US20040213689A1 - Fuel injection pump and rotation-linear motion transforming mechanism with safeguard - Google Patents

Fuel injection pump and rotation-linear motion transforming mechanism with safeguard Download PDF

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Publication number
US20040213689A1
US20040213689A1 US10/827,418 US82741804A US2004213689A1 US 20040213689 A1 US20040213689 A1 US 20040213689A1 US 82741804 A US82741804 A US 82741804A US 2004213689 A1 US2004213689 A1 US 2004213689A1
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US
United States
Prior art keywords
cam ring
cam
plunger
rotation
safeguard
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.)
Abandoned
Application number
US10/827,418
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English (en)
Inventor
Katsumi Mori
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.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MORI, KATSUMI
Publication of US20040213689A1 publication Critical patent/US20040213689A1/en
Abandoned 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics

Definitions

  • the present invention relates generally to a fuel injection pump and a rotation-to-linear motion transforming mechanism installed in such a pump which may be employed in delivering fuel to a common rail for diesel engines, and more particularly to a safeguard for such a fuel injection pump and a rotation-to-linear motion transforming mechanism which is responsive to input of an excessive torque to be broken to avoid breakage of the device itself.
  • Japanese Patent First Publication No. 2000-240531 assigned to the same assignee as that of this application, discloses a typical one of fuel injection pumps which is equipped with a rotation-to-linear motion transforming mechanism, as illustrated in FIG. 5.
  • the rotation-to-linear motion transforming mechanism includes an eccentric cam J 2 , a cam ring J 4 , and a plunger J 6 .
  • the eccentric cam J 2 is coupled to a cam shaft J 1 so that it rotates eccentrically with respect to the cam shaft J 1 .
  • the cam ring J 4 is fitted on the periphery of the eccentric cam J 2 through a hollow cylindrical plain bearing (bush) J 3 and urged by the cam ring J 4 to rotate.
  • the plunger J 6 is disposed within a cylinder head J 5 movably in a direction perpendicular to an axis of rotation of the eccentric cam J 2 and urged by a coil spring into slidable abutment with the cam ring J 4 .
  • the plunger J 6 has a flat surface J 8 formed on an end thereof.
  • the cam ring J 4 has formed on the periphery thereof a flat surface J 7 on which the flat surface J 8 of the plunger J 6 abuts slidably, thereby holding the cam ring J 4 from rotating following rotation of the eccentric cam J 2 . This causes the plunger J 6 to reciprocate within the cylinder head J 5 in synchronization with the rotation of the cam shaft J 1 .
  • the cam ring J 4 is covered with a housing (not shown).
  • a cam chamber is defined between the cam ring J 4 and the housing and filled with fuel which serves to lubricate a contact surface between the cam ring J 4 and the plunger J 6 .
  • the breakage may further cause fragmentations of the plunger J 6 to be forced into a gap between the cam ring J 4 and the housing (usually made of aluminum) surrounding the cam ring J 4 , which results in breakage of the housing.
  • the avoidance of breakage of the housing requires an increased clearance between the cam ring J 4 and the housing, but it results in an increase in size of the fuel injection pump.
  • a rotation-to-linear motion transforming apparatus which comprises: (a) an eccentric cam coupled to a torque input shaft, the eccentric cam being rotated eccentrically with respect to the torque input shaft; (b) a cam ring which is placed in contact of an inner wall thereof with the eccentric cam and to be urged by the eccentric cam to rotate, the cam ring having a flat surface formed on an outer periphery thereof; (c) a plunger placed to be movable linearly in a direction perpendicular to an axis of rotation of the eccentric cam, the plunger having a flat surface which is pressed against the cam ring in slidable abutment with the flat surface of the cam ring so as to hold the cam ring from rotating to move the plunger linearly; and (d) a safeguard provided in the cam ring which is responsive to application of a physical load greater than a given degree in a direction of rotation of the eccentric cam to undergo breakage.
  • the safeguard is provided in a portion of the cam ring which is out of abutment with the plunger and to which a tensile stress is added when resistance to sliding motion of the cam ring relative to the plunger increases. Specifically, when the contact surface between the cam ring and the plunger creates the greater resistance to thrust of the plunger, a smaller load acting on the cam ring in the direction of rotation thereof results in the breakage of the safeguard.
  • the safeguard may be implemented by a groove formed in at least one of an outer periphery and an inner periphery of the cam ring.
  • the groove may be of V-shape, U-shape, or C-shape in cross section.
