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EP0020354B1 - Mehrfache Hydropumpenstruktur mit gemeinsamen Gehäuse - Google Patents

Mehrfache Hydropumpenstruktur mit gemeinsamen Gehäuse Download PDF

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Publication number
EP0020354B1
EP0020354B1 EP79900879A EP79900879A EP0020354B1 EP 0020354 B1 EP0020354 B1 EP 0020354B1 EP 79900879 A EP79900879 A EP 79900879A EP 79900879 A EP79900879 A EP 79900879A EP 0020354 B1 EP0020354 B1 EP 0020354B1
Authority
EP
European Patent Office
Prior art keywords
pump
fluid
end plate
fluid delivery
passage
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
Application number
EP79900879A
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English (en)
French (fr)
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EP0020354A1 (de
EP0020354A4 (de
Inventor
Robert L. Shelby
Bertwin E. Behrends
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.)
Caterpillar Inc
Original Assignee
Caterpillar Tractor Co
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 Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Publication of EP0020354A4 publication Critical patent/EP0020354A4/de
Publication of EP0020354A1 publication Critical patent/EP0020354A1/de
Application granted granted Critical
Publication of EP0020354B1 publication Critical patent/EP0020354B1/de
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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations

Definitions

  • This invention relates to a manifolded, lTl ul- tiple hydraulic pump structure which may be used wherever two or more rotary pumps may be driven by a single drive shaft. It is expressly disclosed herein as applied to a heavy vehicle having a hydraulic transmission and a hydraulic torque converter; but is not limited to such application.
  • Typical of such hydraulic systems are those in heavy vehicles, such as crawler tractors, wheel loaders, and large capacity dump trucks. Such vehicles commonly have a hydraulic transmission and a hydraulic torque converter.
  • the hydraulic system for such a vehicle requires a charging pump for the hydraulic transmission, a fluid conduit from the pump to the transmission, a charging pump for the torque converter, a fluid conduit from the torque converter charging pump to the torque converter, scavenging pumps, scavenging conduits from the transmission and the torque converter to the scavenging pumps, fluid delivery lines to both charging pumps, and return lines from the scavenging pumps to the sump.
  • US-A-2,533,320 discloses a pump structure having a pump casing assembly consisting of a plurality of rotary pump casing elements disposed in face abutting relationship, with sealing means between the casing elements and means detachably securing the casing elements in assembled, face abutting relationship.
  • the casing elements cooperate to define a first pump cavity and a second pump cavity, with a single drive shaft extending through an opening in a drive end plate of the casing elements and through both pump cavities in each of which it carries a rotary pump member.
  • the casing elements also are provided with a plurality of manifold passages.
  • a hydraulic pump assembly comprising: a pump casing assembly consisting of a plurality of rotary pump casing elements disposed in face abutting relationship, including a fluid delivery end plate and a drive end plate, at opposite ends of the casing assembly; the casing elements cooperating to define a first pump cavity and a second pump cavity, and a series of aligned pump drive shaft openings connecting the pump cavities; a drive shaft journalled in the drive shaft openings which has an end portion extending through an opening in the drive end plate and adapted for operative connection to driving means; a first rotary pump in the first pump cavity and a second rotary pump in the second pump cavity, each of the pumps having a pump member mounted on the drive shaft, a plurality of manifold passages formed in the casing elements, including a first fluid inlet passage for admitting fluid to the first pump, a first fluid delivery passage from the first pump and having a port in the fluid delivery end plate, a second fluid inlet passage for admitting fluid to the second pump, and having
  • the improved pump structure comprises a pump casing assembly indicated generally at 20, which includes a charging pump subassembly, indicated generally at 21, and a scavenging pump subassembly, indicated generally at 22.
  • the pump casing elements forming the charging pump subassembly include a drive end plate 23 and a first set of casing elements consisting of a torque converter charging pump element 24, a transmission charging pump casing element 25, and a charging subassembly transi- tio casing element 26.
  • the scavenging pump subassembly 22 consists of a second set of casing elements including a scavenging inlet casing element 27, a scavenging pump casing element 28, and a fluid delivery end plate 29.
  • the casing elements 23-26 of the charging pump subassembly 21 are aligned by means of a pair of alignment pins 30 which make a snug sliding fit in alignment sleeves 31 and screw into threaded bores 32 in the transition casing element 26.
  • Assembly of the charging pump subassembly 21 is by means of four long machine screws 33 which have their heads seated in counterbores 34 in a transition face 35 of the transition casing element 26, and the machine screws 33 extend through aligned bores 36 in the casing elements 24, 25 and 26, and screw into threaded bosses 37 which project from the outer surface of the drive end plate 23.
  • the three casing elements of the scavenging pump subassembly 22 are aligned with one another and with the charging pump subassembly 21 by means of guide pins 38 in the scavenging inlet casing element 27 and the fluid delivery end plate 29 which seat in sockets 39 in the scavenging pump casing element 28 and in the transition face 35 of the transition casing element 26.
  • the three casing elements of the scavenging pump subassembly 22 are assembled by means of four long machine screws 40 which have their heads recessed in counterbores 41 formed in a front face 42 of the subassembly 22, and the machine screws 40 extend through aligned bores 43 in the casing elements 27 and 28 and screw into threaded bores 44 in the fluid delivery end plate 29.
