US3913328A - Oil leakage recycler - Google Patents

Oil leakage recycler Download PDF

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Publication number
US3913328A
US3913328A US487127A US48712774A US3913328A US 3913328 A US3913328 A US 3913328A US 487127 A US487127 A US 487127A US 48712774 A US48712774 A US 48712774A US 3913328 A US3913328 A US 3913328A
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United States
Prior art keywords
chambers
hydraulically actuated
bore
brake apparatus
hydraulic
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
US487127A
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English (en)
Inventor
Ronald J Shaffer
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.)
Westinghouse Air Brake Co
Original Assignee
Westinghouse Air Brake 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 Westinghouse Air Brake Co filed Critical Westinghouse Air Brake Co
Priority to US487127A priority Critical patent/US3913328A/en
Priority to ZA00750620A priority patent/ZA75620B/xx
Priority to CA220,205A priority patent/CA1018467A/en
Priority to DE19752510255 priority patent/DE2510255A1/de
Priority to GB16863/75A priority patent/GB1499014A/en
Priority to BR4290/75A priority patent/BR7503356A/pt
Priority to JP1975094755U priority patent/JPS538871Y2/ja
Application granted granted Critical
Publication of US3913328A publication Critical patent/US3913328A/en
Assigned to BANKERS TRUST COMPANY reassignment BANKERS TRUST COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: U.S. RAILWAY INC.
Assigned to BANKERS TRUST COMPANY reassignment BANKERS TRUST COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMERICAN STANDARD INC., A DE. CORP.,
Assigned to AMERICAN STANDARD INC., A CORP. OF DE reassignment AMERICAN STANDARD INC., A CORP. OF DE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE: 12/29/78 DELAWARE Assignors: WESTINGHOUSE AIR BRAKE COMPANY
Assigned to RAILWAY INC. reassignment RAILWAY INC. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANKERS TRUST COMPANY
Assigned to AMERICAN STANDARD INC. reassignment AMERICAN STANDARD INC. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANKERS TRUST COMPANY
Assigned to CHASE MANHATTAN BANK (NATIONAL ASSOCIATION), THE reassignment CHASE MANHATTAN BANK (NATIONAL ASSOCIATION), THE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RAIL ACQUISITION CORP.
Assigned to WESTINGHOUSE AIR BRAKE COMPANY reassignment WESTINGHOUSE AIR BRAKE COMPANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: AMERICAN STANDARD INC., A DE CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/58—Combined or convertible systems
    • B60T13/581—Combined or convertible systems both hydraulic and pneumatic
    • B60T13/583—Combined or convertible systems both hydraulic and pneumatic using converters
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/06—Details
    • F15B7/08—Input units; Master units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/72—Slack adjusters hydraulic
    • F16D65/74—Slack adjusters hydraulic self-acting in one direction
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/10—Plural pistons interacting by fluid pressure, e.g. hydraulic force amplifiers using different sized pistons

