US20080175735A1 - Inlet pressure attenuator for single plunger fuel pump - Google Patents
Inlet pressure attenuator for single plunger fuel pump Download PDFInfo
- Publication number
- US20080175735A1 US20080175735A1 US12/008,185 US818508A US2008175735A1 US 20080175735 A1 US20080175735 A1 US 20080175735A1 US 818508 A US818508 A US 818508A US 2008175735 A1 US2008175735 A1 US 2008175735A1
- Authority
- US
- United States
- Prior art keywords
- rims
- diaphragm
- fuel pump
- rim
- circumferential
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0041—Means for damping pressure pulsations
Definitions
- the present disclosure relates generally to fuel pumps, and is more particularly concerned with a new and improved single plunger fuel pump.
- the engine drive shaft carries a lobed cam that reciprocates the pumping plunger within a pumping sleeve secured to the housing, between charging (intake) and discharging (output) phases.
- the pumping end of the plunger is situated in the pumping chamber, which fills with fuel at a feed pressure of up to about 4 bar during the charging phase and, preferably subject to initial spill control, pressurizes the fuel in the pumping chamber up to about 200 bar for delivery to, e.g., a common rail.
- the feed fuel is fed directly to the pumping chamber through an inlet valve, which receives flow from an inlet damping chamber.
- the fuel passes one or more attenuator diaphragms in the damping chamber along the flow path to the pumping chamber.
- the diaphragms encapsulate fixed masses of gas, such as helium at two bars. The flexibility of the diaphragms can adjust the volumes of the gas in response to pressure variations in the feed line and thereby maintain a substantially constant feed pressure to the inlet valve.
- a problem encountered with known welded diaphragms is that the substantially continual accommodation of normal pressure fluctuations and the occasional attenuation of spurious pressure transients, stresses the welds and causes leakage, with resulting deterioration of performance or even failure.
- the diaphragm assembly includes a diaphragm formed of two half-shells, having mated flat rims that are welded together along their peripheral edges.
- a compression joint is formed at inward, unwelded portions of the rims and a carrier or frame captures the joined and welded rims.
- Another embodiment is directed to a fuel pump having a single plunger that reciprocates into and out of a pumping chamber situated within a pump housing.
- the pump features a pressurized inlet line through the housing to an inlet valve that feeds the pumping chamber.
- a damping chamber is integrated with the housing, in which fuel passes around at least one gas filled and sealed attenuator diaphragm along a flow path to the inlet valve.
- Each diaphragm is formed of two half-shells, having central convex bulges and mated flat rims which are supported in a diaphragm carrier within the damping chamber.
- the rims are welded together along their outer edges and a compression joint is formed at inward, unwelded portions of the rims to reduce stresses transmitted to the welded edges.
- each half-shell is substantially circular and each rim circumscribes a respective convex bulge.
- the rims are bent over at a circumferential bend line that forms the compression joint.
- the bent over portion of the rims forms a circumferential ridge that is substantially coaxial with the axis of the diaphragm.
- the diaphragm carrier has a radial slot including upper and lower walls between which the ridge is captured.
- Each rim has a flat portion radially inward of the bend line.
- the upper wall extends closely over said flat portions of the rims and the welded outer edges are supported by the lower wall.
- the compression joint isolates the weld from excessive stresses associated with the expansion and contraction of the diaphragm, thereby avoiding leakage of the gas and deterioration or failure of pressure attenuating capability of the diaphragm.
- FIG. 1 is a perspective view of a one plunger fuel pump having a substantially cubic housing or body, with the fuel inlet connector projecting on the right, the single plunger actuation assembly projecting from the left, and the inlet control valve projecting from the top;
- FIG. 2 is staggered section view of the pump of FIG. 1 , through the inlet connection with associated attenuator, and the inlet control valve;
- FIGS. 3A and 3B are enlarged plan and section views of the split diaphragm carrier for the two pressurized diaphragms shown in FIG. 2 , with the section line indicated by A-A;
- FIG. 4 is an enlarged view of the attenuator diaphragm, showing the preferred bending at the rims for stress relief;
- FIG. 5 is an enlarged view of an alternative technique for reducing the stresses at the weld of the diaphragm rims
- FIG. 1 shows a one plunger fuel pump 10 having a substantially cubic housing or body 12 , with the fuel inlet connector 14 projecting on the right, the single plunger actuation assembly 16 projecting from the left, and the inlet control valve 18 projecting from the top.
