US3330422A - Hydraulic cushion device for railway cars - Google Patents

Hydraulic cushion device for railway cars Download PDF

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Publication number
US3330422A
US3330422A US463297A US46329765A US3330422A US 3330422 A US3330422 A US 3330422A US 463297 A US463297 A US 463297A US 46329765 A US46329765 A US 46329765A US 3330422 A US3330422 A US 3330422A
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US
United States
Prior art keywords
cylinder
piston rod
clamping
pressure chamber
reservoir
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
US463297A
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English (en)
Inventor
Robert A Rasmussen
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.)
Pullman Standard Inc
Pullman Inc
Original Assignee
Pullman Inc
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 Pullman Inc filed Critical Pullman Inc
Priority to US463297A priority Critical patent/US3330422A/en
Priority to NL6601539A priority patent/NL6601539A/xx
Priority to BE676914D priority patent/BE676914A/xx
Priority to DE1530207A priority patent/DE1530207C3/de
Priority to CH410066A priority patent/CH458426A/de
Priority to CH1501567A priority patent/CH459289A/de
Application granted granted Critical
Publication of US3330422A publication Critical patent/US3330422A/en
Priority to NL7315877.A priority patent/NL157694B/xx
Anticipated expiration legal-status Critical
Assigned to PULLMAN STANDARD INC., A DE CORP. reassignment PULLMAN STANDARD INC., A DE CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: M.W. KELLOGG COMPANY, THE
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/10—Enclosure elements, e.g. for protection

