EP0253133A2 - Innenzahnrad-Hydraulikpumpe - Google Patents

Innenzahnrad-Hydraulikpumpe Download PDF

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Publication number
EP0253133A2
EP0253133A2 EP87108293A EP87108293A EP0253133A2 EP 0253133 A2 EP0253133 A2 EP 0253133A2 EP 87108293 A EP87108293 A EP 87108293A EP 87108293 A EP87108293 A EP 87108293A EP 0253133 A2 EP0253133 A2 EP 0253133A2
Authority
EP
European Patent Office
Prior art keywords
insert
pump
gear
pump according
gears
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.)
Granted
Application number
EP87108293A
Other languages
English (en)
French (fr)
Other versions
EP0253133A3 (en
EP0253133B1 (de
Inventor
Adriano Marzocchi
Paolo Marzocchi
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT87108293T priority Critical patent/ATE60825T1/de
Publication of EP0253133A2 publication Critical patent/EP0253133A2/de
Publication of EP0253133A3 publication Critical patent/EP0253133A3/en
Application granted granted Critical
Publication of EP0253133B1 publication Critical patent/EP0253133B1/de
Expired legal-status Critical Current

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    • 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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the invention refers to a hydraulic internal gear pump, comprising an internally toothed crown gear and an externally toothed driving gear which are mounted for an axial rotation within a suitable housing, the internally toothed crown gear meshing with the externally toothed driving gear, and being provided with inserts located in the region where the gears are apart from each other, and which operate by contacting the teeth of said gears, whereby the suction (low pressure) zone is separated from the delivery (high pressure) zone of the pump.
  • the sealing inserts In the pumps of known type, the sealing inserts generally are all arranged at the delivery side of the pump, where they act both on the externally toothed gear and on the internally toothed crown gear. It ensues that any friction produced by the sealing inserts and the heat resulting therefrom will subject the pump to unbalanced localized stresses, which impair the pump operation at any high pressure value.
  • Some embodiments are also known, according to which the sealing inserts operate in substantially opposite positions with respect to the axes of rotation of the gears, thus solving the problem of friction and heat distribution to the pump components. These embodiments however have the drawback of producing a friction having a very high value, since each sealing insert acts on both of the gears, at the suction side and at the delivery side of the pump.
  • the invention suggests a hydraulic pump with internal gears, in which the sealing inserts are so made that they act only on a section of the externally toothed gear, at the suction side, and only on a section of the internally toothed gear, at the delivery side, so that the advantage arising from a friction having a limited value is added to the advantage of the proper distribution to the pump components of the heat resulting from any such friction.
  • a first insert in the suction zone of the pump a first insert is provided, which is fixedly secured to the static portion of the pump, and is so constructed that also thanks to a suitable rotatable support for the externally toothed gear, this gear will operate, owing to the pressure in the delivery circuit, by intimately contacting the inward side of the said stationary insert.
  • a second insert is provided on the extension of the body of the said stationary insert and is tightly connected thereto, the said second insert being movable, and being positively sealed in an intimate manner against a sufficient number of teeth of the internally toothed crown gear by the bias of a preload spring and by the pressure in the delivery circuit of the pump.
  • only one sealing insert is provided, which is intermediately fulcrumed about a stationary pin parallel to the gear axes, and which is so long as to have its extremities respectively reaching the delivery zone and the suction zone of the pump.
  • At least one preload spring urges against the crown gear the arm of the insert which is turned toward the delivery zone, and which is so urged also by the pressure in the delivery circuit, since the said arm is to a suitable extent longer than the opposite arm which operates by contacting the externally toothed gear.
  • Compensating shoes may be provided on at least one of the active end sections of the said movable or swingable sealing insert.
