US3738180A - Control devices - Google Patents

Control devices Download PDF

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Publication number
US3738180A
US3738180A US00147118A US3738180DA US3738180A US 3738180 A US3738180 A US 3738180A US 00147118 A US00147118 A US 00147118A US 3738180D A US3738180D A US 3738180DA US 3738180 A US3738180 A US 3738180A
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United States
Prior art keywords
cam
cam follower
rollers
follower means
profile
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Expired - Lifetime
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US00147118A
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English (en)
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G Sola
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Fiat SpA
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Fiat SpA
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    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/1828—Cam, lever, and slide

Definitions

  • ABSTRACT Foreign Application Priority a A control device suitable forthe fuel injection pump of S t 15 1970 It 1 70096 A 70 an mternal combustlon engine 1s shown.
  • the device ep ay comprises a rotatable cam having a plurality of symmetrical lobes and a cam follower having two rollers [22] which are both in Contact with the cam face
  • the Cam 280/ follower is linked to an operating member of an associ- 1 0 ⁇ 23/139 k ated pump.
  • rollers of the cam follower are relatively large to withstand the forces produced at high speed and the pivot for the cam follower is arranged so [56] References Cited that it does not obstruct the space between the two roll- UNITED STATES PATENTS ers.
  • the cam profile is so shaped that the two rollers are 3,263,512 8/1966 Handley 74/569 both always in contact with the surface of the cam so 1,198,283 9/1916 Shira 74/53 that there is no in their movement; 1,777,179 9/1930 Perlman 74/53 1,630,273 5/1927 Nordwick 74/53 14 Claims, 9 Drawing Figures Ill.
  • the present invention relates to a control device for a pump, such as a fuel injection pump for a multicylinder internal combustion engine.
  • the invention relates to a control device of the type comprising a cam profile having a plurality of substantially symmetrical lobes, extending radially outwardly in a single plane perpendicular to the axis of rotation of the cam, and a cam follower having a pair of rollers or sliding blocks supported by a rocker arm, both rollers being engaged on respective opposed lobe faces of the cam.
  • One roller or sliding block is directly associated with an operative element of the associated pump and is moved by the cam to produce a pumping stroke of this operative element and the other roller or sliding block operates as a return element to effect the return stroke of the operative element of the pump.
  • a control device for a fuel injection pump of a multicylinder internal combustion engine having a cam with a plurality of lobes each lobe being symmetric about a radial line through the top dead center of the lobe,'a cam follower having two rollers both in contact with the profile of the cam, the rollers being mounted-at respective ends of a rocker arm which is supported for pivotal movement about an intermediate point midway between the roller axes to a support member attachable to the casing of an associated pump, one of the two rollers being connectable by means of a connecting rod, to an operating member of an associated pump, in which the pivotal support for the said rocker arm does not extend into the region between the two rollers, and in which the part of the profile of each lobe of the cam between the top dead center position and the half lift position of the cam follower is determined to be the appropriate envelope of the successive positions of the one roller when the other roller moves over the part of the profile
  • devices constructed in accordance with this invention should find particular utility in operating the pumping elements of injection pumps having six or more lobes, that is for engines of six or more cylinders.
  • FIG. 1 is a diagrammatic side view, partially cut away, of part of a pump having a control device constructed according to the invention
  • FIG. 2 is a section taken along the line lI-II of FIG. 1, illustrating particularly the assembly of the rocker cam pivot pins;
  • FIG. 3 is a section taken along the line III-III of FIG.
  • FIG. 5 is a diagram illustrating the position of the rollers and of the rocker arm pivot pins in relation to a cam with five lobes, and to a cam with six lobes;
  • FIG. 6 is a qualitative diagram of the rate of motion of a cam follower with respect to the cam profile according to the invention.
  • FIG. 7 is an enlarged diagrammatic view of part of the cam profile showing the main and reversal rollers of the pumping element in a first position corresponding to the half lift position of the cam follower along the stroke of the pumping element;
  • FIG. 8 is a diagrammatic view of the cam profile with the control and reverse rollers of the pumping element in a second position, again corresponding to the half lift position of the cam follower along the stroke of the pumping element;
  • FIG. 9 is an enlarged diagrammatic view of the cam profile showing the position corresponding to the bottom dead center position of the cam follower.
  • FIG. 1 there is shown the lower part 1 of a single pumping element of an injection pump controlled by a cam 2 with six equal lobes, each lobe having respective flanks 3 and 3a on either side of a lobe peak B, the profiles 3 and 3a being symmetrical about a radial line AB from the axis A of rotation of the cam to the peak B.
  • the cam 2 is borne on a sleeve 4 which is driven by a shaft 5 via a claw clutch 6, which may, for example, be helicoidal, to allow for adjustment of the angular position of the cam 2 in relation to the control shaft 5.
  • a claw clutch 6 which may, for example, be helicoidal, to allow for adjustment of the angular position of the cam 2 in relation to the control shaft 5.