Definitions

  • a hydraulic cushioning device for use in railway vehicles including a uid filled cylinder having a piston assembly reciprocal therein with a flexible boot closing off the open end of the cylinder by attachment of one end of the boot at the open end of the cylinder and the other end to the piston assembly.
  • the flexible boot is formed of two superposed chord plies in which one of the plies has a chord angle varying between about 32 and about 59 and the chord angle of the other ply is supplementary thereto.
  • the boot is formed with beaded ends at each end of which one beaded end is clamped to an intermediate cylinder head adjacent the open end of the cylinder and the other end is clamped to a tubular piston rod of the piston assembly.
  • the piston assembly clamping means includes a clamping ring fixed to the piston rod of the piston assembly and a second coacting clamping ⁇ ring slidable lengthwise of the piston rod which is held in clamping relationship by means of a snap ring seated within a groove formed in the piston rod.
  • the present invention relates to hydraulic cushion devices of the type employed in cushion under-frame railway vehicles wherein the coupler carrying structure and the lading supporting structures are relatively slidable lengthwise of each other and the hydraulic cushion device is interposed for interaction between the aforementioned structures to absorb a portion of the impact energy and thereby prevent lading damage.
  • the hydraulic cushion device to which the present invention relates, comprises generally a hydraulic uid filled cylinder and a fluid displacement means including a piston head and piston rod.
  • the cylinder and fluid displacement means are arranged to reciprocate relative to each other between a neutral extended position and to a contracted position upon impact to either the cylinder or fluid displacement means. Relative movement of the cylinder and fluid displacement means is operative to displace the hydraulic fluid from a high pressure chamber to a low pressure chamber which results in absorbing a portion of the kinetic energy of the impact force.
  • Communication between the high pressure chamber and the low pressure chamber is established by way of an oriiice having a metering pin associated therewith.
  • the metering pin serves to vary the effective orifice area during contraction of the cushion device so as to impart a substantially constant force travel characteristic to the cushion unit.
  • the hydraulic cushion device is characterized by a construction which utilizes solely static seals. To this end there is employed a iiexible boot reservoir which closes off the open end of the cylinder and accommodates the hydraulic uid displaced by the piston rod of the uid displacement means.
  • a return spring disposed about the cylinder between the remote ends of the fluid displacement means and cylinder has been used to return the cushion device components to the neutral position.
  • the hydraulic fluid ow is reversed from the exible boot reservoir and low pressure chamber and the hydraulic uid flows from the low ICC pressure chamber to till the volume of the high pressure chamber preparatory to receiving another impact.
  • lt is the principal object of the present invention to provide a new and improved cushion unit of the aforedescribed type wherein the iiuid pressure forces of the hydraulic fluid in the flexible boot reservoir are utilized to provide the necessary force for returning the cushion unit components from the contracted to the neutral extended positions thereof.
  • FlG. 1 is a cross sectional View of the cushion unit embodying the present invention with the components thereof shown in the contracted position;
  • FIG. 2 is a fragmentary cross sectional view of the cushion unit of FIG. l, but showing the flexible boot reservoir in the deiiated state prior to the introduction of hydraulic fluid therein;
  • FIG. 3 is a fragmentary cross sectional view similar to FIG. 2 but showing the flexible boot reservoir filled with hydraulic fluid and with the components thereof in the neutral extended position;
  • FIG. 4 is a fragmentary cross sectional view similar to FIG. 3 but showing the flexible boot reservoir in its fully extended position when the cushion unit components are in the contracted position;
  • FIG. 5 is an enlarged fragmentary view of the piston rod and showing in section the flexible boot reservoir clamped at one end to the piston rod;
  • FIG. 6 is an enlarged fragmentary View of the piston rod and showing in section the flexible boot reservoir clamped to the intermediate cylinder head.
  • FIG. 7 is an enlarged view of the flexible boot reservoir in the deflated state thereof with some of the structure broken away to show underlying details;
  • FIG. 8 is a view similar to FIG. 7 but showing the flexible boot reservoir in its maximum inflated state
  • FIG. 9 is a fragmentary cross sectional view of the iiexible boot reservoir construction.
  • FIG. l0 is a fragmentary cut-away perspective view of the iiexible boot reservoir structure.