  • the shaft 5 shall be rotatably supported in such a manner that any radial stresses to which the gear wheel 4 is subjected due to the high pressure in the delivery circuit of the pump, will be not counterbalanced entirely, in view of the fact that the invention, as it will be more fully stated later, counts also on such stresses in order to assure the proper operation of the pump at any high pressure.
  • references A and M and by dash-and-dot lines there are respectively designated the apertures through which the suction and the delivery duct formed, for example, in one of the cover plates 6 or 6 ⁇ , open into the hollow space defined by the gears 3,4, respectively upstream and downstream of the area in which the said gears are seen to be mutually in mesh.
  • the shaft 5 for the gear 4 is driven in rotation in the fixed direction indicated by arrow F.
  • a moon crescent-shaped insert 9 extending from the suction zone to the delivery zone, is provided within the hollow space defined by the gears 3,4, and is fixedly secured to static components of the pump, in accordance with any one of the embodiments which by way of examples will be disclosed hereinafter.
  • the inward side of insert 9 is so shaped that a section thereof, as shown at 109, situated at a short distance from the suction zone A of the pump, will result into contact with a sufficient number of teeth of the gear wheel 4.
  • the rest of the profile of insert 9 is preferably suitably spaced both from the said gear 4 and from the crown gear 3, but for a possible section designated by 209.
  • the pressure difference between the zones A and M and the dynamic reaction between the gears 3,4 will subject the gear wheel 4 to such a radial stress having a component in the direction of arrow F1, that an intimate contact of said gear with the section 109 of insert 9 is assured, and the separation of said zones A and M is guaranteed, even at any high pressure value in the delivery circuit of the pump.
  • the shaft 5 will be rotatably supported in such a manner as to aid the aforesaid condition, for example, by the provision of a proper play in correspondence of the shaft supports.
  • the insert 9 could operate by contacting the gear wheel 4 with the interposition of a shoe (see hereinafter) tightly secured in a removable manner to the inward side of insert 9, so as to form the previously disclosed sealing surface 109.
  • the insert 9 may be made from any material or composition of materials fit for the purpose for which the said insert is intended. As shown in figure 2, the insert 9 is secured by means of a pair of pins 10,10 ⁇ to the cover plates 6,6 ⁇ of the pump.
  • the pins are passed through the wear plates 11,11 ⁇ which perform their function by contacting the gears of the pump, and which are located underneath the cover plates 6,6 ⁇ with the interposition of annular seals 12,12 ⁇ having in plan view a configuration of the type as shown by way of an example in figure 1, such as to delimit at their interior sealed areas into which the pressure of the delivery circuit of the pump is led through bores 13,13 ⁇ made in the said wear plates, so that the said wear plates will be axially urged against the gears 3,4 whereby to assure the seal and automatically adjust the wear to which the wear plates are subjected.
  • the insert 9 may be formed of one piece with one of the wear plates 11,11 ⁇ or, according to the modified embodiment shown in figure 3, the said insert 9 may be formed of one piece with the pump casing 1 ⁇ incorporating the bottom cover plate 6.
  • the pump will be provided only with the wear plate 11 ⁇ and the relative cover plate 6 ⁇ .
  • the plates 11,11 ⁇ will have a thickness fit for the use for which they are intended, even not proportional to the thickness shown in the drawings.
  • the insert 9 may be removably secured by means, for example, of screws, to one or both of the wear plates 11,11 ⁇ .
  • the outward side of the end section of insert 9, which terminates in correspondence of the delivery zone M of the pump, is shaped as shown at 309 or in any other suitable manner, such that with the said end section there can be associated under sealing conditions and with the possibility of an outward movement, an additional insert 14 having its outward side shaped as shown at 114, in such a manner that it will intimately operate on a sufficient number of teeth of the crown gear 3 so as to affect them throughout their depth, and that between the insert 14 and the end section 309 there will be a small cavity 15 which is fluid-tight relative to the low pressure zone A, and is connected in any suitable manner, for example, to ducts, such that the pressure in the delivery circuit M will flow into the said cavity, whereby the said pressure will guarantee the required sealing of 14 against 3.
