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EP0607999B1 - Method of cooling the shaft of a gear pump rotor - Google Patents

Method of cooling the shaft of a gear pump rotor Download PDF

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Publication number
EP0607999B1
EP0607999B1 EP94102363A EP94102363A EP0607999B1 EP 0607999 B1 EP0607999 B1 EP 0607999B1 EP 94102363 A EP94102363 A EP 94102363A EP 94102363 A EP94102363 A EP 94102363A EP 0607999 B1 EP0607999 B1 EP 0607999B1
Authority
EP
European Patent Office
Prior art keywords
shaft
gear
meshing area
cooling
cooled
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.)
Expired - Lifetime
Application number
EP94102363A
Other languages
German (de)
French (fr)
Other versions
EP0607999A3 (en
EP0607999A2 (en
Inventor
Peter Blume
Roger Stehr
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.)
Maag Pump Systems AG
Original Assignee
Maag Pump Systems AG
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 to EP94102363A priority Critical patent/EP0607999B1/en
Priority to ES94102363T priority patent/ES2086973T3/en
Priority to DE59400195T priority patent/DE59400195D1/en
Priority to DK94102363.2T priority patent/DK0607999T3/en
Priority to AT94102363T priority patent/ATE136988T1/en
Application filed by Maag Pump Systems AG filed Critical Maag Pump Systems AG
Publication of EP0607999A2 publication Critical patent/EP0607999A2/en
Publication of EP0607999A3 publication Critical patent/EP0607999A3/en
Priority to JP02557695A priority patent/JP3737151B2/en
Priority to US08/390,018 priority patent/US5468131A/en
Application granted granted Critical
Publication of EP0607999B1 publication Critical patent/EP0607999B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the present invention relates to a method for cooling the shaft of a gear pump rotor according to the preamble of claim 1, a gear pump rotor according to that of claim 3 and a gear pump according to that of claim 7.
  • Wave cooling is usually extremely simple.
  • the shaft 3 has an axial bore 5, which passes through both bearing areas on the projecting shaft sections 7 and the shaft area 7 v in the toothing area.
  • the toothing region 7 v is understood to mean the region of the rotor shaft which lies radially below the toothing, regardless of whether the gear wheel and shaft are formed in one or more parts.
  • a major disadvantage of this cooling procedure is that the shaft 7, 7 v is cooled indiscriminately up to the cooling medium temperature that rises over the length of the bore and up to the various radial heat flows that normally flow out of the bearing and toothing areas. This can lead to a cooling effect in the region of the toothing 13, which results in an undesirably large drop in the temperature level in the tooth base.
  • this is achieved in a preferred manner by creating gas, in particular air insulation in the toothing area 7 v and / or solid-state insulation and / or reducing the cooling medium contact area in the toothing area per axial expansion unit is compared to the mentioned contact surface on wave areas to be cooled.
  • FIG. 2 in which, as in the following, the same reference numbers are used for the same parts as in FIG. 1, a casing tube 15 is fitted into the bore 5, which ensures a good thermal transition, in particular on shaft areas to be cooled, with its outer wall , bears against the wall of bore 5.
  • the outer diameter of the casing tube 15 is reduced in the toothing region 7 v , whereby an annular groove 17 is formed in this outer wall.
  • the aforementioned heat conduction is reduced in the toothing area 7 v by providing a solid-state insulator 21 on a jacket pipe 15a, in the toothing area 7 v , be this, as shown, by realizing a jacket pipe wall section from a temperature-resistant insulation material or be it through an inner and / or outer wall coating or covering of the casing tube with such a material.
  • the surface is enlarged, for example, a jacket tube 15b to be cooled wavebands 7 per axial extension unit, for example by providing a Nutungsmusters 23 in these sections, in contrast to the formation of the jacket tube inner surface v as a smooth cylindrical surface in the gear portion 7.
  • a thermal solid-state insulator 21a in the toothing region, possibly even, as an alternative or in addition, according to the outer diameter of the casing tube 15b to reduce the embodiment of FIG. 2 in order to keep the cooling in the toothing area optimally low.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)

