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US20040051252A1 - Angled gap compression rings with end relief - Google Patents

Angled gap compression rings with end relief Download PDF

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Publication number
US20040051252A1
US20040051252A1 US10/243,967 US24396702A US2004051252A1 US 20040051252 A1 US20040051252 A1 US 20040051252A1 US 24396702 A US24396702 A US 24396702A US 2004051252 A1 US2004051252 A1 US 2004051252A1
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Prior art keywords
ring
gap
compression ring
longitudinal axis
relieved
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Granted
Application number
US10/243,967
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US6715767B1 (en
Inventor
Paul Meernik
Thomas Perry
Martin Kramer
Larry Byrnes
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GM Global Technology Operations LLC
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Individual
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Priority to US10/243,967 priority Critical patent/US6715767B1/en
Assigned to GENERAL MOTORS CORPORATION reassignment GENERAL MOTORS CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BYRNES, LARRY EDWARD, KRAMER, MARTIN STEPHEN, MEERNIK, PAUL RICHARD, PERRY, THOMAS ARTHUR
Priority to DE10341782A priority patent/DE10341782A1/en
Publication of US20040051252A1 publication Critical patent/US20040051252A1/en
Application granted granted Critical
Publication of US6715767B1 publication Critical patent/US6715767B1/en
Assigned to GM GLOBAL TECHNOLOGY OPERATIONS, INC. reassignment GM GLOBAL TECHNOLOGY OPERATIONS, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GENERAL MOTORS CORPORATION
Assigned to UNITED STATES DEPARTMENT OF THE TREASURY reassignment UNITED STATES DEPARTMENT OF THE TREASURY SECURITY AGREEMENT Assignors: GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Assigned to CITICORP USA, INC. AS AGENT FOR BANK PRIORITY SECURED PARTIES, CITICORP USA, INC. AS AGENT FOR HEDGE PRIORITY SECURED PARTIES reassignment CITICORP USA, INC. AS AGENT FOR BANK PRIORITY SECURED PARTIES SECURITY AGREEMENT Assignors: GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Assigned to GM GLOBAL TECHNOLOGY OPERATIONS, INC. reassignment GM GLOBAL TECHNOLOGY OPERATIONS, INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: UNITED STATES DEPARTMENT OF THE TREASURY
Assigned to GM GLOBAL TECHNOLOGY OPERATIONS, INC. reassignment GM GLOBAL TECHNOLOGY OPERATIONS, INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: CITICORP USA, INC. AS AGENT FOR BANK PRIORITY SECURED PARTIES, CITICORP USA, INC. AS AGENT FOR HEDGE PRIORITY SECURED PARTIES
Assigned to UNITED STATES DEPARTMENT OF THE TREASURY reassignment UNITED STATES DEPARTMENT OF THE TREASURY SECURITY AGREEMENT Assignors: GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Assigned to UAW RETIREE MEDICAL BENEFITS TRUST reassignment UAW RETIREE MEDICAL BENEFITS TRUST SECURITY AGREEMENT Assignors: GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Assigned to GM GLOBAL TECHNOLOGY OPERATIONS, INC. reassignment GM GLOBAL TECHNOLOGY OPERATIONS, INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: UAW RETIREE MEDICAL BENEFITS TRUST
Assigned to GM GLOBAL TECHNOLOGY OPERATIONS, INC. reassignment GM GLOBAL TECHNOLOGY OPERATIONS, INC. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: UNITED STATES DEPARTMENT OF THE TREASURY
Assigned to WILMINGTON TRUST COMPANY reassignment WILMINGTON TRUST COMPANY SECURITY AGREEMENT Assignors: GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Assigned to GM Global Technology Operations LLC reassignment GM Global Technology Operations LLC CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/14—Joint-closures