  • the groove may extend from one end to the other end of the cam ring in an axial direction thereof or alternatively be formed only in a portion of the cam ring.
  • a fuel injection pump for an engine which comprises: (a) a housing having formed therein a cam chamber into which fuel is supplied; (b) an eccentric cam disposed within the cam chamber of the housing in mechanical connection with a torque input shaft into which torque outputted by an engine is inputted, the eccentric cam being rotated eccentrically with respect to the torque input shaft; (c) a cam ring which is placed in contact of an inner wall thereof with the eccentric cam and to be urged by the eccentric cam to rotate, the cam ring having a flat surface formed on an outer periphery thereof; (d) a plunger placed to be movable linearly in a direction perpendicular to an axis of rotation of the eccentric cam, the plunger having a flat surface which is pressed against the cam ring in slidable abutment with the flat surface of the cam ring so as to hold the cam ring from rotating, thereby urging the plunger to reciprocate to increase and decrease a volume of a fuel press
  • the safeguard works to have only the cam ring experience breakage, thus resulting in minimized damage to the fuel injection pump and avoidance of leakage of fuel from the fuel injection pump.
  • the use of the safeguard eliminates the need for increasing a clearance between the housing and the cam ring, that is, the size of the fuel injection pump.
  • the safeguard is provided in a portion of the cam ring which is out of abutment with the plunger and to which a tensile stress is added when resistance to sliding motion of the cam ring relative to the plunger increases. Specifically, when the contact surface between the cam ring and the plunger creates the greater resistance to thrust of the plunger, a smaller load acting on the cam ring in the direction of rotation thereof results in the breakage of the safeguard.
  • the safeguard is implemented by a groove formed in at least one of an outer periphery and an inner periphery of the cam ring.
  • the groove may be of V-shape, U-shape, or C-shape in cross section.
  • the groove may extend from one end to the other end of the cam ring in an axial direction thereof or alternatively be formed only in a portion of the cam ring.
  • FIG. 1 is a sectional view as taken perpendicular to an axis of rotation of a fuel injection pump according to the invention
  • FIG. 2 is a sectional view as taken along the axis of rotation of the fuel injection pump as illustrated in FIG. 1;
  • FIGS. 3 ( a ), 3 ( b ), 3 ( c ), 3 ( d ), 3 ( e ), 3 ( f ), 3 ( g ), and 3 ( h ) are partially sectional views which show time-sequential operations of plungers and a cam ring;
  • FIGS. 4 ( a ), 4 ( b ), 4 ( c ), and 4 ( d ) are partially sectional views which shows time-sequential operations of a safeguard when a contact surface between a plunger and a cam ring is baked;
  • FIG. 5 is a partially sectional view which shows a rotation-to-linear motion transforming mechanism used in a conventional fuel injection pump for automotive engines.
  • FIGS. 1 and 2 there is shown a fuel injection pump 1 according to the invention which is designed to compress and deliver high-pressure fuel to a common rail of a diesel engine (not shown).
  • the fuel injection pump 1 consists essentially of a feed pump 2 , a regulator valve 3 , a fuel regulator valve 4 made of a solenoid control valve (SCV), and a high-pressure pump 5 .
  • the feed pump 2 is illustrated in FIG. 2 as being developed through 90°.
  • the fuel injection pump 1 has a housing assembly made up of a body 6 , a cover 7 , and a cylinder head 8 .
  • the body 6 and the cover 7 are each made of aluminum.
  • the cylinder head 8 is made of iron.
  • the feed pump 2 is implemented by a trochoid pump and driven by a cam shaft 11 to suck the fuel from a fuel inlet 10 and supply it to the high-pressure pump 5 through the fuel regulator valve 4 .
  • the cam shaft 11 is driven by a crankshaft of the engine.
  • the regulator valve 3 is disposed in a fuel path communicating between an outlet and an inlet of the feed pump 2 .
  • the regulator valve 3 is opened to keep the discharge pressure thereof below the allowable level.
  • the fuel regulator valve 4 is equipped with a coil which is energized by an ECU (engine control unit not shown) to control the amount of fuel to be supplied to the high-pressure pump 5 , thereby controlling the pressure of fuel within the common rail.
  • ECU engine control unit not shown
  • the high-pressure pump 5 works to pressurize the fuel supplied from the fuel regulator valve 4 and feed it to the common rail.
  • the high-pressure pump 5 is made up of a rotation-to-linear motion transforming mechanism 13 , two plunger pumps 14 , suction valves 16 , and a discharge valve 17 .
  • the rotation-to-linear motion transforming mechanism 13 works to transform torque transmitted from the engine into reciprocating motion of the plungers 12 .
  • Each of the plunger pumps 14 has a pressurizing chamber 15 into which the fuel is sucked by the motion of the plunger 12 from the suction valve 16 .