  • the fluid delivery end plate 29 is provided with mounting flanges 45 in which there are bolt holes 46; and there are also four peripheral mounting bosses 47 on the transitional pump casing element 26, and aligned with the bosses 47 on the pump casing elements 27, 28 and 29 are mounting bosses 48, and continuous bolt holes 49 extend through the aligned bosses 47 and 48.
  • the bolt holes 46 and the bolt holes 49 receive mounting bolts 50 and 51, respectively, by means of which the subassemblies 21 and 22 are independently secured to a housing wall H of a bevel gear housing which is a part of the vehicle drive.
  • the housing wall H has threaded holes H1 into which the mounting bolts 50 are screwed to secure the scavenging pump subassembly 22 to the wall H and there are also threaded bolt holes H2 in the wall H which receive the mounting bolts 51 that secure the charging pump subassembly 21 to the wall.
  • the threaded bolts 51 also detachably secure the two subassemblies 21 and 22 in face abutting relationship as illustrated in Fig. 1.
  • guide pins 52 which are aligned with the guide pins 38 in the fluid delivery end plate 29 seat in holes H3 in the housing wall H.
  • the pump casing elements 23 and 24 cooperate to define a torque converter charging pump cavity 53; and the casing element 24 also cooperates with casing elements 25 and 26 to define a transmission charging pump cavity 54 (Fig. 6).
  • the three casing elements of the subassembly 22 cooperate to define scavenging pump cavities 55 and 55a (Fig. 9).
  • the pump casing elements of the charging pump subassembly 21 are provided with a series of aligned pump drive shaft openings 56, 57 and 58 which are provided with respective sleeve bearings 56a, 57a and 58a; and in the scavenging pump subassembly 22 are aligned pump drive shaft openings 59, 60 and 61 which are provided, respectively, with sleeve bearings 59a, 60a and 61 a.
  • a charging pump drive shaft segment 62 is journalled in the sleeve bearings 56a-58a, while a scavenging pump drive shaft segment 63 is journalled in the bearings 59-61; and the two drive shaft segments have an axially interfitting drive connection provided by a slot 62a at the inner end of the drive shaft segment 62 and a lug 63a at an end of the drive shaft segment 63 which makes a sliding fit in the slot 62a.
  • the drive shaft segment 62 has an end portion 62b which extends through the drive shaft opening 56 in the drive end plate 23 which is adapted for operative connection to driving means through a drive pulley assembly, indicated generally at 64, by means of which a drive pulley 65 is mounted upon the drive shaft segment 62 through a splined connection 62c.
  • the drive pulley assembly forms no part of the subject matter of the present invention, so it is not described in detail.
  • idler shaft openings 66, 67 and 68 which are provided with respective sleeve bearings 66a-68a; and alongside the drive shaft openings 59, 60 and 61 in the subassembly 22 are idler shaft openings 69, 70 and 71 which are provided, respectively, with sleeve bearings 69a-71 a.
  • a charging pump idler shaft 72 is journalled in the sleeve bearings 66a-68a, while an idler shaft 73 is journalled in the sleeve bearings 69a-71a.
  • meshing gear pump members 74 and 75 which form a rotary, gear type torque converter charging pump
  • intermeshing gear pump members 76 and 77 which provide a rotary transmission charging pump
  • intermeshing gear pump members 78 and 79 which provide a first rotary scavenging pump
  • intermeshing gear pump members 80 and 81 in the scavenging pump cavity 55a provide a second rotary scavenging pump.
  • the first rotary scavenging pump 78-79 scavenges fluid from a torque converter C
  • the second rotary scavenging pump 80-81 scavenges fluid from a transmission T.
  • the present hydraulic pump structure 20 is manifolded to provide a charging fluid inlet passage 82 (Figs. 1, 5, 6 and 8); a torque converter charging delivery passage 83 (Figs. 3, 5, 6 and 7); a transmission charging fluid delivery passage 84 (Figs. 2, 7 and 8); a torque converter scavenging inlet passage 85 (Figs. 1, 2, 9 and 10); a transmission scavenging fluid inlet passage 86 (Figs. 2 and 9); and a scavenging fluid outlet passage 87 (Figs. 2 and 9).
  • the wall is provided with holes which are seen in Figs. 2 and 3 to be in register with the ports for the passages 83, 84, 86 and 87, and said holes are identified in Fig. 3 by the respective numerals H4, H5, H6 and H7.
  • annular seals 88 which are mounted in grooves in certain of the casing element faces in abutment with the adjacent casing element faces and with the wall H, seal the entire structure against leakage from the pump cavities.
  • leakage from the charging delivery passages 83 and 84 is minimized or provided by means of annular seals 89 (see Figs. 6 and 8) at the abutting faces between the casing elements through which those passages pass.
  • the pump structure 20 can be used in any hydraulic system having two rotary pumps that can be driven off the same shaft.
  • a particularly advantageous use is illustrated in Fig. 11, where the pump structure 20 is mounted on a housing wall H of a gear housing G that is in direct communication with the housing for the hydraulic transmission T of a heavy vehicle.
  • This permits a transmission charging conduit 90 to conduct fluid from the transmission charging delivery passage 84 to the transmission through the gear housing and also permits a transmission scavenging conduit 91 to extend through the gear housing. This protects such conduits from damage that could result from their being mounted in exposed locations, and also causes any leakage from the conduits to remain inside the housing.
  • the entrance to the charging fluid inlet passage 82 is very close to, and directly in line with the outlet from a screen F which is also mounted upon the wall H, so that a charging fluid conduit 92 may be straight and only a few inches long.
  • the torque converter charging fluid conduit 93 must go outside the gear housing, its connection to the pump through the hole H4 is inside the housing, and thus more protected than would otherwise be the case.
  • a portion of the gear housing G provides a sump S to receive scavenged fluid from the passage 87 through the conduit 94, for return to the pump through the screen F.
  • 95 is a scavenging fluid conduit which connects the torque converter to the scavenging inlet passage 85 of the scavenging pump subassembly 22.