  • a hydraulic cushion device 10 comprising essentially a hydraulic iiuid filled cylinder 11; a fluid displacement means 12 which is reciprocable relative to the cylinder 11 between the neutral extended position shown for example in FIG. 3 to a contracted position shown in FIG. 4 for displacing dluid from a high pressure chamber 13 to a low pressure chamber 14; a flexible boot reservoir 15 connected between the cylinder 11 and the fluid displacement means 12 for receiving a portion of the hydraulic fluid displaced during contraction; and a metering pin 16 for metering the flow between the high pressure chamber 13 and the low pressure chamber 14.
  • the cylinder 11 is formed from a cylindrical tube 17 which may be made from a suit- 3 able steel or the like. Fixed as by welding to one end of the tube 17 is a follower or base plate 18.
  • the fluiddisplacement means 12 includes a piston head 19 and a tubular piston rod 21 of which lone end is fixed to the low pressure face 22 of the piston head 19.
  • tubular piston rod 21 extends outwardly through the open end of the cylinder 11.
  • the high pressure face 28 of the piston head 19, which may be formed from suitable metal such as cast iron, is formed with a conical feed surface 29 which merges with an axial orifice 31.
  • the axial orifice 31 - is coaxial with the piston rod borer36 Iand the latter cornmunicates with the low pressure chamber via an array ⁇ of ports 32 formed in the tubular piston rod 21 adjacent the piston head 19.
  • the piston rod 21 is of lesser diameter than an axial -opening 33 in an Iintermediate cylinder head 34 so that there is defined between the outer circumference of the tubular pistonrod 21 and the inner circumference of the axial opening 13 an annular passage 36 which provides communication between the low pressure chamber 14 and the flexible boot reservoir 15.
  • hydraulic fluid communication between the high Vpressure: chamber 13 and the flexible boot reservoir 15 is established via the piston head orifice 31, the piston rod bore 26, the array of ports 32, the low pressure chamber 14, and the annular passage 36.
  • the flexible boot reservoir is made from rubber having reinforcing cords and 35 imbedded therein.
  • the ply of cords 30 are applied on an inner rubber liner 40 and are separated from the overlying second ply of cords 'by a skim coat 45 which is also applied over the cords 35.
  • the exterior of the boot 15 is formed by an outer liner 50.
  • the inner liner 40, skim coats 45 and outer liner 50 form 'more or less an homogenous mass so that there are no visible planes of demarcation therebetween, as illustrated for clarity.
  • V The angles at which the cords 30 and 35 are positioned with respect to the horizontal are arranged to ⁇ impart strength to the exible boot reservoir 15 so that the latter may serve las the means for running the cushion unit from the compressed position to the extended position after the force of impact applied to the cushion unit has been dissipated.
  • the cord angle of the lower ply of cords 30 in the extended position be about 32 with respect to the horizontal, as shown, and the cord angle of the upper ply of cords 35 be the supplement of the lower cord angle or about 148.
  • the cord -angles of the cords are arranged so as not to exceed about 59 and 121, respectively.
  • the fiexible boot reservoir is radially expansible under the pressure Vof the hydraulic fluid received therein during the contraction of the cushion unit 10 from the extended to the contracted positions.
  • Such radial expansion is permitted Aby way of the increase in the cord angles of the cord plies 30 and 35.
  • the increase in the cord angles causes the boot to be shortened in its overall length.
  • the ply of cords 30 and 35 are imbedded in the rubber to assume Ia normal or extended position of about 32, there is imparted to the boot a linear force acting between the cylinder 11 and the fluid displacement means 12 which tends to return the latter two components to the neutral position as more fully to be explained hereafter.
  • the boot 15 is formed with a bead 37 which is formed about a wire 38.
  • the beads '37-37 serve to provide a clamping sector for attach- 4 ment to the piston rod 21 and the intermediate cylinder head 34.
  • one end 15a of the boot reservoir 15 is reversely turned or folded inwardly and the associated bead 37 is clamped between a first clamping ring 39 which is fixed to the periphery of the piston rod 21 as by welding and a clamping sleeve 41 slidable on the piston rod 21.
  • the clamping sleeve 41 has fixed to one end a second clamping ring 42 which when positioned yadjacent to the first clamping ring 39 coacts with the latter to clampingly grip the beaded end 37.
  • the outer peripheries of the first and second clamping rings 39 and 42 are each inclined so that the boot reservoir is not subject to sharp edges and is permitted to contact the piston rod periphery along the length thereof.
  • the other end of the clamping sleeve 41 extends outwardly toward the follower plate 27 and is fixed against longitudinal movement by means of a snap ring 43 seated within a groove 44 formed in the periphery of the piston rod 21 as shown in particular in FIG. 4.
  • the above described clamping arrangement is particularly advantageous in that the clamping sleeve 41 is fixed at the area of low stress concentra-tion of the tubular piston rod.
  • the groove 44 into which the snap ring is fastened overlies the plug 24 adjacent the follower plate 27 where the pressure forces and bending moment is at a minimum so that the groove 44 does not affect the strength of the piston rod 21.
