EP0081902A1 - Zahnradpumpe oder -motor - Google Patents

Zahnradpumpe oder -motor Download PDF

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Publication number
EP0081902A1
EP0081902A1 EP19820305754 EP82305754A EP0081902A1 EP 0081902 A1 EP0081902 A1 EP 0081902A1 EP 19820305754 EP19820305754 EP 19820305754 EP 82305754 A EP82305754 A EP 82305754A EP 0081902 A1 EP0081902 A1 EP 0081902A1
Authority
EP
European Patent Office
Prior art keywords
gears
bearings
protrusions
side plates
curved surfaces
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.)
Withdrawn
Application number
EP19820305754
Other languages
English (en)
French (fr)
Inventor
Hideo Teruyama
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.)
KYB Corp
Original Assignee
Kayaba Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Publication of EP0081902A1 publication Critical patent/EP0081902A1/de
Withdrawn legal-status Critical Current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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the present invention relates to a gear pump or motor having gears which engage each other with their external teeth.
  • a gear pump or motor with a cover and a mounting flange provided on both sides of a housing, the shafts protruding on both sides of the two gears and being supported by the bearings provided in the cover and the mounting flange, and with a seal block arranged on the high pressure side of the housing, to seal the tooth tops of the gears on the delivery side.
  • the seal block is supported by the side plates, and the side plates form curved surfaces to accurately fit the bearings as bushings protruding a little toward the chamber of the housing and contact the surface of the seal block which is in contact with the tooth tops on the side opposite to the bushings.
  • the surface of the seal block in contact with the tooth tops may be deeply shaven off by the gears, so as to impair the sealing function.
  • a first object of the present invention is to provide a gear pump or motor, in which the inside diameter of said curved surfaces of said s.ide plates is made larger than the outside diameter of the bearings, so that said curved surfaces may contact the bearings at one point of each of said curved surfaces when they are assembled, to prevent the interference of the respective components during assembling, allowing the optimum control of the tooth top clearances.
  • a second object of the present invention is to provide agear pump or motor, in which the inside diameter of said side plates is made larger beforehand than the outside diameter of the bearings, so that said side plates may contact the bearings with an optimum condition kept when the gear pump or motor is operated.
  • a third object of the present invention is to provide a gear pump or motor, in which the tooth top clearances can be automatically corrected even if the housing expands or contracts due to temperatures during operation.
  • the inside diameter of the curved surfaces of the side plates is made larger than the outside diameter of the bearings, to prevent the interference of the respective components during assembling, and to let said curved surfaces contact said bearings at one point of each of said curved surfaces, for controlling the radial positions of the side plates and the seal block.
  • a gear pump 10 according to the present invention has a housing 11 consisting of a casing 12, a cover 13 and a mounting flange 14.
  • Said casing 12 is cylindrical, and is closed by the cover 13 on one side and by the mounting flange 14 on the ather side.
  • the cover 13 and the mounting flange 14 are connected with both the ends of the casing 12 respectively through seal members 15 and 16 by fitting joints 18 and 19, being fastened firmly by bolts 17. In this joining, dowel pins as used in the ordinary gear pump are not required.
  • the cover 13 and the mounting flange 14 are made of aluminium alloy and the casing 12 is made of steel.
  • the cover and the mounting flange are formed by die casting to enhance the dimensional accuracy, and to be suitable for die casting, aluminium alloy is used as the material.
  • aluminium alloy is intended also to reduce the weight.
  • Steel is selected as the material of the casing to secure high strength.
  • the casing 12 contains a pair of gears 20 and 21 engaged with each other as pumping components.
  • the gears 20 and 21 are provided with shafts 22 & 23, and 24 & 25 respectively on both sides.
  • These shafts 22 to 25 are supported rotatably by bearings 28 & 27 and 28 & 29 as bushings fitted in the cover 13 and the mounting flange 14.
  • These bearings 26 to 29 are protruded at their inner ends to some extent from the cover 13 and the mounting flange 14, to form protrusions 26a, 27a, 28a and 29a.
  • the shaft 25 on one side of said gear 21 is protruded outward through the mounting flange 14, and can be connected with a power source outside the gear pump 10.
  • an oil seal 30 is fitted, to seal the clearance between the shaft 25 and the mounting flange 14.
  • a seal block 31 is provided between the inside wall of the casing 12 and the tooth tops of the gears 20 and 21.
  • the outside curved surface of the seal block 31 is formed to suit the inside wall surface of the casing 12, and inwardly curved surfaces are formed inside to suit the outside contours of the gears 20 and 21.
  • a high pressure area 33 sectioned by a seal member 32, and the high pressure area 33 communicates to the delivery side of the gears 20 and 21 through a radial high pressure introducing hole 34 and an axial high prssure groove 35 formed in the seal block 31.
  • Said seal block 31 is almost equal to the overall width of the chamber in the casing 12 containing the gears 20 and 21 as can be seen from Fig. 2 . Therefore, the seal block 31 is limited in its axial movement by the inside wall surfaces of the cover 13 and the mounting flange 14, but is arranged to be able to move radeally to some extent in the range between the inside wall surface of the casing 12 and the tooth tops of the gears 20 and 21.