Definitions

  • This invention relates to a pneumatically controlled hydraulically actuated brake apparatus that has a hy- [52] Cl "601592; 188/53 R draulic fluid reservoir from which hydraulic fluid is 3 Cl Flsb 7/00 supplied via a check valve to the cylinder of a hydrau [58] held of Search 60535 592? lic fluid motor, movement of the piston of which in 188/52, 153 R, 196 A one direction forces hydraulic fluid under pressure to a brake applying piston to effect a brake application.
  • this invention provides a novel automatically operable means for effecting the return and recycling of the hydraulic fluid that leaks past the sealing rings carried by the pistons embodied in a pneumatically controlled hydraulically actuated brake apparatus and subject on one side to hydraulic fluid at a substantial pressure.
  • a pneumatically controlled hydraulically actuated brake apparatus that includes a hydraulic fluid reservoir and two seal-member-carrying pistons subject on one side to hydraulic fluid at a substantial pressure, suitable conduits through which any hydraulic fluid that may leak from one side of the pistons past the seal members carried thereby to the other side is forced under pressure to return to the fluid reservoir for recycling or resupply therefrom to the one side of the pistons.
  • FIG. 1 is a vertical sectional view of a presently known hydro-pneumatic converter device for supplying hydraulic fluid under pressure to a hydraulic brake applying piston.
  • FIG. 2 is a verticle sectional view of a pneumatically controlled hydraulically actuated brake apparatus embodying the invention.
  • FIG. 3 is a horizontal sectional view of the lower end of the guide member taken along sectional lines 33.
  • FIG. 1 of the drawings A conventional hydro-pneumatic converter device 1 is shown in FIG. 1 of the drawings for supplying hydraulic fluid under pressure to any suitable brake applying hydraulic fluid motor (not shown).
  • FIG. 1 of the drawings The construction and operation of the converter device 1 shown in FIG. 1 of the drawings may be substantially the same as that of the hydro-pneumatic converter device 13 shown and described in the abovementioned U.S. Pat. No. 3,837,443. Therefore, a detailed description of the converter device 1 is deemed unnecessary.
  • the converter device 1 comprises a diaphragm 2 the inner periphery of which is clamped between a diaphragm follower 3 and a diaphragm follower plate 4 secured thereto by a plurality of cap screws 5 two of which appear in FIG. 1.
  • a guide stem 6 Formed integral with the diaphragm follower 3 is a guide stem 6 the lower end of which is slidably disposed in a bore 7 provided therefor in a casing section 8 that constitutes one of a pair of casing sections that form a sectionalized casing of the converter device 1.
  • the interior of the bore 7 below the end of the stem 6 constitutes a chamber 9 that is supplied with hydraulic fluid from a hydraulic fluid reservoir 10 via a valve element 11 when unseated from a valve seat 12 in the manner explained in the abovementioned patent.
  • the guide stem 6 which constitutes a hydraulic piston, in response to the supply ofa pneumatic fluid under pressure to a chamber 14 above the diaphragm 2 via a passageway 15, the guide stem 6 is provided with a suitable seal member 16.
  • this hydraulic fluid is lost and must be replaced by a like quantity of hydraulic fluid from the hydraulic fluid reservoir 10 which heretofore has been provided with a pair of sight glasses or observation windows 18 and 19 located one above the other in order to inform an observer when this reservoir is full of hydraulic fluid and when substantially empty.
  • FIG. 2 of the drawings There is shown in FIG. 2 of the drawings a pneumatically controlled hydraulically actuated brake converter device 20 embodying therein the present invention.
  • the converter device 20 has a sectionalized casing comprising three casing sections 21. 22 and 23 secured together by any suitable means (not shown).
  • the casing section 21 is in the form of two opposed cup-shaped members separated by a wall 24.
  • the upper cup-shaped member of this casing section 21 is closed by an upper cover member 25 that is secured thereto by a plurality of cap screws 26 two of which appear in FIG. 2.
  • the upper cup-shaped member of the casing section 21 and the cover member 25 cooperate to form a hydraulic fluid reservoir 27 that may be filled with oil or some other suitable hydraulic fluid or liquid through a vented filling cap 28 screw-threaded into the cover member 25.
  • the outer periphery of a diaphragm 29 is clamped between the casing sections 21 and 22, and the inner periphery of this diaphragm is clamped between a diaphragm follower 30 and a diaphragm follower plate 31 that is secured to this follower 30 by a plurality of cap screws 32 that pass through smooth bores provided therefor in the plate 31 and have screw-threaded engagement with coaxial screw-threaded bottomed bores in this follower 30.
  • the diaphragm 29 together with the follower 30 and follower plate 31 cooperate with the casing sections 21 and 22 to form on the respective opposite sides of the diaphragm 29 a pair of chambers 33 and 34.
  • Pneumatic fluid under pressure may be supplied to the chamber 34 via a passageway and correspondingly numbered pipe 35 that is connected to such as the brake cylinder port of the usual brake control valve device (not shown) of the air brake equipment on railway vehicles under the control of the operator or locomotive engineer.
  • a master hydraulic piston 36 Formed integral with one side of the diaphragm follower 30 is a master hydraulic piston 36 the lower end of which is received in a bore 37 provided therefore in the casing section 22.
  • a spring 38 disposed about the piston 36 and interposed between the diaphragm follower 30 and the cas ing section 22 serves to yieldingly bias diaphragm 29 and piston 36 in a brake releasing direction to the position in which they are shown in FIG. 2. In this position the upper end of the diaphragm follower 30 abuts an annular stop 39 formed on the lower side of the wall 24.