  • the snap ring as is readily .apparent upon an inspection of FIG. 2, showing the condi-tion of the lboot reservoir 15 without hydraulic fluid stored therein lies inboard ofthe reversely bent portion 15a ⁇ and facilitates the installation without Yinterference from the boot 15.
  • the other beaded end 37 is clamped to the intermediate cylinder head 34 disposed between the open end of Y the cylinder 11 and the base plate 18.
  • the intermediate cylinder head 34 includes an annular-body member 46 which is'fixed within the bore of the cylinder 17 as by snap rings 47. To form a uid tight seal at the inner cylinder. wall a quadrant ring 48 may be seated within a peripheral groove.
  • the inboard face of the annular body member 46 is formed with a circular recess 49, Seated within the recess 49 and held fixed therein as'by a snap ring 51 is an annular orifice plate 52 having the opening 33 which is of greater diameter than the outer periphery of the piston rod 21 and forms therewith the annular passageway 36 providing fluid communication between the low pressure chamber 14 and the flexible boot reservoir 15.
  • the bead end 37 of the flexible boot reservoir 15 isV securely clamped between the inner face of the orifice plate 52 and shoulder 53 formed by a second circular recess 54 located inwardly of the recess 49.
  • the beaded end 37 of the rubber boot is formed of greater thickness than the distance between the shoulder 53 and the inner face of the orifice plate 52 so that it is compressed therein and firmly clamped to the intermediate cylinder head 34.
  • the metering pin 16 which serves to control the hy- Vdraulic fiuid ow through the piston orifice 31 includes a metering body 56 slidable within the piston head yorifice 31 and is of substantially constant diameter along the length thereof.
  • the metering pin 16 may be made from a forging having an annular attachment flange integrally formed on one end thereof and is inserted through anV the length of the metering body 56.
  • rIhe flutes 57 are formed to coact with the piston head orifice 31 by varying the effective cross sectional area of the latter in a manner such that the hydraulic fluid pressure forces within the high pressure chamber 13 remain substantially constant during the contraction of the cushion device 10.
  • the pressure forces of the hydraulic fluid reacting on the flexible boot may be used.
  • the hydraulic fluid which may be poured through the opening accommodating the metering pin 16 prior to the insertion of the latter, is present in a sufficient quantity to exert pressure forces within the flexible boot reservoir in the extended neutral position which pressure forces increase upon the application of an impact force to either end of the cushion unit, This causes the boot 15 to expand radially as heretofore described and thereby causing the chord angles of the cords 30 and 35 to be changed causing a linear force to be applied between the cylinder 11 and fluid displacement means 12. As shown in particular in FIGS.
  • the pressure forces of the hydraulic fluid Within the flexible boot reservoir act on an area defined by the annular cross-section of the boot at the reversely turned end and shall hereinafter be designated as the reaction area.
  • the total pressure forces yof the reaction area are operative on the reversely turned end 15a of the boot reservoir 15 also to apply a substantially linear force parallel to the longitudinal axis of the piston rod 21 in a direction causing the fluid displacement means 12 and cylinder 11 to assume the neutral extended position.
  • the pressure forces of the hydraulic fluid and the boot construction tend to return the cushion unit to its extended position.
  • the force exerted by the boot is Operative to return the fluid displacement means 12 and the cylinder 11 to the neutral position
  • the cushion device 10 of the present invention is employed in a cushion underframe railway and interposed between the sliding sill (not shown) and the stationary sill (not shown). In the absence of an impact on the sliding sill the cushion device 10 assumes the neutral position shown in FIG. l.
  • the fluid displacement means 12 and the cylinder 11 telescope relatively to each other toward the contracted position shown in FIG. l.
  • the piston head 19 and the base plate 18 move toward each other whereupon the piston rod 21 displaces hydraulic fluid Within the low pressure charnber 14 into the flexible boot 15 reservoir via the annular opening 36.
  • hydraulic fluid displaced from the high pressure chamber 13 flows through piston head orifice 31 of gradually diminishing cross-sectional area into the piston rod bore 26. From the piston rod bore 26 the hydraulic fluid flows into the low pressure chamber 14 via the array of ports 32.
  • the hydraulic fluid is discharged into the low pressure chamber 14 at a relatively high velocity which creates considerable turbulence.
  • the turbulence is caused at least in part by the radially directed flow of the hydraulic fluid impinging directly against the bore wall so as to dissipate much of the kinetic energy of the impact in the form of heat.
  • the flexible boot reservoir 15 contains the increased hydraulic fluid displaced by the piston rod 21 as shown in FIG. 3.