- plunger 20 can be seen projecting slightly from the single plunger actuation assembly 16 .
- the feed fuel is fed directly to the pumping chamber 22 through the solenoid controlled inlet valve 18 , which receives flow through a first internal passage 24 of the housing, from the inlet damping chamber 26 .
- the damping chamber receives feed fuel through an inlet fitting 28 , and the fuel passes around the attenuator diaphragms 30 on its way to the first internal passage 24 .
- the diaphragms encapsulate fixed masses of gas, such as helium at two bars, but the flexibility of the diaphragms can adjust the volumes of the gas in response to pressure variations in the feed line and thereby maintain a substantially constant feed pressure to the inlet valve 18 .
- the substantially cylindrical chamber is in part defined by a cup cover 32 welded to the inlet fitting 28 and to the wall of a shallow bore in the housing 12 .
- a diaphragm carrier 36 is annularly disposed against the inside surface 36 of the cup cover 32 .
- the carrier has upper and lower annular grooves or slots 38 , for receiving the rims 40 of respective diaphragms 30 .
- Each slot includes upper and lower walls 42 a and 42 b that closely confront the inner radial portion of each respective diaphragm rim.
- Each diaphragm is formed of two substantially circular half-shells 44 , having central convex bulges 45 and mated flat rims 40 .
- a helium balloon is placed between the half-shells 44 , the shells are urged together, and the rims are TIG welded at the outer circumferences, as indicated by reference numeral 46 .
- This forms a central, substantially cylindrical helium volume and a flat rim having a radial dimension outside of the helium cylinder. While this embodiment features upper and lower slots, it should be clear to those skilled in the art that the object of the disclosure may be practiced with any number of slots.
- the improvement comprises that an annular compression joint is formed on a radially inward, unwelded portion of the rim to reduce stresses transmitted to the welded circumference.
- the joined rims 40 are bent over to form a circumferential ridge 48 , preferably enough to nearly align the bent over circumferential ridge with the axis of the cylinder, shown by reference numeral 50 .
- the bend line L forms the compression joint 41 .
- the circumferential bend line is located within the radially inward 75 percent of the radial dimension of the rim.
- the joined rims have a flat portion 52 radially inward of the bend line.
- the circumferential ridge 48 is captured between the upper and lower walls 42 a and 42 b of a carrier annular groove 38 with the upper wall 42 a extending closely over the rim flat portion 52 while the lower wall 42 b supports the welded outer edges 46 of the rim.
- This technique of forming the diaphragm avoids stress at the weld 46 arising from the use environment, where a constant internal pressure of about 2 bars acts in the direction of separating the rims, and the diaphragm 30 undergoes continual contraction and expansion, because the weld 46 is axially offset from the separation plane between the rims.
- FIG. 5 Another embodiment is shown in FIG. 5 , where the welded rims are not bent over, but a different type of diaphragm carrier 34 has a radial slot 38 such that the walls 42 of the slot along the radially inner portion of the slot closely confront, or are preferably clamped against, the inner radial portion of the rim 40 .
- This clamping is an alternative to the bend line of the embodiment of FIG. 4 , whereby the weld on the outer edges of the rim is isolated from the forces associated with the pressure in and flexing of the diaphragm 30 , by the radially inner clamping. Such clamping would typically leave a space or gap 54 along the radially outer portion of the slot surrounding the weld 46 .
Abstract
Description
- This application claims priority under 35 U.S.C. 119(e) from U.S. Provisional Application No. 60/879,738 filed Jan. 10, 2007 for “Inlet Pressure Attenuator for Single Plunger Fuel Pump”, the entire disclosure of which is hereby incorporated by reference.
- The present disclosure relates generally to fuel pumps, and is more particularly concerned with a new and improved single plunger fuel pump.
- Practitioners in the field of fuel pump design and development for vehicles readily understand the main components of a typical single plunger pump and their function and operation. The engine drive shaft carries a lobed cam that reciprocates the pumping plunger within a pumping sleeve secured to the housing, between charging (intake) and discharging (output) phases. The pumping end of the plunger is situated in the pumping chamber, which fills with fuel at a feed pressure of up to about 4 bar during the charging phase and, preferably subject to initial spill control, pressurizes the fuel in the pumping chamber up to about 200 bar for delivery to, e.g., a common rail.
