EP0093917A1 - Machine à engrenages réversible (moteur ou pompe) - Google Patents

Machine à engrenages réversible (moteur ou pompe) Download PDF

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Publication number
EP0093917A1
EP0093917A1 EP83103941A EP83103941A EP0093917A1 EP 0093917 A1 EP0093917 A1 EP 0093917A1 EP 83103941 A EP83103941 A EP 83103941A EP 83103941 A EP83103941 A EP 83103941A EP 0093917 A1 EP0093917 A1 EP 0093917A1
Authority
EP
European Patent Office
Prior art keywords
seal
pressure
receiving
machine according
support ring
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
EP83103941A
Other languages
German (de)
English (en)
Other versions
EP0093917B1 (fr
Inventor
Wilhelm Dworak
Hayno Dipl.-Ing. Rustige
Günter Wolff
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0093917A1 publication Critical patent/EP0093917A1/fr
Application granted granted Critical
Publication of EP0093917B1 publication Critical patent/EP0093917B1/fr
Expired 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
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a gear machine according to the preamble of the main claim.
  • the shaft bores are connected to one another in the area of the seals.
  • This design of the seal and the resulting pressure fields has the disadvantage that the compensation of the liquid pressure forces acting on the sealing plates is inadequate and that the machine is subject to malfunctions when operating with return pressure.
  • the machine according to the invention with the characterizing features of the main claim has the advantage that the compensation of the pressure forces acting on the sealing plate is so perfected that the machine runs smoothly even when operating with return pressure.
  • FIG. 1 shows a longitudinal section through a gear motor
  • FIG. 2 shows a section along II-II according to FIG. 1
  • FIG. 3 shows an individual part
  • FIG. 4 shows a section along IV-IV according to FIG. 3
  • FIGS. 5, 6 and 7 show another individual part in a top view , Side view and bottom view
  • FIG. 8 shows a section along VIII-VIII according to FIG. 5
  • FIG. 9 shows the individual parts according to FIGS. 3 to 8 in the installed state
  • FIG. 10 shows a further individual part in plan view
  • FIG. 11 shows a section along XI-XI Figure 10
  • Figure 12 is a diagram of the pressure fields.
  • 10 denotes the housing of a gear motor or a gear pump, which is closed on both sides by covers 11, 12.
  • the interior 13 of the housing 10 is formed by two intersecting bores 14, 15 so that it takes the form of an 8.
  • bush-shaped bearing bodies 16 to 19 are arranged in pairs, which have aligned central bores 20 to 23 in pairs.
  • the shaft journals 24, 25 of an externally toothed gear 26 are mounted, in the bearing bodies 18, 19 or their bores 22, 23, the shaft journals 27, 28 of a gear 29, which with the gear 26 combs in external engagement.
  • a shaft extension 31 Connected to the shaft journal 25 of the gearwheel 26 is a shaft extension 31 which penetrates to the outside through a bore 22 formed in the cover 12 and serves to drive the pump or to deliver a torque in engine operation.
  • the two ends of the bores 20, 22 are connected by a channel 33 formed in the cover 11, which leads to a bore 34 penetrating the cover.
  • the gearwheel 29, together with its shaft journals 27, 28, is penetrated by a continuous bore 35 which also has a connection to the bore 34.
  • a channel 37 leads from the bore 32 in the cover 12 to the bore 23 in the bearing body 19. the ends of the shaft journals or the ends of the bores 20-23 are relieved of the load on the bore 34 and the container.
  • FIGS. 10 and 11 most clearly show one of the bearing bodies 16 to 19, for example the bearing body 16. All of the bearing bodies are of the same design.
  • the bearing body 16 has on its end face facing the cover 11 an annular groove 39 which runs at a short distance a from the bore 20 and which, compared to the flattened side 40 of the bearing body, has an approximately segment-shaped, relatively wide extension 41 which extends to the edge of the bearing body.
  • the groove 39 On its area facing the flat side, the groove 39 has a narrow outlet 44 which extends to the flat side 40.
  • the cross section of the groove 39 can be seen in FIG. 9.
  • the groove has a rectangular cross section and a rounded bottom 39 '.
  • a seal is arranged, which consists of a support ring 46 made of plastic and a sealing body 47 made of rubber.
  • the support ring 46 is shown in detail in FIGS. 3 and 4, the sealing body 47 in FIGS. 5 to 8.
  • the support ring 46 has approximately the shape of a pair of glasses and has an approximately sector-like extension 49, 50 on its two diametrically opposite regions, which fits into the extensions 41 on the bearing bodies 16 to 19.
  • the two circular parts are connected by a web 51 which fits into the outlet 44 of the bearing body.