  • the increased volume which is under increased pressure radially expands the boot 15 causing a shortening of the boot length as heretofore described.
  • the radial expansion increases the reaction area and thereby the linear force applied by the boot between the cylinder 11 and the piston rod 21 to return the cushion to the neutral position shown in FIG. 2.
  • a hydraulic cushion unit comprising a cylinder having a bore, a first base plate fixed to one end of said cylinder, a piston head reciprocable within the bore of said cylinder and having an axial orifice, said piston head defining a high pressure chamber on one side thereof with said first base plate and a low pressure chamber on the opposite side thereof, a tubular piston rod fixed at one end to said piston head with the other end extending through the open end of said cylinder, said tubular piston rod having a bore coaxially disposed relative to said axial orifice, a second base plate fixed to said other end of said piston rod, a flexible boot reservoir having beads at each end thereof, said flexible boot reservoir having a reversely turned end portion which is turned inwardly into said boot, an intermediate cylinder head having an orifice, said intermediate cylinder head being fixed to said cylinder and including an orifice and an annular clamping means for holding one of said beaded ends of said flexible boot reservoir clamped to said intermediate cylinder head, a first clamping ring fixed on said piston
  • a hydraulic cushion unit comprising a cylinder having a bore, a first base plate fixed to one end of said cylinder, a .piston head reciprocable within the bore of said cylinder and having 'an axial orifice, said piston head defining a high pressure chamber on one side thereof with said first base plate and a low pressure chamber on the opposite side thereof, a tubular piston rod fixed at one end to said piston head with the other end extending through the open end of said cylinder, said tubular piston rod having a bore coaxially disposed relative to said axial orifice, a second base plate fixed to said other end of said piston rod, a flexible boot reservoir having beads at each end thereof, said flexible boot reservoir having a reversely turned end portion which is turned into said boot, an intermediate cylinder head having an orifice, said intermediate cylinder head being fixed Within said cylinder and including a recess and an annular plate clamping one beaded end of said flexible boot reservoir thereto, said annular plate having an opening defining with said piston rod an annular passage,
  • said retaining means comprises an elongate sleeve of which one end en-gages said second clamping ring and the other Vend lies adjacent to said second base plate, and snap ring means seated in a groove in said piston rod abutting said other end of said sleeve.
  • said flexible boot reservoir is constructed so as to be further radially expanded upon travel of said cushion device to said contracted position upon the application of an impact force to said cushion device, whereby the corresponding increase of the pressure forces of said hydraulic fluid within said ilexible boot reservoir create a reaction force causing the piston head and cylinder to return to Y the neutral position when the impact force has dissipated.
  • said cording comprises two superposed plies of cord of which one ply is arranged to provide between the extended and contracted position of said cushion unit a cord angle Varying between about 32 to 59 with respect to a reference line parallel to the longitudinal axis of said flexible boot reservoir and the other is arranged to provide supplementary cord angles thereto.
  • a hydraulic cushion unit comprising a hydraulic iluid lled cylinder having a closed end and an open end, a fluid displacement means reciprocable within said cylinder between a neutral extended position and a contracted position, and a flexible boot reservoir connected between said cylinder and said fluid displacement means for receiving hydraulic fluid displaced during reciprocation of said fluid displacement means and said cylinder, said exible boot reservoir comprising a rubber boot having two superposed cord plies embedded therein, one of said plies having a cord angle varying between about 32 and 59 as said cylinder and said uid displacement means reciprocate relative to each other, said other of said plies having cord angles varying between rangles supplementary to said one cord ply range of cord angles.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
US463297A 1965-06-11 1965-06-11 Hydraulic cushion device for railway cars Expired - Lifetime US3330422A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US463297A US3330422A (en) 1965-06-11 1965-06-11 Hydraulic cushion device for railway cars
NL6601539A NL6601539A (de) 1965-06-11 1966-02-07
BE676914D BE676914A (de) 1965-06-11 1966-02-23
DE1530207A DE1530207C3 (de) 1965-06-11 1966-03-02 Hydraulisch gedämpfte Stoßaufnahmevorrichtung für Eisenbahnwagen
CH410066A CH458426A (de) 1965-06-11 1966-03-22 Hydraulische Stossdämpfervorrichtung
CH1501567A CH459289A (de) 1965-06-11 1966-03-22 Hydraulische Stossdämpfervorrichtung
NL7315877.A NL157694B (nl) 1965-06-11 1973-11-20 Hydraulische bufferinrichting.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US463297A US3330422A (en) 1965-06-11 1965-06-11 Hydraulic cushion device for railway cars

