EP0846224B1 - Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen - Google Patents
Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen Download PDFInfo
- Publication number
- EP0846224B1 EP0846224B1 EP97915286A EP97915286A EP0846224B1 EP 0846224 B1 EP0846224 B1 EP 0846224B1 EP 97915286 A EP97915286 A EP 97915286A EP 97915286 A EP97915286 A EP 97915286A EP 0846224 B1 EP0846224 B1 EP 0846224B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- fuel
- orifice
- fuel feed
- feed pump
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
Definitions
- the invention relates to a fuel feed pump for a Fuel injection pump for internal combustion engines according to the Genus of claim 1.
- One known from EP 0 166 995 A1 as Gear pump designed fuel delivery pump delivers the fuel from a storage tank into the suction chamber a fuel injection pump.
- the feed pump an intermeshing gear pair on the Fuel from a through an intake pipe with the Storage tank connected into one, via a Delivery line with the suction chamber of the fuel injection pump connected pressure chamber promotes. It is used to control the Pressure in the pressure chamber or the flow rate to the fuel injection pump a bypass channel between the pressure chamber and the suction chamber of the fuel delivery pump.
- the This bypass channel is opened by means of the Bypass channel used pressure valve, which at a certain pressure difference between pressure and suction space in Depending on the spring force of the valve spring one releases certain opening cross-section.
- the Opening time of the pressure valve can be via the Adjust the preload force of the valve spring, including the axial one Position of the abutment of the pressure valve spring is adjustable.
- the known fuel delivery pump has the Disadvantage that the bypass channel receiving the pressure valve outside the feed pump or spatially relatively far from Gear pair is arranged, which is an increased construction and Assembly effort and a large amount of space.
- DE 44 41 505 A is one Fuel delivery pump known to the above Avoids disadvantages.
- the one that receives the pressure valve Bypass channel is integrated in the housing of the feed pump, see above that no additional space is required.
- both fuel delivery pumps have the disadvantage that that when the fuel delivery pump is at a standstill Pumping the existing fuel into the fuel delivery pump leading suction line flow and the fuel feed pump can empty itself. This requires under Circumstances when restarting the ventilation of the suction line.
- the fuel delivery pump according to the invention for a Has fuel injection pump for internal combustion engines on the other hand, the advantage that the suction space of the Fuel feed pump lockable check valve Drain the fuel delivery pump when the engine is not running prevented. This means that immediately after a restart Fuel delivery pump of the internal combustion injection pump Fuel are supplied so that within a short time required delivery pressure for the fuel can be built up can.
- a check valve that the Intake chamber closes can thus be highly efficient Start to be achieved.
- the Fuel feed pump with the engine at a standstill remains wetted so that no corrosion can occur.
- the check valve closing the suction chamber has also have the advantage of having a flow resistance a throttling effect during operation of the fuel delivery pump Act.
- throttling the fuel in the Suction line can the flow rate with increasing speed be reduced. This allows a smooth transition from that steadily increasing flow to the maximum flow can be achieved, whereby a to promote the fuel low labor is required.
- the excess will usually controlled via a pressure relief valve. This makes it possible for the pump characteristic curve to reach a Demand curve can be adjusted, which due to the less throttled amount less heating the Fuel delivery pump can be achieved.
- the check valve works with increasing speed and Flow as suction throttle. This means that the Suction throttle before and after a given pressure difference the throttle only allows a certain amount to pass.
- a multi-substance pump can also be used, for example for lubricating oil, according to the features of claim 1 be trained.
- FIG. 1 to 3 is a first in different views Embodiment of a fuel delivery pump shown that in a feed line, not shown, from a Storage tank for a fuel injection pump for Internal combustion engines is used.
- the Delivery pump in its housing 1 a pump chamber 3 in which a rotating driven meshing pair Gears 7, 9 is arranged. Doing so is on a wave 5 attached first gear 7 by means of a not closer external drive element shown rotating driven and transmits this rotary movement by means of a Front toothing on a meshing with the first gear 7 second gear 9, which on a housing-mounted axis 11th is arranged.