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

Claims (7)

1. Hydraulische Pumpenanordnung, die folgendes aufweist: eine Pumpengehäuseanordnung (20) bestehend aus einer Vielzahl von Drehpumpengehäuseelementen (23-29) angeordnet in Stirnseiten-Anstoßbeziehung, und zwar einschließlich einer Strömungsmittellieferndplatte (29) und einer Antriebsendplatte (23) an entgegengesetzt liegenden Enden der Gehäuseanordnung, wobei die Gehäuseelemente (23-29) zur Bildung eines ersten Pumpenhohlraums (54) und eines zweiten Pumpenhohlraums (55a) zusammenarbeiten, und wobei ferner eine Reihe von ausgerichteten pumpenantriebswellenöffnungen (56-61) die Pumpenhohlräume verbinden; eine in den Antriebswellenöffnungen (56-61) drehbar gelagerte Antriebswelle (62-63), die einen sich durch eine Öffnung (56) in der Antriebsendplatte (23) erstreckenden Endteil 62b aufweist und zur Betriebsverbindung mit Antriebsmitteln geeignet ist (64); eine erste Drehpumpe (76-77) in dem ersten Pumpenhohlraum (54) und eine zweite Drehpumpe (80-81) im zweiten Pumpenhohlraum (55a), wobei jede der Pumpen ein auf der Antriebswelle (62-63) angeordnetes Pumpenglied (76 oder 80) aufweist, eine Vielzahl von Sammeldurchlässen (82, 84, 86, 87) ausgebildet in den Gehäuseelementen (23-29), einschließlich eines ersten Strömungsmitteleinlaß-Durchlasses (82) zum Einlaß von Strömungsmittel zur ersten Pumpe (76-77), einen ersten Strömungymittellieferdurchlaß (84) von der ersten Pumpe (76-77) und mit einer Öffnung in der Strömungsmittellieferendplatte (29), einen zweiten Strömungsmitteleinlaß-Durchlaß (86) zum Einlaß von Strömungsmittel zur zweiten Pumpe (80-81), und mit einer Öffnung in der Strömungsmittellieferendplatte (29), und mit einem Strömungsmittelauslaß-Durchlaß (87) von der zweiten Pumpe (80-81) mit einer Auslaßoffnung in der Strömungsmittellieferendplatte (29); Abdichtmittel (88-89) zwischen den Gehäuseelementen (23-29); Mittel (33, 44, 50, 51) zur lösbaren Befestigung der Gehäuseelemente (23-29) in zusammengebauter Stirnflächen-Anschlagsbeziehung; dadurch gekennzeichnet, daß die Gehäuseelemente (23-29) in ersten (21) und zweiten (22) Unteranordnungen angeordnet sind, wobei die erste Unteranordnung (21) die Antriebsendplatte (23) und einen ersten Satz von Gehäuseelementen (24-26) aufweist, die den ersten Pumpenhohlraum (54) definieren und die den ersten Strömungsmitteleinlaß-Durchlaß (82) enthalten, und wobei ein erster Teil des ersten Strömungumittellieferdurchlasses (84) in einem offenen Lieferende (84a) endet, und wobei die zweite Unteranordnung (22) die Strömungsmittellieferendplatte (29) aufweist und einen Satz von Gehäuseelementen (24 und 28), die einen zweiten Teil des ersten Strömungsmittellieferdurchlasses (84) enthalten, der ein offenes Aufnahmeende in Verbindung mit dem offenen Lieferende (84a) der ersten Unteranordnung aufweist, wobei der zweite Satz von Gehäuseelementen (27 und 28) den zweiten Pumpenhohlraum (55a) definiert und auch den Strömungsmittelauslaß-Durchlaß (87) enthält, und wobei die Antriebswelle gesonderte Segmente (62 und 63) in jeder Unteranordnung (21 und 22) umfaßt, und wobei die Segmente (62 und 63) eine axial zusammenpassende Antriebsverbindung (62a-63a) besitzen.
2. Pumpenanordnung nach Anspruch 1, wobei die Pumpen (76-77 und 80-81) Zahnradpumpen sind, wobei ein erstes Zahnrad (76 oder 80) jeder Pumpe auf der Antriebswelle (62-63) angeordnet ist, und wobei die Gehäuseelemente (23-29) mit ausgerichteten Leerlaufwellenöffnungen (66-71) ausgestattet sind, wobei Leerlaufwellenmittel (72 und 73) in den Leerlaufwellenöffnungen angeordnet sind, und wobei ein zweites Zahnrad (77-81) jeder Pumpe sich auf den Leerlaufwellenmitteln (72-73) befindet.
