US3473325A - Unitary hydraulic shock absorber and actuator - Google Patents
Unitary hydraulic shock absorber and actuator Download PDFInfo
- Publication number
- US3473325A US3473325A US682248A US3473325DA US3473325A US 3473325 A US3473325 A US 3473325A US 682248 A US682248 A US 682248A US 3473325D A US3473325D A US 3473325DA US 3473325 A US3473325 A US 3473325A
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- United States
- Prior art keywords
- pressure
- valve
- piston
- reservoir
- bore
- 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
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Classifications
-
- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/18—Combined units comprising both motor and pump
-
- 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
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S60/00—Power plants
- Y10S60/916—Unitary construction
Definitions
- FIG. 1 is an elevational view of an outboard motor in operative position on a boat to which the invention has been applied;
- FIG. 2 is a perspective view in elevation of the motor shown in FIG. 1 in raised inoperative position;
- FIG. 3 is an elevational view of the hydraulic device incorporating the invention taken broadside
- FIG. 4 is an elevational view of the device shown in FIG. 3 taken at right angles thereto;
- FIG. 5 is an elevational view partly in section taken along line 5-5 of FIG. 3;
- FIG. 6 is an elevational view partly in section taken along line 66 of FIG. 3;
- FIG. 7 is a sectional elevational view taken along line 7-7 of FIG. 4;
- FIG. 8 is a plan view in section taken along line 88 of FIG. 6;
- FIG. 9 is a plan view in section taken along line 9--9 of FIG. 3;
- FIG. 10 is an enlarged view in elevation partly in section superimposing in phantom the parts of the device.
- the invention is shown applied to an outboard motor 20 for use with a boat the transom 22 of which is shown in cross section.
- the outboard motor is mounted on the transom by mounting brackets 24 which embrace the upper edge of the transom to which it is rigidly clamped by means of manually-operated screws 26, to hold the depending drive portion 20 in substantially vertical position to place the propeller (not shown) thereof into nite States Patent 0 "ice the water to drive the boat forward.
- the brackets 24 are provided with a pivotal connection 30 which allows the motor to be tilted upwardly to remove the propeller from the water as shown in FIG.
- a unitary hydraulic tilt mechanism H which may, but does not necessarily include a shock absorbing action.
- the mechanism H incorporates the invention as shown cooperating with the outboard motor and its mounting means for application to a boat.
- the shock absorber action of the device H is effective when the propeller of the outboard motor 20 hits a submerged object when the boat is traveling at a high rate of speed, which propels the motor upwardly about the pivot point 30, often giving rise to dangerous conditions for the motor or for the occupants of the boat.
- the shock absorber aspect of the invention will be further described hereinafter.
- the device H incorporating the invention is provided with hydraulic cylinder (FIG. 3) 31 integrally incorporated in the device H which is capable of expanding by its movable piston and piston rod assembly 31a and applying a force to the outboard motor between a fixed pivot 32 on the outer lower end of an auxiliary bracket 24a and an intermediate pivot point 34 above it which will create the necessary mechanical arrangement to cause the motor to move upwardly.
- the motor is shown in raised position in FIG. 2 as pointed out hereinbefore.
- the lower end of the jack 31 is provided with an integral anchor block 36 which is pierced by an aperture through which a pin projects to form the fixed pivot 32, the pin also projecting through suitable ears 38 on the lower outer end of the auxiliary bracket 24a attached to bracket 24.
- the piston rod assembly 31a of the hydraulic jack 31 is provided with an eye 42 through which a pin projects to form the intermediate pivot 34, a second set of integral ears 44 being provided at a central location of the bracket 124 having apertures aligning with the eye to cooperate with the pin to form the pivot.
- the hydraulic cylinder 31 is so arranged in its pressure connections with a source of controllable pressure, as will be further described hereinafter, that the movable piston assembly 31:: can be expanded or retracted at the will of an operator.
- the motor can either be raised to the position shown in FIG. 2 or to an intermediate position for partial tilt operation, or can be retracted from either position to the normal operation position shown in FIG. 1.