- the gears 7, 9 share the Pump chamber 3 by their tooth engagement in two parts, from which a first part a suction space 13 and a second Form part of a pressure chamber 15.
- the suction chamber 13 is there one each between the tooth grooves on the end face of the first gear 7 and the second gear 9 and Circumferentially formed by the pump edge 3 delivery channel 17 connected to the pressure chamber 15.
- the suction space 13 and the pressure chamber 15 each have a connection opening 19, 21 in the Wall of the pump housing 1 through which the suction chamber 13 with a connecting element 14 a not shown Intake line from the storage tank and the pressure chamber 15 with a Not shown delivery line to the suction chamber Fuel injection pump is connected.
- the pump chamber 3 is on one End face in the axial direction of the shafts 5 and the axis 11 of closed a housing cover 23, which in the illustration 2 was removed and so a view of Pump interior allows.
- a bypass channel 25 is provided in the pump housing 1.
- This bypass channel 25 is through a bore in one that Pump chamber 3 on its facing away from the housing cover 23 Front end limiting, the pressure from the suction side separating and thereby forming a pump chamber wall Housing web 27 formed.
- the bypass channel 25 forming hole is listed as a through hole, one end into the pressure chamber 15 and the other end opens into the intake chamber 13.
- the Bypass channel 25 is formed by a bore shoulder Cross-sectional reduction in the direction of pressure chamber 15, wherein the ring shoulder formed on the bypass channel Valve seat 29 one set in the bypass channel 25 Pressure valve 31 forms.
- Valve closing member 33 of the pressure valve 31 With one on it Sealing surface 35 formed on the pressure chamber side due to the force of a valve spring 37 for contact.
- This Valve spring 37 in the bypass channel 25 engages over one Heel on the valve closing member 33 and is supported on the other hand at one end of the suction chamber Bypass channel 25 inserted sleeve 39 from.
- This Adapter sleeve 39 is analogous to the other components of the Pressure valve 31 via the inlet opening 19 into the bypass channel 25 can be used, the axial installation depth of one Flow cross section releasing, adapter sleeve 39 the Biasing force of the valve spring 37 and thus the opening pressure of the pressure valve 31 in the bypass duct 25, the pressure chamber 15 and the suction chamber 13 is adjustable.
- the adapter sleeve 39 can pressed into the bypass channel 25 or by means of a Be screwed thread, so that a very accurate axial Fixing the position of the clamping sleeve 39 is possible.
- This Hose connector 14 can by means of a quick release Housing 1 pressed or by means of a thread screwed in or by means of a quick connection to the Housing 1 can be fastened.
- a Guided valve closing member 41 In the inlet opening 19 is a Guided valve closing member 41, the intake chamber 13th compared to a feed line, not shown, of one Storage tank for fuel delivery pump closes.
- the Valve closing member 41 has an opening cross section Inlet opening 19 corresponding diameter and is axial in the inlet opening 19 against a valve spring 44 movable.
- the end facing the suction chamber 13 Hose connector 14 forms a reduction in cross section Inlet opening 19 through which a valve seat 42 one in the Inlet opening 19 inserted check valve 40 is formed is.
- valve closing member 41 comes on this valve seat 42 the check valve 40 with one at its to Hose connector 14 facing sealing surface 43 due to the force the valve spring 44 to the system.
- This valve spring 44 in the Inlet opening 19 engages via a paragraph on Valve closing member 41 and is based on the other hand on the inserted in the suction chamber end of the bypass channel 25 Adapter sleeve 39 from.
- This adapter sleeve 39 penetrates the Intake space 13 and adjoins the inlet opening 19.