Abstract

In order to prevent, in a shaft cooling system, the gearing from being cooled in an unacceptable manner, the radial heat flow is reduced in the gearing region (7v) of the shaft, with respect to the heat flow in shaft regions to be cooled (7), for example by an insulating air chamber (19). <IMAGE>

Description

Die vorliegende Erfindung betrifft ein Verfahren zur Kühlung der Welle eines Zahnradpumpen-Rotors nach dem Oberbegriff von Anspruch 1, einen Zahnradpumpen-Rotor nach demjenigen von Anspruch 3 sowie eine Zahnradpumpe nach demjenigen von Anspruch 7.The present invention relates to a method for cooling the shaft of a gear pump rotor according to the preamble of claim 1, a gear pump rotor according to that of claim 3 and a gear pump according to that of claim 7.

In vielen Anwendungsfällen von Zahnradpumpen ist es aufgrund der rheologischen Eigenschaften des Schmiermediums, insbesondere bei Einsatz von Fördermedium als Schmiermedium von Gleitlagern der Rotoren, zweckmässig, eine Wellenkühlung vorzusehen bzw. eine Schmiermediumskühlung, um damit die in den Lagern, insbesondere Gleitlagern, erzeugte Wärme abzuführen. Damit wird eine niedrigere Lagertemperatur erreicht.In many applications of gear pumps, due to the rheological properties of the lubricant, especially when using the pumping medium as the lubricant for the rotor bearings, it is advisable to provide shaft cooling or lubricant cooling in order to dissipate the heat generated in the bearings, especially the sliding bearings. A lower storage temperature is thus achieved.

Ueblicherweise ist eine Wellenkühlung ausserordentlich einfach aufgebaut. Wie in Fig. 1, welche einen vereinfachten Axialschnitt durch einen bekannten Zahnradpumpen-Rotor 1 zeigt, dargestellt, besitzt die Welle 3 eine axiale Bohrung 5, welche beide Lagerbereiche an den vorragenden Wellenabschnitten 7 wie auch den Wellenbereich 7v im Verzahnungsbereich passiert. Als Verzahnungsbereich 7v wird im folgenden der Bereich der Rotorwelle verstanden, welcher radial unter der Verzahnung liegt, unabhängig davon, ob Zahnrad und Welle ein- oder mehrteilig ausgebildet sind.Wave cooling is usually extremely simple. As shown in Fig. 1, which shows a simplified axial section through a known gear pump rotor 1, the shaft 3 has an axial bore 5, which passes through both bearing areas on the projecting shaft sections 7 and the shaft area 7 v in the toothing area. In the following, the toothing region 7 v is understood to mean the region of the rotor shaft which lies radially below the toothing, regardless of whether the gear wheel and shaft are formed in one or more parts.

In die axiale Bohrung 5 ragt, fast bis zum einseitigen Bohrungsende 9, ein Umlenkrohr 11. Ueber einen nicht dargestellten Drehdichtungsanschluss wird das Kühlmedium dem Umlenkrohr 11 zugeführt, durchströmt dieses Rohr axial, wird am Ende des Rohres 11 radial umgelenkt, um axial, im Gegenstrom, wieder rückzufliessen oder umgekehrt. Je nach Vorzeichen der Temperaturdifferenz nimmt das Kühlmedium auf seinem Strömungspfad Wärme auf bzw. gibt Wärme ab. Diesbezüglich wird auf die DE-A-42 11 516 verwiesen.Extends into the axial bore 5, almost to the one-sided bore end 9, of a deflecting tube 11. The cooling medium is fed to the deflecting tube 11 via a rotary seal connection, not shown, flows through this tube axially, is deflected radially at the end of the tube 11 by axially, in counterflow to flow back again or vice versa. Depending on the sign of the temperature difference the cooling medium absorbs or releases heat along its flow path. In this regard, reference is made to DE-A-42 11 516.