  • the discharge valve 17 works to deliver the fuel pressurized in the pressurizing chambers 15 to the common rail. Only either one of the plunger pumps 14 may be installed in the high-pressure pump 5 .
  • the rotation-to-linear motion transforming mechanism 13 is installed within a cam chamber 18 formed in the housing assembly.
  • the rotation-to-linear motion transforming mechanism 13 consists of an eccentric cam 19 , a cam ring 21 , and the plungers 12 .
  • the cam ring 21 is fitted around the eccentric cam 19 .
  • the plungers 12 are pressed against the cam ring 21 so that they reciprocate following movement of the cam ring 21 .
  • the cam chamber 18 is filled with the fuel supplied through a fuel path 22 from the feed pump 2 .
  • the fuel path 22 has formed therein an orifice 22 a .
  • An excess of the fuel within the cam chamber 18 is discharged from a fuel outlet 23 and returned back to the fuel pump (not shown).
  • the eccentric cam 19 is made of a cylindrical member which is joined to or formed integrally with the cam shaft 11 driven by the output torque of the engine. Rotation of the cam shaft 11 causes the eccentric cam 19 to rotate eccentrically with respect to the axis of rotation of the cam shaft 11 .
  • the cam ring 21 is, as clearly shown in FIG. 2, installed to be slidable on the eccentric cam 19 through a hollow cylindrical plain bearing (bush) 24 .
  • the cam ring 21 has formed therein a through hole 21 a within which the eccentric cam 19 and the plain bearing 24 are disposed.
  • the cam ring 21 has formed on the periphery thereof flat surfaces 21 b on which the plungers 12 abut slidably.
  • the two plungers 12 are opposed to each other in alignment across the cam ring 21 .
  • Two of the flat surfaces 21 b on which the plungers 12 abut are opposed to each other.
  • Each of the plungers 12 has a disc or tappet 12 a formed integrally on an end thereof.
  • the tappet 12 a has a flat end surface 12 b (will also be referred to as a plunger surface below) which is in slidable abutment with the flat surface 21 b of the cam ring 21 .
  • a coil spring 25 Disposed between each of the tappets 12 a and the cylinder head 8 is a coil spring 25 which works to urge the plunger surface 12 b into constant abutment with one of the flat surfaces 21 b of the cam ring 21 .
  • the sum of the spring pressure of the springs 25 and the fuel pressure acting on the plungers 12 works to hold the cam ring 21 from turning and urge the cam ring 21 to move eccentrically with the flat surfaces 21 b oriented in the same directions, thereby reciprocating the plungers 12 cyclically.
  • Each of the plungers 12 is slidably retained within a cylindrical chamber 8 a (will also be referred to as a cylinder below) formed in the cylinder head 8 .
  • the plungers 12 are, as described above, reciprocated by the cam ring 21 to increase or decrease the volume of the pressurizing chambers 15 cyclically.
  • each of the plungers 12 moves downward (i.e., toward the center of rotation of the eccentric cam 19 ), it will cause a corresponding one of the pressurizing chambers 15 to be increased in volume, thus resulting in a drop in pressure within the pressurizing chamber 15 .
  • This pressure drop causes the discharge valve 17 to be closed and the suction valve 16 to be opened, thereby sucking into the pressurizing chamber 15 the fuel which has been pressurized by the feed pump 2 and regulated in amount by the fuel regulator valve 4 .
  • the plungers 12 are, as described above, opposed diametrically to each other across the cam ring 21 , so that they are moved in 180° out of phase with each other. In other words, when one of the plungers 12 is experiencing the suction stroke, the other is experiencing the compression stroke.
  • a counterclockwise rotation of the cam shaft 11 will cause the eccentric cam 19 and the cam ring 21 to rotate eccentrically with respect to the cams shaft 11 .
  • the angular position ⁇ of the cam shaft 11 lies within a range of 0° and 180° (i.e., 0° ⁇ 180°)
  • the upper plunger 12 is in the compression stroke.
  • the lower plunger 12 is placed in the suction stroke when the angular position ⁇ of the cam shaft 11 lies within a range of 0° and 180° (i.e., 0° ⁇ 180°). Specifically, the lower plunger 12 moves from the top dead center position to the bottom dead center position within the cylinder chamber 8 a between 0° and 180°.
  • the pressure urging one of the plungers 12 experiencing the compression stroke toward the cam ring 21 is greater than that urging the other plunger 12 experiencing the suction stroke toward the cam ring 21 .
  • the flat surfaces 21 b of the cam ring 21 are in unparallel to each other.
  • the plungers 12 have longitudinal center lines extending parallel to each other (or in alignment with each other). In other words, travel paths of the plungers 12 extend parallel to each other. Therefore, when the pressure acting on one of the plungers 12 is greater than that acting on the other one, one of the flat surface 21 b of the cam ring 21 on which the greater of the pressures acts is urged into surface-to-surface contact with a corresponding one of the plunger surfaces 12 b of the plungers 12 .
