EP0029356B1 - Hydraulische Rotationsmaschine mit kontrollierbar ausgeglichenem Druckfeld - Google Patents

Hydraulische Rotationsmaschine mit kontrollierbar ausgeglichenem Druckfeld Download PDF

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Publication number
EP0029356B1
EP0029356B1 EP19800304096 EP80304096A EP0029356B1 EP 0029356 B1 EP0029356 B1 EP 0029356B1 EP 19800304096 EP19800304096 EP 19800304096 EP 80304096 A EP80304096 A EP 80304096A EP 0029356 B1 EP0029356 B1 EP 0029356B1
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EP
European Patent Office
Prior art keywords
gears
pressure gradient
pressure
fluid
port
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
EP19800304096
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English (en)
French (fr)
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EP0029356A1 (de
Inventor
Charles John Bowden
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.)
SPX Corp
Original Assignee
General Signal Corp
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Publication date
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Application filed by General Signal Corp filed Critical General Signal Corp
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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
    • F04C15/0042—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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter

Definitions

  • This invention concerns improvements in rotary hydraulic machines and, in particular, though not exclusively, concerns improvements in hydraulic gear pumps.
  • Gear pumps and motors are well known hydraulic machines that are used in numerous hydraulic. systems where a relatively fixed displacement of fluid flow is desired.
  • Such gear type machines typically include a pair of meshed gears mounted for rotation in a housing, with the housing having low and high pressure ports disposed on opposite sides of the meshed gear teeth.
  • the gears are thrust toward the low pressure port by the high pressure fluid, thereby generating large loads on the gears, their shafts, the bearings or bushings which support the shafts, and within the housing itself.
  • These relatively large loads can place excessive strains on the aforesaid components, thereby accelerating ordinary wear and tear and contributing to the premature failure of the machine.
  • a common feature of all of the above referenced attempts is that the fluid passages which carry the counterbalancing high pressure fluid are all in direct communication with the highest pressure fluid, i.e. the fluid at the high pressure port.
  • the highest pressure fluid i.e. the fluid at the high pressure port.
  • additional, large vertical loads are placed upon the gears thereby subjecting them to increased wear and tear.
  • a pressure gradient controlled rotary hydraulic machine comprising a low pressure port and a high pressure port, a gear chamber, and a pair of meshed gears rotatably mounted in the chamber for receiving fluid from one port and expelling said fluid from the other port, characterized in that the pressure gradient control includes an interdental fluid passage adjacent said gears in fluid communication with the spaces between adjacent teeth of said gears and so isolated from direct fluid communication with said high and low pressure ports, as to maintain in operation pressures substantially intermediate the pressures at said high and said low pressure in the spaces between adjacent teeth in fluid communication within said interdental fluid passage.
  • the pressure gradient fluid passageway is provided for in a pair of end or wear plates on opposite ends of the gears.
  • the wear plates have a chamfer on the side of the plate facing the gear, adjacent the peripheral edge of the wear plate.
  • the chamfer in the edge of the wear plate is isolated from direct fluid communication with the high and low pressure ports by the wear plate itself and other sealing means that are well known to one skilled in the art. Accordingly, an interdental fluid communication channel is established adjacent the tips of the teeth of the gears.
  • the interdental channel provides a pressure path across the teeth of the gears.
  • the chamfers in the wear plates are leakage paths which lower the pressure acting on the gears near the high pressure side of the pump and raise the pressure acting on the gears near the low pressure side of the pump thereby counterbalancing a portion of the horizontal component of the force acting on the gears without substantially increasing the vertical force on the gears.
  • the length dimensions of the chamfer can be relatively small due to the advantage gained from placing it at the tips of the teeth of the gears.
  • the pressure gradient control is preferably positioned in a replaceable wear plate, one or more such controls could also be included directly in the housing of the pump and/or in the end or adapter covers, or at some other point on the wear plate closer to the hub of the gears.
  • a rotary hydraulic machine in the form of a gear pump 10 includes a central housing 11 having a low pressure or inlet port (not shown) and a high pressure or outlet port indicated by reference numeral 3.
  • housing 11 In housing 11 are two meshing gears 14,15 that are respectively rotatably mounted on driven gear shaft 6 and idler shaft 7.
  • Gear shafts 6 and 7 are mounted in bushing or bearing assemblies 18 which in turn are positioned in adapter cover 13 and end cover 12.