- the hydraulic tilt and shock absorber H is divided into three portions, A, C and M, which cooperate together to form an integrated unit which includes the hydraulic jack 31, a source of pressure with its controls, and a power source consisting of a reversible electric motor M which is energized and controlled from a remote point inside of the boat by means of a cable K.
- the three portions are integrated together into a sealed casing, which protects the parts of the mechanism from ambient conditions such as weather and water to which the device is exposed due to its position on the exterior of the boat body where it may also be subjected to submersion in the water in a following sea.
- the sealed casing is fabricated from castings A and C which are fastened together y suitable mechanical means such as screws 40 and provided with suitable gaskets 46 for sealing as is well known in the art.
- the connections for the hydraulic circuits are all positioned within the casings so that the unit is rugged and not subjected to disruption by breakage or the like, due to its smooth outer contours.
- the reversible electric motor M is mounted against the casting C by means of throughbolts B and provided with gaskets 48 at the 3 joints to form seals.
- the shaft 50 of the motor (FIG. 7) extends in normal relation through the casting C through a seal 52 to drive a gear pump P as will be described further hereinafter.
- the hydraulic jack 31, with its piston and piston rod assembly 31a is housed in an integral portion of the casting A and consists of a cylinder bore 31b in which the assembly 31 reciprocates under the controllable pres sure regulations above and below the piston by communication through an upper inlet 31c and a lower inlet 31d.
- the bore 31b is fitted with a threaded cap 54 through which the piston rod moves being sealed by a gasket 56 as is well known in the art.
- the cap 54 is sealed to the cylinder head by O ring 58.
- the upper inlet 31c to the upper end of the bore 31b is in communication with a pump feed chamber F y passageway 60 which is bored from the chamber F in a longitudinal boss 62 projecting upwardly from the floor 64 of a reservoir R formed in part in the casting A and in part in the cover C to which the cover is fastened by the screws 40 and sealed by gasket 46 as already described.
- the boss 62 adjacent the chamber F is enlarged at 62a as shown in FIG. and is provided with a flat front face 62b flush with the edge 64a of the integral circumambient Wall 64b of the main casting A which forms the reservoir R in part.
- the front face 62! is smooth and cooperates with a similar flat front face 66 of like dimension formed on a boss 67 on the inner side of the cover casting C the two faces being held in contact with each other by suitable means such as bolts 660 to form a metal to metal seal without gaskets.
- the front face 66 on the cover casting C projects a slight distance beyond the plane of the edge 67a of the wall portions of the cover casting C cooperating with the gasket 46 to form the reservoir R, so that when the screws 40 are pulled home to compress the gasket 46, the front faces 62b and 66 are pressed together into close cooperative relation (FIG. 9). Tolerances in manufacture are compensated by the compression of the gasket 46.
- the cooperative relation of the cover C with the main casting A forms the reservoir R and the feed chamber F.
- the upper inlet 310 to the upper end of the bore 31b is also in communication with the reservoir R through a pressure regulating valve 68 which is resiliently pressed against its seat by resilient means 70 anchored on the cover casting C as shown in FIG. 7.
- the lower inlet 31d is also in communication with the reservoir R by means of a manually controllable relief valve 72 (FIG. 9) which includes an elastomer member 172 for reliable sealing, which closes lateral passageway 74 which communicates with the valve seating cavity 76 which in turn communicates with the reservoir R by passageway 78.
- the relief valve 72 is resiliently biased to its seat by helical spring 80, the bias of which is manually controllable by screw member 82 which forms an anchor therefor, the screw members position being controlled by the manual manipulation thereof by a tool inserted in kerf 82a.
- Seal 0 is provided for the member 82 in a well known manner and its removal from the valve cavity is prevented by compressible seal 81 positioned above a spring washer 82b seated in an annular groove 820 in the main casting A.
- the spring bias on the relief valve 72 is reduced, whereby the pressure in the lower side of the bore 31b under the piston is released to allow the motor to be manually lowered, assisted by gravity from the tilted position shown in FIG. 2 to the operative position shown in FIG. 1, in the event there is a power failure to prevent the operation of the electric motor M.