- The feed fuel is fed directly to the pumping chamber through an inlet valve, which receives flow from an inlet damping chamber. The fuel passes one or more attenuator diaphragms in the damping chamber along the flow path to the pumping chamber. The diaphragms encapsulate fixed masses of gas, such as helium at two bars. The flexibility of the diaphragms can adjust the volumes of the gas in response to pressure variations in the feed line and thereby maintain a substantially constant feed pressure to the inlet valve.
- A problem encountered with known welded diaphragms, is that the substantially continual accommodation of normal pressure fluctuations and the occasional attenuation of spurious pressure transients, stresses the welds and causes leakage, with resulting deterioration of performance or even failure.
- It is an object of the present invention to provide an improved technique for stress relieving the junction of juxtaposed thin rims of a pressurized bellows type diaphragm attenuator that is integrated with the inlet feed train of a single plunger fuel pump.
- One embodiment is directed to an attenuator diaphragm assembly for a fuel injection pump. The diaphragm assembly includes a diaphragm formed of two half-shells, having mated flat rims that are welded together along their peripheral edges. A compression joint is formed at inward, unwelded portions of the rims and a carrier or frame captures the joined and welded rims.
- Another embodiment is directed to a fuel pump having a single plunger that reciprocates into and out of a pumping chamber situated within a pump housing. The pump features a pressurized inlet line through the housing to an inlet valve that feeds the pumping chamber. A damping chamber is integrated with the housing, in which fuel passes around at least one gas filled and sealed attenuator diaphragm along a flow path to the inlet valve. Each diaphragm is formed of two half-shells, having central convex bulges and mated flat rims which are supported in a diaphragm carrier within the damping chamber. The rims are welded together along their outer edges and a compression joint is formed at inward, unwelded portions of the rims to reduce stresses transmitted to the welded edges.
- Preferably, each half-shell is substantially circular and each rim circumscribes a respective convex bulge. The rims are bent over at a circumferential bend line that forms the compression joint. The bent over portion of the rims forms a circumferential ridge that is substantially coaxial with the axis of the diaphragm. The diaphragm carrier has a radial slot including upper and lower walls between which the ridge is captured. Each rim has a flat portion radially inward of the bend line. The upper wall extends closely over said flat portions of the rims and the welded outer edges are supported by the lower wall.
- The compression joint isolates the weld from excessive stresses associated with the expansion and contraction of the diaphragm, thereby avoiding leakage of the gas and deterioration or failure of pressure attenuating capability of the diaphragm.
- In the accompanying drawing, like elements are numbered alike in the several Figures:
-
FIG. 1 is a perspective view of a one plunger fuel pump having a substantially cubic housing or body, with the fuel inlet connector projecting on the right, the single plunger actuation assembly projecting from the left, and the inlet control valve projecting from the top; -
FIG. 2 is staggered section view of the pump ofFIG. 1 , through the inlet connection with associated attenuator, and the inlet control valve; -
FIGS. 3A and 3B are enlarged plan and section views of the split diaphragm carrier for the two pressurized diaphragms shown inFIG. 2 , with the section line indicated by A-A; -
FIG. 4 is an enlarged view of the attenuator diaphragm, showing the preferred bending at the rims for stress relief; -
FIG. 5 is an enlarged view of an alternative technique for reducing the stresses at the weld of the diaphragm rims; -
FIG. 1 shows a oneplunger fuel pump 10 having a substantially cubic housing orbody 12, with thefuel inlet connector 14 projecting on the right, the singleplunger actuation assembly 16 projecting from the left, and theinlet control valve 18 projecting from the top. InFIG. 1 ,plunger 20 can be seen projecting slightly from the singleplunger actuation assembly 16. - With further reference to
FIG. 2 , the feed fuel is fed directly to the pumping chamber 22 through the solenoid controlledinlet valve 18, which receives flow through a firstinternal passage 24 of the housing, from theinlet damping chamber 26. The damping chamber receives feed fuel through an inlet fitting 28, and the fuel passes around theattenuator diaphragms 30 on its way to the firstinternal passage 24. The diaphragms encapsulate fixed masses of gas, such as helium at two bars, but the flexibility of the diaphragms can adjust the volumes of the gas in response to pressure variations in the feed line and thereby maintain a substantially constant feed pressure to theinlet valve 18. - The improvement with respect to the
damping chamber 26 will now be described in greater detail with reference toFIGS. 1 , 2, 3 and 4. The substantially cylindrical chamber is in part defined by acup cover 32 welded to the inlet fitting 28 and to the wall of a shallow bore in thehousing 12. Adiaphragm carrier 36 is annularly disposed against theinside surface 36 of thecup cover 32. The carrier has upper and lower annular grooves orslots 38, for receiving therims 40 ofrespective diaphragms 30. Each slot includes upper andlower walls shells 44, having central convex bulges 45 and matedflat rims 40. In an environment at about two bar pressure, a helium balloon is placed between the half-shells 44, the shells are urged together, and the rims are TIG welded at the outer circumferences, as indicated byreference numeral 46. This forms a central, substantially cylindrical helium volume and a flat rim having a radial dimension outside of the helium cylinder. While this embodiment features upper and lower slots, it should be clear to those skilled in the art that the object of the disclosure may be practiced with any number of slots. - The improvement comprises that an annular compression joint is formed on a radially inward, unwelded portion of the rim to reduce stresses transmitted to the welded circumference.