  • the support ring 46 - as shown in FIG. 4 - is U-shaped.
  • the sealing body 47 is inserted into this U-shaped recess. This is shown in Figures 5 to 8. It has the same shape as the support ring 46, but has a different cross section, which is shown in FIG. With its upper broad part 53, the sealing body fits into the U-shaped recess of the support ring 46.
  • the sealing body 53 In its central region, the sealing body 53 has two transverse webs 54, 55, the width of which corresponds to that of the support ring.
  • a central, longer web 56 connects to the webs 54, 55.
  • the web 56 In the installed state, the web 56 forms two spaces 57, 58 with the groove 39, which lie on the bottom of the groove, but which are connected to one another in the operating state when the support ring together with the sealing ring are pressed against the cover. This also indicates the installation position of the two parts in the groove.
  • the support ring 46 bears on the cover 11, 12, while the sealing body 47 faces the groove base.
  • the sealing body 47 has on its diametrically opposite sides circular sector-shaped extensions 60, 61 which fit into extensions 49, 50 of the support ring.
  • the cross section of the sealing body in the area of the extension 60, 61 results from the section according to FIG. 6, from which it can be seen that the web 56 runs out laterally in this area.
  • two axially identical bores 65, 66 penetrate into the interior 13 of the housing and open in the region of the gearwheels 26, 29. These holes are used to supply or discharge the pressure medium.
  • the gear machine works as a gear motor and high-pressure pressure medium is supplied to the bore 65. This is fed through the rotating gears along the circumference of the bore 66 now serving as an outlet.
  • the high-pressure medium penetrates through an approximately triangular gusset 67, which is formed between the interior 13 of the housing and the bearing bodies 16-19 and extends over the entire height thereof, into the gap which is formed between the bearing bodies and the covers is.
  • a first pressure field 68 ', 68''and a second pressure field 46 are now built up on the high-pressure side between the support ring 46 and the end faces of the bearing bodies, which corresponds exactly to the entire surface of the support ring 46 and lies below it - that is, between the grooves 39, 41 44 on the bearing bodies and the support ring 46 - which pressure field if acted upon by high pressure via the grooves 42, 43 on the outer circumference of the bearing body.
  • the support rings 46 are pressed together with the seals 47 by liquid pressure against the covers 11, 12.
  • the pressure prevailing in the outlet bore 66 prevails at the third pressure fields 70 ', 70' 'lying opposite the pressure fields 68', 68 '', because these fields have an approximately triangular gusset 72 which lies between the interior 13 of the housing and the bearing bodies, have connection to bore 66.
  • the outlet pressure can be very low, but also high if a second gear motor is connected to the bore 66.
  • Fourth pressure fields are formed in the annular spaces 74-75 located between the support ring 46 and the bearing bores 20-23. These are always loaded by the leakage oil pressure prevailing in the bores 33, 34, which can be a maximum of 5-8 bar.
  • the bearing bodies 16-19 are brought into sealing contact with the gear side surfaces by the four pressure fields described.
  • the force to be compensated by the annular pressure fields 74, 75 results from an area on the face of the gearwheel, which lies approximately between the root circle of the gearwheels and the diameter of the bores 20-23 times the leakage oil pressure prevailing there.
  • the gear machine is reversible, ie the high pressure can also be supplied at the bore 66, and the low pressure side is then at the bore 65.
  • the high pressure fields are now building up at 70, 71 and again under the support ring surface, the low pressure fields are at 68, 69.
  • the effect is exactly the same as above wrote. It is of course possible to arrange pressurized bearing bodies only on one side of the gearwheels, while the other two bearing bodies are not pressurized and rest rigidly on the cover. It is also possible to store the shaft journals directly in the housing, i.e.
  • FIG. 12 again clearly shows the position of the four pressure fields, 68, 69 and support ring surface 46 (all cross-hatched) being acted upon by the same pressure (high pressure), surfaces 70, 71 by the return pressure (hatched in the right direction) and the ring surfaces (left-handed) hatched) from the leakage oil pressure.
EP83103941A 1982-05-12 1983-04-22 Machine à engrenages réversible (moteur ou pompe) Expired EP0093917B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823217753 DE3217753A1 (de) 1982-05-12 1982-05-12 Reversierbare zahnradmaschine (pumpe oder motor)
DE3217753 1982-05-12