- the reversible electric motor M is connected by its drive shaft 50 to the driver gear 84 of the gear pump P (FIGS. 6 and 7) by a non-circular portion as shown, the driver gear 84 driving the idler gear 86, both being positioned in a cavity 87 in the fiat face 66, the idler gear 86 being mounted on a stud 88, press fitted into a bore in the floor of the cavity 87 to freely rotate thereon, If
- a shallow bore 50b may also be provided in the flat face 62b to form a clearance for the projecting end of the drive shaft 50a extending beyond the forward face of the driver gear 84 (see FIG. 8) to allow for manufacturing tolerances.
- the cavity 90 behind the gear pump and concentric with the shaft 50 communicates with the reservoir R by passageway 92, which relieves the seal 52 for the shaft 50 from a pressure build up arising from the leakage from the gear pump and also supplies lubrication for the shaft at that point.
- a pair of passageways 94 and 96 communicating with passageway 92 are provided terminating at the flat face 66, each being provided with a ball check valve 94a and 96a respectively acting against a seat. Their purpose will be described hereinafter.
- the cavity 100 communicates with a bore 102 in which is seated valve block 104 (FIGS. 7 and 9) being sealed therein by O ring 106, the valve block having a serrated forward face 104a to allow the pressure to enter a flared inner hole 108 and also to cooperate with the flat face 66 on the cover C to hold the block in position in the bore 102 (FIG. 9).
- the cover C has its flat face 66 pierced by a smaller bore 110 concentric with the bore 102 in the opposite casting A, in which is slidably positioned an actuator 112 sealed by an O ring 114, the actuator having a concentric nose 112a extending into the flared central opening 108 to contact the head 116 of a movable hexagonal valve member 118, mounted in counterbore 119 when urged in that direction by pressure acting in an annular chamber 110a on the rear side of the actuator 112, about a stop member 11017.
- the pressure is zero or negative in chamber 11011.
- valve member 118 of hexagonal outer conformation is disclosed and claimed in my copending application Ser. No. 682,247, filed Nov. 13, 1967, assigned to the same assignee.
- an elastomeric sealing member 120 is seated in a forward cavity 122 of the valve member, the flange 124 of the cavity being serrated to allow pressure in the counterbore to flow into the region of the sealing member 120.
- the sealing member has a projecting land 126 beneath the head 116 which coacts with a small annular lip 128 positioned about the converging opening of the flared hole 108 into which the head 116 slidably fits with minimum tolerance, all as described in the aforementioned copending application.
- the elastomeric member 120 is urged toward the lip 128 by helical bias spring 130' positioned in and seated against the undercut of a second counterbore 132 concentric with passageway 31d and bores 102, 119 and 110. Stops 134 are provided in the bore 119 to prevent the bore from being closed by the valve member 118 when in retracted position.
- the chamber F is in communication with the reservoir R via the ball checked passageway 94, which is positioned between a groove g in the flat face 62b at the lower end of the chamber F (FIGS. 6 and 10) which terminates in bore 92 to communicate with the reservoir R.
- the ball valve 94a is so arranged that when the chamber F is feeding fluid to the pump P and therefore is substantially zero pressure, the valve will be open to allow fluid to flow from the reservoir R to the chamber F to make up for piston rod volume.
- the pump P has its direction of rotation reversed so that the driver gear 84 rotates in a counterclockwise direction (FIG. 10)
- fluid will be pumped into chamber F to build up a pressure therein, which will cause the ball valve 94a to close to cut off further communication between the chamber F and the reservoir R.
- the reservoir R is provided with a screw-threaded filler opening 150 in the upper side of the casting C, whereby hydraulic fluid can be added to the system as required to maintain the level L in the reservoir as determined by the lower side of the opening with the piston in retracted position.
- a screw plug 150:: is provided to close the opening.
