US3814122A - Device for preventing foaming of oil - Google Patents

Device for preventing foaming of oil Download PDF

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Publication number
US3814122A
US3814122A US00305584A US30558472A US3814122A US 3814122 A US3814122 A US 3814122A US 00305584 A US00305584 A US 00305584A US 30558472 A US30558472 A US 30558472A US 3814122 A US3814122 A US 3814122A
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US
United States
Prior art keywords
oil
pressure chamber
oil tank
pressure
discharge
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 - Lifetime
Application number
US00305584A
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English (en)
Inventor
S Akaike
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.)
Hitachi Astemo Ltd
Original Assignee
Atsugi Motor Parts 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 Atsugi Motor Parts Co Ltd filed Critical Atsugi Motor Parts Co Ltd
Application granted granted Critical
Publication of US3814122A publication Critical patent/US3814122A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/047—Preventing foaming, churning or cavitation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/4673—Plural tanks or compartments with parallel flow
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y10T137/7764—Choked or throttled pressure type
    • Y10T137/7765—Pilot valve within main valve head

Definitions

  • anoil pump usually a vane pump
  • the revolving speed of the engine e.g.,'an internal combustion engine
  • Y 500 to 7,000 rpm revolutions per minute
  • the present invention uses an 0 intermediate pressure chamber between the outlet of an oil pump, supplying pressure oil to the hydraulic .power unit, and an oil tank surrounding the oil pump,
  • FIG. 1 is a sectional view of a' hydraulic power unit for-automobiles, according to the present-invention;
  • FIG.2 is'a front view of the hydraulic power unit;
  • FIG. 3 is a partially cut away front view of the hydraulic power unit; t FIG. 4 is a sectional view taken along the line IVIV of'FIG. 3; and
  • the surplus oil is passed to an oil tank through a by-pass type flow-rate control valve, for ensuring the constant oil flow to the members being controlled, regardless of the revolving speed of the automobile-driving engine.
  • the foaming of the oil is accompanied with unpleasant noise, which is referred to as relief noise".
  • the relief noise is particularly annoying when the vane pump is driven at a high speed without ha'ving'any load to the hydraulic power unit, because sustantially the entire discharge from the vane pump is released "through the narrow gap of the flow-rate control valve under such conditions.
  • foamed oil is drawn into the vane pump from the oil tank, it tends to disturb the lubrication of the pump and to cause cavitation which may lead to accelerated wearing of the pump.
  • an object of the present invention is to obviate the aforesaid difficulties of the conventional hydraulic power units.
  • FIG. 5- is a sectionalview similar to FIG. 4, illustrating the open position of a flow-rate control valve.
  • the oil pump 5 may be a vane pump, and in such a case, a rotor (not shown) of the vane pump is connected to the inner end of the rotary shaft 3.
  • the pulley 4 may be driven by a part of the output from automobile-driving engine (not shown).
  • the oil pump 5 has an inlet port 6 and adischarge port 7.
  • An oil-tight cover 8 encloses the oil pump 5, with a spacing therefrom. The cover 8 is secured to the body 2 while inserting an oil-tight packing 9 therebetween,
  • an oil tank 10 is formed by using the spacing between the oil pump 5 and the cover 8.
  • the cover 8 has an oil inlet opening 1 l, which is normatters from oil being supplied to the hydraulic power unit.
  • the oil pump 5 has a hollow boss defining a passage 14 communicating with the outlet port .7 of the pump.
  • the passage-l4 of the boss 15 communicates with a corresponding hole passing through the
  • the nipple 17 has an orifice 17a formed at the end facing the outlet port7'of the'pum'p 5.
  • Pressure o'il delivered to the loads (not shown) of the hydraulic power unit through an orifice 17a returns to theoil tank 10 at a return path coupling 20 which is sealingly secured to the cover 8.
  • the coupling 20 has a strainer 21 which'is disposed within the oil tank 10.
  • a flow-rate control valve 40 which includes a cylindrical valve hole 23- bored in the boss 15, so as to extend in parallel with the passage l4'thereof, as shown in FIGS. 3 to 5.
  • the opening of the port 22 at the valve hole 23 is comparatively wide and extends nearly through a semi-circle about-the longitudinal central axis of the valve hole 23.
  • a piston valve is slidably fitted in the cylindrical valve hole 23, so as to selectively communicate thev port 22 with an annular groove 28 bored on the peripheral surface of the valve hole 23 with a short distance from the port 22, as shown in FIGS. 4 and 5.
  • the piston valve 25 is biased by a coiled spring 24 in a direction to interrupt the communication between the port 22 and the annular groove 28.