Definitions

  • This invention relates to engine piston compression rings having modified gap end configurations.
  • ring joints have been used including lap joints, angle joints, seal joints, and butt joints.
  • modified ring joints may still allow end butting to occur under severe conditions such as low temperature cold starting and warm up.
  • the present invention provides engine piston compression rings which can minimize negative effects of ring gap end butting while optionally providing smaller ring gaps and reduced gas blowby in normal operation.
  • the invention controls deflection of the ring ends by using an angled joint and a relieved ring end.
  • the angled joint and an appropriately placed relief area allow the relieved ring end to deflect a substantial distance after butting of the ring ends and before the relieved end engages a wall of an associated ring groove of the piston.
  • the direction of deflection is controlled by the angle and direction of the ring joint. Deflecting the relieved portion of the ring end allows additional relative ring expansion after ring end butting without increasing the ring load against the cylinder bore. Thus, harmful effects of end butting are minimized and the gap between the ring ends can be reduced, resulting in reduced blowby.
  • a compression ring has a gap that forms an angle with respect to a radius drawn from a longitudinal axis. Butting of the ring ends at the gap causes one end of the ring to be deflected inward and that one end is relieved for a portion along an inner edge. The relieved portion slopes outward toward the ring end where the radial thickness of the ring is smallest. This design creates end relief, which allows the relieved end of the ring to bend into the annular piston ring groove instead of increasing ring load against the cylinder bore.
  • a variation of the previously described embodiment has a slot adjacent the relieved portion that extends outward from the inner edge to promote bending of the relieved end. This slot decreases the force required during end butting to move the relieved end inward toward the piston instead of increasing ring load against the cylinder bore.
  • the relieved portion is generally circumferential with a transition portion to the full ring thickness. This design creates end relief, which allows the relieved end to bend a greater distance than the previous embodiments.
  • the compression ring has a gap that forms an angle with respect to the longitudinal axis of the ring. Butting of the ring ends at the gap causes one end of the ring to slide up on the angled other end so that the one end is relieved for a portion along the upper side of the ring. The relieved portion slopes downward toward the ring end where the longitudinal thickness of the ring is smallest.
  • This design creates a form of end relief which allows the relieved end of the ring to slide toward the top of the annular piston ring groove instead of bending in toward the inner diameter of the ring groove like the other embodiments referred to.
  • the invention is particularly useful in avoiding negative effects of ring end butting which may occur under severe low temperature cold engine starting and warm-up conditions. However, it can also reduce effects of end butting under other conditions and may be used to reduce ring gap dimensions with resulting reductions of gas blowby during normal engine running.
  • FIG. 1 is a top view of a first embodiment of engine piston compression ring according to the invention
  • FIG. 2 is an enlarged side view from the line 2 - 2 of FIG. 1 showing the gap portion of the ring;
  • FIG. 4 is a view similar to FIG. 3 showing a modified embodiment of piston compression ring
  • FIG. 7 is an enlarged fragmentary side view of the embodiment of FIG. 6.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

An engine piston compression ring designed to reduce the negative effects of ring end butting and reduce blowby. The compression ring has a gap forming an angle with a longitudinal axis of the ring or with a radius drawn from the axis. A relieved portion is provided along the upper or inner side of the ring adjacent one end, depending upon the direction of the gap angle. The relieved portion slopes along the upper or inner side toward the one end where the longitudinal thickness of the ring is smallest.

