EP1852612B1 - Pompe a engrenage - Google Patents

Pompe a engrenage Download PDF

Info

Publication number
EP1852612B1
EP1852612B1 EP06714031.9A EP06714031A EP1852612B1 EP 1852612 B1 EP1852612 B1 EP 1852612B1 EP 06714031 A EP06714031 A EP 06714031A EP 1852612 B1 EP1852612 B1 EP 1852612B1
Authority
EP
European Patent Office
Prior art keywords
gear
gears
gear pump
casing
fluid
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP06714031.9A
Other languages
German (de)
English (en)
Other versions
EP1852612A4 (fr
EP1852612A1 (fr
Inventor
Motohiro Okada
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shimadzu Mectem Inc
Original Assignee
Shimadzu Mectem Inc
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
Priority claimed from PCT/JP2005/015675 external-priority patent/WO2006090495A1/fr
Application filed by Shimadzu Mectem Inc filed Critical Shimadzu Mectem Inc
Publication of EP1852612A1 publication Critical patent/EP1852612A1/fr
Publication of EP1852612A4 publication Critical patent/EP1852612A4/fr
Application granted granted Critical
Publication of EP1852612B1 publication Critical patent/EP1852612B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F04C13/002—Pumps for particular liquids for homogeneous viscous liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0096—Heating; Cooling

