the blade and the surface of another blade adjacent thereto is minimized between the leading edge of the blade and the trailing edge of the other blade. Is achieved by doing so.
  • the above-mentioned object is to provide a centrifugal control apparatus comprising: a flow control device for controlling a suction flow rate of a fluid in a suction flow passage at an impeller inlet; and a diffuser with blades in which the blades arranged in a diffuser constitute a circular cascade.
  • the flow control device is rotatable from a direction perpendicular to the suction flow path to a direction parallel to the suction flow path, and is divided into a flow control plate and a flow control plate in opposite directions.
  • the blade of the vaned diffuser is configured such that the distance between the leading edge of the vane and the surface of another adjacent vane is the distance between the leading edge of the vane and the trailing edge of the other vane.
  • the normal toward the outer peripheral direction is the inner circular shape.
  • FIG. 1 is a longitudinal sectional view of a centrifugal compressor according to a first embodiment of the present invention.
  • FIG. 2 is a view of the flow regulating plate of the embodiment shown in FIG. 1 as viewed from the upstream side of the flow regulating plate.
  • FIG. 3 is a view of the flow control plate of the embodiment shown in FIG. 1 as viewed from the downstream side of the flow control plate.
  • FIG. 4 is a view of the impeller of the embodiment shown in FIG. 1 as viewed from the rotation axis direction of the impeller.
  • FIG. 5 is a view showing the effect of the vaned diffuser of the embodiment shown in FIG.
  • FIG. 6 is a view showing the arrangement of the blades of the centrifugal compressor according to the second embodiment of the present invention in the blades and the diffuser with blades.
  • FIG. 7D is a diagram showing the arrangement of the blades in the impeller and the diffuser with blades of the centrifugal compressor according to the third embodiment of the present invention.
  • FIG. 8 is a longitudinal sectional view of a centrifugal compressor according to a fourth embodiment of the present invention.
  • FIG. 9 is a diagram of the embodiment shown in FIG. 8 in which the flow regulating plate is set to the opening degree and viewed from above the flow regulating plate.
  • FIG. 10 is a view of the embodiment shown in FIG. 8 in which the flow rate adjusting plate is set to the opening degree and viewed from the downstream side of the flow rate adjusting plate.
  • FIG. 11 is a longitudinal sectional view of a centrifugal compressor according to a fifth embodiment of the present invention.
  • FIG. 12 is a view in which the flow rate adjusting plate of the embodiment shown in FIG. 11 is fully opened and viewed from above the flow rate adjusting plate.
  • FIG. 13 is a view of the embodiment shown in FIG. 11 with the flow control plate fully opened and viewed from the downstream side of the flow control plate.
  • FIG. 14 is shown in FIG. 11; FIG. 14 is a view in which the flow rate adjusting plate of the embodiment is set to the opening between the blocks and viewed from above the flow rate adjusting plate.
  • FIG. 15 is a view of the flow regulating plate of the embodiment shown in FIG. 11 set to the middle opening, viewed from the downstream side of the flow regulating plate.
  • FIG. 16 is a view of the embodiment shown in FIG. 11 in which the flow control plate is fully closed and viewed from the h direction of the flow control plate.
  • FIG. 17 is a view of the embodiment shown in FIG. 11 in which the flow control plate is fully closed and viewed from the downstream side of the flow control plate.
  • FIG. 18 is a view of the sixth embodiment of the present invention in which the flow control plate is fully opened and viewed from above the flow control plate.
  • FIG. 19 is a view of the embodiment shown in FIG. 18 with the flow control plate fully opened and viewed from the downstream side of the flow control plate.
  • FIG. 20 is a view of the embodiment shown in FIG. 18 in which the flow rate adjustment plate is set at an intermediate opening and viewed from above the flow rate adjustment plate.
  • FIG. 21 is a view of the embodiment shown in FIG. 18 in which the flow control plate is set to the opening degree and viewed from the downstream side of the flow control plate.
  • FIG. 22 is a view of the embodiment shown in FIG. 18 in which the flow control plate is fully closed and viewed from above the flow control plate.
  • FIG. 23 is a view of the embodiment shown in FIG. 18 in which the flow regulating plate is fully closed and viewed from the downstream side of the flow regulating plate.
  • 1 to 5 show a first embodiment of the present invention.
  • a flow control device including a suction flow passage provided upstream of an impeller inlet and two flow control plates rotatable in opposite directions to each other.
  • Centrifugal compression for centrifugal chillers comprising a single-blade diffuser consisting of a single circular cascade in which the distance between the leading edge and the adjacent blade surface is minimized at the trailing edge of another adjacent blade It is an example of a machine.
  • FIG. 1 is a longitudinal sectional view including an impeller rotation shaft of a centrifugal compressor.
  • Centrifugal B The compressor is a blade group 1, a diffuser 2, a casing 3 containing these, It is constituted by a suction channel 4.
  • the apparatus includes a flow ft adjusting plate 5 and a flow adjusting device 7 including an actuator 6 (drive source) for driving the flow adjusting plate 5 to rotate.
  • the flow rate adjusting plate 5 is rotatably supported and driven by the actuator 6.
  • the diffuser 2 has a plurality of diffuser blades 8. Fluid flows in the direction of the arrow.
  • FIG. 1 2 and 3 are diagrams showing the operation of the flow control device 7.
  • FIG. 2 and 3 are diagrams showing the operation of the flow control device 7.
  • FIG. 2 is a view of the flow control plate 5 in FIG. 1 viewed from the h direction of the rotation axis
  • FIG. 3 is a view of the flow control plate 5 viewed from the downstream side. Fluid flows in as shown by the arrows. In the fully open or fully closed state, the flow control plate, which has been frequently used, flows almost the same as one damper.
  • the flow rate can be adjusted by the pre-rotation M in the blade, similar to the suction vane: 1 upstream, and therefore significant energy is possible.
  • the suction passage is almost completely closed by a suction vane (or suction damper) at startup to reduce the starting current of the drive motor.
  • the present embodiment is also configured so that it can be fully closed.
  • the synchronous rotation drive of the two flow control plates 5, 5 ' can be, for example, an electric type using a servomotor, a link mechanism, a gear mechanism, or a combination thereof.
  • the structure is significantly simpler than conventional suction vanes that use four or more movable vanes.
  • FIG. 4 is a view of the impeller 1 and the diffuser impeller 8 as viewed from the direction of the rotation axis of the impeller. Since the distance bt between the leading edge of the diffuser blade 8 and the surface of another adjacent blade is minimized at the trailing edge of another adjacent blade, the passage surrounded by the blade surface on both sides is Do not configure.
  • FIG. 5 shows a vaned diffuser composed of a circular blade row configured so that the distance bt between the leading edge of the diffuser blade 8 and the surface of another adjacent blade is minimum at the trailing edge of the adjacent blade
  • FIG. 9 is a diagram illustrating a combined effect of a combination with a flow rate adjusting plate 5 provided in a suction passage at an impeller inlet.
  • the figure shows the relationship between the suction flow rate Q and the head H at the opening degree of the flow rate adjusting plate 5 of 100% and 40%, respectively, in the conventional diffuser with a vane having a passage surrounded by a blade surface.
  • a bladed diffuser without a passage portion of the present embodiment is provided.
  • the operating range on the small flow rate side can be expanded in the centrifugal compressor of the present embodiment, as compared with the centrifugal compressor forming the passage.
  • the flow rate adjusting plate 5 has an opening of 100%, unstable phenomena such as surging including the piping system of the centrifugal compressor will occur on the side with a flow rate smaller than the flow rate Q1, so that the passage of the diffuser with vanes ⁇ ⁇ Operation due to nothing There is no difference in the flow rate range.
  • the flow rate adjusting plate 5 When the flow rate adjusting plate 5 has an opening of 40%, a distinct difference appears in the operating flow rate range depending on the presence or absence of the above-mentioned passage portion of the diffuser with blades.
  • the opening of the flow control plate 5 When the opening of the flow control plate 5 is reduced, the head is reduced due to the increase of the power loss and the swirling action by the flow control plate 5.
  • the flow-rate rise characteristic of the centrifugal compressor including the flow control plate 5 is obtained by subtracting the head decrease at the opening of 40% from the characteristic when the flow control plate 5 has the opening of 100%.
  • the flow is higher than when the flow rate adjustment plate 5 is at an opening of 100%. Therefore, there is a strong tendency to suppress unstable events such as surging.
  • the centrifugal compressor of the present embodiment provided with the vaned diffuser having no passage, the flow-rate rising characteristic from the flow rate Q 1 ′ to the flow rate Q 2 on the smaller flow rate side becomes lower rightward. Operation of the centrifugal compressor becomes possible.
  • FIG. 6 shows a second embodiment
  • the distance bt between the leading edge and the adjacent blade surface is configured to be minimum at the trailing edge of the adjacent blade, and does not form a path surrounded by the blade surface. It constitutes a diffuser and further enhances the pressure recovery performance.
  • a normal ⁇ extending toward the outer periphery at the leading edge position of the sled line i is disposed on the outer periphery.
  • the normal g that does not intersect with the diffuser blades 8 that constitute the circular cascade and that is set at the trailing edge of the sled line i and that is directed toward the outer periphery is the diffuser that constitutes the circular cascade arranged on the outer periphery. It is configured to intersect with the wing 8.
  • the blade surface between the inner and outer circular cascades has high pressure recovery performance, and at low flow rates, even if a part of the flow in the passage surrounded by the blade surface lacks kinetic energy and the fluid cannot flow out to the outer periphery, Since the normal ⁇ is configured so as not to intersect with the diffuser blades 8 constituting the circular cascade arranged on the outer periphery, the fluid can return to the circumferential side as indicated by the notch h. For this reason, it has the feature that large-scale backflow does not occur over the entire passage surrounded by the blade surface, and therefore, there is no significant decrease in pressure recovery performance.
  • FIG. 7 shows a third embodiment.
  • the diffuser with vanes 8 is constituted by a triple cascade, so that high performance and a wide flow rate range can be realized.
  • Fig. 8 is a longitudinal sectional view including the rotating shaft of the impeller of the centrifugal compressor.
  • Fig. 9 is a view of the flow regulating plate 5 in Fig. 8 viewed from above the rotating shaft.
  • Fig. 10 is a flow regulating plate.
  • FIG. 5 is a view of a portion 5 viewed from the downstream side.
  • the rectifying plate 9 is provided with a cross section downstream of the suction flow path 4 including the rotation axis of the flow rate adjusting plate 5. It is arranged in. The operation of the current plate 9 will be described with reference to FIG. 2 and FIG.
  • the flows b and b ′ are in direct contact with each other on the downstream side of the flow rate adjusting plate 5, and therefore, the speeds other than the length direction of the suction flow path 4 are different.
  • the component, and thus the swirl is reduced.
  • the direct contact between the flows b and b ' is prevented, so that the swirling flow is not reduced, and the flow b descends from the heel side to the lower side and flows from the lower side to the h side.
  • the flow b ′ contributes to the generation of swirling flow. For this reason, the swirling flow has a feature that it becomes stronger than in the first embodiment.
  • FIGS. 11 to 17 show a fifth embodiment of the present invention.
  • FIG. 11 is a vertical cross-sectional view of the centrifugal compressor including the rotating shaft of the impeller
  • Fig. 12 is a diagram of the flow regulating plate 5 in the figure when fully opened as viewed from above the rotating shaft
  • Fig. 13 is a flow rate.
  • FIG. 4 is a view when the adjustment plate 5 is fully opened as viewed from the downstream side of the flow adjustment plate 5.
  • Fig. 14 and Fig. 5 show the intermediate opening of the flow control plate 5
  • Fig. 16 and Fig. 17 show the flow control plate 5 when fully closed.
  • a flow straightening plate having the same function as in the fourth embodiment is used.
  • It is formed integrally with the adjustment plate 5. That is, the flow regulating plate 5 divided into two semicircular shapes, preferably at each end thereof, is rectified in a direction substantially perpendicular to the flow regulating plate 5 and parallel to the flow direction of the fluid. Plate 10 is to be attached.
  • the mounting structure integrally forms the flow regulating plate 5 and the rectifying plate] 0.
  • FIGS. 18 to 23 show a sixth embodiment.
  • FIGS. 18 and 19 show the state in which the flow control plate 5 is fully opened.
  • the guide plate 11 is installed in parallel with the flow control plate 5 so that flow resistance does not occur when fully opened.
  • the intermediate opening of FIGS. 20 and 21 after the fluid flows toward the center of the flow control plate 5, the flowing b and the rising b b ′ are both guide plates. The turn is further strengthened because it is securely guided by 1 ⁇ .
  • FIGS. 22 and 23 show the flow control plate 5 when fully closed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

On réduit les pertes d'énergie, le bruit et les vibrations lorsqu'un compresseur centrifuge fonctionne à faible débit et on augmente la plage de débits d'exploitation à faible débit. Un dispositif de régulation de débit (7) pour régulariser un débit d'aspiration comporte une plaque de régularisation de débit fendue (5) tournant dans un sens perpendiculaire à un passage de flux d'aspiration (4) et dans un sens parallèle au passage de flux d'aspiration, et une source d'entraînement (6) pour entraîner en rotation les parties de ladite plaque (5) dans des sens opposés l'une par rapport à l'autre. Des aubes (8) prévue sur un diffuseur (2) sont disposées de sorte que la distance entre un bord d'attaque d'une aube (8) et une surface d'une autre aube (8) adjacente soit minimum entre le bord d'attaque de la première aube (8) et le bord de fuite de l'autre aube (8) adjacente.
PCT/JP1996/002715 1996-09-20 1996-09-20 Compresseur centrifuge et turbomachine frigorifique dans lequel il est utilise WO1998012435A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP1996/002715 WO1998012435A1 (fr) 1996-09-20 1996-09-20 Compresseur centrifuge et turbomachine frigorifique dans lequel il est utilise
JP51447598A JP3735376B2 (ja) 1996-09-20 1996-09-20 遠心圧縮機及びこの遠心圧縮機を用いるターボ冷凍機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1996/002715 WO1998012435A1 (fr) 1996-09-20 1996-09-20 Compresseur centrifuge et turbomachine frigorifique dans lequel il est utilise

Publications (1)

Publication Number Publication Date
WO1998012435A1 true WO1998012435A1 (fr) 1998-03-26

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Application Number Title Priority Date Filing Date
PCT/JP1996/002715 WO1998012435A1 (fr) 1996-09-20 1996-09-20 Compresseur centrifuge et turbomachine frigorifique dans lequel il est utilise

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JP (1) JP3735376B2 (fr)
WO (1) WO1998012435A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2872216A1 (fr) * 2004-06-24 2005-12-30 Bosch Gmbh Robert Dispositif de compression
CN101929465A (zh) * 2009-06-19 2010-12-29 德昌电机(深圳)有限公司 排水泵
CN109751283A (zh) * 2017-11-06 2019-05-14 福特全球技术公司 用于双壳可变进口装置的系统和方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111503059B (zh) * 2020-04-10 2022-01-25 上海交通大学 离心压气机入口气流脉动调节装置

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5750959B2 (fr) * 1976-10-04 1982-10-29
JPH05133396A (ja) * 1991-11-13 1993-05-28 Hitachi Ltd 遠心形流体機械のデイフユーザ

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5750959B2 (fr) * 1976-10-04 1982-10-29
JPH05133396A (ja) * 1991-11-13 1993-05-28 Hitachi Ltd 遠心形流体機械のデイフユーザ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
MICROFILM OF THE SPECIFICATION AND DRAWINGS ANNEXED TO THE WRITTEN APPLICATION OF JAPANESE UTILITY MODEL, Application No. 34095/1991 (Laid-Open No. 127900/1992) (MITSUBISHI HEAVY INDUSTRIES, LTD.), (20-11-92). *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2872216A1 (fr) * 2004-06-24 2005-12-30 Bosch Gmbh Robert Dispositif de compression
CN101929465A (zh) * 2009-06-19 2010-12-29 德昌电机(深圳)有限公司 排水泵
CN101929465B (zh) * 2009-06-19 2013-12-11 德昌电机(深圳)有限公司 排水泵
CN109751283A (zh) * 2017-11-06 2019-05-14 福特全球技术公司 用于双壳可变进口装置的系统和方法

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