  • Drive shaft 6 extends beyond adapter cover 13 where it is connectable to a power source (not shown).
  • Centering plates 16, 17 serve to align the bearing assemblies 18, gear shafts 6 and 7, covers 12, 13 as well as central housing 11 with one another.
  • Adjacent the end faces of gears 14 and 15 are a pair of wear plates 20, 21 which carry the pressure gradient control chamfer passageway 24 of the preferred embodiment of the invention.
  • the wear plate 20 has a general figure-eight configuration with openings 22, 23 for accommodating the gear shafts 6 and 7.
  • the gear facing surface 34 of wear plate 20 is usually faced with bronze or other suitable wearing material.
  • the gear teeth 30 of gears 14, 15 are partially superimposed on the representation of wear plate 20 in order to illustrate the relative positioning of pressure gradient control chamfer passageway 24.
  • a zone indicated by Roman numeral I designates a portion of the wear plate adjacent the high pressure port.
  • the gear teeth 30 in zone I effectively isolate chamfer 24 from direct fluid communication with the high pressure port 3.
  • the chamfer portion 24 adjacent a plurality of gear teeth 30.
  • the interdental spaces 31 between gear teeth 30 are placed in fluid communication by means of chamfer 24 of wear plate 20. Proceeding further clockwise to a zone designated by Roman numeral III, the interdental spaces 31 are no longer in fluid communication with each other and the gear teeth 30 effectively seal off the low pressure port 4 from fluid communication with chamfer 24.
  • Zone I There is a pressure drop across Zone I due to the restricted fluid passage between the tips of the teeth and the housing.
  • the pressure at the boundary of Zones I and II is at an intermediate value, somewhat less than the outlet pressure.
  • Chamfer 24 transfers that intermediate pressure across to the low pressure side of the gears 14, 15.
  • the vertical loads imposed on gear shafts 6, 7 and bearing assemblies 18 are less than the vertical loads imposed upon those members in the case where the highest pressure fluid, i.e., the fluid at the high pressure outlet 3, is diverted back across the wear plate to balance the force at the high pressure port 3.
  • the interdental spaces 31 of the gears are effectively tied together and acted upon by the intermediate pressure in chamfer 24. Accordingly, the gears themselves are partially pressure balanced horizontally, thereby relieving a portion of the radial load upon the bearing assemblies 18.
  • the pressure gradient control that is achieved by this invention is graphically illustrated in Figure 6.
  • a comparative test was conducted using an ordinary wear plate without any pressure gradient control chamfer (A), one with a chamfer extending into the high pressure port 3 (B), and one having the chamfer illustrated in Figure 2 (C). The test was conducted at the same inlet temperature, output pressures and speed for all three wear plates.
  • test results are indicated in polar coordinates, with 90° corresponding to the centre line of the two gears. Pressures were measured at a number of equally spaced angular locations. Pressure measurements are represented on a percentage of maximum pump output pressure as measured at the discharge port 3.
  • the particular pump used for the comparative test had an inlet port disposed at 18° and a delivery (discharge) port at 205°.
  • the object of the pressure gradient control is to minimize the pressure force applied from the discharge (left) side, and increase the balancing force on the gears in order to thereby reduce the bearing load on the inlet (right) side.
  • the polar graph (A) of a standard wear plate shows relatively little balancing pressure. One can see that the pressure differential on either side of the 90° line changes rapidly and soon falls off to 0°.
  • the wear plate having the chamfer extended to the high pressure port (B) has some balancing force, but the overall applied load is relatively high.
  • the preferred embodiment of the invention (C) has the best overall results, showing lower vertical loads than (B) and increased horizontal balancing force. Those skilled in the art will recognize that the profile of the preferred embodiment (C) can be altered to approach either (A) or (B) by reducing or lengthening the chamfer 24.
  • wear plate 20 The opposite or bearing facing surfaces of the wear plate 20 includes a numeral 3 shaped recess 28 for accommodating a balance seal 29 (partially shown) therein.
  • balance seals and recesses are common elements of wear plates and are thus well known to those skilled in the art.
  • the gear facing side of the wear plate has a relief recess 25 extending between the two gear shaft openings 22, 23.
  • a pair of port recesses 26 are disposed adjacent the portion of the wear plate approximate to the inlet and outlet ports 3, 4.
  • the pressure gradient control could be placed directly into the housing 11 adjacent the tips of the gears 14, 15 or combined with another pressure gradient control in the wear plates.
  • the pressure gradient control could be spaced inwardly from the periphery of the wear plate 20; however, such a configuration would require that the chamfer be longer since the gear teeth are wider. If the gear pump did not have wear plates and the gear teeth were adjacent the end and adapter covers, the pressure gradient control could be placed in the covers or the housing, or in both the housing and the covers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (5)