Definitions

  • the present invention relates to a gear pump suitable for feeding a high-pressure and high-viscosity fluid such as a molten resin.
  • the fluid containment phenomenon is taken as an example of the problems of the gear pump having an involute tooth profile. It is a general example for the involute gear to have a meshing rate larger than 1 and have a meshing period of two groups of teeth. Under this circumstance, when the fluid is contained between the above two groups of teeth, the volume of the contained area changes with the rotation of the gear, such that if the pressure of the contained fluid is increased during compression, the power is wasted, and meanwhile, the so-called unsuitable phenomenon of vacuum or air bubbles is generated during expansion. However, the containment phenomenon causes more severe effects during the compression than that during the expansion.
  • the above containment phenomenon causes more obvious influences especially when the viscosity or suction pressure and discharge pressure of the fed fluid are relatively higher. More particularly, as for the application of feeding the molten resin, the fluid at a high temperature of about 300°C, a high pressure of about 20 MPaG, and a high viscosity of about 300 Pa • s is fed. Since the containment phenomenon causes an excessive load applied on the gear bearing, the lifetime of the bearing is shortened. Now, the process of improving the bearing or providing a sufficient allowance or margin between each unit of the bearings (for example, increasing the bearing diameter, reducing the rotation speed) have been proposed currently, whereas such a process causes an increase in the overall size of the pump external dimension and an increase in the driving force.
  • the present invention provides a gear pump suitable for feeding a high-pressure and high-viscosity fluid such as a high molecular polymer or a molten resin.
  • the gear pump of the present invention is characterized in including: a casing, having a suction port for guiding in a fluid and a discharge port for discharging the fluid; and a pair of gears, disposed within the casing, wherein the fluid is fed from the suction port to the discharge port by the rotation of the gears meshing with each other.
  • the pair of gears is double-helical gears having a one-point continuous contact tooth profile.
  • the ratio of the gear diameter to the gear width of each gear is set to 1.1 - 1.15.
  • the ratio D/B is set to 1.1 - 1.15, so as to restrain the bearing load and ensure the efficiency.
  • the ratio D/B is smaller than 1.1, a bearing may be damaged due to the excessively increased bearing load, and the gear pump is unsuitable for feeding the molten resin.
  • the ratio D/B is larger than 1.15, in accordance with an increase in the overall size of the pump external dimension, the power that can be achieved is decreased.
  • the number of teeth for the gear is 10 to 12 and a twisting angle of the gear is 28° to 32° when the pair of gears consists of two double-helical gears, and a number of teeth for the gear is 8 to 12 and a twisting angle of the gear is 14° to 18° when the pair of gears consists of two helical gears.
  • gear pumps of the present invention are characterized in including: a casing, having a suction port for guiding in a fluid and a discharge port for discharging the fluid; and a pair of gears, disposed within the casing, wherein the fluid is fed from the suction port to the discharge port by the rotation of the gears meshing with each other.
  • the pair of gears is helical gears having a one-point continuous contact tooth profile. The ratio of the gear diameter to the gear width of each gear is set to 1.1 - 1.15.
  • the pair of gears made as helical gears also can be integrated with a gear shaft, and due to the simple structure, the processing and productivity are improved.
  • the present invention can achieve a gear pump suitable for feeding a high-pressure and high-viscosity fluid such as a high molecular polymer or a molten resin.
  • a gear pump 100 of Embodiment 1 shown in FIGs. 1 and 2 is, for example, used in petroleum plant, chemical plant, polymer plant, and molding/fiber spinning apparatus for feeding high-viscosity substances such as molten resin and other high molecular polymers under a high pressure.
  • the high-viscosity substance can be an intermediate or final product.
  • the gear pump 100 is a so-called external gear pump.
  • a drive gear 2 and a driven gear 3 are disposed therein to mesh with each other.
  • the pump functions to feed the fluid obtained in the tooth space from the suction side to the discharge side.
  • the suction side is located at the above part, whereas the discharge side is located at the lower part.
  • a tank is disposed right above the suction port 11 for storing the high molecular polymer or molten resin, and the molten resin in the tank is sucked therein and discharged under a specific discharging pressure.
  • the drive gear 2 and the driven gear 3 are respectively set to be double-helical gears having a one-point continuous contact tooth profile.
  • the teeth of the two gears 2 and 3 are set to have circular-arc tooth profile.
  • the ratio D/B of the gear diameter D to the gear width B is set to 1.1 - 1.15, which is set under the condition that the gear pump 100 is used to feed a high-temperature molten resin of about 300°C under a high pressure of about 20 MpaG.
  • the specific values of the gear diameter D and the gear width B are limited by a gear shaft diameter required for transmitting the rotation driving force to the gear, and a shaft diameter required for restraining the bending deformation of the gear shaft.
  • the ratio D/B of the gear diameter D to the gear width B is limited in the range of 1.1 to 1.15, and the number of teeth Z and the twisting angle (helical angle) ⁇ of the gears 2 and 3 are determined.
  • the shaft diameter and the bearing length relevant to the performance are set to be identical in the two gear pumps.
  • the fluid viscosity is about 300 Pa • s
  • the discharge pressure is 20 MpaG
  • the circular-arc gear pump achieves the same performance as the involute gear pump.
  • the circular-arc tooth profile will not generate the containment phenomenon.
  • the discharge pressure pulse in the circular-arc gear pump is 0.4 %, and that in the involute gear pump is 4%, and these two values are obtained under the operation conditions of a fluid viscosity of about 300 Pa • s, a discharge pressure of 20 MpaG, and a rotation number of 30 rpm.
  • the discharge pressure pulse changes with the measurement position and other measurement environments, and the discharge pulse of the circular-arc gear pump is reduced to 1/10 of that of the involute gear pump.
  • the gear pump 100 of this embodiment is mainly used for feeding high-pressure and high-viscosity fluids. Therefore, the inner peripheral profile of the casing 1 must be molded to sufficiently draw-up the high-viscosity fluid into the tooth spaces of the gears 2 and 3, and prevent the high-pressure fluid obtained in the tooth space from leaking from the tooth tip.
