EP0846229B1 - Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen - Google Patents

Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen Download PDF

Info

Publication number
EP0846229B1
EP0846229B1 EP97914124A EP97914124A EP0846229B1 EP 0846229 B1 EP0846229 B1 EP 0846229B1 EP 97914124 A EP97914124 A EP 97914124A EP 97914124 A EP97914124 A EP 97914124A EP 0846229 B1 EP0846229 B1 EP 0846229B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel
delivery
closing member
space
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
Application number
EP97914124A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0846229A1 (de
Inventor
Stanislaw Bodzak
Hanspeter Mayer
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0846229A1 publication Critical patent/EP0846229A1/de
Application granted granted Critical
Publication of EP0846229B1 publication Critical patent/EP0846229B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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

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.
  • 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 Intake space of the fuel delivery pump is provided.
  • the This bypass channel is opened by means of the Bypass channel used pressure valve, which at a determined 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.
  • German patent application P 44 41 505.2 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.
  • This known fuel delivery pump has the disadvantage on that in operation Internal combustion engine the amount of fuel delivered significantly is higher than the required amount of fuel. The too much The amount of fuel delivered is from the bypass valve Pressure chamber led into the suction chamber, and through that The resulting pressure drop across the valve turns the energy into heat converted, resulting in a loss of work performance.
  • the fuel delivery pump according to the invention for a Has fuel injection pump for internal combustion engines in contrast the advantage that a control loop in the Fuel feed pump can be created, the pressure and is volume controlled. This can reduce the power loss by one considerably reduced.
  • By throttling the in the power flow supplied to the intake chamber can be prevented be that in the event of a sudden increase in pressure as a result of a part of the delivery rate too large on the pressure side amount of fuel delivered within the fuel delivery pump is pumped through a bypass channel and through the pressure drop at the bypass valve converts energy into heat becomes.
  • the arrangement according to the invention enables that by a flow short circuit via the bypass valve and one Throttling the amount of fuel fed into the intake chamber Pressure peaks in the pressure chamber can be reduced and the amount supplied is reduced by the suction throttling.
  • That arranged in a housing of the fuel delivery pump and an inlet opening leading into the intake space closing throttle valve also has the advantage on that a fuel delivery pump with a low Installation space can be formed.
  • the throttle valve is advantageously via a spool with the Pressure valve connected so that direct control of the Throttle valve can be given via the pressure valve.
  • This The arrangement also has a reduced-component arrangement on, making it inexpensive and easy to assemble simplified design of a fuel delivery pump can be created.
  • a multi-substance pump e.g. For Lubricating oil
  • the features of a feed pump according to the claim 1 have.
  • 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.
  • One on one first shaft 5 attached first gear 7 by means of a external drive element not shown driven in rotation and transmits this rotary movement by means of a spur gear on a with the first gear 7 intermeshing second gear 9 on a second housing-mounted shaft 11 is arranged.
  • the gears 7, 9 divide the pump chamber 3 by their meshing two parts, a first part of a suction chamber 13 and a second part form a pressure chamber 15.
  • the intake space 13 is one between the tooth grooves on the End face of the first gear 7 and the second gear 9 and the circumference formed by the pump edge 3 Delivery channel 17 connected to the pressure chamber 15. Also points the suction chamber 13 and the pressure chamber 15 each one Connection opening 19, 21 in the wall of the pump housing 1, through which the suction space 13 with a connecting element 14 one Suction line (not shown) from the storage tank and the pressure chamber 15 with a delivery line, not shown is connected to the suction chamber of the fuel injection pump.
  • the connection opening in the suction chamber 13 forms a Inlet opening 19 and the connection opening in the pressure chamber 15 an outlet opening 21.
  • the pump chamber 3 is on one of them Front in the axial direction of the shafts 5 and 11 of one Closed cover 23, which in the representation of the Fig. 2 was removed and so a view of the pump interior enables.
  • a channel 25 is provided in the pump housing 1.
  • This channel 25 is through a hole in one 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 channel 25 forming hole is listed as a through hole whose one end in the pressure chamber 15 and the other end in the Intake chamber 13 opens and forms a bypass channel.
  • the bypass channel 25 has a through one Bore shoulder formed cross-sectional reduction in the direction Pressure chamber 15, the bypass channel side formed Ring shoulder a valve seat 29 one in the channel 25 set pressure valve 31 forms.
  • valve closing member 33 of the pressure valve 31 With a on its end face formed on the pressure chamber side 25 due to the force of a valve spring 37 for contact.