  • a small preload spring 16 for example of the leaf type, received in a housing 17 formed between the components 14 and 309, guarantees the required sealing of insert 14 against the crown gear 3. It is evident that since the insert 9 is stationary, it is not adversely conditioned by the movements of insert 14. Consequently, also the relative movements of gears 3,4 do not impair the performance of the sealing inserts.
  • the friction areas of inserts 9 and 14 are widely apart from each other, in substantially diametrically opposite positions with respect to the gear wheel 4. Therefore, any heat generated at the said friction areas 109 and 114 is evenly distributed to the pump assembly, thus avoiding any localized stresses which instead occur in the pumps of known type. This condition guarantees a safe operation of the pump even at any high pressure in the delivery circuit M.
  • the insert 9 ⁇ is of a length which is substantially limited to the length of the sealing surface 109 and is fixedly secured to stationary components of the pump, for example according to one of the possibilities as disclosed in connection with the embodiment shown in figure 1.
  • the end of insert 9 ⁇ which is turned toward the high pressure zone, cooperates with the associated end section of an additional insert 19 which is intermediately fulcrumed about a pin 20 fixedly secured to the cover plates 6-6 ⁇ and parallel to shaft 5, the axis of said pin being the center of the said articulated surfaces 18, the tight connection of which is ensured by the provision of a linear seal 21.
  • insert 19 is so shaped that it will intimately contact a sufficient number of teeth of the crown gear 3, against which it is urged by the bias of a preload spring 16 ⁇ and by the pressure in the delivery zone M of the pump.
  • the insert 19 can operate on the crown gear 3 either by directly contacting same or with the interposition of a shoe 22 made of any suitable material, and which can be easily replaced whenever it is worn out.
  • the shoe 22 can be removably secured to insert 19, for example, by means of screws, or, as shown in figure 5, it can be associated with the said insert so as to be allowed to perform an articulated movement around an axis parallel to the fulcrum 20, whereby to uniformly adapt itself to the crown gear 3 even when the angle of incidence of insert 19 with this crown gear changes.
  • the stationary insert 9 has been eliminated and replaced with the insert 19 ⁇ which is now so sized that it has its extremities reaching the delivery zone M and the suction zone A respectively, and which is intermediately fulcrumed about a pin 20 ⁇ , similarly to the embodiment shown in figure 5.
  • the arm 119 ⁇ of insert 19 ⁇ which is turned toward the delivery side is to a suitable extent longer than the opposite arm 219 ⁇ which is turned toward the suction side A, the whole in such a manner that the action of the pressure in the delivery circuit will force the said insert to turn in anti-clockwise direction as viewed in figure 6, thus assuring the required contact of 109 ⁇ with 3 and of 209 ⁇ with 4.
  • Numeral 16 ⁇ denotes a preload spring which guarantees the fluid-tight cooperation of insert 19 ⁇ with the gears in the initial step of starting the pump.
  • this insert may work on at least one of the two gears or on both, with the interposition of a compensating shoe.
  • a shoe 23 is arranged on the arm 219 ⁇ of insert 19 ⁇ with the interposition of at least one seal 24 and an expanding elastic means 25, as well as in such a manner that also the pressure in the delivery circuit by penetrating between a portion of members 23,219 ⁇ , will guarantee the steady cooperation of said shoe with the externally toothed gear.
  • the surface of these inserts which does not contact the gears 3,4 may be suitably finned and/or roughened.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP87108293A 1986-06-18 1987-06-09 Innenzahnrad-Hydraulikpumpe Expired EP0253133B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87108293T ATE60825T1 (de) 1986-06-18 1987-06-09 Innenzahnrad-hydraulikpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT1249986 1986-06-18
IT12499/86A IT1189767B (it) 1986-06-18 1986-06-18 Pompa idraulica ad ingranaggi interni capace di operare a pressioni an che molto elevate