- a hydraulic device for moving a load in at least two directions comprising a sealed casing divided into a main portion and a second portion cooperating together, each provided with inner and outer planar surfaces facing each other in a cooperative relation to form the sealed casing, a cylinder with a piston assembly movable therein integrally formed in the main casing element with pressure connections for each side of the piston assembly to move the piston assembly in two directions by application of fluid pressure, a reversible gear pump positioned in a cavity in the inner planar surface of the second casing portion, aligned cavities in the inner planar faces of the main portion and the second portion, a control valve seated in the cavity in the main portion, a movable piston to open the control valve in the aligned cavity in the second portion, cooperating cavitie between the inner and outer cooperating planar surfaces in both casing members to provide a reservoir for fluid, grooves formed in the inner planar surface of the main casing portion to cooperate with the gear pump to provide communication with the control valve, passageways in the cas
- the hydraulic device defined in claim 1 further characterized by having the passageways forming the connective communications between the reversible pump, the cylinder with its piston assembly and the reservoir formed by bores in the portions of the sealed casing means.
- the device defined in claim 3 further characterized by having at least one valve in the bores of the casing portions which is directly controlled by the fluid pressure.
- the device defined in claim 1 further characterized by having at least one valve under manual control in the main casing portion to change the predetermined position of the piston assembly.
- control valves being adapted to be responsive to high pressures in the fluid system arising from shock movements of the piston assembly to absorb the shock sufliciently to prevent disruption of the elements of the device.
- the device defined in claim 1 further characterized by providing the main casing portion with mounting 7 8 means at its lower end which allow limited rotation of the 2,984,985 5/ 1961 MacMillin. deviee about pivot means to provide a tilting action to a 2,928,243 3/1960 Albright 6052 rotatable load. 3,301,313 l/ 1967 Schurink 6052 XR References Cited 2,716,995 9/ 1955 Baugh et a1 6()52. XR
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Actuator (AREA)
Description
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US68224867A | 1967-11-13 | 1967-11-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3473325A true US3473325A (en) | 1969-10-21 |
Family
ID=24738871
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US682248A Expired - Lifetime US3473325A (en) | 1967-11-13 | 1967-11-13 | Unitary hydraulic shock absorber and actuator |
Country Status (1)
Country | Link |
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US (1) | US3473325A (en) |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3688733A (en) * | 1970-09-25 | 1972-09-05 | Outboard Marine Corp | Mechanical arrangement for trimming an outboard motor |
US4551973A (en) * | 1982-10-28 | 1985-11-12 | Syntex (U.S.A.) Inc. | Hydraulic power source and valve therefor |
US4654014A (en) * | 1985-10-02 | 1987-03-31 | Sween Corporation | Outboard motor trim system |
US4687448A (en) * | 1985-12-13 | 1987-08-18 | Peirce James G | Outboard motor tilt and trim adaptor apparatus and safety device |
US4786263A (en) * | 1987-10-01 | 1988-11-22 | Outboard Marine Corporation | Marine propulsion device power tilt and trim mechanism |