  • the piston valve 25 has a stopper 27 which limits the movement of the piston valve 25,
  • Another annular oil-tight packing 26 is disposed between the boss 15 and the body 2, for preventing the leakage of the pressure oil through the boundary therebetween.
  • the piston valve 25 has an axialhole 31, which extends coaxially with the longitudinal central axis of the piston valve 25 and has an open endat the back of the piston valve 25.
  • Lateral holes 32 extend at right angles to the longitudinal axial center-line of the piston valve, so as to communicate the axial hole 31 with the port 29 toward the chamber 30 at the lower end of the hole 31, as shown in FIGS. 4 and 5.
  • a valve seat 33 is screwed in the open top end of the axial hole 31.
  • the coiled spring 36 acts to normally urge the valve holder 35 upwards so as to'keep a central passage of the valve seat 33 as blocked or closedby the spherical valve 34.
  • valve hole 23 such communication between the valve hole 23 and the nipple 17 is provided by a passage 37 formed through 'the'wall of the valve hole 23 and a radial hole 38 bored through the wall of the nipple 17, as shown in FIGSQ4 and 5.
  • the pressure difference between theline pressure at the downstream of the orifice 17a of the nipple 17 and the discharge pressure of the oil pump 5 at the discharge port 7 is a applied across the piston valve 25.
  • the pressure acting on the lower surface of the piston valve 25 increases, so as to raise the valve 25 for widening the passage from the lower portion of the valve hole 23 to the annular groove 28, as shown in FIG. 5.
  • the amount of by-pass oil toward the intermediate pressure chamber 30 increases. .
  • the oil delivered to the intermediate pressure chamber 30 is gradually released to the oil tank 10 through the orifice 30a. Accordingly, as the discharge pressure from the oil pump 5 is-raised, the amount of the pressure oil discharged to the oil tank 10 increases, so as to keep the .line pressure downstream of the orifice 17a substantially at a desired constant level.
  • a stay bolt 39 extends through the intermediate pressure chamber 30, so as to securely hold the cover 8 and the mounting bracket 18 against the open top ofthe chamber 30 for closing it.
  • Such stay bolt 39 is not essential in the present invention, andit may be dispensed with if the open top of the chamber 30 is properly closed by the nipple 17 and associated fastening means.
  • the line pressure downstream of the orifice 17a is kept substantially at the desired constant level.
  • the oil being by-passed is not directly released to the oil tank 10, but it is once introduced to the lower portion of the intermediate pressure chamber 30, and then allowed to proceed into the oil tank through the orifice 30a at the upper portion of the chamber 30.
  • the foaming of theoil and the relief noise are completely eliminated.
  • the inventor has found that favorable results can be obtained when the differential pressure across the orifice 30a, i.e., between the intermediate pressure chamber 30 and the oil tank 10, is 0.5 Kg/cm to 3 Kglcm If the orifice 30a is too large, the differential pressure across it cannot be maintained in the aforesaid range, so that the desired function of the intermediate pressure chamber cannot be achieved. On the other hand, if the orifice 30a is too small, resistance-to the by-pass flow of the oil becomes excessively high, and the desired flow-rate control characteristic and the desired constant line-pressure characteristic cannot be obtained. 7
  • a foampreventing device to be used in a hydraulic power unit in cooperation with a by-pass type flow-rate control valve, for keeping a constant line pressure regardless of the revolving speed and discharge pressure of an oil pump.
  • The'foam-preventing device also eliminates relief noise by prohibiting the by-pass oil from foaming.
  • the foam-preventing device of the present invention is effective in eliminating detrimental effects of foamed oil on the lubrication of an oil pump
  • a device forpreventing foaming of oil being bypassed in an automobile hydraulic power unit which latter includes a by-pass type flow-rate control valve which selectively by-passes part of the discharge from an oil pump into an oil tank so as to ensure desired oil flow toward loads of the unit, the device comprising an intermediate pressure chamber communicating with the outlet of said control valve through one port and having one orifice formed through a wall of said pressure chamber which faces said oil tank, whereby the entirety of the discharge part from said oil pump is guided to flow toward said oil tank through said orifice of the pressure chamber, the pressure of the discharge being regulated at a level between that at the discharge from said oil pump and that in said oil tank.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Control Of Transmission Device (AREA)
  • Rotary Pumps (AREA)
US00305584A 1972-04-26 1972-11-10 Device for preventing foaming of oil Expired - Lifetime US3814122A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1972049296U JPS5715361Y2 (de) 1972-04-26 1972-04-26