  • the piston 36 is provided with a bore 40 and two coaxial counterbores 41 and 42, the counterbore 41 extending through the diaphragm follower 30 to the upper side thereof and the counterbore 42 extending through the piston 36 to the lower end thereof.
  • a tapered valve seat 43 is formed between the lower end of the bore 40 and the upper end of the counterbore 42 for a poppet-type valve 44 formed at the upper end of a cylindrical member 45 slidably mounted in the counterbore 42.
  • a snap ring 46 is inserted in a groove formed in the wall surface of the counterbore 42 and a spring 47 is interposed between this snap ring 46 and the cylindri cal member 45 for biasing an O-ring seal 48 carried by the valve 44 into seating contact with the valve seat 43 upon initial downward movement ofthe piston 36 from the position shown in FIG. 2.
  • the hydraulic piston 36 Adjacent the lower end thereof the hydraulic piston 36 is provided with a peripheral annular groove in which is disposed a seal member 49 the purpose of which is to inhibit flow of hydraulic fluid under pressure from a chamber 50 below the piston 36 to the chamber 34 via the small clearance space between the wall surface of the bore 37 and the peripheral surface of the piston 36 that is necessary to provide for a sliding fit between this piston 36 and the wall surface of the bore 37.
  • a seal member 49 Adjacent the lower end thereof the hydraulic piston 36 is provided with a peripheral annular groove in which is disposed a seal member 49 the purpose of which is to inhibit flow of hydraulic fluid under pressure from a chamber 50 below the piston 36 to the chamber 34 via the small clearance space between the wall surface of the bore 37 and the peripheral surface of the piston 36 that is necessary to provide for a sliding fit between this piston 36 and the wall surface of the bore 37.
  • a guide member 51 that extends into the counterbore 41 in the hydraulic piston 36. Adjacent its lower end, the guide member 51 is provided with a peripheral annular groove in which is carried a seal member 52 the purpose of which is to prevent leakage of pneumatic fluid under pressure from the chamber 34 to the bottom of the counterbore 41 and thence via the bore 40 and past valve 44 to the chamber 50 which is filled with hydraulic fluid. Furthermore. seal member 52 prevents leakage of the hydraulic fluid from the bottom of the counterbore 41 into the chamber 34.
  • a bottomed bore 53 Extending through the wall 24 and into the guide member 51 is a bottomed bore 53 the upper end of this bottomed bore being surrounded by a cup-shaped filter 54 that is disposed in the hydraulic fluid reservoir 27 and is constructed of, for example, screen wire.
  • the filter 54 is provided with an outturned flange through which extend a pair of screws 55 that have screwthreaded engagement with screw-threaded bottomed bores provided therefor in the wall 24.
  • the casing section 23 is provided with a pair of parallel spaced-apart bushed bracket members 58 and 59 to enable the converter device 20 to be secured to a railway vehicle.
  • the casing section 23 is provided with a bottomed bore 60 into the right-hand end of which, as viewed in FIG. 2, opens one end of a passageway 61 that extends through the casing section 23 and at its opposite end opens into the chamber 50.
  • a piston 62 Slidably mounted in the bottomed bore 60 is a piston 62 that has formed integral therewith a piston rod 63 that extends through a bore 64 provided therefor in a lower cover member 65 that is secured to the left-hand end of the casing section 23, as viewed in FIG. 2, by any suitable means (not shown).
  • the piston rod 63 Adjacent its left-hand end, the piston rod 63 is provided with a bore 66 into which is pressed a wear bushing 67 to enable the piston rod 63 to be operatively connected by a linkage (not shown) to such as, for example, a disc brake or any other device that may be operated by the converter device 20.
  • a linkage (not shown) to such as, for example, a disc brake or any other device that may be operated by the converter device 20.
  • Extending through the piston 62 and into the piston rod 63 is a tapered cavity 68 and a tapered coaxial counterbore 69.
  • the purpose in making this cavity 68 and counterbore 69 tapered is to enable the escape of air bubbles that may become entrapped in the hydraulic fluid that is supplied from the chamber 50 to this cavity and counterbore and a chamber 70 formed by the cooperative relationship of the piston 62 and the casing section 23 via the passageway 61.
  • the casing section 23 is provided with a bore 71 and a coaxial screwthreaded counterbore 72 for receiving a removable screw-threaded plug 73.
  • the periphery of the piston 62 is provided with an annular groove in which is disposed a seal member 74 to inhibit flow of hydraulic fluid under pressure from the chamber 70 into that portion of the bottomed bore 60 on the left-hand side of this piston 62.
  • the converter device 20 shown in FIG. 2 of the drawings is provided with means new to be described for returning the hydraulic fluid or liquid that leaks past the seal members 49 and 74 to the hydraulic fluid reservoir 27 in order that this fluid may not be lost but recycled or reused.
  • a passageway 75 extends substantially vertically through the casing sections 22 and 23.
  • This passageway 75 opens at its upper end into the chamber 33 and at its lower end at the wall surface of the bottomed bore 60 adjacent the left-hand end thereof. Accordingly, this passageway 75 provides a conduit through which the hydraulic fluid that may leak past the seal member 49 into the chamber 33 may be conveyed or drained from this chamber into that portion of the bottomed bore 60 at the left-hand side of the piston 62.