  • connection between the roller 7 and the pumping element 1, as can also be seen in FIG. 3, is achieved by means of connecting rods 16 and which are joined, at one end, to the axle 9 of the roller 7 and at the other end to a pin 17 which joins them to a cursor 18, which in its turn, is connected to a mushroom head 19 of the pumping element 1.
  • the mushroom head 19 is located in a groove 200 of the cursor 18 so as to allow for possible rotation of the pumping element 1 in relation to the cursor l8, and so as to maintain a rigid axial coupling with the cursor 18.
  • the rocker arm 11 comprises two generally plate-like elements 20 and 20a, spaced from each other by a distance which is equal at least to the length of the rollers 7 and 8; these elements 20 and 20a, are shaped in the form of an isosceles triangle with rounded vertices, and are rigidly connected by a bridge 21 which leaves sufficient space free between the elements 20 and 20a for the rollers 7 and 8 to be housed.
  • the rollers 7 and 8 are mounted on axles 9 and 10 which are inserted into the holes 22-22:: and 23-2311 (the latter not visible in FIG. 4).
  • each plate 20 and 20a there is a stub shaft or pin 24 and 24a, aligned with each other and with the axis G about which the rocker arm 11 is pivoted.
  • the rocker arm 11 can carry two rollers 7 and 8 of a diameter which is large enough to bear the high pressures on the profile of the cam, and at the same time allows the use of pivot pins 24 and 24a which, while not interfering with the rollers 7 and 8, can nevertheless be of dimensions sufficient to increase to a satisfactory degree their resistance to the fatigue strains of the rocker arm during operation under heavy loads (more than 700 kgs), which loads are transmitted from the pumping element chamber on to the main or control roller 7.
  • the rocker arm 11, as can be seen from both FIG. 2 and FIG. 4, is supported for pivoting motion about the axis G, by a support member 12 which comprises a substantially U shaped element with a base 25, and limbs 26 and 26a.
  • a support member 12 which comprises a substantially U shaped element with a base 25, and limbs 26 and 26a.
  • the diameter of the apertures 27 and 27a is greater than the diameter of the stub shafts or pins 24 and 24a, and the port of the openings 28 and 28a is only very slightly greater than the diameter of the said stub shafts or pins.
  • rocker arm This allows the rocker arm to be assembled by inserting the pin stubs 24 and 24a radially through openings 28 and 28a, and subsequently sliding the bushes 29 and 29a over the stub shafts or pins 24 and 24a and into the apertures 27 and 27a to hold the stub shafts and hence the rocker arm 11 in position.
  • These bushes 29 and 29a whose outer diameter matches the inner diameter of the apertures 27 and 27a, prevent the rocker arm from slipping out of its supports.
  • the center portion, or base is provided with a collar having a central bore 31 through which passes the sliding block 18 connected to the pumping element 1.
  • the base 25 is moreover provided with a projecting tongue 32, to assist in locating and securing the support member 12 in the upper part of the casing of the pump 14. This can be effected because the base 25 and the tongue 32 are provided with holes 33 and 34 respectively for receiving screws 35 and 36 (see FIG. 1) by means of which the support 12 with the rocker arm 11 mounted on to it, can be attached to the casing 13 of the pump 14.
  • the structure also allows simple assembly and disassembly of the rocker arm and of the rollers so-that it is possible to replace the latter by others of greater or smaller diameter to compensate for possible differences due to working and/or to wear, without having to touch the cam 2.
  • This has the advantage of not changing the phasing of the cam 2 during maintenance operations on the pump when it is assembled on an engine.
  • the base diameter of the cam 2 is indicated Db and its outer diameter is indicated De.
  • the lift of the cam, that is the stroke which the pumping element 1 has to make is indicated h.
  • the angle a subtended at the center of the cam by each lobe, is only 60". Since, when a roller is in a position corresponding to the bottom dead center of the cam profile, the other roller will have to be in a position corresponding to the upper dead center, the angle 3, subtended at the center A of the cam between the axes D and E of the roller will be equal to a/2.
  • the distance ED between the centers of the two rollers will be given by:
  • the profile of the lobes by initially defining the first portion of the flank which, together with the roller 7, generates the first half stroke h/2 and subsequently to form the second part of the profile of the lobes up to the top dead center (p.m.s.) by envelopement, that is by defining the second part of the profile to be the appropriate envelope of the successive positions of one roller when the other roller moves over the first part of the profile.
  • the profiles 3 and 3a of the cam 2 are symmetrical in relation to the radial line AB (see FIG. l) the cam having to serve both for right hand and for the left hand rotation, once the first section of profile up to the point m of FIG.
  • the remaining portion of the profile up to the top dead center can be made by envelopement of the successive positions of the roller 7 with respect to the corresponding positions of the roller 6 during the movement of the roller 7 over the first section of the profile.
  • the profile P of the upper part of the flanks of the lobes is thus suitable to sustain the heavy loads due to the pumping element 1.
  • the technical solution of the present invention also takes into account the kinematic determining condition according to which it is only after the half stroke h/2 of the pumping element 1 has been passed that deceleration and hence a reduction in the linear velocity of the pumping element commences.
  • the dynamic conditions due to the inversion of the direction of acceleration and hence of the forces of inertia, impose the necessity that in proximity to the position m of the rollers on the flanks of the lobes which corresponds to the half stroke position of the pumping element there shall be the least possible play between the rollers 7, 8 and the flanks of the cam lobes over which they move.