3. Pumpenanordnung nach Anspruch 1 oder 2, wobei erste befestigte Mittel (50) die zweite Unteranordnung (22) an einem Träger (H) befestigen, und wobei zweite Befestigungsmittel (51) die erste Unteranordnung (21) an demselben Träger (H) befestigen und ebenfalls Mittel vorsehen zur lösbaren Befestigung der beiden Unteranordnungen (21 und 22) in anstoßender Beziehung mit den verbundenen Antriebswellensegmenten.
4. Pumpenanordnung nach Anspruch 1 oder 2, wobei Mittel (50 und 51) vorgesehen sind zur Befestigung der Gehäuseanordnung mit der Strömungsmittellieferendplatte (29), und zwar anstoßend an einer Wand (H) eine Gehäuses (G), welches direkt mit hydraulischen Leistungselementen (T) in Verbindung steht, wobei die Wand (H) ein Loch (H5) in Ausrichtung mit der Öffnung des ersten Strömungsmittellieferdurchlasses (84) aufweist, ferner ein Lock (H6) ausgerichtet mit dem Eingang zum zweiten Strömungsmitteleinlaß-Durchlaß (86) und mit einem Loch (H7) ausgereichtet mit der Öffnung des Strömungsmittelauslaß-Durchlasses (87), wodurch sämtliche Strömungsmittelverbindungen zwischen der Pumpenstruktur (20) und -dem hydraulischen Leistungselement (T) innerhalb des Gehäuses (G) angeordnet sein können.
5. Pumpenanordnung nach Anspruch 1 zur Verwendung in einem Hydrauliksystem für ein schweres Fahrzeug, welches einen hydraulischen Drehmomentwandler (C) und ein hydraulisches Getriebe (T) aufweist, wobei der erste Pumpenhohlraum (54) einen Getriebeladehohlraum vorsieht und der zweite Pumpenhohlraum (55a) einen ersten Spülpumpenhohlraum, wobei die Pumpengehäuseelemente (23-26) ebenfalls einen Drehmomentwandler Pumpenladehohlraum (53) definieren, und wobei die Elemente (27-29) einen zweiten Spülpumpenhohlraum (55) definieren, wobei eine Vielzahl von Sammeldurchlässen (82-87) in den Gehäuseelementen (23-29) ausgebildet ist, um hydraulisches Strömungsmittel einzulassen und Strömungsmittel von allen Hohlräumen zu liefern, und wobei in den entsprechenden Ladepumpenhohlräumen (53 und 54) eine Rotor-Drehmomentwandlerladepumpe (74-75) und eine Rotor-Getriebeladepumpe (76-77) vorgesehen sind, und wobei ferner erste und zweite Dreh-Spülpumpen (78-79 und 80-81) in den jeweiligen Pumpenhohlräumen (55a und 55) vorgesehen sind, und wobei ferner jede der Pumpen ein Pumpenglied (74, 76, 78 oder 80) aufweist, und zwar angeordnet auf dem zugehörigen Antriebswellensegment (62, 63), wobei der erste Strömungsmitteleinlaß-Durchlaß (82) Strömungsmittel zu den beiden Ladepumpen (74-75 und 76-77) eintreten läßt, wobei ein den Strömungsmittellieferdurchlaß (83) ladender Drehmomentwandler Strömungsmittel von der Drehmomentwandlerladepumpe (74-75) liefert und eine Öffnung in der Strömungsmittellieferendplatte (29) aufweist, wobei der Strömungsmittellieferdurchlaß (84) Strömungsmittel von der Getriebeladepumpe (76-77) liefert, wobei ferner ein erster Spülströmungsmitteleinlaß-Durchlaß (85) Strömungsmittel von Drehmomentwandler (C) zur ersten Spülpumpe (78-79) einläßt, wobei der zweite Strömungsmitteleinlaß-Durchlaß (86) Strömungsmittel vom Getriebe (T) zu der zweiten Spülpumpe (80-81) eintreten läßt, wobei schließlich der Strömungsmittelauslaß-Durchlaß (87) Strömungsmittel von den Spülpumpen liefert.
6. Pumpenanordnung nach Anspruch 5, wobei ein direktes kurzes verbindendes Rohr (92) zwischen einem Strömungsmittelfilter (F) und der Einlaßöffnung des Ladeströmungsmitteleinlaß-Durchlasses (82) vorgesehen ist.
7. Hydraulisches System für ein schweres Fahrzeug, welches einen hydraulischen Drehmomentwandler (C) und ein hydraulisches Getriebe (T) aufweist, und zwar einschließlich einer Pumpenanordnung gemäß einem der Ansprüche 1 bis 6.
EP79900879A 1978-12-26 1978-12-26 Mehrfache Hydropumpenstruktur mit gemeinsamen Gehäuse Expired EP0020354B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1978/000239 WO1980001401A1 (en) 1978-12-26 1978-12-26 Manifolded multiple hydraulic pump structure