US5049099A (en) * | 1983-06-15 | 1991-09-17 | Sanshin Kogyo Kabushiki Kaisha | Power tilt device |
US5149285A (en) * | 1989-07-03 | 1992-09-22 | Kabushiki Kaisha Showa Seisakusho | Tilt/trim device for outboard engine |
JPH05238482A (en) * | 1992-11-30 | 1993-09-17 | Sanshin Ind Co Ltd | Power tilt device |
US5746055A (en) * | 1995-03-13 | 1998-05-05 | Sanshin Kogyo Kabushiki Kaisha | Hydraulic tilt and trim control for marine propulsion |
US5975967A (en) * | 1997-02-04 | 1999-11-02 | Showa Corporation | Tilt device for marine propulsion device and method for assembling the tilt device |
US6220029B1 (en) * | 1998-03-13 | 2001-04-24 | Hoerbiger Hydraulik Gmbh | Operating arrangement |
US6309265B1 (en) * | 1999-04-09 | 2001-10-30 | Sanshin Kogyo Kabushiki Kaisha | Power tilt and trim system for outboard drive |
US6572421B2 (en) | 2000-09-01 | 2003-06-03 | Showa Corporation | Tilt device for marine propulsion unit |
US6662559B1 (en) * | 2000-08-18 | 2003-12-16 | Cook Manufacturing Corporation | Hydraulic actuator |
US20080295505A1 (en) * | 2006-01-16 | 2008-12-04 | Volvo Construction Equipment Ab | Method for Springing a Movement of an Implement of a Work Machine |
EP2808562A1 (en) * | 2012-12-11 | 2014-12-03 | Pro Motion, LLC | Self-contained fluid-power servomechanism |
US9695846B2 (en) | 2014-09-25 | 2017-07-04 | The Boeing Company | Micro dampers for prevention of un-commanded motion in mechanical feedback actuators |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1993612A (en) * | 1927-05-20 | 1935-03-05 | Gen Electric | Electroresponsive operating means |
US2640323A (en) * | 1950-12-15 | 1953-06-02 | Detroit Harvester Co | Power unit of the fluid pressure type |
US2657533A (en) * | 1951-03-26 | 1953-11-03 | Borg Warner | Hydraulic control system |
US2693824A (en) * | 1947-01-04 | 1954-11-09 | Vickers Inc | Power transmission valve |
US2716995A (en) * | 1950-09-23 | 1955-09-06 | Gen Motors Corp | Valve for reversible fluid pump |
US2928243A (en) * | 1958-03-12 | 1960-03-15 | Roper Hydraulics Inc | Pump control system |
US2984985A (en) * | 1959-02-16 | 1961-05-23 | Macmillin Hydraulic Engineerin | Hydraulic operating and control system |
US3301313A (en) * | 1963-02-01 | 1967-01-31 | Goetaverken Ab | Hydraulic driving means for operating hatch covers |
-
1967
- 1967-11-13 US US682248A patent/US3473325A/en not_active Expired - Lifetime
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1993612A (en) * | 1927-05-20 | 1935-03-05 | Gen Electric | Electroresponsive operating means |
US2693824A (en) * | 1947-01-04 | 1954-11-09 | Vickers Inc | Power transmission valve |
US2716995A (en) * | 1950-09-23 | 1955-09-06 | Gen Motors Corp | Valve for reversible fluid pump |
US2640323A (en) * | 1950-12-15 | 1953-06-02 | Detroit Harvester Co | Power unit of the fluid pressure type |
US2657533A (en) * | 1951-03-26 | 1953-11-03 | Borg Warner | Hydraulic control system |
US2928243A (en) * | 1958-03-12 | 1960-03-15 | Roper Hydraulics Inc | Pump control system |
US2984985A (en) * | 1959-02-16 | 1961-05-23 | Macmillin Hydraulic Engineerin | Hydraulic operating and control system |
US3301313A (en) * | 1963-02-01 | 1967-01-31 | Goetaverken Ab | Hydraulic driving means for operating hatch covers |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3688733A (en) * | 1970-09-25 | 1972-09-05 | Outboard Marine Corp | Mechanical arrangement for trimming an outboard motor |
US4551973A (en) * | 1982-10-28 | 1985-11-12 | Syntex (U.S.A.) Inc. | Hydraulic power source and valve therefor |
USRE34844E (en) * | 1983-06-15 | 1995-01-31 | Sanshin Kogyo Kabushiki Kaisha | Power tilt device |