Ein wesentlicher Nachteil bei diesem Kühlvorgehen besteht darin, dass die Welle 7, 7v, bis auf die über die Bohrungslänge ansteigende Kühlmediumstemperatur und bis auf die normalerweise aus den Lager- und Verzahnungsbereichen abfliessenden, verschiedenen radialen Wärmeströme, unterschiedslos gekühlt wird. Dies kann zu einem Kühleffekt im Bereiche der Verzahnung 13 führen, der eine unerwünscht starke Absenkung des Temperaturniveaus im Zahngrund zur Folge hat.A major disadvantage of this cooling procedure is that the shaft 7, 7 v is cooled indiscriminately up to the cooling medium temperature that rises over the length of the bore and up to the various radial heat flows that normally flow out of the bearing and toothing areas. This can lead to a cooling effect in the region of the toothing 13, which results in an undesirably large drop in the temperature level in the tooth base.

Es ist Aufgabe der vorliegenden Erfindung, diesen Nachteil zu beheben.It is an object of the present invention to remedy this disadvantage.

Dies wird mit einem Kühlverfahren eingangs genannter Art erreicht, welches sich nach dem kennzeichnenden Teil von Anspruch 1 auszeichnet.This is achieved with a cooling method of the type mentioned at the outset, which is characterized in accordance with the characterizing part of claim 1.

Dadurch, dass im Verzahnungsbereich 7v der Welle 7 gemäss Fig. 1, nun aber erfindungsgemäss, eine geringere Wärmeleitung zum Kühlmedium pro Axialausdehnungseinheit, und betrachtet auf gleichen Zylinderflächen, erstellt wird als in zu kühlenden Wellenbereichen, insbesondere Lagerbereichen, wird erreicht, dass die erwähnte nachteilige Verzahnungskühlung massgeblich reduziert wird, ohne den erwünschten Kühleffekt, insbesondere in Lagerbereichen, zu beeinflussen.Due to the fact that in the toothed area 7 v of the shaft 7 according to FIG. 1, but now according to the invention, a lower heat conduction to the cooling medium per axial expansion unit, and viewed on the same cylinder surfaces, is created than in shaft areas to be cooled, in particular bearing areas, it is achieved that the mentioned disadvantageous gear cooling is significantly reduced without affecting the desired cooling effect, especially in storage areas.

Dem Wortlaut von Anspruch 2 folgend, wird dies in bevorzugter Art und Weise dadurch erreicht, dass eine Gas-, insbesondere Luftisolation im Verzahnungsbereich 7v und/oder eine Festkörperisolation erstellt wird und/oder die Kühlmediums-Kontaktfläche im Verzahnungsbereich pro Axialausdehnungseinheit verringert wird gegenüber der erwähnten Kontaktfläche an gewollt zu kühlenden Wellenbereichen.According to the wording of claim 2, this is achieved in a preferred manner by creating gas, in particular air insulation in the toothing area 7 v and / or solid-state insulation and / or reducing the cooling medium contact area in the toothing area per axial expansion unit is compared to the mentioned contact surface on wave areas to be cooled.

An einem Zahnradpumpen-Rotor eingangs genannter Art wird die der vorliegenden Erfindung zugrundegelegte Aufgabe durch dessen Ausbildung nach dem kennzeichnenden Teil von Anspruch 3 erreicht.On a gear pump rotor of the type mentioned in the introduction, the object on which the present invention is based is achieved by its design according to the characterizing part of claim 3.

Bevorzugte Ausführungsvarianten des erfindungsgemässen Zahnradpumpen-Rotors sind in den Ansprüchen 4 bis 6 spezifiziert, wobei die erfindungsgemäss bevorzugte Realisationsform einer geringeren radialen Wärmeleitung nach Anspruch 3 sich je durch die in den Ansprüchen 4 bis 6 spezifizierten Massnahmen oder Kombinationen mindestens zweier dieser Massnahmen realisieren lässt.Preferred embodiment variants of the gear pump rotor according to the invention are specified in claims 4 to 6, the preferred form of realization of a lower radial heat conduction according to claim 3 according to the invention being able to be implemented by the measures or combinations specified in claims 4 to 6 of at least two of these measures.