- the inlet opening 19 has a cross section that the Corresponds to the outer diameter of the clamping sleeve 39, so that the Valve spring 44 is located on the end face of the clamping sleeve 39 can support. Due to the length of the adapter sleeve 39, the can also extend into the inlet opening 19, as well the immersion depth of the hose connector 14 in the Inlet opening 19 is the biasing force of the valve spring 44th adjustable so that a certain opening pressure of the Pressure valve 40 is adjustable in the inlet opening 19.
- the Pressure valves 31 and 40 are advantageously identical in construction executed so that an inexpensive design is possible is. Furthermore, the pressure valve 31 and that work Check valve 40 independently of each other.
- the clamping sleeve 39 has the suction space 13 in it penetrating area opening slots so that the over a fuel line, not shown, of the fuel delivery pump supplied fuel at the check valve 40 can flow past and through the opening slots of the Adapter sleeve 39 can be fed to the suction chamber 13. About these slit-shaped opening can also from the pressure chamber 15 in the bypass channel 25 returned fuel into the intake chamber 13 can be returned.
- FIG. 4 is an alternative embodiment of a Check valve 50 against the check valve 40 in Fig. 3 shown.
- the check valve 50 shown in FIG. 4 is formed as a structural unit and has a ring cross section 51 on which abuts a shoulder 52 of the inlet opening 19.
- a Connection element 14 screwed into the inlet opening 19 or pressed in.
- One is not connected to this connection element 14 shown fuel line connectable.
- To the Ring cross section 51 closes a cup-shaped one Housing 53 in which a valve spring 54 is mounted, the a valve closing member 56 for abutting the ring cross section 51 brings.
- the ring cross section 51 is a valve seat educated.
- the valve closing member 56 can counter the Valve spring 54 can be deflected by the fuel.
- the openings 59 act analogously to those in the Valve closing member 41 arranged in the peripheral wall Wells as a throttle, which the flow of the Fuel with increasing speed of the fuel delivery pump can decrease.
- clamping sleeve 39 is opposite the embodiment in Fig. 3 shortened so that this can be used completely in the bypass channel 25.
- the Check valve 50 integrated in a connecting element 14 is, so that a simple assembly of the connecting element 14th with a check valve 50 integrated therein can.
- the Valve closing member 56 formed as a ball or the like is.
- the pressure valve 31 and the check valves 40, 50 can made of fuel and temperature resistant plastics or made of metallic materials or in combination his.
- the fuel delivery pump works in in the following way: In the operation of the internal combustion engine Fuel injection pump and the fuel feed pump driven proportional to the speed of the internal combustion engine. This is done with the one shown in FIGS. 1 to 4 Delivery pump by means of a shaft 5 from the outside attacking mechanical, not shown Transmission element. By rotating the first gear 7 and 9 meshing with this second gear Fuel from the intake space 13 along the delivery channel 17 promoted in the pressure chamber 15. This creates in the intake space 13 a negative pressure sufficient to check valve 40, 50 open and fuel through the intake pipe from the To suck up the storage tank. The one built up in the pressure chamber 15 Fuel pressure causes a fuel delivery from this via a delivery line into the suction chamber of the supply Fuel injection pump.
- the check valve 40, 50 acts as a throttle that smoothly transitions the characteristic curve 60 compared to a theoretical course of the characteristic curve 61 according to 5, which would also correspond to a characteristic curve, if there was no check valve 40, 50.
- the horizontal line 62 is through the maximum Flow rate of the fuel delivery pump depending on the Opening pressure of the pressure valve 31 in the bypass channel 25 fixed.
- the throttling effect is based on the fact that in the Valve closing member 41 evenly distributed over the circumference Wells are arranged that allow the Fuel after lifting the valve closing member 41 from the Valve seat 42 flows through these openings to intake chamber 13 can.
- the Fuel after the valve closing member 56 is lifted off the valve seat 51 via openings 59 of the housing 53 for Intake space.
- the maximum is controlled in parallel Fuel pressure in the pressure chamber 15 and thus the flow rate to the fuel injection pump via the bypass duct 25 by the valve closing member 33 of the pressure valve used therein 31 from a certain pressure in the pressure chamber 15 from the valve seat 29 lifts off and thus an outflow cross section at the bypass duct 25 opens, over which a part of the high pressure Fuel quantity from the pressure chamber 15 into the intake chamber 13 flows out. This will result in the not shown Fuel line flowing through the connecting element 14 Flow reduced.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19625565A DE19625565C2 (de) | 1996-06-26 | 1996-06-26 | Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen |
DE19625565 | 1996-06-26 | ||
PCT/DE1997/000273 WO1997049910A1 (de) | 1996-06-26 | 1997-02-13 | Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0846224A1 EP0846224A1 (de) | 1998-06-10 |
EP0846224B1 true EP0846224B1 (de) | 2000-12-27 |
Family
ID=7798073
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97915286A Expired - Lifetime EP0846224B1 (de) | 1996-06-26 | 1997-02-13 | Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US6099263A (cs) |
EP (1) | EP0846224B1 (cs) |
CZ (1) | CZ290647B6 (cs) |
DE (2) | DE19625565C2 (cs) |
WO (1) | WO1997049910A1 (cs) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6773240B2 (en) | 2002-01-28 | 2004-08-10 | Visteon Global Technologies, Inc. | Single piston dual chamber fuel pump |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19913805A1 (de) * | 1999-03-26 | 2000-04-20 | Bosch Gmbh Robert | Druckbegrenzungs- und Sicherheitsventil |
JP3893959B2 (ja) * | 2001-11-29 | 2007-03-14 | アイシン精機株式会社 | オイルポンプの調圧弁機構搭載構造 |
DE102004003113A1 (de) * | 2004-01-21 | 2005-08-11 | Siemens Ag | Vorrichtung zum Steuern eines Druckes in einer Kraftstoff-Vorlaufleitung |
US7395814B1 (en) | 2006-09-11 | 2008-07-08 | Brunswick Corporation | Electronic voltage regulation for a marine returnless fuel system |
JP4656044B2 (ja) * | 2006-11-10 | 2011-03-23 | 株式会社豊田自動織機 | 圧縮機の吸入絞り弁 |
CN102052120B (zh) * | 2010-11-27 | 2013-01-02 | 奇瑞汽车股份有限公司 | 一种机油泵 |
US10513343B2 (en) | 2015-08-03 | 2019-12-24 | Parker-Hannifin Corporation | Integral pump pressure relief valve |
US11022115B2 (en) * | 2017-06-02 | 2021-06-01 | Purdue Research Foundation | Controlled variable delivery external gear machine |
CN214889781U (zh) * | 2021-03-08 | 2021-11-26 | 烟台杰瑞石油装备技术有限公司 | 柱塞泵底座和柱塞泵装置 |
Family Cites Families (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2310078A (en) * | 1938-12-24 | 1943-02-02 | Vickers Inc | Pump or motor for power transmission |
US2397480A (en) * | 1939-06-20 | 1946-04-02 | Jr Dicks Phelps Fullerton | Variable-speed transmission |
US2263548A (en) * | 1940-03-07 | 1941-11-18 | American Locomotive Co | Reversible rotary liquid pump |
US2481646A (en) * | 1943-08-18 | 1949-09-13 | Western Electric Co | Variable delivery gear pump |
US3146720A (en) * | 1961-12-06 | 1964-09-01 | Dresser Ind | Pressure relief means for pump |
FR1385040A (fr) * | 1964-02-24 | 1965-01-08 | Charmilles Sa Ateliers | Pompe à engrenages |
US3628893A (en) * | 1970-05-04 | 1971-12-21 | Poerio Carpigiani | Liquid and air mixing gear pump |
US3935917A (en) * | 1974-10-18 | 1976-02-03 | Tyrone Hydraulics, Inc. | Hydraulic pump control system |
US4013053A (en) * | 1975-05-02 | 1977-03-22 | Stewart-Warner Corporation | Fuel pump |
US4200207A (en) * | 1978-02-01 | 1980-04-29 | Nordson Corporation | Hot melt adhesive foam pump system |
JPS57193791A (en) * | 1981-05-25 | 1982-11-29 | Jidosha Kiki Co Ltd | Oil pump |
FR2551495B1 (fr) * | 1983-09-07 | 1985-11-08 | Snecma | Procede et dispositif pour reduire l'auto-echauffement d'un circuit de carburant de turbomachine |
DE3342385A1 (de) * | 1983-11-24 | 1985-06-05 | Montblanc-Simplo Gmbh, 2000 Hamburg | Zahnradpumpe |
DE3424883A1 (de) * | 1984-07-06 | 1986-02-06 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
US4902202A (en) * | 1987-07-29 | 1990-02-20 | Hydreco, Inc. | Variable discharge gear pump with energy recovery |
JPH0255892A (ja) * | 1988-08-19 | 1990-02-26 | Kobe Steel Ltd | スクリュ式真空ポンプ |
FI83808C (fi) * | 1988-10-05 | 1991-08-26 | Tampella Oy Ab | Foerfarande foer styrning av luftproduktionen i en skruvkompressor. |
US5338161A (en) * | 1991-06-19 | 1994-08-16 | Dana Corporation | Gear pump having internal bypass valve |
AT402542B (de) * | 1992-06-02 | 1997-06-25 | Hoerbiger Ventilwerke Ag | Ansaugregelventil |
SE470446B (sv) * | 1992-08-21 | 1994-03-28 | Electrolux Ab | Hydraulmotor försedd med en by-pass-ledning mellan in- och utloppsledning, i vilken by-pass-ledning är anordnad en huvudventil för pådrag respektive stopp av hydraulmotorn |
DE4238040A1 (de) * | 1992-11-11 | 1994-05-19 | Vdo Schindling | Saugstrahlpumpe zum Fördern von Kraftstoff |
US5397219A (en) * | 1993-06-21 | 1995-03-14 | C. Cretors & Company | Integral liquid pump and drainback valve |
DE59402095D1 (de) * | 1993-07-23 | 1997-04-17 | Teves Gmbh Alfred | Hydraulische bremsanlage mit bremsschlupf- und antriebsschlupfregelung |
DE9319462U1 (de) * | 1993-12-17 | 1995-04-27 | Lucas Industries Public Limited Company, Solihull, West Midlands | Kolbenpumpe zum Fördern von Hydraulikflüssigkeit in einer blockiergeschützten Fahrzeugbremsanlage |
DE4441505A1 (de) * | 1994-11-22 | 1996-05-23 | Bosch Gmbh Robert | Kraftstoff-Förderpumpe für eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
-
1996
- 1996-06-26 DE DE19625565A patent/DE19625565C2/de not_active Expired - Fee Related
-
1997
- 1997-02-13 EP EP97915286A patent/EP0846224B1/de not_active Expired - Lifetime
- 1997-02-13 US US09/029,378 patent/US6099263A/en not_active Expired - Fee Related
- 1997-02-13 DE DE59702810T patent/DE59702810D1/de not_active Expired - Fee Related
- 1997-02-13 WO PCT/DE1997/000273 patent/WO1997049910A1/de active IP Right Grant
- 1997-02-13 CZ CZ1998548A patent/CZ290647B6/cs not_active IP Right Cessation
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6773240B2 (en) | 2002-01-28 | 2004-08-10 | Visteon Global Technologies, Inc. | Single piston dual chamber fuel pump |
Also Published As
Publication number | Publication date |
---|---|
DE19625565A1 (de) | 1998-01-08 |
WO1997049910A1 (de) | 1997-12-31 |
DE59702810D1 (de) | 2001-02-01 |
EP0846224A1 (de) | 1998-06-10 |
DE19625565C2 (de) | 1998-07-23 |
US6099263A (en) | 2000-08-08 |
CZ290647B6 (cs) | 2002-09-11 |
CZ54898A3 (cs) | 1998-10-14 |
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