  • one of the plungers 12 that is experiencing the suction stroke has the surface 12 b thereof inclined to the flat surface 21 b of the cam ring 21 to create the gap therebetween into which the fuel within the cam chamber 18 flows for lubrication.
  • the water enters between the flat surface 21 b of the cam ring 21 and the plunger surface 12 b for some reason it will result in a lack of lubrication therebetween, which may lead to baking of a contact surface between the flat surface 21 b and the plunger surface 12 b .
  • the eccentric cam 19 revolving the cam ring 21 eccentrically is, as described above, driven by the output of the engine.
  • the baking of the contact surface thus, causes a greater toque outputted from the engine to be transmitted through the contact surface to the plungers 12 , which results in breakage of the plungers 12 .
  • the breakage may further cause fragmentations of the plungers 12 to be forced into a gap between the cam ring 21 and the housing body 6 surrounding the cam ring 21 , which results in breakage of the housing body 6 .
  • the cam ring 21 is, as shown in FIG. 1, equipped with safeguards 26 which are responsive to input of a given degree of torque to the cam ring 21 to break the cam ring 21 mechanically.
  • the safeguards 26 are preferably designed to break the cam ring 21 upon input of torque which is somewhat greater in degree than a maximum torque acting on the cam ring 21 when the fuel injection pump 1 is operating normally and at least smaller than a failure strength of the housing body 6 surrounding the cam ring 21 .
  • the safeguards 26 are implemented by structural portions of the cam ring 21 which have a mechanical strength weak enough to create cracks in the cam ring 21 when an excessive torque is applied to the cam ring 21 .
  • the safeguards 26 are each made of a V-groove formed in an outer wall of the cam ring 21 .
  • Each of the V-grooves may extend from one end to the other end of the cam ring 21 in an axial direction of the cam ring 21 or alternatively be formed only in a portion of the outer wall of the cam ring 21 .
  • the safeguards 26 are formed in diametrically opposed side surfaces of the cam ring 21 which do not abut the plungers surfaces 12 b and at locations on which a greater tensile stress acts when the resistance to sliding motion of the cam ring 21 and the plungers 12 undesirably increases, for example, when the contact surfaces between the cam ring 21 and the plungers 12 are baked.
  • Only the one safeguard 26 may be formed in the cam ring 21 .
  • the two safeguards 26 are preferably used in order to ensure the breakage of the cam ring 21 if either of the plungers 12 is seized.
  • the eccentric cam 19 is driven by the output of the engine, so that it continues to rotate even when the contact surface, as indicated by A in FIG. 4( b ), between the flat surface 21 b of the cam ring 21 and the plunger surface 12 b is baked during the compression stroke of the plunger 12 .
  • Each of the safeguards 26 is provided in a portion of the cam ring 21 on which a great tensile stress acts. Thus, if a plunger thrust resistance is developed on the contact surface between the cam ring 21 and each of the plungers 12 , the safeguards 26 are responsive to a physical load on the cam ring 12 in a direction of rotation thereof to undergo breakage and thus work to minimize the damage to parts other than the cam ring 21 .
  • Each of the safeguards 26 may alternatively be made of a dent or a groove that is different in shape from V.
  • the safeguards 26 may be made of a U- or C-shaped groove.
  • the safeguards 26 may alternatively be formed only in an inner peripheral wall of the cam ring 21 or both in the outer and inner peripheral walls of the cam ring 21 .
  • Each of the safeguards 26 may alternatively be implemented by decreasing the thickness between the outer and inner peripheral surfaces of the cam ring 21 to form thick walls.
  • the thick wall may extend from one end to the other of the cam ring 21 in the axial direction of the cam ring 21 or alternatively be formed intermediate between the ends of the cam ring 21 .
  • Each the safeguards 26 may alternatively be implemented by one or some holes extending through the outer and inner peripheral surfaces of the cam ring 21 .
  • Each of the safeguards 26 may alternatively be located in a portion of the cam ring 21 which is responsive to a compressive stress to create a crack in the cam ring 21 .
  • the safeguards 26 are preferably designed to be broken upon application of a physical load in a direction of rotation of the cam ring 21 .
  • the safeguards 26 are, as described above, provided in the rotation-to-linear motion transforming mechanism 13 , but may be used in any other type of rotation-to-linear motion transforming mechanism equipped with a cam ring and a plunger.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US10/827,418 2003-04-23 2004-04-20 Fuel injection pump and rotation-linear motion transforming mechanism with safeguard Abandoned US20040213689A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003-118964 2003-04-23
JP2003118964A JP3861846B2 (ja) 2003-04-23 2003-04-23 回転直線変換装置および燃料噴射ポンプ