Publications (3)

Publication Number Publication Date
EP0020354A4 EP0020354A4 (de) 1980-11-14
EP0020354A1 EP0020354A1 (de) 1981-01-07
EP0020354B1 true EP0020354B1 (de) 1983-07-13

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP79900879A Expired EP0020354B1 (de) 1978-12-26 1978-12-26 Mehrfache Hydropumpenstruktur mit gemeinsamen Gehäuse

Country Status (5)

Country Link
EP (1) EP0020354B1 (de)
JP (1) JPS55501062A (de)
BR (1) BR7808767A (de)
IT (1) IT1127744B (de)
WO (1) WO1980001401A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19647052C2 (de) * 1996-11-14 1999-06-10 Bosch Gmbh Robert Einrichtung zum Fördern von Arbeitsmedien einer Brennkraftmaschine eines Kraftfahrzeuges
RU179974U1 (ru) * 2017-06-14 2018-05-29 Александр Владимирович Печников Устройство для нанесения двухкомпонентных составов

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2533320A (en) * 1949-01-04 1950-12-12 Du Pont Rotary gear-type metering pump
US2751846A (en) * 1952-04-18 1956-06-26 Clark Equipment Co Rotary pump or motor
FR1205452A (fr) * 1957-04-15 1960-02-03 Borg Warner Groupe de pompes à engrenage avec carter en cuvette formant réservoir
US3101673A (en) * 1961-06-16 1963-08-27 Thompson Ramo Wooldridge Inc Implement and power steering pump
US3314369A (en) * 1965-10-05 1967-04-18 Kawasaki Kokuki Kogyo Kabushik Dual gear pumps
GB1252746A (de) * 1967-12-23 1971-11-10
FR2121296A5 (de) * 1971-01-08 1972-08-18 Massey Ferguson Services Nv

Also Published As

Publication number Publication date
WO1980001401A1 (en) 1980-07-10
IT7928097A0 (it) 1979-12-18
JPS55501062A (de) 1980-12-04
BR7808767A (pt) 1981-06-30
IT1127744B (it) 1986-05-21
EP0020354A1 (de) 1981-01-07
EP0020354A4 (de) 1980-11-14

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