GB2162285A - Fuel injection pump - Google Patents

Fuel injection pump Download PDF

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Publication number
GB2162285A
GB2162285A GB8515895A GB8515895A GB2162285A GB 2162285 A GB2162285 A GB 2162285A GB 8515895 A GB8515895 A GB 8515895A GB 8515895 A GB8515895 A GB 8515895A GB 2162285 A GB2162285 A GB 2162285A
Authority
GB
United Kingdom
Prior art keywords
drive shaft
cross
pump
fuel injection
injection 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.)
Granted
Application number
GB8515895A
Other versions
GB2162285B (en
GB8515895D0 (en
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 GB8515895D0 publication Critical patent/GB8515895D0/en
Publication of GB2162285A publication Critical patent/GB2162285A/en
Application granted granted Critical
Publication of GB2162285B publication Critical patent/GB2162285B/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

In a fuel injection pump, in which a pump and distributor plunger (15) rotating and moving to- and-fro is driven by a rotating drive shaft (11) via a cross-slide coupling (12), to prevent a rattling noise and the cross slide (25) of the cross-slide coupling from striking during the stroke drive of the pump and distributor plunger, a damping member is assigned to the cross slide. The damping member is preferably a compression spring which is arranged between the drive shaft and the cross-slide. <IMAGE>

Description

SPECIFICATION Fuel injection pump The innovation relates to a fuel injection pump for internal-combustion engines according to the pre-characterising clause of Claim 1. In a pump of this type known, for example, from German Auslegeschrift 2,1 58,689, the crosspiece of the cross-slide coupling, which transmits the drive torque from the claws of the drive shaft to the claws of the pump and distributor member, is arranged so as to be freely movable in the axial direction between the pairs of claws. The injection pump constructed in this way operates reliably and with very little noise. However, when it is subjected to high stress, for example as result of increased injection pressures in the case of direct injection, a clearly audible rattling noise occurs in the upper speed range.But a more serious disadvantage is that, when the rattling noise occurs, the functioning of the injectionrate adjusting device is also influenced adversely.
After it had been ascertained that the rattling noise occurs because the crosspiece repeatedly strikes against the end face of the drive shaft located on the output side, when the claws of the pump and distributor member, during its to-and-fro movement, drags along with it the cross-piece which, as a result of its inertia, continues to move relative to the claws of the pump and distributor member in the end region of the return stroke and which then strikes against the drive shaft, this particular problem was solved in a simple way by arranging, according to the invention, the damping member as indicated in the characterising clause of Claim 1.
Advantageous further developments of the innovation are described in the sub-claims.
The design of the fuel injection pump according to Claims 2 and 3 makes it possible to use the known crosspiece in unchanged form. In the design according to Claim 4, in which the crosspiece is pressed against the drive shaft, the axial position of the crosspiece remains unchanged. A resistant damping member which is particularly simple to produce is proposed in Claim 5.
An exemplary embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Fig. 1 shows a side view, partly in section, of a fuel distributor injection pump for an internal-combustion engine in simplified form, and Figure 2 shows a cross-slide coupling of the injection pump according to Fig. 1 as an enlarged detail A from Fig. 1.
A drive shaft 11 is mounted rotatably in a housing 10 of the fuel injection pump. This drive shaft 11 is coupled via a cross-slike coupling 1 2 to an eccentric disc 1 3 which is connected to a pump plunger 1 5 sliding in a cylinder bush 14. The eccentric disc 1 3 has a running surface 1 6 with a number of end cams 1 7 corresponding to the number of cylinders of the internal-combustion engine.
The running surface 1 6 of the eccentric disc 1 3 rests against rollers 1 8 which are retained in a fixed roller ring 1 9. The eccentric disc 1 3 forming a unit together with the pump plunger 1 5 is pressed against the rollers 1 8 via a yoke 21 by helical compression springs 20.
To control the fuel injection quantities, a control slide 22, on which known adjusting means 23 engage, surrounds the pump plunger 1 5 and slides on it.
The cross-slide coupling 12, which serves for transmitting the rotary drive from the drive shaft 11 to the pump plunger 1 5 which rotates and swings to-and-fro, has a cross disc 25 with four grooves 26 of specific width distributed uniformly over the periphery.
Claws 28 engage in two grooves 26 located opposite one another, project axis-parallel from a collar 27 of the drive shaft 11 and rest positively against the flanks of the groove 26.
In the same way, two claws 29 projecting axis-parallel from the eccentric disc 1 3 engage from the other side into the other two grooves 26 offset by 90 . In the end of the drive shaft 11 with the collar 27 there is an axial recess 30, in which a helical compression spring 31 is located. This is retained at one end by means of a turn on the bottom of the recess 30 in a swidened portion 32 and at its other end projects a specific length beyond the plane of the bottom 33 of the claws 28 of the drive shaft 11. The cdross disc 25 rests against this end when the eccentric disc 1 3 is pushed into the left-hand dead-centre position by the compression springs 20.
The compression spring 31 functioning as a damping member has a braking effect when struck by the cross disc 25, when the latter is dragged to-and-fro axially during the to-andfro movement of the eccentric disc 1 3 and the pump plunger 1 5 and, as a result of its inertia, runs up against the end of the drive shfaft 11 with the claws 28 at the end of a cycle of movement, thus preventing an impact. It may be noted, in addition, that, instead of a helical compression spring 31 made of steel, it is also possible to use other types of damping members which are flexible and which can consist of rubber or plastic.
As an alternative to the exemplary embodiment illustrated and described, in which the damping member is arranged between the drive shaft 11 and the cross disc 25, the flexible damping member can also be arranged between the eccentric disc 1 3 and the cross disc. For this purpose, the cross disc must be provided with an axial blind bore which receives the damping member.
1. Fuel injection pump with a drive shaft,
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (6)