  • opening at the wall surface of the bottomed bore 60 adjacent the left-hand end thereof and diametrically opposite the opening of the passageway 75 at the wall surface of this bottomed bore 60 is one end of a passageway 76 that extends through the casing sections 23, 22, and 21 and the top cover member 25 and at its opposite end opens at a surface 77 formed on the lower side of this cover member 25, it being noted that this surface 77 is disposed a short distance above the surface of the hydraulic fluid in the reservoir 27.
  • the maximum cross sectional area of the passageway 76 should not exceed 0.0123 square inches for the reason that hydraulic fluid or liquid, as hereinafter explained, is forced by pneumatic pressure from that portion of the bottomed bore 60 on the left-hand side of the piston 62 through this passageway 76 back into the hydraulic fluid reservoir 27. Due to the surface tension of this hydraulic fluid, if the cross sectional area of the passageway 76 is in excess of 0.0123 square inches, the pneumatic pressure would blow through the hydraulic fluid or liquid so that this hydraulic fluid would not be forced back into the reservoir 27 as desired.
  • the wall surface of the bore 64 in the lower cover member 65 is provided with a pair of spacedapart annular grooves in which are disposed respectively seal members 78 and 79 that encircle the peripheral surface of the piston rod 63 to form a seal therewith. Consequently, as the piston 62 is moved in the direction of the left-hand by the supply of hydraulic fluid under pressure to the chamber to decrease the volume of that portion of the bottomed bore 60 on the left-hand side of the piston 62, the pressure in this volume will increase.
  • a pneumatically controlled hydraulically actuated brake apparatus comprising a plurality of casing sections certain of which are provided with bores, a pair of tandem arranged abutments one of which is movable in opposite directions in one of said bores responsively to the application and release of pneumatic pressure to one of two chambers formed on the respective opposite sides of the other of said abutments by the cooperative relationship of said other abutment and a pair of said casing sections, a hydraulic reservoir from which a hydraulic medium may be supplied to said one bore, a third abutment movable in another of said bores responsively to the hydraulic pressure established in one of two chambers formed on the respective opposite sides thereof by movement of said one abutment in one direction in said one bore, and seal means carried by each of said one and said third abutment to respectively inhibit flow of hydraulic medium from said one bore to the other one of said two chambers and from said one of said two chambers to the other chamber on the other side of said abutment, wherein the improvement comprises:
  • first conduit means connecting said first other chamber and said second other chamber
  • a pneumatically controlled hydraulically actuated brake apparatus as recited in claim 1, further characterized in that movement of said other abutment ofsaid pair of tandem arranged abutments in one direction in response to the supply of pneumatic pressure to said one of said first two chambers is effective to decrease the volume of the other of said first two chambers thereby increasing the pressure therein to cause flow of hydraulic medium therefrom to the hydraulic reservoir via said first conduit means, said second other chamber and said second conduit means.
  • a pneumatically controlled hydraulically actuated brake apparatus as recited in claim 1, further characterized in that movement of said other abutment of said pair of tandem arranged abutments in one direction in response to the supply of pneumatic pressure to said one of said first two chambers is effective to decrease the volume of the other of said first two chambers thereby increasing the pressure therein to cause flow of hydraulic medium therefrom to said second other chambver via said first conduit means, and move ment of said third abutment in one direction in response to the supply of hydraulic pressure to said one of said second two chambers is effective to decrease the volume of the other of said second two chambers thereby increasing the pressure therein to cause flow of hydraulic medium therefrom to the hydraulic reservoir via said second conduit means.
  • a pneumatically controlled hydraulically actuated brake apparatus as recited in claim 1, further characterized in that the hydraulic reservoir is formed in one of said plurality of casing sections.
  • a pneumatically controlled hydraulically actuated brake apparatus as recited in claim 6, further characterized by seal means carried by one of those casing sections having therein said one bore and said another bore, said seal means being disposed in surrounding relation to said first conduit and interposed between said casing sections to prevent leakage of hydraulic medium from said first conduit.
  • a pneumatically controlled hydraulically actuated brake apparatus as recited in claim 7, further characterized by seal means carried by one of each two pair of adjacent casing sections of said plurality of casing sections, each of said seal means being disposed in surrounding relation to said second conduit means and interposed between the respective pair of adjacent casing sections to prevent leakage of hydraulic medium from said second conduit.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Braking Arrangements (AREA)
  • Braking Systems And Boosters (AREA)
US487127A 1974-07-10 1974-07-10 Oil leakage recycler Expired - Lifetime US3913328A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US487127A US3913328A (en) 1974-07-10 1974-07-10 Oil leakage recycler
ZA00750620A ZA75620B (en) 1974-07-10 1975-01-29 Oil leakage recycler
CA220,205A CA1018467A (en) 1974-07-10 1975-02-14 Oil leakage recycler
DE19752510255 DE2510255A1 (de) 1974-07-10 1975-03-08 Pneumatisch-hydraulische bremsvorrichtung
GB16863/75A GB1499014A (en) 1974-07-10 1975-04-23 Pneumatically controlled hydraulically actuated brake apparatus
BR4290/75A BR7503356A (pt) 1974-07-10 1975-05-28 Aperfeicoamento em aparelho de freio acionado hidraulicamente e controlado
JP1975094755U JPS538871Y2 (de) 1974-07-10 1975-07-09