Description

    TECHNICAL FIELD
  • This invention relates to engine piston compression rings having modified gap end configurations. [0001]
    • BACKGROUND OF THE INVENTION
  • It is known in the art relating to engine piston compression rings that joints between the ring ends should allow enough space to normally avoid ring gap end butting. The traditional approach used to minimize end butting has been to increase the gap size between the ring ends. However, increasing the gap size between the ring ends increases the amount of combustion gas blowby. [0002]
  • Various types of ring joints have been used including lap joints, angle joints, seal joints, and butt joints. However, modified ring joints may still allow end butting to occur under severe conditions such as low temperature cold starting and warm up. [0003]
    • SUMMARY OF THE INVENTION
  • The present invention provides engine piston compression rings which can minimize negative effects of ring gap end butting while optionally providing smaller ring gaps and reduced gas blowby in normal operation. [0004]
  • The invention controls deflection of the ring ends by using an angled joint and a relieved ring end. The angled joint and an appropriately placed relief area allow the relieved ring end to deflect a substantial distance after butting of the ring ends and before the relieved end engages a wall of an associated ring groove of the piston. The direction of deflection is controlled by the angle and direction of the ring joint. Deflecting the relieved portion of the ring end allows additional relative ring expansion after ring end butting without increasing the ring load against the cylinder bore. Thus, harmful effects of end butting are minimized and the gap between the ring ends can be reduced, resulting in reduced blowby. [0005]
  • In one embodiment of the invention, a compression ring has a gap that forms an angle with respect to a radius drawn from a longitudinal axis. Butting of the ring ends at the gap causes one end of the ring to be deflected inward and that one end is relieved for a portion along an inner edge. The relieved portion slopes outward toward the ring end where the radial thickness of the ring is smallest. This design creates end relief, which allows the relieved end of the ring to bend into the annular piston ring groove instead of increasing ring load against the cylinder bore. [0006]
  • A variation of the previously described embodiment has a slot adjacent the relieved portion that extends outward from the inner edge to promote bending of the relieved end. This slot decreases the force required during end butting to move the relieved end inward toward the piston instead of increasing ring load against the cylinder bore. [0007]
  • In another embodiment of the invention having a similarly angled gap, the relieved portion is generally circumferential with a transition portion to the full ring thickness. This design creates end relief, which allows the relieved end to bend a greater distance than the previous embodiments. [0008]
  • In a differing fourth embodiment, the compression ring has a gap that forms an angle with respect to the longitudinal axis of the ring. Butting of the ring ends at the gap causes one end of the ring to slide up on the angled other end so that the one end is relieved for a portion along the upper side of the ring. The relieved portion slopes downward toward the ring end where the longitudinal thickness of the ring is smallest. This design creates a form of end relief which allows the relieved end of the ring to slide toward the top of the annular piston ring groove instead of bending in toward the inner diameter of the ring groove like the other embodiments referred to. [0009]
  • The invention is particularly useful in avoiding negative effects of ring end butting which may occur under severe low temperature cold engine starting and warm-up conditions. However, it can also reduce effects of end butting under other conditions and may be used to reduce ring gap dimensions with resulting reductions of gas blowby during normal engine running. [0010]
  • These and other features and advantages of the invention will be more fully understood from the following description of certain specific embodiments of the invention taken together with the accompanying drawings.[0011]
    • BRIEF DESCRIPTION OF THE DRAWINGS
  • In the drawings: [0012]
  • FIG. 1 is a top view of a first embodiment of engine piston compression ring according to the invention; [0013]
  • FIG. 2 is an enlarged side view from the line [0014] 2-2 of FIG. 1 showing the gap portion of the ring;
  • FIG. 3 is an enlarged top view of the gap portion of the ring shown in FIG. 2; [0015]
  • FIG. 4 is a view similar to FIG. 3 showing a modified embodiment of piston compression ring; [0016]