  • This Valve spring 37 in channel 25 engages on a shoulder Valve closing member 33 and is supported on the other hand one inserted into the suction chamber end of the channel 25 Adapter sleeve 39 from.
  • This adapter sleeve 39 is analogous to that remaining components of the pressure valve 31 via the inlet opening 19 can be used in the channel 25, with the axial Installation depth of the one that releases a flow cross-section Collet 39, the biasing force of the valve spring 37 and thus the opening pressure of the pressure valve 31 in the channel 25 the Pressure chamber 15 and the suction chamber 13 is adjustable.
  • the Adapter sleeve 39 can be pressed into the channel 25 or be screwed in by means of a thread, so that a very exact axial position fixing of the clamping sleeve 39 is possible.
  • a throttle valve 40 is arranged in the inlet opening 19.
  • This throttle valve 40 has a connecting element 14 which is screwed into the inlet opening.
  • This Connection element 14 can also by means of a Quick release or by means of a quick connection in the inlet opening 19 may be introduced.
  • the connecting element 14 has a collar 41 on the edge region of the inlet opening 19 rests and a correct position in the axial direction Positioning allows.
  • the connecting element 14 has a valve seat 42 on which a sealing surface 43 of a valve closing member 44 via a Control slide 46 comes to the plant, which is integral with the Valve closing member 33 of the pressure valve 31 is connected.
  • the Valve closing member 44 points counter to the fuel delivery direction a guide element 47, which in cross section seen conical and is integral with the Valve closing member 44 is connected.
  • a guide element 47 which in cross section seen conical and is integral with the Valve closing member 44 is connected.
  • One on the cone surface subsequent cylindrical portion 48 of the Guide element 47 is coaxial with the inside diameter of the Connection element 14 is formed and is in the axial direction slidably guided to the connecting element 14.
  • the guide element 47 has a plurality of depressions on so that the fuel supplied is essentially can flow past the guide element 47 undisturbed.
  • Four are advantageously offset from one another by 90 ° Wing provided, which extends to the inner wall of the Extension element 14 extend.
  • the valve closing member 44 with the guide element 47 can advantageously be made of plastic and is to a free end of the spool 46 via a locking and / or snap connection attachable.
  • a spherical valve seat can be provided instead of the conical valve seat 42 .
  • a spherical valve seat can be provided instead of the conical valve seat 42 .
  • other geometric shapes may be possible allow the leading into the suction chamber 15 Cable cross section is closable.
  • FIG. 4 is an alternative embodiment of a Throttle valve 50 with respect to throttle valve 40 in FIG. 3 shown.
  • An adapter sleeve 39 introduced into the channel 25 extends through the suction space 13 to the inlet opening 19 and has a passage 51 through a coaxial Bore 52 to the inlet opening and one radially in the Intake chamber 13 leading throttle bore 53 is formed.
  • the Adapter sleeve 39 is designed as a throttle bush in which Control slide 46 is guided axially movable.
  • the Control slide 46 is integral with the valve closing member 33 connected and has at its opposite end Valve closing member 54, which is formed by an O-ring is, which seals the bore 52 of the clamping sleeve 39.
  • the Bore 52 of the adapter sleeve 39 is the valve seat of the Throttle valve 50 is formed.
  • the pressure valve 31 When the internal combustion engine is at a standstill, the pressure valve 31 with the operatively connected throttle valve 50 in FIG. 4 shown position arranged. When closed of the pressure valve 31, the throttle valve 50 is in an open Held in position, causing fuel from the storage tank in the intake chamber 13 can flow. In the operation of the Internal combustion engine increases in the pressure chamber 15 due to the too much fuel delivered the pressure, causing the Pressure valve 31 opens against the valve spring 37. At the same time, the throttle valve 50 is over the Control spool 46 to the right towards Inlet opening 19 moves. With a slight overpressure opens the pressure valve 31, causing a flow short circuit from the Pressure chamber 15 to the suction chamber 13 via the bypass duct 56 given is.
  • valve closing member 54 is over the spool 56 moves to the right, causing the Cross section of the bore 53 is reduced and the Suction throttle effect is increased, so less fuel can flow into the suction space 13.
  • the valve lift increases of the valve closing member 33 until the valve closing member 54 of the throttle valve 50, the bore 52 before the throttle bore 53 closes in the fuel delivery direction. In this Position gives the valve body 33 of the pressure valve 31 Bypass channel 56 completely free, creating a Flow short circuit between the pressure chamber 15 and the Intake space 13 is given and a fuel return from the pressure chamber 15 in the suction chamber 13 is made possible.
  • valve closing member 33 points in recesses on its peripheral wall so that the fuel in can flow into the bypass channel 25.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP97914124A 1996-06-26 1997-02-06 Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen Expired - Lifetime EP0846229B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19625564A DE19625564C2 (de) 1996-06-26 1996-06-26 Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen
DE19625564 1996-06-26
PCT/DE1997/000223 WO1997049917A1 (de) 1996-06-26 1997-02-06 Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0846229A1 EP0846229A1 (de) 1998-06-10
EP0846229B1 true EP0846229B1 (de) 2000-05-03

Family

ID=7798072

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97914124A Expired - Lifetime EP0846229B1 (de) 1996-06-26 1997-02-06 Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen

Country Status (5)

Country Link
US (1) US6095763A (cs)
EP (1) EP0846229B1 (cs)
CZ (1) CZ289161B6 (cs)
DE (2) DE19625564C2 (cs)
WO (1) WO1997049917A1 (cs)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19913804A1 (de) * 1999-03-26 2000-09-28 Bosch Gmbh Robert Kraftstoff-Förderpumpe
DE10250554A1 (de) 2002-10-30 2004-05-19 Robert Bosch Gmbh Vorrichtung mit einem Gehäuse und mit wenigstens einem im Gehäuse angeordneten rotierenden Bauteil
DE10337849A1 (de) * 2003-08-18 2005-03-17 Robert Bosch Gmbh Flüssigkeitspumpe
US7395814B1 (en) 2006-09-11 2008-07-08 Brunswick Corporation Electronic voltage regulation for a marine returnless fuel system
WO2008107065A1 (de) * 2007-03-06 2008-09-12 Ixetic Bad Homburg Gmbh Pumpe mit einem magnetisch angesteuertem schaltventil zur saugdrosselung
CN104260013B (zh) * 2014-09-23 2016-08-24 苏州农业职业技术学院 一种基于蜗杆蜗轮与曲柄连杆传动的手动压紧装置
DE102018131587A1 (de) * 2018-12-10 2020-06-10 Nidec Gpm Gmbh Regelbare Schraubenspindelpumpe

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2310078A (en) * 1938-12-24 1943-02-02 Vickers Inc Pump or motor for power transmission
US2481646A (en) * 1943-08-18 1949-09-13 Western Electric Co Variable delivery gear pump
US2739446A (en) * 1954-12-06 1956-03-27 Vickers Inc Power transmission
US3146720A (en) * 1961-12-06 1964-09-01 Dresser Ind Pressure relief means for pump
US3253607A (en) * 1964-06-10 1966-05-31 Trw Inc Combination pump and flow regulator
US3628893A (en) * 1970-05-04 1971-12-21 Poerio Carpigiani Liquid and air mixing gear pump
DE2200301A1 (de) * 1971-02-03 1972-08-10 Apaw Sa Zahnradpumpe zur Herstellung von Luft-Fluessigkeitsgemischen,insbesondere in Softeis- und Schlagsahnemaschinen od.dgl.
US3935917A (en) * 1974-10-18 1976-02-03 Tyrone Hydraulics, Inc. Hydraulic pump control system
FR2508112B1 (fr) * 1981-06-19 1986-05-02 Citroen Sa Regulateur de pompe par etranglement a l'aspiration avec limiteur de pression incorpore
FR2551495B1 (fr) * 1983-09-07 1985-11-08 Snecma Procede et dispositif pour reduire l'auto-echauffement d'un circuit de carburant de turbomachine
WO1986006797A2 (fr) * 1985-05-09 1986-11-20 Barmag Aktiengesellschaft Pompe a capacite variable
US4902202A (en) * 1987-07-29 1990-02-20 Hydreco, Inc. Variable discharge gear pump with energy recovery
US5338161A (en) * 1991-06-19 1994-08-16 Dana Corporation Gear pump having internal bypass valve
EP0522505A3 (en) * 1991-07-09 1993-07-14 Toyoda Koki Kabushiki Kaisha Variable-displacement vane pump
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
US5397219A (en) * 1993-06-21 1995-03-14 C. Cretors & Company Integral liquid pump and drainback valve
JPH10507982A (ja) * 1993-07-23 1998-08-04 アイティーティー・オートモーティブ・ヨーロップ・ゲーエムベーハー ブレーキスリップ制御およびトラクションスリップ制御付き液圧ブレーキシステム
JPH07223549A (ja) * 1994-02-10 1995-08-22 Honda Motor Co Ltd パワーステアリング用流量制御装置
US5496155A (en) * 1994-02-24 1996-03-05 Trw Inc. Rotary device having plural mounting orientations and fluid connections
DE4441505A1 (de) * 1994-11-22 1996-05-23 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Also Published As

Publication number Publication date
DE59701565D1 (de) 2000-06-08
US6095763A (en) 2000-08-01
DE19625564A1 (de) 1998-01-08
CZ54998A3 (cs) 1999-05-12
CZ289161B6 (cs) 2001-11-14
WO1997049917A1 (de) 1997-12-31
DE19625564C2 (de) 2000-06-08
EP0846229A1 (de) 1998-06-10

Similar Documents

Publication Publication Date Title
DE3722665C2 (cs)
DE1528951C3 (de) Verdrängerpumpe zur Förderung einer stark dampf- und blasenhaltigen Flüssigkeit
WO2020120064A1 (de) Regelbare schraubenspindelpumpe
EP0846229B1 (de) Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen
EP0846224B1 (de) Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen
DE4441505A1 (de) Kraftstoff-Förderpumpe für eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE10244551A1 (de) Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE102018008905A1 (de) Hohlzapfenpumpe mit Fördermengenregelung
EP2807365A1 (de) Kraftstoffhochdruckpumpe eines einspritzsystems
DE19513822C2 (de) Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges
EP0290864B1 (de) Innenachsige Drehkolbenmaschine
EP0846228B1 (de) Kraftstoff-förderpumpe für eine kraftstoff-einspritzpumpe für brennkraftmaschinen
DE19638335C2 (de) Förderpumpe
EP0822329B1 (de) Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen
DE10220281A1 (de) Kraftstoffpumpe, insbesondere für eine Brennkraftmaschine mit Direkteinspritzung
DE102012203724A1 (de) Kraftstofffördereinrichtung für ein Kraftstoffeinspritzsystem mit einem Überströmventil sowie Überströmventil
DE3943299A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE102007008177A1 (de) Bypass-Druckbegrenzung für Außenzahnrad-Regelölpumpen
DE10014548A1 (de) Zahnradförderpumpe
DE102010063398A1 (de) Kraftstofffördereinrichtung für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102011082588A1 (de) Überströmventil mit abgeflachter Kennlinie zur Druckbegrenzung in einem Niederdruckbereich einer Kraftstoffeinspritzvorrichtung
DE102007058759A1 (de) Rückschlagventil für eine Schmierstoffpumpe sowie Schmierstoffpumpe
EP1942277A2 (de) Staudruck-Regelung für Hydraulikpumpen
DE4011846A1 (de) Aggregat zum foerdern von kraftstoff
WO2009095011A2 (de) Druckumschaltung für ölpumpen

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19980630

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 19990607

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REF Corresponds to:

Ref document number: 59701565

Country of ref document: DE

Date of ref document: 20000608

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20000706

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20060215

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20060228

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20060407

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070207

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20070206

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20071030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070901

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20060220

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070206

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070228

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20060221

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070206