  • the characteristics of this part of the profile are arranged, so that the second part P of the profile of the lobe, made by envelopement from the first part P is of convex curvature, of variable radius, and has from the half stroke to about three-fourths of the whole stroke a curve of radii about half of the diameter of the roller 7 and around five-sixths of the stroke, has a curve of radii about onethird of the diameter of the roller. At approximately nine-tenths of the total stroke the curve may be reduced to radii equal to or slightly less than one-fourth of the diameter of the rollers. At the peaks of the lobes the curve does not go down to radii less than one-fifth of the diameter of the rollers.
  • the stroke h of the pumping element can be used up to percent without altering the rate of injection and without other disadvantages.
  • the initial profile P. of the lobes has a concave curve with a radius Rm between 35 and 45 mm depending on the diameter chosen for the main roller and on the desired initial velocity of the pump element. More particularly the initial profile P from the bottom dead center up to the half stroke position h/2, comprises a first substantially rectilinear section r coinciding with the said curve c of radius Rm terminating at the point corresponding to approximately A h, and a third section r also rectilinear and tangential to the intermediate section curve c and extending to the point m corresponding to the half stroke position h/2.
  • the remainder of the profile, that is the final profile P of the lobe, from the half stroke position h/ 2, up to the top dead center at the peak of the lobe is formed by envelopement of the initial profile P,, as has been discussed above.
  • the gradient of third section r2, between the positions corresponding to Ah and Ah, may have a slope of between 0.5 and 0.30 mm per degree of rotation of the cam.
  • it can be defined in such a way that, with the pumping element 1 having its diameter (I no greater than twice the stroke h, a theoretical gradient of fuel delivery of the pumping element of between 30 and 45 mm per degree of rotation of the cam is obtained.
  • a control device for a fuel injection pump of a multi-cylinder internal combustion engine said control device having a casing, a cam rotatably mounted in the casing,
  • said cam having a surface including a plurality of lobes, each said lobe being symmetric about a radial line passing through the top dead center of said lobe,
  • cam follower means comprising a rocker arm having at each end thereof a roller, said rollers both being in contact with the surface of said cam,
  • a support member attached to the casing support means on said rocker arm cooperating with said support member to support said rocker arm for pivotal movement about an axis intermediate said rollers, said support means being outside the region between said rollers and a connecting rod having one end operatively connected to one of said rollers and the other end connected to a cursor slidable in said support members, said cam surface being shaped such that the part of the profile of each lobe of said cam between the top dead center position and the half lift position of said cam follower is determined to be the appropriate envelope of the successive positions of said roller when the other said roller moves over the part of the profile of said cam between the bottom dead center position and said half lift position of said cam follower.
  • said rocker arm comprises two plate-like elements, each said plate-like element having substantially the form of an isosceles triangle with rounded vertices and with a base longer than the sides, a bridge element rigidly connecting said plate-like elements side by side at the vortex opposite said base, said support means including a stub shaft projecting outwardly from each of said plate-like elements, means forming axially aligned apertures in each pair of the other rounded vertices of the plate-like elements an axle means for said rollers disposed in said apertures.
  • said support member for said rocker arm comprises a substantially U- shaped element having in each limb thereof a circular aperture of diameter larger than the diameter of each said stub shaft,
  • each said aperture communicating laterally with a respective said slot so as to provide a passage of width at least equal to the diameter of each said stub shaft'to allow the radial introduction thereof into said aperture
  • each said aperture having an external diameter equal to the diameter of the respective aperture, said bush arranged for insertion into said aperture over said stub shaft, said bush serving to lock each said stub shaft in position in said aperture.
  • said first portion of said profile of each said lobe comprises a first rectilinear section, said concave curved section with radius between 35 and 45 mm, and a second rectilinear section formed by said rectilinear section extending to said half lift position of said cam follower means, both of said rectilinear sections being tangential to said curved section.
  • said first rectilinear section subtends an angle between 2 and 5 at the center of said cam
  • said curved section subtends an angle of between 7 and 9 at said center of said cam
  • said second rectilinear section subtends an angle between 2 and 5 at said center of said cam.
  • said second rectilinear section of said first part of said cam lobe extending at least between said point corresponding substantially to the quarter lift position of said cam follower means and said point corresponding to said half lift position of said cam follower means, has a gradient arranged so that when said device is used with a pump having a diameter no greater than twice the stroke, will provide a-- theoretical gradient of delivery from said pump of between 30 mm and 45 mm per degree of rotation of said cam.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US00147118A 1970-09-15 1971-05-26 Control devices Expired - Lifetime US3738180A (en)