1. Druckgradientgesteuerte rotierende hydraulische Maschine (10) mit einem Niederdruckanschluß (4), einem Hochdruckanschluß (3), einer Zahnradkammer (11) und zwei miteinander kämmende "Zahnräder" (14, 15), die in der Kammer drehbar gelagert sind und vom einen Anschluß Fluid empfangen und das Fluid über den Anschluß abgeben, dadurch gekennzeichnet, daß die Einrichtung zur druckgradientenabhängigen Steuerung einen interdentalen Fluidkanal (24) aufweist, der im Bereich der Zahnräder angeordnet ist und mit Zahnlücken (31) zwischen einander benachbarten Zähnen der Zahnräder (14, 15) in Strömungsverbindung steht und gegenüber einer direkten Strömungsverbindung mit dem Hoch- und dem Niederdruckanschluß (3, 4) derart isoliert ist, daß er im Betrieb in den zwischen einander benachbarten Zähnen vorhandenen Zahnlücken, die mit dem interdentalen Fluidkanal in Strömungsverbindung stehen, einen Druck aufrechterhält, der im wesentlichen zwischen den an dem Hoch- und dem Niederdruckanschluß (3, 4) vorhandenen Drücken liegt.
2. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß im Bereich mindestens der einen Stirnfläche der genannten Zahnräder (14,15) eine Endplatte (20, 21) vorgesehen und in dieser Endplatte (20, 21) der Fluidkanal (24) für die druckgradientenabhängige Steuerung vorgesehen ist.
3. Maschine nach Anspruch 2, dadurch gekennzeichnet, daß der Fluidkanal (24) für die druckgradientenabhängige Steuerung im Bereich der Spitzen der Zähne (30) der Zahnräder einen abgeschrägten Umfangsteil der Endplatte (20, 21) besitzt.
4. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß die rotierende hydraulisch Maschine (10) ein Gehäuse (11, 12, 13) besitzt, das die Zahnradkammer (11) umschließt und in dem der Fluidkanal (24) für die druckgradientenabhängige Steuerung vorgesehen ist.
5. Maschine nach Anspruch 1 oder 4, dadurch gekennzeichnet, daß die rotierende hydraulische Maschine (10) einen Enddeckel (12) und einen Adapterdeckel (13) besitzt, die auf entgegengesetzten Seiten der Zahnradkammer (11) angeordnet sind, und daß der Fluidkanal (24) für die druckgradientenabhängige Steuerung (24) in mindestens einem dieser Deckel (12, 13) vorgesehen ist.
EP19800304096 1979-11-19 1980-11-14 Hydraulische Rotationsmaschine mit kontrollierbar ausgeglichenem Druckfeld Expired EP0029356B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US9588379A 1979-11-19 1979-11-19
US95883 1979-11-19

Publications (2)

Publication Number Publication Date
EP0029356A1 EP0029356A1 (de) 1981-05-27
EP0029356B1 true EP0029356B1 (de) 1985-05-22

Family

ID=22254026

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19800304096 Expired EP0029356B1 (de) 1979-11-19 1980-11-14 Hydraulische Rotationsmaschine mit kontrollierbar ausgeglichenem Druckfeld

Country Status (5)

Country Link
EP (1) EP0029356B1 (de)
JP (1) JPS5675990A (de)
BR (1) BR8007522A (de)
CA (1) CA1162106A (de)
DE (1) DE3070679D1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0802326B1 (de) * 1996-04-15 2001-07-25 Haldex Barnes GmbH Zahnradmaschine mit kontrollierbar ausgeglichenem Druckfeld
GB2312476B (en) * 1996-04-24 1999-12-08 Sauer Sundstrand Ltd Pressure balance control in gear pumps
CN108425838B (zh) * 2018-04-13 2024-03-19 合肥长源液压股份有限公司 一种可减小齿轮所受径向力的齿轮油泵

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2310078A (en) * 1938-12-24 1943-02-02 Vickers Inc Pump or motor for power transmission
GB541961A (en) * 1939-03-16 1941-12-19 Frederic Mcintyre A metering or spinning pump primarily for use in the manufacture of rayon or other synthetic fibres
US2980028A (en) * 1957-08-19 1961-04-18 Thompson Ramo Wooldridge Inc Gear pump journal and face lubrication
US3833319A (en) * 1973-03-21 1974-09-03 Dowty Hydraulic Units Ltd Positive-displacement liquid-pressure machines and pressure-balanced journal/thrust bushes therefor
AT355916B (de) * 1976-07-13 1980-03-25 Akzo Nv Zahnradpumpe mit verminderter leistungsaufnahme zum foerdern viskoser fluessigkeiten

Also Published As

Publication number Publication date
EP0029356A1 (de) 1981-05-27
DE3070679D1 (en) 1985-06-27
CA1162106A (en) 1984-02-14
JPS5675990A (en) 1981-06-23
BR8007522A (pt) 1981-06-02

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