EP1852612B1 - Zahnradpumpe - Google Patents

Zahnradpumpe Download PDF

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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
English (en)
French (fr)
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EP1852612A1 (de
EP1852612A4 (de
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/ja
Application filed by Shimadzu Mectem Inc filed Critical Shimadzu Mectem Inc
Publication of EP1852612A1 publication Critical patent/EP1852612A1/de
Publication of EP1852612A4 publication Critical patent/EP1852612A4/de
Application granted granted Critical
Publication of EP1852612B1 publication Critical patent/EP1852612B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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.

Claims (7)

  1. Eine Zahnradpumpe (100, 500), umfassend:
    ein Gehäuse (1), das eine Saugöffnung (11) zum Einleiten eines Fluids und eine Auslassöffung (12) zum Auslassen des Fluids, und
    ein innerhalb des Gehäuses (1) angeordnetes Zahnradpaar (2, 3, 502, 503), wobei das Fluid der Auslassöffnung (12) von der Saugöffnung (11) durch Rotation der ineinander greifenden Zahnräder (2, 3, 502, 503) zuführbar ist, und ein Verhältnis von Zahnraddurchmesser zu Zahnradbreite von jedem Zahnrad zwischen 1,1 und 1,15 eingestellt ist, wobei das Zahnradpaar aus zwei Doppelschrägstirnrädern (2,3) oder zwei Schrägstirnrädern (502, 503) besteht, und wobei die Zahnradpumpe (100, 500) dadurch gekennzeichnet ist, dass das Zahnradpaar (2, 3, 502, 503) aus zwei Zahnrädern besteht, die ein Zahnprofil mit kontinuierlichem Einpunkt-Kontakt aufweisen, und die Anzahl von Zähnen der Zahnräder 10 bis 12 und der Verdrehwinkel der Zahnräder 28° bis 32° beträgt, wenn das Zahnradpaar aus zwei Doppelschrägstirnrädern (2, 3) besteht, oder dass die Anzahl von von Zähnen der Zahnräder 8 bis 12 und der Verdrehwinkel der Zahnräder 14° bis 18° beträgt, wenn das Zahnradpaar aus zwei Schrägstirnrädern (502, 503) besteht.
  2. Die Zahnradpumpe (100, 500) gemäß Anspruch 1, wobei im inneren peripheren Profil des Gehäuses (1), in Achsrichtung betrachtet, der Winkel, der von den Liniensegmenten, die jeweils zwischen den Positionen (P2), an denen sich jede Zahnspitze der rotierenden Zahnräder von der inneren peripheren Oberfläche des Gehäuses (1) entfernt, und der Position des Wälzpunkts (P0) der Zahnräder (2, 3, 502, 503) gebildet wird, 48° bis 102° beträgt.
  3. Die Zahnradpumpe (100, 500) gemäß Anspruch 1 oder 2, wobei im inneren peripheren Profil des Gehäuses (1), in Achsrichtung betrachtet, der Kreisbogenwinkel, der zwischen der Position (P1), an der sich eine Zahnspitze der rotierenden Zahnräder eng an die innere periphere Oberfläche des Gehäuses (1) annähert, und der Position (P2), an der sich eine Zahnspitze der Zahnräder (2, 3, 502, 503) von der inneren peripheren Oberfläche des Gehäuses entfernt, gebildet wird, 72° bis 108° beträgt.
  4. Ein Verfahren zur Herstellung eines hochmolekularen Polymers, eines geschmolzenen Harzes oder eines Formkörpers daraus, wobei die Zahnradpumpe (100, 500) gemäß einem der Ansprüche 1 - 3 in einem Prozess zur Herstellung des hochmolekularen Polymers oder des geschmolzenen Harzes oder in einem Prozess zur Herstellung des Formkörpers des hochmolekularen Polymers oder des geschmolzenen Harzes verwendet wird.
  5. Eine Polymerisationsvorrichtung, die die Zahnradpumpe (100, 500) gemäß einem der Ansprüche 1 - 3 verwendet.
  6. Eine Formkörpervorrichtung, die die Zahnradpumpe (100, 500) gemäß einem der Ansprüche 1 - 3 verwendet.
  7. Eine Faserspinnvorrichtung, die die Zahnradpumpe (100, 500) gemäß einem der Ansprüche 1 - 3 verwendet.
EP06714031.9A 2005-02-24 2006-02-17 Zahnradpumpe Active EP1852612B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2005048965 2005-02-24
PCT/JP2005/015675 WO2006090495A1 (ja) 2005-02-24 2005-08-29 歯車ポンプ
PCT/JP2006/302890 WO2006090652A1 (ja) 2005-02-24 2006-02-17 歯車ポンプ

Publications (3)

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

Family

ID=36927293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06714031.9A Active EP1852612B1 (de) 2005-02-24 2006-02-17 Zahnradpumpe

Country Status (2)

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

Cited By (1)

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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

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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

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JPS5138922B1 (de) * 1968-02-19 1976-10-25
JPS501004Y1 (de) * 1968-04-19 1975-01-11
JPS5064804A (de) * 1973-10-11 1975-06-02
JPS56127391U (de) * 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

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* 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

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

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