  • the gears 20 and 21 are made of steel to maintain the strength, and are made to be somewhat more narrow than the overall width in said casing 12.
  • clearances are formed between the side surfaces of the gears and the cover 13 and the mounting flange 14, by narrowing the width of the gears 20 and 21, and in the clearances, side plates 36 and 37 made of steel are provided.
  • the side plate 38 is positioned between the cover 13 and the side surfaces of the gears 20 and 21 facing it, while the side plate 37 is positioned between the mounting flange 14 and the side surfaces of the gears 20 and 21 facing it.
  • the side plate 36 consists of a central portion 36a and branching portions 36b and 36c.
  • the central portion 38a is positioned between said protrusions 26a and 28a of the bearings 26 and 28, and the branching portions 36b and 38c are formed to suit the circumferences of the protrusions 26a and 28a.
  • the inside diameter of the curved surfaces 36d and 36e formed by the inward curves of the central portion 38a and the branching portions 36b and 36c is made a little larger thah the outside diameter of the protrusions 26a and 28a of the bearings 28 and 28, and at points P and Q, said curved surfaces 38d and 36e contact the protrusions 26a and 28a.
  • Said points P and Q can be selected freely as far as they contact the circumferences of the bearings 26 and 28 at one point each to control the radial movement.
  • the distance S between the points P and Q is only required to be longer than the clearance l 2 between the bearings 26 and 28.
  • the distance S between both the points P and Q satisfies the following relation with the distance l 1 between the axial centers 0 1 and 0 2 of the shafts 22 and 24 and with the distance l 2 between the bearings 28 and 28.
  • the outwardly curved surfaces of said branching portions 36b, 36c, 37b and 37c of the side plates are the same in form as the outside contours of the gears 20 and 21, viz. as the inwardly curved surfaces of the seal block. 31, and support the inwardly curved surfaces of the seal block 31.
  • the outwardly curved surfaces of the side plates 36 and 37 keep arcs dimensionally somewhat smaller than the outside contours of the gears 20 and 21, when the curved surfaces 38d, 36e, 37d and 37e of the side plates 36 and 37 are supported by the circumferential surfaces of the protrusions 26a to 29a of the bearings 26 to 29.
  • pressure areas 40 and 41 sectioned by seal members 38 and 39 are formed in the inside wall portions of the cover 13 and the mounting flange 14 respectively adjacent to the side plates 36 and 37.
  • the pressure medium is sucked toward the suction side of the chamber in the casing 12 through an axial passage 43 from an inlet port 42 provided at-one side of the cover 13 (see Fig.1), and is carried toward the delivery side by the gears 20 and 21 rotating mutually in the other directions.
  • the pressure medium carried as mentioned above is fed from the high pressure groove 35 formed in the seal block 31 through an axial passage 44 formed in the cover 13 and an outlet port 45 opening toward the other side of the cover 13(see Fig. 1), to an actuator not illustrated.
  • said high pressure acts also on the pressure area 33 at the rear of the seal block 31 through the high pressure introducing hole 34, and the seal block 31, being loaded with the high pressure on the rear side, is pressed against the tooth tops of the gears 20 and 21.
  • the seal block 31 is shaved off on the inwardly curved surfaces by the tooth tops of the gears 20 and 21, and the tooth tops of the gears 20 and 21 slightly bite the seal block 31, for good sealing of the tooth tops of the gears 20 and 21.
  • the depth of bite by the tooth tops of the gears 20 and 21 into the seal block 31 is as far as the inwardly curved surfaces of the seal block 31 are supported in contact with the outwardly curved surfaces of the side plates 38 and 37.
  • the seal block 31 cannot be positioned, and furthermore, the tooth tops of the gears 20 and 21 cannot be sealed, to lower the pump efficiency.
  • the inside diameter of the curved surfaces 36d, 36e, 37d and 37e of the seal blocks is made beforehand larger than the outside diameter of the protrusions of the bearings 26 to 29, and one point is selected at the position where each side plate does not play, for pressure contact with said protrusions only at the pressure contact point.
  • said pressure contact points of the curved surfaces 36d and 38e are most desirable to be so selected that the distance S between the pressure contact point P and Q satisfies the relation of l 2 ⁇ S ⁇ l 1 with the distance l 1 between the axial centers 0 1 and 0 2 of the shafts 22 and 24 and with the clearance l 2 between both the bearings 26 and 28.
  • the cover 13 and the mounting flange 14 contract, and therefore the clearance l 2 between the bearings supported by them becomes shorter than that at room temperature.
  • the gears and side plates made of steel are smaller in the coefficient of contraction than the cover and the mounting flange made of aluminium alloy, the correlation between the gears and the side plates on one hand and the cover and the mounting flange on the other hand becomes irregular.
  • the inside diameter of the curved surfaces 50d and 50e of the side plate 50 is made larger than the outside diameter of the protrusions of the bearings 28 to 29, and said curved surfaces 50d and 50e are arranged not to contact said protrusions during assembling.
  • a sufficiently large constriction 50f is formed, to correspond to said high pressure groove 35.
  • constriction 50f decreases the rigidity of the branching portions 50b and 50c at the portion corresponding to the constriction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
EP19820305754 1981-10-31 1982-10-28 Zahnradpumpe oder -motor Withdrawn EP0081902A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP16331481U JPS5867994U (ja) 1981-10-31 1981-10-31 ギヤポンプ又はモ−タ
JP163314/81 1981-10-31

Publications (1)

Publication Number Publication Date
EP0081902A1 true EP0081902A1 (de) 1983-06-22

Family

ID=15771474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820305754 Withdrawn EP0081902A1 (de) 1981-10-31 1982-10-28 Zahnradpumpe oder -motor

Country Status (2)

Country Link
EP (1) EP0081902A1 (de)
JP (1) JPS5867994U (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1095025C (zh) * 1997-04-24 2002-11-27 丹福斯有限公司 流体机械
CN112709692A (zh) * 2020-12-29 2021-04-27 西安精密机械研究所 一种提高海水泵容积效率的轴向补偿机构以及海水泵

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4585730B2 (ja) * 1999-07-30 2010-11-24 日立オートモティブシステムズ株式会社 歯車ポンプ及び歯車ポンプの組立方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2993450A (en) * 1957-11-09 1961-07-25 Robert Bosch G M B H Fa Gear pump
US3472170A (en) * 1965-10-12 1969-10-14 Otto Eckerle High pressure gear pump or motor with compensation for play and wear
GB1311868A (en) * 1969-10-30 1973-03-28 Dewandre Co Ltd C Gear pumps
GB1428654A (en) * 1972-02-25 1976-03-17 Renold Ltd Gear pumps

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2993450A (en) * 1957-11-09 1961-07-25 Robert Bosch G M B H Fa Gear pump
US3472170A (en) * 1965-10-12 1969-10-14 Otto Eckerle High pressure gear pump or motor with compensation for play and wear
GB1311868A (en) * 1969-10-30 1973-03-28 Dewandre Co Ltd C Gear pumps
GB1428654A (en) * 1972-02-25 1976-03-17 Renold Ltd Gear pumps

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1095025C (zh) * 1997-04-24 2002-11-27 丹福斯有限公司 流体机械
CN112709692A (zh) * 2020-12-29 2021-04-27 西安精密机械研究所 一种提高海水泵容积效率的轴向补偿机构以及海水泵
CN112709692B (zh) * 2020-12-29 2023-02-17 西安精密机械研究所 一种提高海水泵容积效率的轴向补偿机构以及海水泵

Also Published As

Publication number Publication date
JPS5867994U (ja) 1983-05-09

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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

AK Designated contracting states

Designated state(s): DE FR GB

17P Request for examination filed

Effective date: 19831209

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

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Withdrawal date: 19840702

RIN1 Information on inventor provided before grant (corrected)

Inventor name: TERUYAMA, HIDEO