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US487127A US3913328A (en) 1974-07-10 1974-07-10 Oil leakage recycler

Publications (1)

Publication Number Publication Date
US3913328A true US3913328A (en) 1975-10-21

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US487127A Expired - Lifetime US3913328A (en) 1974-07-10 1974-07-10 Oil leakage recycler

Country Status (7)

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US (1) US3913328A (de)
JP (1) JPS538871Y2 (de)
BR (1) BR7503356A (de)
CA (1) CA1018467A (de)
DE (1) DE2510255A1 (de)
GB (1) GB1499014A (de)
ZA (1) ZA75620B (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4077218A (en) * 1974-12-19 1978-03-07 Underwater And Marine Equipment Limited Articulated joint
US4109467A (en) * 1976-07-07 1978-08-29 Lukas George N Hydraulic booster system
US4319671A (en) * 1980-06-02 1982-03-16 Wabco, Ltd. Hydro-pneumatic brake actuator arranged to maintain a constant brake shoe clearance
US4323144A (en) * 1980-07-16 1982-04-06 American Standard Inc. Hydro-pneumatic brake actuator arranged to maintain a constant brake shoe clearance
EP0122195A1 (de) * 1983-04-08 1984-10-17 Bendix Espana S.A. Hydropneumatische Bremsvorrichtung
DE3815731A1 (de) * 1988-05-07 1989-11-16 Teves Gmbh Alfred Hauptbremskolben mit zentralregelventil und filtern
CN114763844A (zh) * 2021-01-15 2022-07-19 玛珂***分析和开发有限公司 计量阀

