EP3096016B1 - Volumetrische pumpe - Google Patents

Volumetrische pumpe Download PDF

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Publication number
EP3096016B1
EP3096016B1 EP16169752.9A EP16169752A EP3096016B1 EP 3096016 B1 EP3096016 B1 EP 3096016B1 EP 16169752 A EP16169752 A EP 16169752A EP 3096016 B1 EP3096016 B1 EP 3096016B1
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EP
European Patent Office
Prior art keywords
shaft
drive shaft
drawing shaft
pump
bearing
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
EP16169752.9A
Other languages
English (en)
French (fr)
Other versions
EP3096016A1 (de
Inventor
Alessandro PANNO
Marco Guidetti
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.)
Casappa SpA
Original Assignee
Casappa SpA
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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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • 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
    • 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
    • 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
    • F04C2240/50—Bearings
    • 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 volumetric pump, in particular a gear pump.
  • Gear pump means a pump in which the change in volume induced by the meshing of two rolling bodies is exploited to transfer energy to a fluid.
  • gear pumps comprising:
  • the reference number 1 indicates a volumetric pump, in particular a gear pump.
  • the gears interact with a fluid transiting through the pump, determining an increase in energy.
  • gear pump means a pump in which the change in volume induced by the meshing of two rolling bodies (typically cogwheels) is exploited to determine a transfer of energy to the fluid.
  • the pump 1 comprises:
  • the pump 1 is a gear pump and the drive shaft 2 is advantageously solidly constrained to at least one of the gears which determine an increase in energy of the fluid (said gears coincide with rolling bodies placed in direct contact with the fluid; conveniently, the drive shaft 2 and at least one of said rolling bodies are in a single monolithic body; advantageously, the rolling bodies are cogwheels).
  • the drawing shaft 3 is operatively linked to the drive shaft 2 and transfers its radial loads to the latter, whilst being constrained to means for neutralising its axial loads.
  • the drawing shaft 3 is placed, directly or indirectly by means of a transmission member, between a motor (typically of the internal combustion type) for driving the pump 1 and the drive shaft 2.
  • a motor typically of the internal combustion type
  • the pump 1 comprises an external casing 7.
  • the external casing 7 is part of the protective enclosure of the pump.
  • the external casing 7 is obtained by casting.
  • the drive shaft 2 lies internally of the casing 7 of the pump 1.
  • the drawing shaft 3 projects externally of the casing 7 in order to enable a direct or indirect connection with a motor.
  • a part of the drawing shaft 3 outside the casing 7 defines a power take-off operatively connected to the motor.
  • the casing 7 comprises a mouth 73 for the drawing shaft 3 to pass through the casing 7.
  • the pump 1 also comprises a static support structure 4 for the drive shaft 2.
  • the support structure 4 comprises:
  • the first bearing 41 is advantageously a single cylindrical body.
  • the first bearing 41 is static.
  • the drive shaft 2 rotates inside the first bearing 41.
  • the first bearing 41 is in contact with the drive shaft 2 (possibly through an interposed layer of lubricant) and the support 40.
  • the first bearing 41 is not, however, in contact with the drawing shaft 3.
  • the radial thickness of the first bearing 41 is comprised between 0.5 and 3 millimetres. Conveniently, the ratio between the axial extent and outer diameter of the first bearing 41 is comprised between 0.5 and 1.5.
  • the pump 1 also comprises at least a thrust bearing 71 which axially abuts, directly or indirectly, a first portion 33 of the drawing shaft 3 in order to neutralise axial loads bearing on the drawing shaft 3.