  • FIG. 5 is a view similar to FIGS. 3 and 4 showing another modified embodiment of piston compression ring; [0017]
  • FIG. 6 is an enlarged fragmentary top view showing the gap portion of a distinct alternative embodiment of piston compression ring according to the invention; and [0018]
  • FIG. 7 is an enlarged fragmentary side view of the embodiment of FIG. 6. [0019]
    • DESCRIPTION OF THE PREFERRED EMBODIMENT
  • Referring now to FIGS. 1 and 2 of the drawings in detail, [0020] numeral 10 generally indicates an engine piston compression ring. Ring 10 includes an inner edge 12, outer face 14, upper side 16, and a lower side 18. A gap 20 is cut through the ring to provide for installation and expansion. Ring 10 is centered on a longitudinal axis 22 and has a radius 24 extending through the gap 20. The gap extends parallel with the longitudinal axis 22.
  • FIGS. [0021] 3-7 following indicate various embodiments of the invention wherein like numerals refer to like features.
  • FIG. 3 shows enlarged the portion of the [0022] ring 10 in the circle 2 of FIG. 1 including the gap 20. Gap 20 is defined by opposed ends 26, 28 of the ring and is cut at an angle with respect to the radius 24. The inner edge 12 of the ring is cut away adjacent the end 28 to form a relieved portion 30. The relieved portion 30 is sloped outward toward the end 28, where the radial thickness of the ring is smallest. Dashed line 32 indicates the outline of the normal ring thickness, showing the region of end relief.
  • FIG. 4 is similar to FIGS. [0023] 1-3 but differs in that the ring 33 includes a slot 34 adjacent to relieved portion 30 to increase resilience of the relieved portion 30.
  • FIG. 5 is similar to FIGS. [0024] 1-3 but differs in that ring 35 has a modified relieved portion 36. Relieved portion 36 has a reduced radial thickness with a generally circumferential configuration and adjoins a transition portion 38 extending to the full ring depth for further increasing resilience. Dashed line 40 indicates the outline of the normal ring thickness.
  • FIGS. 6 and 7 show another embodiment of [0025] piston compression ring 42 wherein a gap 44 is cut through the ring to provide for installation and expansion. The ring is also centered on a longitudinal axis 22 and has a radius 24 extending through the gap 44. The ring differs from the previously described embodiments in that the gap 44 forms an angle with respect to the longitudinal axis 22 but is aligned with the radius 24. Gap 44 is defined by opposed ends 46, 48 of the ring. The upper side 16 of the ring is cut away adjacent the end 46 to form a relieved portion 50. The relieved portion 50 slopes downward toward the end 46 where the longitudinal thickness of the ring is smallest. Dashed line 52 indicates the outline of the normal ring thickness, showing the region of end relief.
  • In operation of the embodiments of FIGS. [0026] 1-7 the ring ends may butt in extreme conditions, such as cold engine starting and warm up. In the embodiments of FIGS. 1-5 extreme conditions may cause the gap 20 to close and the ring ends 26, 28 to butt. Further relative expansion of the ring then causes the relieved end 28 to slide along the opposite angled end 26 as the relieved end 28 is deflected inward toward the inner diameter of the annular piston ring groove. This allows additional relative expansion of the ring to occur without increasing the ring load against the cylinder bore.
  • In the embodiments of FIGS. [0027] 6-7 extreme conditions may cause the gap 44 to close and the ring ends 46, 48 to butt. Further relative expansion of the ring then causes the relieved end 46 to slide along the opposite angled end 48 as the relieved end 46 is deflected upward toward the top of the annular piston ring groove. This allows additional expansion to occur without increasing the ring load against the cylinder bore.
  • The placement and amount of ring end relief which may be provided may be varied to suit particular engine characteristics, operating conditions and piston ring design. However, the advantages of the concept, of which the foregoing embodiments represent only examples, include extension of the ability of an engine to operate in severe conditions of cylinder bore contraction or piston ring expansion and/or the reduction of ring end gap dimensions with resulting reductions of gas blowby. [0028]
  • While the invention has been described by reference to certain preferred embodiments, it should be understood that numerous changes could be made within the spirit and scope of the inventive concepts described. Accordingly, it is intended that the invention not be limited to the disclosed embodiments, but that it have the full scope permitted by the language of the following claims. [0029]