Publications (1)

Publication Number Publication Date
US3330422A true US3330422A (en) 1967-07-11

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ID=23839615

Family Applications (1)

Application Number Title Priority Date Filing Date
US463297A Expired - Lifetime US3330422A (en) 1965-06-11 1965-06-11 Hydraulic cushion device for railway cars

Country Status (5)

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US (1) US3330422A (de)
BE (1) BE676914A (de)
CH (2) CH458426A (de)
DE (1) DE1530207C3 (de)
NL (1) NL6601539A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410416A (en) * 1967-05-11 1968-11-12 Pullman Inc Hydraulic cushioning device for railway vehicles
US3669225A (en) * 1970-01-30 1972-06-13 Moulton Development Ltd Vehicle suspension unit
WO2012091714A1 (en) * 2010-12-30 2012-07-05 Mcconway & Torley Llc Improved coupler and clevis for a railway car

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2893104A (en) * 1957-05-23 1959-07-07 Gen Motors Corp Air suspension
US2920885A (en) * 1954-12-14 1960-01-12 Continental Gummi Werke Ag Hollow bodies for air cushioning in particular for vehicles
US3033557A (en) * 1957-06-19 1962-05-08 Gen Motors Corp Pneumatic containers and method and apparatus for making the same
US3038717A (en) * 1957-02-04 1962-06-12 Firestone Tire & Rubber Co Air spring
US3043582A (en) * 1956-10-02 1962-07-10 Goodyear Tire & Rubber Rolling lobe type air spring and method of manufacture
US3148869A (en) * 1963-01-29 1964-09-15 Pullman Inc Hydraulic cushion device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2920885A (en) * 1954-12-14 1960-01-12 Continental Gummi Werke Ag Hollow bodies for air cushioning in particular for vehicles
US3043582A (en) * 1956-10-02 1962-07-10 Goodyear Tire & Rubber Rolling lobe type air spring and method of manufacture
US3038717A (en) * 1957-02-04 1962-06-12 Firestone Tire & Rubber Co Air spring
US2893104A (en) * 1957-05-23 1959-07-07 Gen Motors Corp Air suspension
US3033557A (en) * 1957-06-19 1962-05-08 Gen Motors Corp Pneumatic containers and method and apparatus for making the same
US3148869A (en) * 1963-01-29 1964-09-15 Pullman Inc Hydraulic cushion device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410416A (en) * 1967-05-11 1968-11-12 Pullman Inc Hydraulic cushioning device for railway vehicles
US3669225A (en) * 1970-01-30 1972-06-13 Moulton Development Ltd Vehicle suspension unit
WO2012091714A1 (en) * 2010-12-30 2012-07-05 Mcconway & Torley Llc Improved coupler and clevis for a railway car

Also Published As

Publication number Publication date
BE676914A (de) 1966-08-23
CH459289A (de) 1968-07-15
DE1530207B2 (de) 1973-07-12
CH458426A (de) 1968-06-30
NL6601539A (de) 1966-12-12
DE1530207C3 (de) 1974-01-31
DE1530207A1 (de) 1970-04-23

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Legal Events

Date Code Title Description
AS Assignment

Owner name: PULLMAN STANDARD INC., 200 S. MICHIGAN AVE., CHICA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:M.W. KELLOGG COMPANY, THE;REEL/FRAME:004370/0168

Effective date: 19840224