  • the thrust bearing 71 directly abuts a first portion of the drawing shaft 3.
  • the thrust bearing 71 abuts the first portion 33 by interposition of the elements indicated by the reference numbers 31 and 711.
  • the pump 1 comprises a pair of thrust bearings 71, axially interposed between which is the first portion 33 of the drawing shaft 3 or an element constrained and/or solidly joined thereto in order to neutralise axial loads bearing on the drawing shaft 3. In this manner, the axial loads originating from the drawing shaft 3 will not be transferred onto the driven shaft 2.
  • the pair of thrust bearings 71 is a pair of axial sliding bearings (thus devoid of rolling elements).
  • the pair of thrust bearings 71 comprises a pair of sliding rings 710.
  • the sliding rings 710 are advantageously positioned side by side at a predetermined distance and preferably parallel.
  • said rings 710 extend perpendicularly to a rotation axis of the drawing shaft 3. Conveniently, they are spaced at a distance of less than 10 millimetres from each other.
  • the pair of thrust bearings 71 is interposed between the first sliding bearing 41 and the mouth 73 passing through the casing 7.
  • each of said thrust bearings 71 is comprised between 0.5 and 3 millimetres.
  • the minimum distance between the first bearing 41 and the mouth 73 passing through the casing 7 is comprised between 25 and 70 millimetres.
  • the drawing shaft 3 is not supported by roller bearings. Conveniently, nor is the drive shaft 2 supported by roller bearings.
  • the drawing shaft 3 and drive shaft 2 are coaxial, one of the two comprising a seating 6 for housing an end of the other. Conveniently, the drawing shaft 3 and the drive shaft 2 reciprocally mesh internally of the housing seating 6.
  • the drawing shaft 3 and the drive shaft 2 comprise in combination a coupling which enables any radial loads to be transferred from the drawing shaft 3 to the drive shaft 2.
  • the coupling which enables any radial loads to be transferred from the drawing shaft 3 to the drive shaft 2 comprises transversal sections of the drawing shaft 3 and the drive shaft 2, which are complementarily shaped and fitted into one another. They thus enable correct centring of the shafts 2 and 3.
  • the housing seat 6 is fashioned in said drawing shaft 3.
  • the drive shaft 2 thus projects inside the drawing shaft 3.
  • the drive shaft 2 has a first plurality 21 of teeth that mesh with a second plurality 35 of teeth belonging to said drawing shaft 3.
  • the first plurality 21 of teeth project radially from a base away from the rotation axis of the drawing shaft 3, whilst the second plurality 35 of teeth project radially from a base toward the rotation axis of the drawing shaft 3.
  • the pump 1 comprises an oil seal 72 which contributes to delimiting said lubricating chamber 71.
  • the oil seal 72 extends radially between the drawing shaft 3 and a part of the casing 7.
  • the present invention also relates to a functioning method of a volumetric pump, in particular with gears interacting with a fluid transiting through the pump in order to determine an increase in energy thereof.
  • the pump 1 has one or more of the features described previously.
  • the pump 1 comprises a drive shaft 2 and a shaft 3 drawing in rotation said drive shaft 2.
  • the drive shaft 2 could be solidly constrained to at least one of the gears.
  • the method comprises the steps of:
  • the invention thus conceived enables multiple advantages to be obtained.
  • it permits a reduction in the overall dimensions of the pump.
  • the use of sliding bearings rather than roller bearings enables greater compactness (especially in the axial direction of the drawing shaft 3) and cost savings.
  • the drive shaft 2 is supported by radial sliding bearings that are used not only to neutralise the radial loads generated by the shaft 2, but also to neutralise the radial loads originating from the shaft 3.
  • the axial loads bearing on the shaft 3 are neutralised by a pair of thrust bearings and are thus not transferred to the shaft 2.