Die Erfindung wird anschliessend beispielsweise anhand von Figuren erläutert.The invention is subsequently explained, for example, using figures.

Es zeigen:

Fig. 1
eine bekannte Wellenkühlung;
Fig. 2
einen Ausschnitt in Darstellung analog zu derjenigen von Fig. 1 einer ersten Ausführungsvariante eines erfindungsgemässen Zahnradpumpen-Rotors zur Realisation des erfindungsgemässen Verfahrens in einer ersten Variante;
Fig. 3
in Darstellung analog zu Fig. 2, einen erfindungsgemässen Rotor in einer zweiten Variante bzw. eine zweite Variante zur Ausführung des erfindungsgemässen Verfahrens;
Fig. 4
eine dritte Variante des erfindungsgemässen Zahnradpumpen-Rotors bzw. des erfindungsgemässen Verfahrens.
Show it:
Fig. 1
a well-known wave cooling;
Fig. 2
a detail in a representation analogous to that of Figure 1 of a first embodiment of a gear pump rotor according to the invention for realizing the inventive method in a first variant;
Fig. 3
in illustration analogous to FIG. 2, a rotor according to the invention in a second variant or a second variant for carrying out the method according to the invention;
Fig. 4
a third variant of the gear pump rotor according to the invention or of the method according to the invention.

Gemäss Fig. 2, worin, wie auch im folgenden, für dieselben Teile dieselben Bezugsziffern wie in Fig. 1 gewählt sind, ist in die Bohrung 5 ein Mantelrohr 15 eingepasst, welches insbesondere an zu kühlenden Wellenbereichen mit seiner Aussenwandung, einen guten thermischen Uebergang sichernd, an der Wandung der Bohrung 5 anliegt. Der Aussendurchmesser des Mantelrohres 15 ist im Verzahnungsbereich 7v verringert, womit in dieser Aussenwandung eine ringförmige Nut 17 gebildet wird. Diese bildet mit der Wandung der Bohrung 5 eine ringförmige Luftkammer 19, welche eine wesentlich geringere Wärmeleitung pro Axialausdehnungseinheit zwischen Welle und Kühlmedium im Verzahnungsbereich 7v sicherstellt als an zu kühlenden Bereichen, betrachtet auf denselben Zylinderflächen Z, deren eine in Fig. 2 beispielsweise eingetragen ist.According to FIG. 2, in which, as in the following, the same reference numbers are used for the same parts as in FIG. 1, a casing tube 15 is fitted into the bore 5, which ensures a good thermal transition, in particular on shaft areas to be cooled, with its outer wall , bears against the wall of bore 5. The outer diameter of the casing tube 15 is reduced in the toothing region 7 v , whereby an annular groove 17 is formed in this outer wall. With the wall of the bore 5, this forms an annular air chamber 19, which ensures a substantially lower heat conduction per axial expansion unit between the shaft and the cooling medium in the toothing region 7 v than at regions to be cooled, viewed on the same cylinder surfaces Z, one of which is entered in FIG. 2, for example .

Gemäss Fig. 3 wird erfindungsgemäss im Verzahnungsbereich 7v die erwähnte Wärmeleitung dadurch reduziert, dass an einem Mantelrohr 15a, im Verzahnungsbereich 7v, ein Festkörperisolator 21 vorgesehen ist, sei dies, wie dargestellt, durch Realisation eines Mantelrohr-Wandungsabschnittes aus einem temperaturfesten Isolationsmaterial oder sei dies durch eine Innen- und/oder Aussenwandbeschichtung oder -belegung des Mantelrohres mit einem derartigen Material.3, according to the invention, the aforementioned heat conduction is reduced in the toothing area 7 v by providing a solid-state insulator 21 on a jacket pipe 15a, in the toothing area 7 v , be this, as shown, by realizing a jacket pipe wall section from a temperature-resistant insulation material or be it through an inner and / or outer wall coating or covering of the casing tube with such a material.