Publications (1)

Publication Number Publication Date
US3814122A true US3814122A (en) 1974-06-04

Family

ID=12826944

Family Applications (1)

Application Number Title Priority Date Filing Date
US00305584A Expired - Lifetime US3814122A (en) 1972-04-26 1972-11-10 Device for preventing foaming of oil

Country Status (6)

Country Link
US (1) US3814122A (de)
JP (1) JPS5715361Y2 (de)
CA (1) CA960110A (de)
DE (1) DE2255986C3 (de)
FR (1) FR2181643B1 (de)
GB (1) GB1391225A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4478189A (en) * 1982-12-08 1984-10-23 Lucas Industries Fuel injection system
US4862995A (en) * 1987-06-04 1989-09-05 Steve Faria Oil discharge diffuser

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0238512U (de) * 1988-09-06 1990-03-14
JP3688752B2 (ja) * 1995-04-04 2005-08-31 株式会社 神崎高級工機製作所 作業車両における油供給装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2667893A (en) * 1950-02-03 1954-02-02 Air Associates Inc Relief valve
US2870781A (en) * 1956-06-22 1959-01-27 Hydraulic Unit Specialities Co Relief valve
US2984187A (en) * 1956-02-20 1961-05-16 Thompson Ramo Wooldridge Inc Power steering pump
US3205789A (en) * 1964-05-05 1965-09-14 Melvin A Mandelko Cylinder unit

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR875610A (fr) * 1940-09-20 1942-09-29 Messerschmitt Boelkow Blohm Dispositif pour empêcher la formation de mousse dans les étranglements traversés par des liquides, en particulier dans les soupapes de sûreté des installations à huile sous pression à bord des avions
JPS5034251B1 (de) * 1969-04-01 1975-11-07

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2667893A (en) * 1950-02-03 1954-02-02 Air Associates Inc Relief valve
US2984187A (en) * 1956-02-20 1961-05-16 Thompson Ramo Wooldridge Inc Power steering pump
US2870781A (en) * 1956-06-22 1959-01-27 Hydraulic Unit Specialities Co Relief valve
US3205789A (en) * 1964-05-05 1965-09-14 Melvin A Mandelko Cylinder unit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4478189A (en) * 1982-12-08 1984-10-23 Lucas Industries Fuel injection system
US4862995A (en) * 1987-06-04 1989-09-05 Steve Faria Oil discharge diffuser

Also Published As

Publication number Publication date
FR2181643B1 (de) 1978-03-03
GB1391225A (en) 1975-04-16
AU4827372A (en) 1974-05-16
JPS497392U (de) 1974-01-22
DE2255986B2 (de) 1979-01-11
DE2255986C3 (de) 1979-09-06
DE2255986A1 (de) 1973-11-08
CA960110A (en) 1974-12-31
FR2181643A1 (de) 1973-12-07
JPS5715361Y2 (de) 1982-03-31

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