US5049099A (en) * | 1983-06-15 | 1991-09-17 | Sanshin Kogyo Kabushiki Kaisha | Power tilt device |
US4654014A (en) * | 1985-10-02 | 1987-03-31 | Sween Corporation | Outboard motor trim system |
US4687448A (en) * | 1985-12-13 | 1987-08-18 | Peirce James G | Outboard motor tilt and trim adaptor apparatus and safety device |
US4786263A (en) * | 1987-10-01 | 1988-11-22 | Outboard Marine Corporation | Marine propulsion device power tilt and trim mechanism |
US5149285A (en) * | 1989-07-03 | 1992-09-22 | Kabushiki Kaisha Showa Seisakusho | Tilt/trim device for outboard engine |
JPH05238482A (en) * | 1992-11-30 | 1993-09-17 | Sanshin Ind Co Ltd | Power tilt device |
US5746055A (en) * | 1995-03-13 | 1998-05-05 | Sanshin Kogyo Kabushiki Kaisha | Hydraulic tilt and trim control for marine propulsion |
US5975967A (en) * | 1997-02-04 | 1999-11-02 | Showa Corporation | Tilt device for marine propulsion device and method for assembling the tilt device |
US6220029B1 (en) * | 1998-03-13 | 2001-04-24 | Hoerbiger Hydraulik Gmbh | Operating arrangement |
US6309265B1 (en) * | 1999-04-09 | 2001-10-30 | Sanshin Kogyo Kabushiki Kaisha | Power tilt and trim system for outboard drive |
US6662559B1 (en) * | 2000-08-18 | 2003-12-16 | Cook Manufacturing Corporation | Hydraulic actuator |
US6572421B2 (en) | 2000-09-01 | 2003-06-03 | Showa Corporation | Tilt device for marine propulsion unit |
US20080295505A1 (en) * | 2006-01-16 | 2008-12-04 | Volvo Construction Equipment Ab | Method for Springing a Movement of an Implement of a Work Machine |
US8065875B2 (en) * | 2006-01-16 | 2011-11-29 | Volvo Construction Equipment Ab | Method for springing a movement of an implement of a work machine |
EP2808562A1 (en) * | 2012-12-11 | 2014-12-03 | Pro Motion, LLC | Self-contained fluid-power servomechanism |
US9695846B2 (en) | 2014-09-25 | 2017-07-04 | The Boeing Company | Micro dampers for prevention of un-commanded motion in mechanical feedback actuators |
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Legal Events
Date | Code | Title | Description |
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AS | Assignment |
Owner name: ELTRA CORPORATION, OHIO Free format text: CERTIFIED COPY OF MERGER FILED IN THE OFFICE OF SECRETARY OF STATE OF DELAWARE ON JUNE 6, 1980, SHOWING MERGER AND CHANGE OF NAME OF ASSIGNOR;ASSIGNOR:ATREL CORPORATION;REEL/FRAME:003992/0237 Effective date: 19811020 Owner name: ELTRA CORPORATION, A CORP. OF NY Free format text: CERTIFIED COPY OF MERGER FILED IN THE OFFICE OF SECRETARY OF STATE OF DELAWARE ON JUNE 6, 1980, SHOWING MERGER AND CHANGE OF NAME OF ASSIGNOR;ASSIGNOR:ATREL CORPORATION (INTO);REEL/FRAME:003992/0237 Effective date: 19811020 |
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Owner name: PRESTOLITE ELECTRIC INCORPORATED, OHIO Free format text: RELEASE BY SECURED PARTY OF SECURITY AGREEMENTS RECORDED ON REEL 4568 FRAME 0105 AND REEL 4626 FRAME 0084-0095;ASSIGNOR:CITICORP NORTH AMERICA, INC., FORMERLY CITICORP INDUSTRIAL CREDIT, INC.;REEL/FRAME:005967/0610 Effective date: 19911025 Owner name: PRESTOLITE ELECTRIC INCORPORATED Free format text: RELEASE BY SECURED PARTY OF SECURITY AGREEMENTS RECORDED ON REEL 4568 FRAME 0105 AND REEL 4626 FRAME 0084-0095;ASSIGNOR:CITICORP NORTH AMERICA, INC., FORMERLY CITICORP INDUSTRIAL CREDIT, INC.;REEL/FRAME:005967/0610 Effective date: 19911025 Owner name: PEI 1991 ACQUISITION, INC., OHIO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:PRESTOLITE ELECTRIC INCORPORATED;REEL/FRAME:005967/0628 Effective date: 19911029 Owner name: PEI 1991 ACQUISITION, INC. Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:PRESTOLITE ELECTRIC INCORPORATED;REEL/FRAME:005967/0628 Effective date: 19911029 |