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US3220217A - Driving mechanism for producing turning movements substantially without side forces - Google Patents

Driving mechanism for producing turning movements substantially without side forces Download PDF

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Publication number
US3220217A
US3220217A US245551A US24555162A US3220217A US 3220217 A US3220217 A US 3220217A US 245551 A US245551 A US 245551A US 24555162 A US24555162 A US 24555162A US 3220217 A US3220217 A US 3220217A
Authority
US
United States
Prior art keywords
claws
sleeve
driving mechanism
forces
driving
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
US245551A
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English (en)
Inventor
Kravits Arthur
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.)
MIRKOZ MUSZAKI IRODAI ES KOZSZ
MIRKOZ MUSZAKI IRODAI ES KOZSZUKSEGLETI CIKKEKET GYARTO ES JAVITO K SZ
Original Assignee
MIRKOZ MUSZAKI IRODAI ES KOZSZ
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 MIRKOZ MUSZAKI IRODAI ES KOZSZ filed Critical MIRKOZ MUSZAKI IRODAI ES KOZSZ
Application granted granted Critical
Publication of US3220217A publication Critical patent/US3220217A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M41/121—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 with piston arranged axially to driving shaft
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/13—Special devices for making an explosive mixture; Fuel pumps
    • F02M2700/1317—Fuel pumpo for internal combustion engines
    • F02M2700/1358—Fuel pump with control of fuel inlet to the pumping 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
    • 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
    • Y10T74/18024—Rotary to reciprocating and rotary