Bei der Variante gemäss Fig. 4 ist die Oberfläche beispielsweise eines Mantelrohres 15b in zu kühlenden Wellenbereichen 7 pro axiale Ausdehnungseinheit vergrössert, beispielsweise durch Vorsehen eines Nutungsmusters 23 in diesen Abschnitten, im Gegensatz zur Ausbildung der Mantelrohr-Innenfläche als glatte Zylinderfläche im Verzahnungsbereich 7v. Wie aus Fig. 4 ohne weiteres ersichtlich und gestrichelt bei 21a dargestellt, ist es ohne weiteres möglich, Vorsehen vergrösserter Kontaktflächen zum Kühlmedium hin an zu kühlenden Wellenbereichen mit Vorsehen eines thermischen Festkörperisolators 21a im Verzahnungsbereich zu kombinieren, gegebenenfalls sogar, als Alternative oder zusätzlich, den Aussendurchmesser des Mantelrohres 15b gemäss der Ausführung von Fig. 2 zu reduzieren, um die Kühlung im Verzahnungsbereich optimal gering zu halten.In the variant according to FIG. 4, the surface is enlarged, for example, a jacket tube 15b to be cooled wavebands 7 per axial extension unit, for example by providing a Nutungsmusters 23 in these sections, in contrast to the formation of the jacket tube inner surface v as a smooth cylindrical surface in the gear portion 7. As from Fig. 4 readily visible and shown in dashed lines at 21a, it is readily possible to combine the provision of enlarged contact surfaces to the cooling medium at shaft regions to be cooled with the provision of a thermal solid-state insulator 21a in the toothing region, possibly even, as an alternative or in addition, according to the outer diameter of the casing tube 15b to reduce the embodiment of FIG. 2 in order to keep the cooling in the toothing area optimally low.

Claims (7)

  1. Method for cooling a shaft (7, 7v) of a gear pump rotor (1), on which a cooling medium is driven axially through the shaft, characterised in that in the gear-meshing area (7v) of shaft (1) a lower heat conduction to the cooling medium (7v) per axial extension unit is created than in remaining shaft areas (7) to be cooled viewed through the same cylinder surfaces (Z) on the areas (7, 7v).
  2. Method according to claim 1, characterised in that the lower heat conduction is achieved by the provision of a gas insulation, in particular air insulation (19) and/or of a solid insulation (21, 21a) and/or by reducing the cooling-medium contact surface.
  3. Gear pump rotor comprising a gear-meshing area (7v) and a bearing shaft protruding with respect to the gear-meshing area, which has an axial channel arrangement (5, 9, 11) for a cooling medium, which channel extends through the gear-meshing area (7v) of shaft (1), characterised in that the gear-meshing area (7v) has a lower radial heat conduction per axial extension unit than shaft areas (7) to be cooled, viewed with respect to the same cylinder surfaces on the areas (7, 7v).
  4. Gear pump rotor according to claim 3, characterised in that in the gear-meshing area (7v) the channel arrangement surface per said unit is smaller than it (23) is in the shaft areas (7) to be cooled.
  5. Rotor according to one of claims 3 or 4, characterised in that in the gear-meshing area (7v) an annular gas chamber (19) is provided which preferably is realised by a pipe let axially into an axial bore (5) which pipe comprises an outside groove (19) in the gear-meshing area (7v).
  6. Rotor according to one of claims 3 to 5, characterised in that in the gear-meshing area (7v) an annular insert (21, 21a) is provided, the radial thermal conductibility of which is less than the thermal conductibility of a corresponding ring, viewed on the shaft sections (7) to be cooled.
  7. Gear pump comprising two rotors of which at least one is constructed according to one of claims 3 to 6.
EP94102363A 1994-02-17 1994-02-17 Method of cooling the shaft of a gear pump rotor Expired - Lifetime EP0607999B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
ES94102363T ES2086973T3 (en) 1994-02-17 1994-02-17 PROCEDURE FOR REFRIGERATING THE ROTOR TREE OF A GEAR PUMP.
DE59400195T DE59400195D1 (en) 1994-02-17 1994-02-17 Process for cooling the shaft of a gear pump rotor
DK94102363.2T DK0607999T3 (en) 1994-02-17 1994-02-17 Method of cooling the shaft of a gear pump motor
AT94102363T ATE136988T1 (en) 1994-02-17 1994-02-17 METHOD FOR COOLING THE SHAFT OF A GEAR PUMP ROTOR
EP94102363A EP0607999B1 (en) 1994-02-17 1994-02-17 Method of cooling the shaft of a gear pump rotor
JP02557695A JP3737151B2 (en) 1994-02-17 1995-02-14 Method for cooling shaft of gear pump rotor, gear pump rotor and gear pump
US08/390,018 US5468131A (en) 1994-02-17 1995-02-17 Method for cooling the shaft of a gear pump rotor, a gear pump rotor, and a gear pump comprising such a rotor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP94102363A EP0607999B1 (en) 1994-02-17 1994-02-17 Method of cooling the shaft of a gear pump rotor