Publications (3)

Publication Number Publication Date
EP0253133A2 true EP0253133A2 (de) 1988-01-20
EP0253133A3 EP0253133A3 (en) 1988-08-17
EP0253133B1 EP0253133B1 (de) 1991-02-06

Family

ID=11140883

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87108293A Expired EP0253133B1 (de) 1986-06-18 1987-06-09 Innenzahnrad-Hydraulikpumpe

Country Status (4)

Country Link
EP (1) EP0253133B1 (de)
AT (1) ATE60825T1 (de)
DE (1) DE3767934D1 (de)
IT (1) IT1189767B (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2299134A (en) * 1995-03-23 1996-09-25 Sauer Sundstrand Ltd Internal gear pump
WO1998025029A1 (en) * 1996-12-03 1998-06-11 Danfoss A/S Motor pump unit
GB2323636A (en) * 1997-03-27 1998-09-30 Unisia Jecs Corp Compound gear pump and engine hydraulic circuits therewith
US6425747B2 (en) * 1999-12-08 2002-07-30 Luk Lamellen Und Kupplungsbau Gmbh Gearing with mating internal and spur gears
WO2014060137A3 (de) * 2012-10-19 2014-08-28 Robert Bosch Gmbh Innenzahnradpumpe für eine hydraulische fahrzeugbremsanlage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2114874A1 (de) * 1971-03-27 1972-10-12 Dowty Technical Developments Ltd., Brockhampton, Cheltenham (Großbritannien) Hydraulische Verdrängungspumpe
DE2300484A1 (de) * 1973-01-05 1974-07-18 Otto Eckerle Hochdruck-zahnradpumpe
DE2533646C2 (de) * 1975-07-28 1986-04-17 Otto Sion Wallis Eckerle Hochdruck-Zahnradpumpe oder -motor
DE2641278A1 (de) * 1976-09-14 1978-03-16 Voith Getriebe Kg Innenzahnradpumpe
GB1594942A (en) * 1978-01-11 1981-08-05 Smiths Industries Ltd Gear pumps
DE2943768A1 (de) * 1979-10-30 1981-05-14 Breinlich, Richard, Dr., 7120 Bietigheim-Bissingen Innenzahnrad - motoren oder pumpen - aggregat

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2299134A (en) * 1995-03-23 1996-09-25 Sauer Sundstrand Ltd Internal gear pump
GB2299134B (en) * 1995-03-23 1998-06-24 Sauer Sundstrand Ltd Internal gear pump
WO1998025029A1 (en) * 1996-12-03 1998-06-11 Danfoss A/S Motor pump unit
KR100391007B1 (ko) * 1996-12-03 2003-07-12 댄포스 아/에스 모터 펌프 유니트
GB2323636A (en) * 1997-03-27 1998-09-30 Unisia Jecs Corp Compound gear pump and engine hydraulic circuits therewith
GB2323636B (en) * 1997-03-27 1999-05-12 Unisia Jecs Corp Compound gear pumps and engine hydraulics circuits using same
US6045338A (en) * 1997-03-27 2000-04-04 Unisia Jecs Corporation Compound gear pumps and engine hydraulic circuits using same
US6425747B2 (en) * 1999-12-08 2002-07-30 Luk Lamellen Und Kupplungsbau Gmbh Gearing with mating internal and spur gears
WO2014060137A3 (de) * 2012-10-19 2014-08-28 Robert Bosch Gmbh Innenzahnradpumpe für eine hydraulische fahrzeugbremsanlage

Also Published As

Publication number Publication date
EP0253133A3 (en) 1988-08-17
IT1189767B (it) 1988-02-04
IT8612499A1 (it) 1987-12-18
ATE60825T1 (de) 1991-02-15
EP0253133B1 (de) 1991-02-06
DE3767934D1 (de) 1991-03-14
IT8612499A0 (it) 1986-06-18

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