Landscapes

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

Claims (8)

  1. Volumetrische Pumpe, umfassend:
    i) eine Antriebswelle (2);
    ii) eine Welle (3), die die Antriebswelle (2) in Drehung versetzt, wobei diese in Drehung versetzende Welle (3) koaxial zur Antriebswelle (2) angeordnet ist, wobei entweder die in Drehung versetzende Welle (3) oder die Antriebswelle (2) eine Gehäuseaufnahme (6) eines Endes der anderen umfasst, wobei die Gehäuseaufnahme (6), die in Drehung versetzende Welle (3) und die Antriebswelle (2) in Kombination eine Kupplung umfassen;
    iii) eine statische Halterungskonstruktion (4) der Antriebswelle (2), umfassend:
    - eine Halterung (40), im Vergleich zu der sich die Antriebswelle (2) drehen kann;
    - Neutralisierungsmittel der Radiallasten, die auf der in Drehung versetzenden Welle (3) lasten und im Wesentlichen mit einem oder mehreren Gleitlagern ohne Wälzelemente übereinstimmen, die radial zwischen der Antriebswelle (2) und der Halterung (40) eingesetzt sind, wobei ein oder mehrere Gleitlager mindestens ein erstes Gleitlager (41) umfassen;
    iv) mindestens ein Drucklager (71), das axial direkt oder indirekt an einem ersten Abschnitt (33) der in Drehung versetzenden Welle (3) anschlägt, um Axiallasten zu neutralisieren, die auf der in Drehung versetzenden Welle (3) lasten,
    dadurch gekennzeichnet, dass die Kupplung die Übertragung jeglicher Radiallasten von der in Drehung versetzenden Welle (3) auf die Antriebswelle (2) ermöglicht, da die in Drehung versetzende Welle (3) keine Lager umfasst, um den Radiallasten entgegenzuwirken, wobei die Kupplung, die die Übertragung jeglicher Radiallasten von der in Drehung versetzenden Welle (3) auf die Antriebswelle (2) ermöglicht, Quersektionen der in Drehung versetzenden Welle (3) und der Antriebswelle (2) umfasst, wobei diese Sektionen passend zueinander ausgebildet und ineinander eingepasst sind,
    wobei die in Drehung versetzende Welle (3) und die Antriebswelle (2) innerhalb der Gehäuseaufnahme (6) zusätzlich zur Kupplung, die die Übertragung jeglicher Radiallasten von der in Drehung versetzenden Welle (3) auf die Antriebswelle (2) ermöglicht, in Kombination verzahnte Mittel zur Übertragung des Antriebsmoments von der in Drehung versetzenden Welle (3) auf die Antriebswelle (2) umfasst, wobei die verzahnten Übertragungsmittel auf einen ersten Teil (9) der Antriebswelle (2) und auf die in Drehung versetzende Welle (3) wirken,
    wobei die passend zueinander ausgebildeten Sektionen für die Übertragung von Radiallasten auf einen zweiten Teil (90) der Antriebswelle (2) und der in Drehung versetzenden Welle (3) wirken, wobei der zweite Teil (90) der Antriebswelle (2) und der in Drehung versetzenden Welle (3) das Zentrieren der Antriebswelle (2) und der in Drehung versetzenden Welle (3) erlaubt.
  2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Pumpe eine Getriebepumpe ist und mindestens ein Paar Zahnräder umfasst, die mit dem Medium interagieren und eine Erhöhung dessen Energie herbeiführen, wobei die Antriebswelle (2) fest mit mindestens einem der Zahnräder verbunden ist.
  3. Pumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das erste Gleitlager (41) eine geschmierte Buchse (410) umfasst, die fest mit der statischen Halterungskonstruktion (4) verbunden ist, und in der sich die Antriebswelle (2) dreht.
  4. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie eine externe Einhausung (7) umfasst, wobei die in Drehung versetzende Welle (3) extern aus der externen Einhausung (7) hervorsteht, um eine direkte oder indirekte Verbindung mit einem Motor zu erlauben.
  5. Pumpe nach Anspruch 4, dadurch gekennzeichnet, dass eine Schmierkammer (70) innerhalb der externen Einhausung (7) bereitgestellt ist, wobei diese Schmierkammer (70) mit dem ersten Gleitlager (41) und mit dem Drucklager (71) in Kommunikation ist.
  6. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das mindestens eine Drucklager (71) eine Vielzahl von Drucklagern umfasst, wobei der erste Abschnitt (33) der in Drehung versetzenden Welle (3) eine Schulter (30) umfasst, die am Paar von Drucklagern (71) anschlägt und die zwischen diesen (71) eingepasst ist.
  7. Pumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die in Drehung versetzende Welle (3) eine Umfangsaufnahme (31) umfasst, die in einer Ebene liegt, die quer zur Rotationsachse der in Drehung versetzenden Welle (3) verläuft, wobei die Pumpe (1) einen Seegerring (32) umfasst, der
    - mindestens zum Teil in dieser Aufnahme (31) positioniert ist;
    - am Drucklager (71) durch mindestens einen ersten Ring (711) anschlägt, der zwischen dem Seegerring (32) und dem Drucklager (71) eingesetzt ist.
  8. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die in Drehung versetzende Welle (3) und die Antriebswelle (2) nicht von Wälzlagern getragen werden.
EP16169752.9A 2015-05-20 2016-05-16 Volumetrische pumpe Active EP3096016B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITUB20150780 2015-05-20

Publications (2)

Publication Number Publication Date
EP3096016A1 EP3096016A1 (de) 2016-11-23
EP3096016B1 true EP3096016B1 (de) 2021-04-07

Family

ID=53900996

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16169752.9A Active EP3096016B1 (de) 2015-05-20 2016-05-16 Volumetrische pumpe

Country Status (2)

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EP (1) EP3096016B1 (de)
CN (1) CN106168210B (de)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2412588A (en) * 1943-05-31 1946-12-17 Pesco Products Co Gear divider with pressure loaded bushings

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2801593A (en) * 1954-05-03 1957-08-06 Roper Corp Geo D Rotary pump
US6244842B1 (en) * 1999-11-09 2001-06-12 James B. Tieben Pump
CN2575331Y (zh) * 2002-10-17 2003-09-24 关岐生 沥青齿轮油泵
WO2012103926A1 (de) * 2011-01-31 2012-08-09 Robert Bosch Gmbh Zahnradpumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2412588A (en) * 1943-05-31 1946-12-17 Pesco Products Co Gear divider with pressure loaded bushings

Also Published As

Publication number Publication date
CN106168210B (zh) 2020-07-14
CN106168210A (zh) 2016-11-30
EP3096016A1 (de) 2016-11-23

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