Publications (3)

Publication Number Publication Date
EP0607999A2 EP0607999A2 (en) 1994-07-27
EP0607999A3 EP0607999A3 (en) 1994-09-21
EP0607999B1 true EP0607999B1 (en) 1996-04-17

Family

ID=8215692

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94102363A Expired - Lifetime EP0607999B1 (en) 1994-02-17 1994-02-17 Method of cooling the shaft of a gear pump rotor

Country Status (7)

Country Link
US (1) US5468131A (en)
EP (1) EP0607999B1 (en)
JP (1) JP3737151B2 (en)
AT (1) ATE136988T1 (en)
DE (1) DE59400195D1 (en)
DK (1) DK0607999T3 (en)
ES (1) ES2086973T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002001072A1 (en) 2000-06-28 2002-01-03 Coperion Werner & Pfleiderer Gmbh & Co. Kg Gear pump

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE238495T1 (en) 1997-11-07 2003-05-15 Maag Pump Systems Ag METHOD FOR TEMPERATURE STABILIZATION IN GEAR PUMPS
US6179594B1 (en) 1999-05-03 2001-01-30 Dynisco, Inc. Air-cooled shaft seal
US6213745B1 (en) 1999-05-03 2001-04-10 Dynisco High-pressure, self-lubricating journal bearings
CN108150410A (en) * 2017-12-27 2018-06-12 郑州沃华机械有限公司 A kind of smelt gear pump dedicated for rubber production device
JP2023070489A (en) 2021-11-09 2023-05-19 株式会社日立産機システム screw compressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB324687A (en) * 1928-10-01 1930-02-03 Steiner Hans Improvements in rotary piston compressors
US4073607A (en) * 1976-07-29 1978-02-14 Ingersoll-Rand Company Gas compressor system
DE3627956A1 (en) * 1986-08-18 1988-03-03 Wankel Gmbh Eccentric shaft of a rotary piston internal combustion engine
JPH0645135B2 (en) * 1990-10-08 1994-06-15 株式会社神戸製鋼所 Gear pump for molten resin

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002001072A1 (en) 2000-06-28 2002-01-03 Coperion Werner & Pfleiderer Gmbh & Co. Kg Gear pump
US6761546B2 (en) 2000-06-28 2004-07-13 Coperion Werner & Pfleiderer Gmbh & Co. Kg Gear pump having bearings with cooling ducts

Also Published As

Publication number Publication date
DK0607999T3 (en) 1996-05-13
EP0607999A3 (en) 1994-09-21
US5468131A (en) 1995-11-21
EP0607999A2 (en) 1994-07-27
JP3737151B2 (en) 2006-01-18
DE59400195D1 (en) 1996-05-23
ATE136988T1 (en) 1996-05-15
ES2086973T3 (en) 1996-07-01
JPH07259752A (en) 1995-10-09

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