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US20040213689A1 true US20040213689A1 (en) 2004-10-28

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US10/827,418 Abandoned US20040213689A1 (en) 2003-04-23 2004-04-20 Fuel injection pump and rotation-linear motion transforming mechanism with safeguard

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JP (1) JP3861846B2 (ja)
DE (1) DE102004019626B4 (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103047100A (zh) * 2013-01-10 2013-04-17 无锡开普机械有限公司 具有凸轮轴轴套的转子泵
US20180045187A1 (en) * 2015-02-25 2018-02-15 A.H.M.S., Inc. Drive mechanism module for a reciprocating pump
CN118510988A (zh) * 2021-07-14 2024-08-16 康明斯-斯堪尼亚高压共轨系统有限责任公司 燃油泵组件

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006043187B3 (de) * 2006-09-14 2008-04-03 Siemens Ag Fluidpumpe, insbesondere Hochdruck-Kraftstoffpumpe für Einspritzsysteme von Brennkraftmaschinen
DE102007002730B4 (de) * 2007-01-18 2012-03-01 Continental Automotive Gmbh Radialkolbenpumpe zur Kraftstoffförderung sowie Herstellungsverfahren hierfür
JP5633387B2 (ja) * 2011-01-24 2014-12-03 株式会社デンソー 燃料供給ポンプ

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5850817A (en) * 1995-11-29 1998-12-22 Lucas Industries Public Limited Co. Fuel pump
US5873784A (en) * 1993-10-25 1999-02-23 Toyota Jidosha Kabushiki Kaisha Power steering system having a mechanical safety breaker
US20010015200A1 (en) * 2000-02-18 2001-08-23 Katsumi Mori Fuel injection pump
US20030106427A1 (en) * 2001-12-07 2003-06-12 Koichi Nagai Fuel injection pump
US20030108443A1 (en) * 2001-12-12 2003-06-12 Masashi Suzuki Fuel injection pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4088738B2 (ja) * 1998-12-25 2008-05-21 株式会社デンソー 燃料噴射ポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5873784A (en) * 1993-10-25 1999-02-23 Toyota Jidosha Kabushiki Kaisha Power steering system having a mechanical safety breaker
US5850817A (en) * 1995-11-29 1998-12-22 Lucas Industries Public Limited Co. Fuel pump
US20010015200A1 (en) * 2000-02-18 2001-08-23 Katsumi Mori Fuel injection pump
US20030106427A1 (en) * 2001-12-07 2003-06-12 Koichi Nagai Fuel injection pump
US20030108443A1 (en) * 2001-12-12 2003-06-12 Masashi Suzuki Fuel injection pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103047100A (zh) * 2013-01-10 2013-04-17 无锡开普机械有限公司 具有凸轮轴轴套的转子泵
US20180045187A1 (en) * 2015-02-25 2018-02-15 A.H.M.S., Inc. Drive mechanism module for a reciprocating pump
US10415554B2 (en) * 2015-02-25 2019-09-17 A.H.M.S., Inc. Drive mechanism module for a reciprocating pump
CN118510988A (zh) * 2021-07-14 2024-08-16 康明斯-斯堪尼亚高压共轨系统有限责任公司 燃油泵组件

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Publication number Publication date
DE102004019626B4 (de) 2015-07-09
JP3861846B2 (ja) 2006-12-27
JP2004324497A (ja) 2004-11-18
DE102004019626A1 (de) 2004-11-25

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AS Assignment

Owner name: DENSO CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MORI, KATSUMI;REEL/FRAME:015236/0961

Effective date: 20040409

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION