US3644064A - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

Info

Publication number
US3644064A
US3644064A US29113A US3644064DA US3644064A US 3644064 A US3644064 A US 3644064A US 29113 A US29113 A US 29113A US 3644064D A US3644064D A US 3644064DA US 3644064 A US3644064 A US 3644064A
Authority
US
United States
Prior art keywords
regulator
shuttle
bypass channel
cylinder
improvement
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
US29113A
Other languages
English (en)
Inventor
Konrad Eckert
Gerald Hofer
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
Application granted granted Critical
Publication of US3644064A publication Critical patent/US3644064A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages

Definitions

  • This invention relates to a fuel injection pump for internal combustion engines and is of the type wherein the delivered fuel quantities are variable by interrupting the fuel delivery during each pressure stroke of the pump piston. Such interruption is effected by opening a bypass channel (leading from the pump work chamber) by means of a reciprocating regulator member which is displaced in the forward direction against the force of a return spring by a fuel volume driven by an auxiliary pump operating synchronously with the main fuel pump.
  • the regulator member is provided with an oblique control edge and is turnable so that the travelling path of the regulator member prior to opening the bypass channel may be varied as a function of the angular position of the regulator member.
  • the viscosity of the fuel changes as a function of the temperature in the fuel injection pumps of the above type, the temperature variations have a disadvantageous effect on the regulation and further, the fuel present in the regulator circuit forms a system capable of oscillation in which resonance phenomena interfering with the fluid abutment might appear.
  • adjusting means are provided for an rpm-dependent fuel quantity control ensuring that the initial or starting position of the regulator member is constant and thus independent of load and r.p.m. conditions.
  • FIG. 1 is a schematic sectional view of a first embodiment of the invention
  • FIG. 2 is a diagram depicting two sets of graphs showing the stroke of the regulator member and the pump piston as a function of the angular position of the pump piston driving means and
  • FIG. 3 is a sectional view of a second embodimentof the invention.
  • a stepped piston 2, 3 which is driven by means (e.g., including a cam) not shown.
  • Said piston is adapted to execute a reciprocating axial motion as well as a rotary motion about its axis. While the reciprocating motion serves for delivering the fuel to the engine, the rotary motion serves for fuel distribution.
  • a first piston portion or main piston 2 having a relatively small diameter, operates in a cylinder 5 and bounds therewith a pump work chamber 6 of the fuel injection pump proper.
  • the main piston 2 is provided with a circumferential annular groove 10 which is in continuous communication with the pump work chamber 6 through an axial channel Ill.
  • the annular groove 10 controls a fuel supply bore 12 through which the pump work chamber 6, as long as the pump piston is in the vicinity of its lower dead center, is supplied with fuel from a suction chamber 13.
  • a pressure control valve 16 In each pressure conduit 15 (only one shown) there is disposed a pressure control valve 16.
  • the regulator shuttle 9 During each pressure stroke of the piston 2, 3, the regulator shuttle 9 is displaced in a cylinder 18 against the force of a return spring 19 which moves said regulator shuttle into its initial position during the suction strokes of the piston. When in its initial position, the regulator shuttle 9 engages with its collar 20 an abutment 21 forming part of the housing 1.
  • the regulator shuttle 9 is provided with a circumferential annular groove 22 which is bounded by obliquely extending control edges 23 and 24.
  • the annular groove 22 controls a bypass channel formed of portions 25a, 25b and 250 connecting the pump work chamber 6 with the suction chamber 13.
  • the bypass channel portion 250 extending between the pump work chamber 6 and the cylinder 13 is in continuous communication with the annular groove 22.
  • bypass channel portions 25a and 25b, both merging into the suction chamber 13, are controlled, respectively, by means of the oblique control edges 23 and 24.
  • Fuel delivery from the pump work chamber 6 through one of the pressure channels 15 takes place only during those periods of each pressure stroke of piston 2, when both bypass channel portions 25a and 25b are closed by the regulator shuttle 9. If either bypass channel 25a or 25b is in communication with bypass channel portion 250 through annular groove 22, no fuel delivery through pressure conduits 15 takes place, since the fuel driven by piston 2, flows from pump work chamber 6 to suction chamber 13 through bypass channel 250, 25a, or bypass channel 250, 25b.
  • the regulator shuttle 9 maintains bypass channel portion 25a open and bypass channel portion 25b closed.
  • the regulator shuttle 9 executes first a prestroke during which no fuel delivery takes place, since bypass channel portion 25a is still open.
  • the prestroke terminates as the control edge 23 of the regulator shuttle 9 closes the bypass channel portion 25a. This moment marks the beginning of the delivery period since both bypass channel portions 25a and 25b are closed.
  • the control edge 24 opens the bypass channel portion 25b at which moment the delivery period is terminated.
  • control edge 23 determines the beginning of the fuel injection, while the control edge 24 determines the termination thereof.
  • the travelling path of control shuttle 9, during which injection takes place may be altered by varying the angular position of the regulator shuttle 9. In this manner, the quantities delivered by the fuel injection pump may be set.
  • the regulator shuttle 9 is angularly adjustable by a rigid assembly formed of a shaft 28 extending outwardly from the housing 1, a disc 26 disposed axially spaced from collar 20 and simultaneously serving as a spring seat disc for return spring 19 and a pin 27 affixed to disc 26 and extending into a depression 29 of collar 20.
  • the displacement of the regulator shuttle 9 be relatively large.
  • the radial area or work face 94 of regulator shuttle 9 exposed to the fuel pressure in cylinder 18 is greater than the surface area of auxiliary piston 3 generating the fuel pressure in channel 8 and cylinder 18.
  • the regulator shuttle 9 displaces fuel from the cylinder 18 through channel 8 in an unthrottled manner, so that, independent of rpm. and load conditions, the regulator shuttle 9 will always be permitted to return to its initial position (engaging the stationary abutment 21) before the subsequent pressure stroke of piston 2, 3 begins.
  • the shaft 28 is turnable by an r.p.m. regulator schematically shown at R, which effects, by virtue of the oblique control edge 23, a load-dependent shift in the beginning of the injection.
  • the r.p.m. regulator may be of the electric, hydraulic, pneumatic or mechanical type; it may control idling and terminal r.p.m.s. or may be effective over a large r.p.m. range.
  • auxiliary piston 3 In order to make possible a solely r.p.m.-dependent adjustment of the start of the fuel injection for any given injected fuel quantity per stroke (that is, for any given angular position of the regulator shuttle 9), in auxiliary piston 3 there is provided a channel 30 which extends from the pump work chamber of the auxiliary pump 3, 7.
  • the channel 30 has a throttle 31 which is controlled as a function ofthe r.p.m. by an axially displaceable sleeve 32 surrounding the auxiliary piston 3.
  • the fuel in channels 8, 30 and in cylinder 18 communicates with the suction chamber 13, so that there is insufficient pressure to displace the regulator shuttle 9 in the forward direction against the force of the return spring 19.
  • the throttle 31 is closed by the sleeve 32, at which moment the forward motion of the regulator shuttle 9 begins.
  • the sleeve 32 dependsent upon the position of the sleeve 32, during the beginning of the pressure stroke of the pump piston 2, 3, one part of the fuel is discharged from the pump work chamber of the auxiliary pump 3, 7 into the suction chamber 13, whereby the forward motion of the regulator shuttle 9 and thus the beginning of the injection may be delayed to a greater or lesser extent.
  • the sleeve 32 is displaceable by a hydraulic, electric, pneumatic or mechanical device schematically indicated at 33.
  • the suction chamber 13 is supplied with fuel by a continuously operating delivery pump 34 which draws fuel from a tank 35. in order to obtain in the suction chamber 13 a pressure increase in response to an r.p.m. increase to operate, for example, a hydraulic device 33, between the pressure side and the suction side of the fuel delivery pump 34 there is provided a return conduit containing a pressure control valve 36.
  • the ordinate indicates the displacement of the regulator shuttle 9 as a function of the angular position at (indicated along the abscissa) of a driving means (usually a cam) associated with the pump piston to cause a reciprocating motion thereof.
  • the ordinate indicates the piston stroke s of the pump piston as a function of said angle a.
  • the curve l characterizes the motion of the regulator shuttle 9 when the sleeve 32 is in a relatively low position (as viewed in FIG. 1).
  • the regulator shuttle 9 begins its forward motion.
  • the control edge 23 closes the bypass channel portion 25a.
  • the fuel injection is interrupted and the fuel still present in the pump work chamber 6 is displaced during the remainder of the pressure stroke of the piston from the pump work chamber 6 into the suction chamber 13.
  • the flow passage section 31 is, for example, due to an increasing r.p.m., enlarged (i.e., the sleeve 32 is shifted to a relatively higher position)
  • the axial motion of the regulator shuttle 9 is characterized by curve ll.
  • the pump piston has to travel a distance s, before the regulator shuttle 9 begins its forward motion. Only when the driving means reaches an angular position 01 will the control edge 23 close the bypass channel portion 25a.
  • FIG. 3 the second embodiment shown therein operates substantially in the same manner as the first embodiment described in connection with HO. 1 except for some structural and functional differences now to be described.
  • the pump piston in addition to stepped portions 2 and 3, has a third stepped portion 4 which operates in a cylinder 38 and serves as a delivery pump drawing fuel from the tank 35 through a supply channel 39 and introducing it to the suction chamber 13.
  • the pump 3, 7 is the injection pump proper, whereas the pump 2, 5 associated with the pump work chamber 6 operates as the auxiliary pump.
  • the sleeve 32 is displaced against a spring 40 by the pressure prevailing in the suction chamber 13. In this manner the flow passage section 31 is changed.
  • This regulation may be effected, for example, by electrical means,
  • the sleeve 32 may be displaced only if a solenoid shutoff valve 41 opens a channel 42 which connects the chamber 46 containing the spring 40 with the supply channel 39.
  • Signals characterizing the actual position of the sleeve 32 may be applied by an electromagnetically operated position sensor 43 to an electronic control device (not shown) for setting the beginning of the injection.
  • a control device 44 for setting the delivered fuel quantities receives signals from an electronic r.p.m. regulator (not shown) to which the signals characterizing the actual r.p.m. are applied by an r.p.m. sensor 45.
  • pressure conduit means communicating with said pump work chamber to carry fuel pressurized in said pump work chamber by each pressure stroke of said main piston
  • G means to operate said auxiliary piston synchronously with said main piston
  • a regulator shuttle slidably disposed in said third cylinder and having a work face and at least one oblique control edge
  • M. rpm-dependent means connected to said regulator shuttle for angularly displacing the latter to vary the position of said control edge as a function of the rpm
  • said regulator shuttle includes an axially extending groove maintaining said bypass channel continuously open during displacement of said regulator shuttle if the latter is in a predetermined angular position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US29113A 1969-04-09 1970-04-16 Fuel injection pump for internal combustion engines Expired - Lifetime US3644064A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19691917928 DE1917928A1 (de) 1969-04-09 1969-04-09 Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen
US2911370A 1970-04-16 1970-04-16

Publications (1)

Publication Number Publication Date
US3644064A true US3644064A (en) 1972-02-22

Family

ID=25757256

Family Applications (1)

Application Number Title Priority Date Filing Date
US29113A Expired - Lifetime US3644064A (en) 1969-04-09 1970-04-16 Fuel injection pump for internal combustion engines

Country Status (5)

Country Link
US (1) US3644064A (US20080293856A1-20081127-C00150.png)
AT (1) AT302729B (US20080293856A1-20081127-C00150.png)
DE (1) DE1917928A1 (US20080293856A1-20081127-C00150.png)
FR (1) FR2043132A5 (US20080293856A1-20081127-C00150.png)
GB (1) GB1306543A (US20080293856A1-20081127-C00150.png)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3827832A (en) * 1971-10-19 1974-08-06 Bosch Gmbh Robert Means for reducing fuel delivery of fuel injection pumps in the low rpm range
US3943903A (en) * 1973-07-14 1976-03-16 C. A. V. Limited Liquid fuel injection pumping apparatus
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
DE3019343A1 (de) * 1980-05-21 1981-11-26 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3013088A1 (de) * 1980-04-03 1981-10-15 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPS57188759A (en) * 1981-05-15 1982-11-19 Diesel Kiki Co Ltd Distribution type fuel injector
DE3144277C2 (de) * 1981-11-07 1995-06-01 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3633912C2 (de) * 1985-10-15 1996-06-20 Volkswagen Ag Kraftstoffeinspritzpumpe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3417703A (en) * 1965-10-15 1968-12-24 Bosch Gmbh Robert Fuel injection pump
US3421486A (en) * 1967-04-10 1969-01-14 Allis Chalmers Mfg Co Fuel injection control

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3417703A (en) * 1965-10-15 1968-12-24 Bosch Gmbh Robert Fuel injection pump
US3421486A (en) * 1967-04-10 1969-01-14 Allis Chalmers Mfg Co Fuel injection control

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3827832A (en) * 1971-10-19 1974-08-06 Bosch Gmbh Robert Means for reducing fuel delivery of fuel injection pumps in the low rpm range
US3943903A (en) * 1973-07-14 1976-03-16 C. A. V. Limited Liquid fuel injection pumping apparatus
US4073275A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump
DE3019343A1 (de) * 1980-05-21 1981-11-26 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
GB1306543A (en) 1973-02-14
AT302729B (de) 1972-10-25
DE1917928A1 (de) 1970-11-12
FR2043132A5 (US20080293856A1-20081127-C00150.png) 1971-02-12

Similar Documents

Publication Publication Date Title
US3699939A (en) Fuel injection pump for internal combustion engines and method of fuel control
US3837324A (en) Fuel injection system for internal combustion engines
US4951631A (en) Fuel injection device, in particular, a unit fuel injector, for internal combustion engines
US5056488A (en) Fuel injection system in particular unit fuel injector, for internal combustion engines
US4279385A (en) High pressure fuel injection apparatus for internal combustion engines
US4463725A (en) Fuel injection device for internal combustion engines, in particular a pump/nozzle for diesel engines
GB1390422A (en) Fuel injection systems for internal combustion engines
GB2136885A (en) Fuel injection system for an internal combustion engine
US4211203A (en) Fuel injection pump
US5042718A (en) Solenoid-valve-controlled fuel injection device, for an air-compressing internal combustion engine
US3638631A (en) R.p.m. regulator for fuel injection pumps
US3644064A (en) Fuel injection pump for internal combustion engines
US4976244A (en) Fuel injection device for internal combustion engines, in particular unit fuel injection
US5273017A (en) Fuel injection pump for internal combustion engines
US4430974A (en) Fuel injection pump for internal combustion engines
US3827832A (en) Means for reducing fuel delivery of fuel injection pumps in the low rpm range
US3620648A (en) Fuel injection system for internal combustion engines
US5040511A (en) Fuel injection device for internal combustion engines, in particular unit fuel injector
US4136654A (en) Fuel injection nozzle for preliminary and main injection into internal combustion engines
US3777731A (en) Fuel injection system in a distributor-type injection pump for internal combustion engine
US5168847A (en) Fuel injection pump for internal combustion engines
US4741314A (en) Fuel injection pump for internal combustion engine
US3848576A (en) Fuel injection pump for internal combustion engines
GB1322538A (en) Fuel injection pumps for internal combustion engines
US3403629A (en) Fuel injection pump for internal combustion engines