- In one embodiment, after welding along the outer edges of the half-
shells 44, the joinedrims 40 are bent over to form acircumferential ridge 48, preferably enough to nearly align the bent over circumferential ridge with the axis of the cylinder, shown byreference numeral 50. The bend line L forms thecompression joint 41. In general, the circumferential bend line is located within the radially inward 75 percent of the radial dimension of the rim. The joined rims have aflat portion 52 radially inward of the bend line. Generally, thecircumferential ridge 48 is captured between the upper andlower walls annular groove 38 with theupper wall 42 a extending closely over the rimflat portion 52 while thelower wall 42 b supports the weldedouter edges 46 of the rim. - This technique of forming the diaphragm avoids stress at the
weld 46 arising from the use environment, where a constant internal pressure of about 2 bars acts in the direction of separating the rims, and thediaphragm 30 undergoes continual contraction and expansion, because theweld 46 is axially offset from the separation plane between the rims. - Another embodiment is shown in
FIG. 5 , where the welded rims are not bent over, but a different type ofdiaphragm carrier 34 has aradial slot 38 such that the walls 42 of the slot along the radially inner portion of the slot closely confront, or are preferably clamped against, the inner radial portion of therim 40. This clamping is an alternative to the bend line of the embodiment ofFIG. 4 , whereby the weld on the outer edges of the rim is isolated from the forces associated with the pressure in and flexing of thediaphragm 30, by the radially inner clamping. Such clamping would typically leave a space orgap 54 along the radially outer portion of the slot surrounding theweld 46. - While preferred embodiments have been set forth for purposes of illustration, the foregoing description should not be deemed a limitation of the disclosure herein, or of the scope of disclosure or claims that may be presented in a regular application based on the present application. Accordingly, various modifications, adaptations and alternatives may occur to one skilled in the art without departing from the spirit and scope of the present disclosure.
Claims (16)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/008,185 US20080175735A1 (en) | 2007-01-10 | 2008-01-09 | Inlet pressure attenuator for single plunger fuel pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US87973807P | 2007-01-10 | 2007-01-10 | |
US12/008,185 US20080175735A1 (en) | 2007-01-10 | 2008-01-09 | Inlet pressure attenuator for single plunger fuel pump |
Publications (1)
Publication Number | Publication Date |
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US20080175735A1 true US20080175735A1 (en) | 2008-07-24 |
Family
ID=39609012
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/008,185 Abandoned US20080175735A1 (en) | 2007-01-10 | 2008-01-09 | Inlet pressure attenuator for single plunger fuel pump |
Country Status (2)
Country | Link |
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US (1) | US20080175735A1 (en) |
WO (1) | WO2008086012A1 (en) |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090044783A1 (en) * | 2007-08-17 | 2009-02-19 | Michael Fischer | Fuel pump for a fuel system of an internal combustion engine |
US20110110807A1 (en) * | 2009-02-18 | 2011-05-12 | Denso Corporation | High-pressure pump |
US20120006303A1 (en) * | 2009-03-17 | 2012-01-12 | Toyota Jidosha Kabushiki Kaisha | Pulsation damper |
US20120087817A1 (en) * | 2010-10-06 | 2012-04-12 | Lucas Robert G | Three element diaphragm damper for fuel pump |
JP2017032069A (en) * | 2015-07-31 | 2017-02-09 | トヨタ自動車株式会社 | Damper device |
DE102016203217A1 (en) * | 2016-02-29 | 2017-08-31 | Continental Automotive Gmbh | Damper capsule, pressure pulsation damper and high-pressure fuel pump |
US20190145364A1 (en) * | 2016-04-28 | 2019-05-16 | Denso Corporation | High pressure pump |
WO2019178349A1 (en) * | 2018-03-14 | 2019-09-19 | Nostrum Energy Pte. Ltd. | Pump for internal combustion engine and method of forming the same |
US11242832B2 (en) | 2018-05-18 | 2022-02-08 | Eagle Industry Co., Ltd. | Structure for attaching metal diaphragm damper |
US11261835B2 (en) * | 2018-05-18 | 2022-03-01 | Eagle Industry Co., Ltd. | Damper device |
US11293391B2 (en) | 2018-05-18 | 2022-04-05 | Eagle Industry Co., Ltd. | Damper device |
US11326568B2 (en) | 2018-05-25 | 2022-05-10 | Eagle Industry Co., Ltd. | Damper device |
US11346312B2 (en) | 2018-05-18 | 2022-05-31 | Eagle Industry Co., Ltd. | Damper unit |
US20220333568A1 (en) * | 2019-08-09 | 2022-10-20 | Robert Bosch Gmbh | High-Pressure Fuel Pump |
Families Citing this family (2)
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JP5979092B2 (en) | 2013-07-23 | 2016-08-24 | トヨタ自動車株式会社 | Pulsation damper and high-pressure fuel pump |
CN107709821B (en) * | 2015-07-31 | 2019-09-24 | 伊格尔工业股份有限公司 | The manufacturing method of diaphragm damper device and its holding member and diaphragm damper device |
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US4649884A (en) * | 1986-03-05 | 1987-03-17 | Walbro Corporation | Fuel rail for internal combustion engines |
US5088463A (en) * | 1990-06-28 | 1992-02-18 | Mcguane Industries | Fuel supply system for internal combustion engines |
US20020053464A1 (en) * | 1997-10-29 | 2002-05-09 | Schreiber Chris M. | Stress relief bend useful in an integrated circuit redistribution patch |
US7124738B2 (en) * | 2003-07-22 | 2006-10-24 | Hitachi, Ltd. | Damper mechanism and high pressure fuel pump |
-
2008
- 2008-01-09 US US12/008,185 patent/US20080175735A1/en not_active Abandoned
- 2008-01-09 WO PCT/US2008/000325 patent/WO2008086012A1/en active Application Filing
Patent Citations (4)
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US4649884A (en) * | 1986-03-05 | 1987-03-17 | Walbro Corporation | Fuel rail for internal combustion engines |
US5088463A (en) * | 1990-06-28 | 1992-02-18 | Mcguane Industries | Fuel supply system for internal combustion engines |
US20020053464A1 (en) * | 1997-10-29 | 2002-05-09 | Schreiber Chris M. | Stress relief bend useful in an integrated circuit redistribution patch |
US7124738B2 (en) * | 2003-07-22 | 2006-10-24 | Hitachi, Ltd. | Damper mechanism and high pressure fuel pump |
Cited By (30)
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US7654249B2 (en) * | 2007-08-17 | 2010-02-02 | Robert Bosch Gmbh | Fuel pump for a fuel system of an internal combustion engine |
US20090044783A1 (en) * | 2007-08-17 | 2009-02-19 | Michael Fischer | Fuel pump for a fuel system of an internal combustion engine |
US8430655B2 (en) * | 2009-02-18 | 2013-04-30 | Denso Corporation | High-pressure pump |
US20110110807A1 (en) * | 2009-02-18 | 2011-05-12 | Denso Corporation | High-pressure pump |
US20120006303A1 (en) * | 2009-03-17 | 2012-01-12 | Toyota Jidosha Kabushiki Kaisha | Pulsation damper |
US9057348B2 (en) * | 2009-03-17 | 2015-06-16 | Toyota Jidosha Kabushiki Kaisha | Pulsation damper |
US20130209289A1 (en) * | 2010-10-06 | 2013-08-15 | Stanadyne Corporation | Three Element Diaphragm Damper For Fuel Pump |
WO2012047283A3 (en) * | 2010-10-06 | 2012-07-05 | Stanadyne Corporation | Three element diaphragm damper for fuel pump |
CN103597199A (en) * | 2010-10-06 | 2014-02-19 | 斯塔纳迪恩公司 | Three element diaphragm damper for fuel pump |
US8727752B2 (en) * | 2010-10-06 | 2014-05-20 | Stanadyne Corporation | Three element diaphragm damper for fuel pump |
WO2012047283A2 (en) | 2010-10-06 | 2012-04-12 | Stanadyne Corporation | Three element diaphragm damper for fuel pump |
US9243623B2 (en) * | 2010-10-06 | 2016-01-26 | Stanadyne Llc | Three element diaphragm damper for fuel pump |
US20120087817A1 (en) * | 2010-10-06 | 2012-04-12 | Lucas Robert G | Three element diaphragm damper for fuel pump |
EP2625419A4 (en) * | 2010-10-06 | 2018-01-17 | Stanadyne Corporation | Three element diaphragm damper for fuel pump |
US10883462B2 (en) * | 2015-07-31 | 2021-01-05 | Toyota Jidosha Kabushiki Kaisha | Damper device with a plurality of stacked diaphragms coupled together by a coupler having holders forming a space provided between a peripheral weld of the diaphragms and the coupler |
JP2017032069A (en) * | 2015-07-31 | 2017-02-09 | トヨタ自動車株式会社 | Damper device |
CN107850023A (en) * | 2015-07-31 | 2018-03-27 | 丰田自动车株式会社 | Damper device |
US20180223782A1 (en) * | 2015-07-31 | 2018-08-09 | Toyota Jidosha Kabushiki Kaisha | Damper device |
DE112016003490B4 (en) | 2015-07-31 | 2023-12-14 | Denso Corporation | DAMPER DEVICE |
DE102016203217A1 (en) * | 2016-02-29 | 2017-08-31 | Continental Automotive Gmbh | Damper capsule, pressure pulsation damper and high-pressure fuel pump |
DE102016203217B4 (en) * | 2016-02-29 | 2020-12-10 | Vitesco Technologies GmbH | Damper capsule, pressure pulsation damper and high-pressure fuel pump |
US10883463B2 (en) * | 2016-04-28 | 2021-01-05 | Denso Corporation | High pressure pump |
US20190145364A1 (en) * | 2016-04-28 | 2019-05-16 | Denso Corporation | High pressure pump |
WO2019178349A1 (en) * | 2018-03-14 | 2019-09-19 | Nostrum Energy Pte. Ltd. | Pump for internal combustion engine and method of forming the same |
US11242832B2 (en) | 2018-05-18 | 2022-02-08 | Eagle Industry Co., Ltd. | Structure for attaching metal diaphragm damper |
US11261835B2 (en) * | 2018-05-18 | 2022-03-01 | Eagle Industry Co., Ltd. | Damper device |
US11293391B2 (en) | 2018-05-18 | 2022-04-05 | Eagle Industry Co., Ltd. | Damper device |
US11346312B2 (en) | 2018-05-18 | 2022-05-31 | Eagle Industry Co., Ltd. | Damper unit |
US11326568B2 (en) | 2018-05-25 | 2022-05-10 | Eagle Industry Co., Ltd. | Damper device |
US20220333568A1 (en) * | 2019-08-09 | 2022-10-20 | Robert Bosch Gmbh | High-Pressure Fuel Pump |
Also Published As
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Owner name: STANADYNE CORPORATION, CONNECTICUT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LUCAS, ROBERT;DJORDJEVIC, ILIJA;REEL/FRAME:020373/0968 Effective date: 20080107 |
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Owner name: WELLS FARGO FOOTHILL, LLC, AS AGENT, GEORGIA Free format text: SECURITY AGREEMENT;ASSIGNOR:STANADYNE CORPORATION;REEL/FRAME:023129/0296 Effective date: 20090813 Owner name: WELLS FARGO FOOTHILL, LLC, AS AGENT,GEORGIA Free format text: SECURITY AGREEMENT;ASSIGNOR:STANADYNE CORPORATION;REEL/FRAME:023129/0296 Effective date: 20090813 |
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Owner name: STANADYNE LLC, CONNECTICUT Free format text: RELEASE OF SECURITY INTEREST IN PATENTS;ASSIGNOR:WELLS FARGO CAPITAL FINANCE, LLC (FORMERLY KNOWN AS WELLS FARGO FOOTHILL, LLC);REEL/FRAME:042388/0697 Effective date: 20170502 |