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IT7009670 1970-09-15

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US (1) US3738180A (enrdf_load_stackoverflow)
JP (1) JPS5115162B1 (enrdf_load_stackoverflow)
DE (1) DE2146144A1 (enrdf_load_stackoverflow)
FR (1) FR2105817A5 (enrdf_load_stackoverflow)
GB (1) GB1301772A (enrdf_load_stackoverflow)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4481839A (en) * 1981-04-23 1984-11-13 Sasib S.P.A. Modular rocking lever for cam mechanisms
US4535641A (en) * 1981-06-13 1985-08-20 Lucas Industries Plc Reciprocating plunger fuel injection pump
US4803889A (en) * 1986-07-11 1989-02-14 Lucas Industries Public Limited Company Fuel injection pump
US20100037865A1 (en) * 2006-09-28 2010-02-18 Walter Fuchs Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly
US20100074781A1 (en) * 2005-01-26 2010-03-25 Seiko Epson Corporation Fluid transporting device, and fluid transporter
CN101865266A (zh) * 2010-05-26 2010-10-20 广州中国科学院工业技术研究院 一种往复运动机构及将旋转运动转换为往复运动的方法
CN108374740A (zh) * 2018-01-29 2018-08-07 中国第汽车股份有限公司 一种用于驱动供油泵柱塞的凸轮及供油泵柱塞驱动装置
US11131282B2 (en) * 2019-03-01 2021-09-28 Denso Corporation Fuel injection pump
GB2598598A (en) * 2020-09-03 2022-03-09 Delphi Tech Ip Ltd Fuel pump
US20240167462A1 (en) * 2022-11-21 2024-05-23 The Regents Of The University Of Michigan Desmodromic mechanism and fluid pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6192975U (enrdf_load_stackoverflow) * 1984-11-26 1986-06-16
JPS6287774U (enrdf_load_stackoverflow) * 1985-11-22 1987-06-04