Definitions

  • this disadvantage is overcome in that the relative positions of the loaded parts are determined, not by unbalanced individual forces, but by means of devices which may be called automatic force compensators which function in the manner of a balance in the direction in which friction is caused and automatically generate self-compensating forces.
  • the moving parts are not pressed transversely to their guide means. This applies to both mechanically static and mechanically dynamic forces and also to the static forces produced by the liquid pressure and, finally, to those forces produced by the dynamic effect of the flow of liquid (gas oil).
  • FIG. 1 is an axial longitudinal section of an embodiment of the distributor pump of the invention having automatic force compensators.
  • the compensating sleeve used for the drive is in the form of an oil pump and the piston thereof is hydrostatically and hydrodynamically compensated.
  • FIGS. 2, 2a, 3, 3a, 4, 4a, 4b, 4c, 4d, 4d, 5 and 5a illustrate diagrammatically automatic force compensating devices and other details.
  • the pump casing is denoted by 1 and the pump cylinder by 2.
  • 3 denotes a pump piston which is driven by a driving sleeve 4 and a pin 39 so that it reciprocates and rotates simultaneously.
  • This piston is constructed in such a manner that it is compensated both hydrostatically and hydrodynamically.
  • 4 denotes the driving and compensating sleeve of the invention for relieving lateral load, that is, for compensating the movement of the piston.
  • This sleeve also serves to convey the gas oil in such a way that it acts as a lubricant.
  • the balls 5 are compensating members of an automatic torque compensator, which may be called a centripetally operating compensator.
  • a centripetally operating compensator As soon as the torque of the claws 6 of the pinion 6 (FIG. 1) is transmitted by the balls 5 to the claws 4' of the compensating sleeve 4, the forces acting on the individual claws 4 must form a compensated couple of forces which cannot have any lateral components if the angle a of the bearing surfaces is greater than the angle of friction.
  • the bearing surfaces of the claws adjacent the balls can also be curved to reduce specific surface pressure.
  • the halls do not prevent the reciprocating movement of the sleeve 4 in the axial direction, as the balls can roll freely in this direction.
  • the function of the device is as follows:
  • FIG. 1 shows the distributor in the sucking stroke, in which the gas oil (or other motor fuel) is admitted under pressure at the screw thread 26 of the head 25 and it flows through the bore 28 of a regulating valve situated in the cylinder 27 and there after it streams in the direction of the geometrical axis of the device, that is to say through the central bore, from which it arrives into the radial bores 30.
  • These bores are connected to the bores of a packing 25 and to the channels 31 from which the oil flows into radial bores and then into the radial sucking channels 32 of the piston 3. Now the oil comes into a central channel shown in dotted lines in the drawing and forming part of the working space of the pump.
  • the said cams engage the roller 9 pivoted on a holder 7 (FIGS. 5, 5a, etc.), so that the said cams of the sleeve 4, in consequence of the rotation of this sleeve, cause an axial movement of the sleeve, because holder 7, by means of its pivots 8, bears on a fixed part of the pump, but may be swung on this part.
  • the shape of these cams may vary, as is well known, in accordance with the movement it is desired to impart to sleeve 4.
  • the said axial movement of the sleeve 4 corresponds to shape of the cam and produces the compression stroke.
  • the sleeve 4 and the piston 3 are turned by 45.
  • the gas oil or in general the motor fuel
  • the oil comes into the compression channels 31' and from this it is pressed through packings (not shown, but like the packing 25) into outlet openings 29, from which it is let to the individual cylinders of the engine.
  • the balls do not have a centripetal mutual influence but a centrifugal one and the forces are transmitted by means of screws 50a and the ring 51.
  • the balls move radially, due to inaccuracies in machining, whereby the gaps between the claws 48, 49 also alter slightly whereupon the pressure exerted on the claws is practically completely compensated by transmission of pressure between balls 47 through ring 51.
  • ring 51 floats relative to claws 4S and 49.
  • the screws 50a can be adjusted by means of the nuts 50 so that the angular position of the claws 48 in relation to the claws 49 can be adjusted, which changes the instant of injection.
  • the above-described devices serve to compensate the torque, but the force of thrust is also compensated, as shown in FIGS. 1, 4 and 4a.
  • the automatic thrust compensator 7 co-operates by means of pins 8 and rollers 9 with the cams on the disc-like extension 12 on the driving sleeve 4 to actuate the piston 3 in its pressure thrust without any lateral load.
  • the compensator 7 is supported by pins 8 (FIG. 4) which are pivoted on the bearings 42, 42'.
  • the rollers 9 are secured by a ring 11 and a pin 10.
  • FIGS. 4d and 4d an embodiment of the compensator 7 is shown in which, instead of radial cams 12 and rollers 9, pins and limiting sleeve 11, conical rollers 9 are used which are supported on balls and which cooperate with conical cams on the sleeve 4.
  • FIGS. 4b and 40 show an embodiment of the thrust compensator 7 in which pairs of conical earns 12' and 12" and pairs of rollers 9'a and 9"a as also pairs of conical rollers 9' and 9" are used.
  • the compensator 7 has a two-armed lever 7' which can swing about the pin 8 and which does not transmit any lateral forces, since it co-operates with the compensator 7 in the manner of a balance.
  • four cams operate simultaneously.
  • FIGS. 5 and 5a the piston 3 is moved by the sleeve 4 in its suction stroke without the, occurrence of lateral forces, due to the compensating devices shown in these figures. Since the compensator 15 can be turned about the pin 17 and also, since the pins 17 and sleeves 17 can move freely in the axial direction in the recess in the guide piece 42, the two thrusts cancel out in a similar manner to that effected by the compensator 7. Actuation is effected by means of the compression spring 18 which is supported by a ring 19 which turns in the manner of a balance about a fulcrum 20 in a recess of the counter bearing 20.
  • the above-described devices are suitable for compensating the dynamic forces which occur when the pump is in use.
  • the above-described automatic compensators obviate all lateral forces and thus prevent any wear of the parts under a friction load.
  • the advantages of a practically frictionless mode of operation are enhanced by the relief of the pressure side in a closed space by using a specifically designed cam.
  • a cam would include a pressure portion, a relief portion and an effective suction portion.
  • the channels leading from the working chamber to the pressure side open and remain open during the relief portion.
  • the communicating channels from the suction side to the working chamber are opened after a certain angle has been traversed. This avoids the occurrence of currents having too high speeds and large pressure differentials so that the control edges are not worn down by liquid currents and the pumping rate is accurately maintained for a long time.
  • a driving mechanism for producing turning movement substantially without side forces comprising a driving member having two claws, a driven member coaxially mounted with said driving member and having two claws opposite the first-mentioned claws, said driving claws having surfaces confronting surfaces on said driven claws, and rolling means disposed one between each pair of the claws engaging said confronting surfaces to transmit driving torque between said members, said rolling means directly engaging each other to transmit force between said rolling means, the angle between said confronting surfaces engaging the rolling means being larger than the angle of friction.
  • a driving mechanism for producing turning movement substantially without side forces comprising a driving member having two claws, a driven member coaxially mounted with the said driving member and having two claws opposite the first-mentioned claws, said driving claws having surfaces confronting surfaces of said driven claws, rolling means disposed one between each pair of the claws engaging said confronting surfaces to transmit the driving torque between said members, and balancing means in contact with both of said rolling means and movable relative to said claws to transmit force between said rolling means, the angle between said confronting surfaces engaging said rolling means being larger than the angle of friction.

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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)
  • Transmission Devices (AREA)
US245551A 1961-12-20 1962-12-18 Driving mechanism for producing turning movements substantially without side forces Expired - Lifetime US3220217A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT964161A AT239003B (de) 1961-12-20 1961-12-20 Verteilereinspritzpumpe

Publications (1)

Publication Number Publication Date
US3220217A true US3220217A (en) 1965-11-30

Family

ID=3615996

Family Applications (1)

Application Number Title Priority Date Filing Date
US245551A Expired - Lifetime US3220217A (en) 1961-12-20 1962-12-18 Driving mechanism for producing turning movements substantially without side forces

Country Status (4)

Country Link
US (1) US3220217A (de)
AT (1) AT239003B (de)
CH (1) CH429301A (de)
GB (1) GB1032128A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4344305A (en) * 1979-03-22 1982-08-17 British Aerospace Torque shaft coupling
EP0192978A1 (de) * 1985-02-28 1986-09-03 Robert Bosch Gmbh Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1677311A (en) * 1927-02-18 1928-07-17 Carl W Weiss Universal joint
US1865950A (en) * 1930-05-28 1932-07-05 Fay J A & Egan Co Coupling for sander drum shafts
US1939455A (en) * 1930-11-21 1933-12-12 Gen Electric Electric power converting apparatus
US2007897A (en) * 1934-05-03 1935-07-09 Mccrosky Tool Corp Floating coupling
US2033733A (en) * 1934-05-26 1936-03-10 Myard Francis Emile Homokinetic transmission joint
US2060473A (en) * 1936-11-10 Flexible coupling
US2480039A (en) * 1944-12-11 1949-08-23 Gear Grinding Mach Co Shaft coupling
US2582535A (en) * 1948-04-14 1952-01-15 Preeision Mecanique Soc Fuel injection pump
US2593788A (en) * 1945-05-04 1952-04-22 Fuel Charger Corp Fuel pump
DE864021C (de) * 1944-08-17 1953-01-22 Anton Dipl-Ing Leitner Selbstspannendes Reibungsgetriebe
DE877082C (de) * 1950-07-06 1953-05-21 Otto Dr-Ing Lutz Wälzgetriebe
US2679804A (en) * 1953-02-11 1954-06-01 American Bosch Corp Fuel injection pump
GB741628A (en) * 1952-07-08 1955-12-07 Wassilieff Victor Irreversible self-locking device
US2804778A (en) * 1952-08-26 1957-09-03 Wallace & Tiernan Company Inc Variable driving mechanism
US2810376A (en) * 1954-07-29 1957-10-22 Bosch Gmbh Robert Injection pump
GB789014A (en) * 1955-04-05 1958-01-15 Edward Harry Gibson An improved joint for transmitting rotary movement
US2878692A (en) * 1954-01-19 1959-03-24 Fiat Spa Variable transmission
FR1186247A (fr) * 1957-07-17 1959-08-18 Prec Mecanique Perfectionnements apportés aux pompes à piston à débit variable du genre de celles pour l'injection de combustible dans les moteurs
FR1209066A (fr) * 1956-12-19 1960-02-29 Bosch Gmbh Robert Pompe d'injection de combustible pour moteur
US2928352A (en) * 1957-04-17 1960-03-15 Bosch Gmbh Robert Injection pump

Patent Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2060473A (en) * 1936-11-10 Flexible coupling
US1677311A (en) * 1927-02-18 1928-07-17 Carl W Weiss Universal joint
US1865950A (en) * 1930-05-28 1932-07-05 Fay J A & Egan Co Coupling for sander drum shafts
US1939455A (en) * 1930-11-21 1933-12-12 Gen Electric Electric power converting apparatus
US2007897A (en) * 1934-05-03 1935-07-09 Mccrosky Tool Corp Floating coupling
US2033733A (en) * 1934-05-26 1936-03-10 Myard Francis Emile Homokinetic transmission joint
DE864021C (de) * 1944-08-17 1953-01-22 Anton Dipl-Ing Leitner Selbstspannendes Reibungsgetriebe
US2480039A (en) * 1944-12-11 1949-08-23 Gear Grinding Mach Co Shaft coupling
US2593788A (en) * 1945-05-04 1952-04-22 Fuel Charger Corp Fuel pump
US2582535A (en) * 1948-04-14 1952-01-15 Preeision Mecanique Soc Fuel injection pump
DE877082C (de) * 1950-07-06 1953-05-21 Otto Dr-Ing Lutz Wälzgetriebe
GB741628A (en) * 1952-07-08 1955-12-07 Wassilieff Victor Irreversible self-locking device
US2804778A (en) * 1952-08-26 1957-09-03 Wallace & Tiernan Company Inc Variable driving mechanism
US2679804A (en) * 1953-02-11 1954-06-01 American Bosch Corp Fuel injection pump
US2878692A (en) * 1954-01-19 1959-03-24 Fiat Spa Variable transmission
US2810376A (en) * 1954-07-29 1957-10-22 Bosch Gmbh Robert Injection pump
GB789014A (en) * 1955-04-05 1958-01-15 Edward Harry Gibson An improved joint for transmitting rotary movement
FR1209066A (fr) * 1956-12-19 1960-02-29 Bosch Gmbh Robert Pompe d'injection de combustible pour moteur
US2928352A (en) * 1957-04-17 1960-03-15 Bosch Gmbh Robert Injection pump
FR1186247A (fr) * 1957-07-17 1959-08-18 Prec Mecanique Perfectionnements apportés aux pompes à piston à débit variable du genre de celles pour l'injection de combustible dans les moteurs

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4344305A (en) * 1979-03-22 1982-08-17 British Aerospace Torque shaft coupling
EP0192978A1 (de) * 1985-02-28 1986-09-03 Robert Bosch Gmbh Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Also Published As

Publication number Publication date
GB1032128A (en) 1966-06-08
CH429301A (de) 1967-01-31
AT239003B (de) 1965-03-10

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