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49109305U (de) * 1973-01-13 1974-09-18
GB1539206A (en) * 1975-09-12 1979-01-31 Bekaert Sa Nv Apparatus and method for demisting streams of gases
JPS55131304U (de) * 1979-03-14 1980-09-17
AT392497B (de) * 1989-06-02 1991-04-10 Voest Alpine Maschinenbau Gleitstuhl, gleitplatte bzw. rippenplatte fuer schienenweichen oder -kreuzungen
DE9201972U1 (de) * 1992-02-15 1993-06-17 Hydraulik Techniek, Emmen Zugzylinder

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2058063A (en) * 1932-11-18 1936-10-20 Wagner Electric Corp Braking apparatus
US2585389A (en) * 1950-03-11 1952-02-12 Gen Motors Corp Hydraulic control
US2827766A (en) * 1954-12-09 1958-03-25 Lionel E Weiss Hydro-pneumatic press apparatus
US3107624A (en) * 1961-06-12 1963-10-22 Milton Roy Co Hydraulically-operated automatic air release valve for pulsating-pressure pumps
US3199415A (en) * 1957-06-03 1965-08-10 Arthur J Stanton Pneumatic motor
US3200596A (en) * 1962-04-30 1965-08-17 Power Control Products Inc Cylinder and piston arrangement

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2058063A (en) * 1932-11-18 1936-10-20 Wagner Electric Corp Braking apparatus
US2585389A (en) * 1950-03-11 1952-02-12 Gen Motors Corp Hydraulic control
US2827766A (en) * 1954-12-09 1958-03-25 Lionel E Weiss Hydro-pneumatic press apparatus
US3199415A (en) * 1957-06-03 1965-08-10 Arthur J Stanton Pneumatic motor
US3107624A (en) * 1961-06-12 1963-10-22 Milton Roy Co Hydraulically-operated automatic air release valve for pulsating-pressure pumps
US3200596A (en) * 1962-04-30 1965-08-17 Power Control Products Inc Cylinder and piston arrangement

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4077218A (en) * 1974-12-19 1978-03-07 Underwater And Marine Equipment Limited Articulated joint
US4109467A (en) * 1976-07-07 1978-08-29 Lukas George N Hydraulic booster system
US4319671A (en) * 1980-06-02 1982-03-16 Wabco, Ltd. Hydro-pneumatic brake actuator arranged to maintain a constant brake shoe clearance
US4323144A (en) * 1980-07-16 1982-04-06 American Standard Inc. Hydro-pneumatic brake actuator arranged to maintain a constant brake shoe clearance
EP0122195A1 (de) * 1983-04-08 1984-10-17 Bendix Espana S.A. Hydropneumatische Bremsvorrichtung
DE3815731A1 (de) * 1988-05-07 1989-11-16 Teves Gmbh Alfred Hauptbremskolben mit zentralregelventil und filtern
CN114763844A (zh) * 2021-01-15 2022-07-19 玛珂***分析和开发有限公司 计量阀
CN114763844B (zh) * 2021-01-15 2024-06-11 玛珂***分析和开发有限公司 计量阀

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Publication number Publication date
ZA75620B (en) 1976-01-28
DE2510255A1 (de) 1976-01-22
GB1499014A (en) 1978-01-25
BR7503356A (pt) 1976-07-06
JPS538871Y2 (de) 1978-03-08
CA1018467A (en) 1977-10-04
JPS5110485U (de) 1976-01-26

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