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1198283A (en) * 1914-09-16 1916-09-12 William C Alexander Motion-converting device.
US1630273A (en) * 1926-06-17 1927-05-31 Duplex Motor Company Duplex-cam motor
US1777179A (en) * 1929-04-29 1930-09-30 Perlman David Four-cylinder, four-cycle cam and lever radial motor
US3262715A (en) * 1964-08-21 1966-07-26 Paul D Abbott Vehicle having selectively fixed or floating steerable wheels
US3263512A (en) * 1963-02-12 1966-08-02 Handley John Cam follower mechanism

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1198283A (en) * 1914-09-16 1916-09-12 William C Alexander Motion-converting device.
US1630273A (en) * 1926-06-17 1927-05-31 Duplex Motor Company Duplex-cam motor
US1777179A (en) * 1929-04-29 1930-09-30 Perlman David Four-cylinder, four-cycle cam and lever radial motor
US3263512A (en) * 1963-02-12 1966-08-02 Handley John Cam follower mechanism
US3262715A (en) * 1964-08-21 1966-07-26 Paul D Abbott Vehicle having selectively fixed or floating steerable wheels

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4481839A (en) * 1981-04-23 1984-11-13 Sasib S.P.A. Modular rocking lever for cam mechanisms
US4535641A (en) * 1981-06-13 1985-08-20 Lucas Industries Plc Reciprocating plunger fuel injection pump
US4803889A (en) * 1986-07-11 1989-02-14 Lucas Industries Public Limited Company Fuel injection pump
US8888473B2 (en) 2005-01-26 2014-11-18 Seiko Epson Corporation Fluid transporting device of the peristaltic type with a push pin and push plate arrangement
US20100074781A1 (en) * 2005-01-26 2010-03-25 Seiko Epson Corporation Fluid transporting device, and fluid transporter
US8157546B2 (en) * 2005-01-26 2012-04-17 Seiko Epson Corporation Fluid transporting device of the peristaltic type with a push pin and push plate arrangement
US8834138B2 (en) 2005-01-26 2014-09-16 Seiko Epson Corporation Fluid transporting device of the peristaltic type with a push pin and push plate arrangement
US8858201B2 (en) 2005-01-26 2014-10-14 Seiko Epson Corporation Fluid transporting device of the peristaltic type with a push pin and push plate arrangement
US9309880B2 (en) 2005-01-26 2016-04-12 Seiko Epson Corporation Fluid transporting device of the peristaltic type with a push pin and push plate arrangement
US20100037865A1 (en) * 2006-09-28 2010-02-18 Walter Fuchs Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly
CN101865266A (zh) * 2010-05-26 2010-10-20 广州中国科学院工业技术研究院 一种往复运动机构及将旋转运动转换为往复运动的方法
CN108374740A (zh) * 2018-01-29 2018-08-07 中国第汽车股份有限公司 一种用于驱动供油泵柱塞的凸轮及供油泵柱塞驱动装置
US11131282B2 (en) * 2019-03-01 2021-09-28 Denso Corporation Fuel injection pump
GB2598598A (en) * 2020-09-03 2022-03-09 Delphi Tech Ip Ltd Fuel pump
US20240167462A1 (en) * 2022-11-21 2024-05-23 The Regents Of The University Of Michigan Desmodromic mechanism and fluid pump

Also Published As

Publication number Publication date
JPS5115162B1 (enrdf_load_stackoverflow) 1976-05-14
DE2146144A1 (de) 1972-03-23
GB1301772A (enrdf_load_stackoverflow) 1973-01-04
FR2105817A5 (enrdf_load_stackoverflow) 1972-04-28

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