Claims (9)

1. An engine piston compression ring centered on a longitudinal axis and having upper and lower sides, an inner edge, an outer face, and an end gap defined by circumferentially opposed ends, and the improvement wherein:
the gap forms an angle with respect to one of the longitudinal axis and a radius drawn from the longitudinal axis; and
one of the ends is relieved for a distance from the gap along one of the inner edge and the upper side.
2. A compression ring as in claim 1 wherein the gap forms an angle with respect to a radius drawn from the longitudinal axis and the inner edge includes a relieved portion adjacent the one end.
3. A compression ring as in claim 2 wherein the relieved portion slopes outward toward the one end.
4. A compression ring as in claim 3 wherein a slot adjacent the relieved portion extends outward from the inner edge to promote flexing of the relieved portion.
5. A compression ring as in claim 2 wherein the relieved portion is of reduced radial thickness with a generally circumferential configuration.
6. A compression ring as in claim 2 wherein the gap extends parallel with the longitudinal axis.
7. A compression ring as in claim 1 wherein the gap forms an angle with respect to the longitudinal axis and the upper side includes a relieved portion adjacent the one end.
8. A compression ring as in claim 6 wherein the relieved portion slopes downward toward the one end.
9. A compression ring as in claim 8 wherein the gap is aligned with a radius drawn from the longitudinal axis.
US10/243,967 2002-09-12 2002-09-12 Angled gap compression rings with end relief Expired - Fee Related US6715767B1 (en)

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Application Number Priority Date Filing Date Title
US10/243,967 US6715767B1 (en) 2002-09-12 2002-09-12 Angled gap compression rings with end relief
DE10341782A DE10341782A1 (en) 2002-09-12 2003-09-10 Compression rings with angled gap and end finishing

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Application Number Priority Date Filing Date Title
US10/243,967 US6715767B1 (en) 2002-09-12 2002-09-12 Angled gap compression rings with end relief

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US6715767B1 US6715767B1 (en) 2004-04-06

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2878773A1 (en) * 2013-11-13 2015-06-03 MTU Aero Engines GmbH Gas turbine with slotted retention ring
US20190257424A1 (en) * 2018-02-22 2019-08-22 Hyundai Motor Company Piston ring for engine
GB2638278A (en) * 2024-02-19 2025-08-20 Phinia Delphi Luxembourg Sarl Fuel pump and sealing arrangement therefor

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EP1536167B1 (en) * 2002-05-29 2012-08-08 Nok Corporation Seal ring
US7510195B2 (en) * 2003-11-21 2009-03-31 Honeywell International Inc. High temperature and high pressure compressor piston ring
DE102006022027A1 (en) * 2006-05-10 2007-11-15 Mahle International Gmbh Piston ring for the piston of an internal combustion engine
BRPI0605175B1 (en) * 2006-12-05 2020-01-21 Mahle International Gmbh piston ring for internal combustion engines
JP5029044B2 (en) * 2007-02-01 2012-09-19 Ｎｏｋ株式会社 Seal ring
EP2136212A4 (en) * 2007-03-28 2012-07-25 Ntn Toyo Bearing Co Ltd Rotation sensor
ES2710496T3 (en) 2009-10-12 2019-04-25 Toray Industries Axial labyrinth seal for spirally wound membrane module systems
DE102009052587A1 (en) * 2009-11-10 2011-05-12 Federal-Mogul Burscheid Gmbh piston ring
RU2016114799A3 (en) * 2013-10-18 2018-06-28 Exco Technologies Ltd Wear ring for die-casting piston, die-casting piston incorporating same, and method of forming same
EP3246603B1 (en) * 2015-01-14 2020-09-16 Nok Corporation Seal ring and sealing structure
US10359112B2 (en) * 2016-03-28 2019-07-23 Progress Rail Locomotive Inc. Piston ring set for internal combustion engine and system and method thereof