  • FIG. 2 detailed illustration is given with reference to FIG. 2 .
  • the positions where the tooth tip of the rotating gears 2 and 3 closely approaches the inner peripheral surface of the casing 1 are set to be P 1 , P 1 , the positions where the tooth tip begins to depart from the inner peripheral surface of the casing 1 are set to be P 2 , P 2 , the pitch point of the two gears 2 and 3 is set to be P 0 , and the centers of the gears 2 and 3 are set to be Pc, Pc.
  • an angle E 1 formed between the line passing through the centers Pc and Pc of the two gears 2 and 3 and the line segment connecting the center Pc of the gears 2 and 3 and the slip-start point P 1 of the tooth tip must be ensured to be about 0°-6° as seen from the side section (as seen from the section vertical to the surface of the gear shaft).
  • the position of the slip-start point P 1 is closer to the discharge side than the line passing through the centers Pc, Pc of the two gears 2 and 3.
  • the circular arc angle E 4 formed from the slip-start point P 1 to the slip-end point P 2 of the tooth tip (taking Pc as the center) is preferably ensured to be 72° or larger than 72° as seen from the side section.
  • the circular arc angle E 4 is based on ensuring two or more tooth spaces of the gears 2 and 3. In spite of this, if E 4 is increased, the flow path communicating with the discharge port 12 becomes narrowed, which is more likely to affect the discharge process of the fluid, and thus E 4 should be restrained to be about 108° as seen from the side section.
  • an angle E 2 formed between the line segment connecting the slip-start point P 1 and the pitch point P 0 and the line segment connecting the slip-end point P 2 and the pitch point P 0 is 33° - 66° as seen from the side section. Therefore, an angle E 3 formed between two line segments respectively connecting the slip-end point P 2 , P 2 and the pitch point P 0 of the two gears 2 and 3 is 48° - 102° as seen from the side section.
  • the upper limit of E 3 must be set to be about 102°.
  • the lower limit of E 3 is set to be about 48°, so as to allow the transmitted fluid obtained in the gear space to smoothly flow down to the discharge port 12.
  • the gears 2 and 3 are double-helical gears having a one-point continuous contact tooth profile, and for the gears 2 and 3, the ratio D/B of the gear diameter D to the gear width B is set to be 1.1 - 1.15; thus the undesirable influence on the bearing caused by the fluid containment phenomenon is avoided. Moreover, the ratio D/B is set to be 1.1 - 1.15, which can restrain the bearing load and ensure the efficiency, and the increased in the overall size of the pump external dimension is avoided.
  • the gear pump 100 of this embodiment is more suitable for feeding the high-pressure, high-viscosity fluid.
  • the angle E 3 is set to be 48° - 102° and the angle E 4 is set to be 72° - 108°, such that the fluid can be sufficiently sucked into the gear spaces of the gears 2 and 3, and the fluid obtained in the tooth space is prevented from leaking from the tooth tip.
  • the gear pump 100 of the present invention having the above structure is used in the process for manufacturing the high molecular polymer or the molten resin, or the process for manufacturing the molding of the high molecular polymer or the molten resin.
  • the gear pump 100 is suitable for the applications of manufacturing high molecular polymer, molten resin, or the molding thereof.
  • the gear pump 100 of the present invention is used to feed the monomer from the monomer tank 110 to the polymerization tank 120, for being used in the process of manufacturing the high molecular polymer; otherwise, the gear pump 100 is used to feed the high molecular polymer into a molding apparatus 300 or a fiber spinning apparatus 400, for being used in the process of manufacturing the molding thereof.
  • the process of using the gear pump 100 of the present invention to produce the high molecular polymer can be integrated with the process for manufacturing the molding thereof to constitute a single production line shown in FIG 3 .
  • the monomer tank 110 and the polymerization tank 120 shown in FIG. 3 can also be replaced with a resin particle tank and a molten resin tank, so as to form a production line for manufacturing the molten resin and the molding thereof.
  • the monomer tank 110, the gear pump 100, and the polymerization tank 120 shown in FIG. 3 can also constitute a polymerization apparatus 200.
  • the molding apparatus 300 or the fiber spinning apparatus 400 can be separated from the gear pump 100; otherwise, the gear pump 100 can be integrated into the molding apparatus 300 or the fiber spinning apparatus 400.
  • FIGs. 4 and 5 show a gear pump 500 according to a second embodiment of the present invention.
  • the gear pump 500 is formed by disposing a drive gear 502 and a driven gear 503 meshing with each other within the internal space of the casing 1.
  • a pump functions to feed the fluid obtained in the tooth space from the suction side to the discharge side.
  • the drive gear 502 and the driven gear 503 are both helical gears having a one-point continuous contact tooth profile.
  • the teeth of the two gears 502 and 503 are circular-arc teeth.
  • the ratio D/B of the diameter D to the gear width B is 1.1 -1.15.
  • the above double-helical gear is set to 32° or less than 32° in the above tooth processing steps.
  • ⁇ is 16° or larger than 16°, which does not affect the tooth processing steps.
  • the helical gear with circular-arc tooth profile can also achieve substantially the same performance.
  • Embodiment 2 if the same effect as Embodiment 1 can be obtained, and the drive gear 502 and the driven gear 503 are both helical gears, a gear/shaft can be integrated and produced. Thus, the processing and productivity are improved due to the simple structure.
  • the gear pump 500 can be used to replace the gear pump 100 shown in FIG. 3 , and can also be incorporated into the molding apparatus 300 or the fiber spinning obtained, and the drive gear 502 and the driven gear 503 are both helical gears, a gear/shaft can be integrated and produced. Thus, the processing and productivity are improved due to the simple structure.
  • the gear pump 500 can be used to replace the gear pump 100 shown in FIG 3 , and can also be incorporated into the molding apparatus 300 or the fiber spinning apparatus 400.
  • the gear pump of the present invention can be, for example, applied in (but not limited to) the petroleum plant or chemical plant, polymerization plant, and molding/fiber spinning apparatus for feeding high-viscosity substances such as molten resin and other high molecular polymers under a high pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (7)

  1. Pompe à engrenages (100, 500), comprenant :
    un boîtier (1), ayant un orifice d'aspiration (11) pour introduire le fluide et un orifice de décharge (12) pour évacuer le fluide ; et
    une paire de roues dentées (2, 3, 502, 503), disposées à l'intérieur du boîtier (1), dans lequel le fluide est amené depuis l'orifice d'aspiration (11) vers l'orifice de décharge (12) par la rotation des roues dentées (2, 3, 502, 503) s'engrenant l'une dans l'autre, et un rapport entre le diamètre et la largeur de chaque roue dentée se situant entre 1,1 et 1,15, dans lequel la paire de roues dentées consiste en deux roues dentées à denture double-hélicoïdale (2, 3) ou hélicoïdale (502, 503), et dans lequel la pompe à engrenages (100, 500) est caractérisée en ce que la paire de roues dentées (2, 3, 502, 503) consiste en deux roues dentées ayant un profile de dents assurant un contact ponctuel continu, un nombre de dents entre 10 et 12 et un angle de torsion entre 28° et 32° dans le cas des deux roues à denture double-hélicoïdale (2, 3), et un nombre de dents entre 8 et 12 et un angle de torsion entre 14° et 18° dans le cas des deux roues à denture hélicoïdale (502, 503).
  2. Pompe à engrenages (100, 500) selon la revendication 1, dans laquelle dans un profil périphérique interne du boîtier (1), l'angle formé par les segments de ligne reliant respectivement les positions (P2) où chaque pointe de dent de l'engrenage rotatif s'écarte de la surface périphérique interne du boîtier (1), avec le point primitif (P0) des roues dentées (2, 3, 502, 503), se situe entre 48° et 102° comme indiqué dans la section de direction de l'axe.
  3. Pompe à engrenages (100, 500) selon la revendication 1 ou 2, dans laquelle dans un profil périphérique interne du boîtier, un angle d'arc de cercle formé entre la position (P1) où la pointe de dent de l'engrenage rotatif s'approche étroitement de la surface périphérique interne du boîtier (1), et la position (P2) où la pointe de dent de la roue dentée (2, 3, 502, 503) s'écarte de la surface périphérique interne du boîtier, se situe entre 72° et 108° comme indiqué dans la section de direction de l'axe.
  4. Méthode de fabrication d'un polymère de masse moléculaire élevée, d'une résine fondue ou d'un moulage de ceux-ci, dans laquelle la pompe à engrenages (100, 500) selon l'une quelconque des revendications de 1 à 3 est utilisée dans un procédé de fabrication d'un polymère de masse moléculaire élevée ou d'une résine fondue, ou dans un procédé de fabrication de moulage d'un polymère de masse moléculaire élevée ou d'une résine fondue.
  5. Appareil de polymérisation, utilisant la pompe à engrenages (100, 500) selon l'une quelconque des revendications de 1 à 3.
  6. Appareil de moulage, utilisant la pompe à engrenages (100, 500) selon l'une quelconque des revendications de 1 à 3.
  7. Appareil de filage de fibres, utilisant la pompe à engrenages (100, 500), selon l'une quelconque des revendications de 1 à 3.
EP06714031.9A 2005-02-24 2006-02-17 Pompe a engrenage Active EP1852612B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2005048965 2005-02-24
PCT/JP2005/015675 WO2006090495A1 (fr) 2005-02-24 2005-08-29 Pompe a engrenage
PCT/JP2006/302890 WO2006090652A1 (fr) 2005-02-24 2006-02-17 Pompe a engrenage

Publications (3)

Publication Number Publication Date
EP1852612A1 EP1852612A1 (fr) 2007-11-07
EP1852612A4 EP1852612A4 (fr) 2010-07-07
EP1852612B1 true EP1852612B1 (fr) 2017-07-05

Family

ID=36927293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06714031.9A Active EP1852612B1 (fr) 2005-02-24 2006-02-17 Pompe a engrenage

Country Status (2)

Country Link
EP (1) EP1852612B1 (fr)
WO (1) WO2006090652A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109931258A (zh) * 2018-11-21 2019-06-25 中国航发西安动力控制科技有限公司 一种燃油齿轮泵的齿轮副

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20070172A1 (it) * 2007-03-14 2008-09-15 Mario Antonio Morselli Apparecchiatura idraulica ad ingranaggi perfezionata
CN102562576A (zh) * 2012-01-17 2012-07-11 浙江中禾机械有限公司 一种送浆泵
JP6002005B2 (ja) * 2012-11-02 2016-10-05 住友ゴム工業株式会社 ギアポンプ押出し機、及びそれに用いる押出しギアの製造方法
DE102016216159A1 (de) * 2016-08-29 2018-03-01 Robert Bosch Gmbh Außenzahnradpumpe für ein Abwärmerückgewinnungssystem
RU206547U1 (ru) * 2021-06-21 2021-09-15 Сергей Иванович Никитин Шестеренный насос
RU210280U1 (ru) * 2021-12-20 2022-04-05 Сергей Иванович Никитин Шестеренный насос

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5138922B1 (fr) * 1968-02-19 1976-10-25
JPS501004Y1 (fr) * 1968-04-19 1975-01-11
JPS5064804A (fr) * 1973-10-11 1975-06-02
JPS56127391U (fr) * 1980-02-07 1981-09-28
DE4012929C2 (de) * 1989-04-29 1996-02-08 Barmag Barmer Maschf Zahnradpumpe
JP2005048965A (ja) 2003-07-29 2005-02-24 Hitachi Home & Life Solutions Inc 分離型空気調和機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109931258A (zh) * 2018-11-21 2019-06-25 中国航发西安动力控制科技有限公司 一种燃油齿轮泵的齿轮副

Also Published As

Publication number Publication date
EP1852612A4 (fr) 2010-07-07
WO2006090652A1 (fr) 2006-08-31
EP1852612A1 (fr) 2007-11-07

Similar Documents

Publication Publication Date Title
US20090060770A1 (en) Gear pump
EP1852612B1 (fr) Pompe a engrenage
US9109595B2 (en) Helical gear pump
KR101012465B1 (ko) 기어펌프
US6170975B1 (en) Multi-shaft extruder kneading discs, kneading disc blocks and extruder
US9932980B2 (en) Gear pump bearing dam
US4343602A (en) Gear wheel pump with reduced power requirement
EP1785638A2 (fr) Dispositif de roulement à rouleaux coniques à lubrication liquide
CN102365462A (zh) 叶片泵
CN101438061A (zh) 真空泵
US5368457A (en) Fluid compressor having a molded helical blade
AU760694B2 (en) Gear pump for pumping highly viscous fluids
JPH04325785A (ja) ギヤポンプ
EP1380753A2 (fr) Roue dentée pour pompe à huile à engrenages du type à roue mobile interne
US3817668A (en) Gear wheel pump with feed passage of constant hydraulic cross section
CN109000141A (zh) 一种能减少磨损的转子式机油泵
DE10334481A1 (de) Antrieb einer Spindelvakuumpumpe
JP2010019204A (ja) 内接歯車ポンプ用ロータ
JP2010248978A (ja) 一軸偏心ねじポンプシステム、ステータ劣化状態判定装置およびステータ劣化状態判定方法
CN220869559U (zh) 用于驱动泡沫泵的容积式水轮机及泡沫比例混合装置
JP7514541B2 (ja) 連結軸及び一軸偏心ねじポンプ
KR20010033665A (ko) 차등 용량을 갖는 기어 펌프시리즈 및 상기 시리즈의 개별기어 펌프들을 제조하는 방법
CN117212023A (zh) 用于驱动泡沫泵的容积式水轮机及泡沫比例混合装置
JP2512443Y2 (ja) 溶融樹脂用ギアポンプ
JP2592113Y2 (ja) 高圧粘性流体用歯車ポンプ

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070823

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE IT LI

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): CH DE IT LI

A4 Supplementary search report drawn up and despatched

Effective date: 20100607

17Q First examination report despatched

Effective date: 20160519

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170223

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE IT LI

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602006052948

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: BUGNION S.A., CH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602006052948

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20180406

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 602006052948

Country of ref document: DE

Owner name: SHIMADZU INDUSTRIAL SYSTEMS CO., LTD., OTSU-SH, JP

Free format text: FORMER OWNER: SHIMADZU MECTEM INC., OTSU, SHIGA, JP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20231228

Year of fee payment: 19

Ref country code: CH

Payment date: 20240301

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20240111

Year of fee payment: 19