Publications (2)

Publication Number Publication Date
EP0093917A1 true EP0093917A1 (fr) 1983-11-16
EP0093917B1 EP0093917B1 (fr) 1987-07-08

Family

ID=6163311

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83103941A Expired EP0093917B1 (fr) 1982-05-12 1983-04-22 Machine à engrenages réversible (moteur ou pompe)

Country Status (4)

Country Link
US (1) US4465444A (fr)
EP (1) EP0093917B1 (fr)
BR (1) BR8302454A (fr)
DE (2) DE3217753A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2585083A1 (fr) * 1985-07-16 1987-01-23 Hydroperfect Internal Hpi Dispositif a action hydraulique pure pour la compensation hydrostatique de pompes et moteurs hydrauliques du type a engrenage
EP0411225A1 (fr) * 1989-08-03 1991-02-06 Permco, Inc Lubrification des tourillons pour pompe à engrenages

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4636155A (en) * 1984-06-29 1987-01-13 Commercial Shearing, Inc. Hydraulic seal having U-shaped gasket and a plurality of plastically deformable posts
DE3766245D1 (de) * 1987-04-24 1990-12-20 Vickers Systems Gmbh Zahnradpumpe oder -motor fuer fluide.
DE8707256U1 (fr) * 1987-05-20 1988-09-22 Robert Bosch Gmbh, 7000 Stuttgart, De
EP0293585B1 (fr) * 1987-05-30 1991-06-12 Robert Bosch Gmbh Machine réversible à engrenages (pompe ou moteur)
IT1220330B (it) * 1988-04-08 1990-06-15 Sauer Sundstrand Spa Macchina ad ingranaggi fungente da pompa o motore
US6979185B2 (en) * 2000-08-01 2005-12-27 Kaempe Staffan I Bi-rotational pump/hydraulic actuator
JP2005163676A (ja) * 2003-12-03 2005-06-23 Seiko Epson Corp ギヤポンプ、及び液体噴射装置
CN102465870B (zh) * 2010-11-08 2014-12-17 西安航空动力控制科技有限公司 一种带有轴向密封补偿的行星齿轮泵
RU2477388C2 (ru) * 2010-12-21 2013-03-10 Государственное образовательное учреждение высшего профессионального образования "Братский государственный университет" Шестеренный насос
US11624361B1 (en) 2022-02-16 2023-04-11 Caterpillar Inc. Anchored low pressure gear pump wear plate

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1210824A (en) * 1966-12-05 1970-11-04 Borg Warner Reversible pump or motor
FR2193455A5 (fr) * 1972-07-14 1974-02-15 Trw Inc
FR2434264A1 (fr) * 1978-08-24 1980-03-21 Commercial Shearing Pompe ou moteur rotatif a engrenage et a plaques de butee
GB2033478A (en) * 1978-11-03 1980-05-21 Bosch Gmbh Robert Rotary positive-displacement fluidmachines

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2866416A (en) * 1950-06-16 1958-12-30 Borg Warner Pressure loaded pump
US2654325A (en) * 1950-08-11 1953-10-06 Borg Warner Gear type pump with pressure loaded bushing and wear insert element
US3270680A (en) * 1964-12-17 1966-09-06 Kingston Products Corp Pressure loaded gear pump
US3292551A (en) * 1965-04-26 1966-12-20 Clark Equipment Co Gear pump or motor
US3473476A (en) * 1967-11-13 1969-10-21 Lear Siegler Inc Gear pump seal
SU879023A1 (ru) * 1979-09-25 1981-11-07 Кировоградский Ордена "Знак Почета" Завод Тракторных Гидроагрегатов Им. Хху Съезда Кпсс Шестеренна гидромашина внешнего зацеплени

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1210824A (en) * 1966-12-05 1970-11-04 Borg Warner Reversible pump or motor
GB1210825A (en) * 1966-12-05 1970-11-04 Borg Warner Reversible positive-displacement fluid pump or motor
FR2193455A5 (fr) * 1972-07-14 1974-02-15 Trw Inc
FR2434264A1 (fr) * 1978-08-24 1980-03-21 Commercial Shearing Pompe ou moteur rotatif a engrenage et a plaques de butee
GB2033478A (en) * 1978-11-03 1980-05-21 Bosch Gmbh Robert Rotary positive-displacement fluidmachines

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2585083A1 (fr) * 1985-07-16 1987-01-23 Hydroperfect Internal Hpi Dispositif a action hydraulique pure pour la compensation hydrostatique de pompes et moteurs hydrauliques du type a engrenage
EP0211723A1 (fr) * 1985-07-16 1987-02-25 Hydroperfect International Hpi Dispositif à action hydraulique pure pour la compensation hydrostatique de pompes et moteurs hydrauliques du type à engrenage
EP0411225A1 (fr) * 1989-08-03 1991-02-06 Permco, Inc Lubrification des tourillons pour pompe à engrenages

Also Published As

Publication number Publication date
DE3217753A1 (de) 1983-11-17
US4465444A (en) 1984-08-14
BR8302454A (pt) 1984-01-17
EP0093917B1 (fr) 1987-07-08
DE3372395D1 (en) 1987-08-13

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