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US1280739A (en) * 1915-06-03 1918-10-08 John B Jameson Piston-ring.
US1344342A (en) * 1918-10-08 1920-06-22 Oscar W Hanson Piston packing-ring
US1357729A (en) * 1918-06-26 1920-11-02 Eva C Schaap Piston-ring and mounting therefor
US1360820A (en) * 1919-11-03 1920-11-30 Arthur B Thompson Piston packing-ring
US1360733A (en) * 1917-04-13 1920-11-30 Deutsch Piston-ring
US1398439A (en) * 1921-01-18 1921-11-29 Mcmaster Frederick Keith Piston-ring
US1470113A (en) * 1920-11-11 1923-10-09 Morris A Davis Piston ring
US1499571A (en) * 1920-11-11 1924-07-01 Morris A Davis Piston ring
US1658440A (en) * 1926-11-20 1928-02-07 Adam W Hanigan Piston packing
US1757877A (en) * 1928-10-01 1930-05-06 Fisher H Roberts Piston ring
US1833887A (en) * 1930-12-03 1931-12-01 William C Andrews Piston ring
US2462586A (en) * 1946-01-02 1949-02-22 New York Air Brake Co Seal for resisting high pressures
US2569777A (en) * 1946-10-12 1951-10-02 Hastings Mfg Co Piston ring
US2812196A (en) * 1954-05-20 1957-11-05 Gen Motors Corp Piston ring turbine shaft seal
US4251083A (en) * 1979-05-15 1981-02-17 Adriel Montes Piston ring with tongue and groove joint
US4449721A (en) * 1980-12-18 1984-05-22 Tokico Ltd. Split piston ring having stepped ends
US5087057A (en) * 1990-01-19 1992-02-11 Kurkowski Ronald C Helical cut seal
US5253878A (en) * 1991-06-04 1993-10-19 Kabushiki Kaisha Riken Compression ring for internal-combustion engines

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1280739A (en) * 1915-06-03 1918-10-08 John B Jameson Piston-ring.
US1360733A (en) * 1917-04-13 1920-11-30 Deutsch Piston-ring
US1357729A (en) * 1918-06-26 1920-11-02 Eva C Schaap Piston-ring and mounting therefor
US1344342A (en) * 1918-10-08 1920-06-22 Oscar W Hanson Piston packing-ring
US1360820A (en) * 1919-11-03 1920-11-30 Arthur B Thompson Piston packing-ring
US1470113A (en) * 1920-11-11 1923-10-09 Morris A Davis Piston ring
US1499571A (en) * 1920-11-11 1924-07-01 Morris A Davis Piston ring
US1398439A (en) * 1921-01-18 1921-11-29 Mcmaster Frederick Keith Piston-ring
US1658440A (en) * 1926-11-20 1928-02-07 Adam W Hanigan Piston packing
US1757877A (en) * 1928-10-01 1930-05-06 Fisher H Roberts Piston ring
US1833887A (en) * 1930-12-03 1931-12-01 William C Andrews Piston ring
US2462586A (en) * 1946-01-02 1949-02-22 New York Air Brake Co Seal for resisting high pressures
US2569777A (en) * 1946-10-12 1951-10-02 Hastings Mfg Co Piston ring
US2812196A (en) * 1954-05-20 1957-11-05 Gen Motors Corp Piston ring turbine shaft seal
US4251083A (en) * 1979-05-15 1981-02-17 Adriel Montes Piston ring with tongue and groove joint
US4449721A (en) * 1980-12-18 1984-05-22 Tokico Ltd. Split piston ring having stepped ends
US5087057A (en) * 1990-01-19 1992-02-11 Kurkowski Ronald C Helical cut seal
US5253878A (en) * 1991-06-04 1993-10-19 Kabushiki Kaisha Riken Compression ring for internal-combustion engines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2878773A1 (en) * 2013-11-13 2015-06-03 MTU Aero Engines GmbH Gas turbine with slotted retention ring
US20190257424A1 (en) * 2018-02-22 2019-08-22 Hyundai Motor Company Piston ring for engine
US10844956B2 (en) * 2018-02-22 2020-11-24 Hyundai Motor Company Piston ring for engine
GB2638278A (en) * 2024-02-19 2025-08-20 Phinia Delphi Luxembourg Sarl Fuel pump and sealing arrangement therefor

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DE10341782A1 (en) 2004-04-08
US6715767B1 (en) 2004-04-06

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