**WARNING** start of CLMS field may overlap end of DESC **. SPECIFICATION Fuel injection pump The innovation relates to a fuel injection pump for internal-combustion engines according to the pre-characterising clause of Claim 1. In a pump of this type known, for example, from German Auslegeschrift 2,1 58,689, the crosspiece of the cross-slide coupling, which transmits the drive torque from the claws of the drive shaft to the claws of the pump and distributor member, is arranged so as to be freely movable in the axial direction between the pairs of claws. The injection pump constructed in this way operates reliably and with very little noise. However, when it is subjected to high stress, for example as result of increased injection pressures in the case of direct injection, a clearly audible rattling noise occurs in the upper speed range.But a more serious disadvantage is that, when the rattling noise occurs, the functioning of the injectionrate adjusting device is also influenced adversely. After it had been ascertained that the rattling noise occurs because the crosspiece repeatedly strikes against the end face of the drive shaft located on the output side, when the claws of the pump and distributor member, during its to-and-fro movement, drags along with it the cross-piece which, as a result of its inertia, continues to move relative to the claws of the pump and distributor member in the end region of the return stroke and which then strikes against the drive shaft, this particular problem was solved in a simple way by arranging, according to the invention, the damping member as indicated in the characterising clause of Claim 1. Advantageous further developments of the innovation are described in the sub-claims. The design of the fuel injection pump according to Claims 2 and 3 makes it possible to use the known crosspiece in unchanged form. In the design according to Claim 4, in which the crosspiece is pressed against the drive shaft, the axial position of the crosspiece remains unchanged. A resistant damping member which is particularly simple to produce is proposed in Claim 5. An exemplary embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Fig. 1 shows a side view, partly in section, of a fuel distributor injection pump for an internal-combustion engine in simplified form, and Figure 2 shows a cross-slide coupling of the injection pump according to Fig. 1 as an enlarged detail A from Fig. 1. A drive shaft 11 is mounted rotatably in a housing 10 of the fuel injection pump. This drive shaft 11 is coupled via a cross-slike coupling 1 2 to an eccentric disc 1 3 which is connected to a pump plunger 1 5 sliding in a cylinder bush 14. The eccentric disc 1 3 has a running surface 1 6 with a number of end cams 1 7 corresponding to the number of cylinders of the internal-combustion engine. The running surface 1 6 of the eccentric disc 1 3 rests against rollers 1 8 which are retained in a fixed roller ring 1 9. The eccentric disc 1 3 forming a unit together with the pump plunger 1 5 is pressed against the rollers 1 8 via a yoke 21 by helical compression springs 20. To control the fuel injection quantities, a control slide 22, on which known adjusting means 23 engage, surrounds the pump plunger 1 5 and slides on it. The cross-slide coupling 12, which serves for transmitting the rotary drive from the drive shaft 11 to the pump plunger 1 5 which rotates and swings to-and-fro, has a cross disc 25 with four grooves 26 of specific width distributed uniformly over the periphery. Claws 28 engage in two grooves 26 located opposite one another, project axis-parallel from a collar 27 of the drive shaft 11 and rest positively against the flanks of the groove 26. In the same way, two claws 29 projecting axis-parallel from the eccentric disc 1 3 engage from the other side into the other two grooves 26 offset by 90 . In the end of the drive shaft 11 with the collar 27 there is an axial recess 30, in which a helical compression spring 31 is located. This is retained at one end by means of a turn on the bottom of the recess 30 in a swidened portion 32 and at its other end projects a specific length beyond the plane of the bottom 33 of the claws 28 of the drive shaft 11. The cdross disc 25 rests against this end when the eccentric disc 1 3 is pushed into the left-hand dead-centre position by the compression springs 20. The compression spring 31 functioning as a damping member has a braking effect when struck by the cross disc 25, when the latter is dragged to-and-fro axially during the to-andfro movement of the eccentric disc 1 3 and the pump plunger 1 5 and, as a result of its inertia, runs up against the end of the drive shfaft 11 with the claws 28 at the end of a cycle of movement, thus preventing an impact. It may be noted, in addition, that, instead of a helical compression spring 31 made of steel, it is also possible to use other types of damping members which are flexible and which can consist of rubber or plastic. As an alternative to the exemplary embodiment illustrated and described, in which the damping member is arranged between the drive shaft 11 and the cross disc 25, the flexible damping member can also be arranged between the eccentric disc 1 3 and the cross disc. For this purpose, the cross disc must be provided with an axial blind bore which receives the damping member. CLAIMS
1. Fuel injection pump with a drive shaft, with a pump and distributor member moving axially to-and-fro and simultaneously rotating, and with a cross-sliding coupling which connects the drive shaft to the pump and distributor member and which has on the output side of the drive shaft and on the drive side of the pump and distributor member claws directed relatively towards one another and between them a cross slide, characterised in that a flexible damping member (31) is arranged axially next to the cross-slide (25).
2. Fuel injection pump according to Claim 1, characterised in that the damping member (31) is arranged between the drive shaft 111) and the cross slide (25).
3. Fuel injection pump according to Claim 2, characterised in that the damping member (31) is retained in an axial recess (30) in the drive shaft (11).
4. Fuel injection pump according to Claim 1, characterised in that the damping member (31) is arranged between the pump and distributor plunger (15) and the cross slide (25).
5. Fuel injection pump according to one of Claims 1 to 4, characterised in that the damping member is a compression spring (31).
6. A fuel injection pump substantially as herein described with reference to the accompanying drawing.
GB08515895A 1984-07-24 1985-06-24 Fuel injection pump Expired GB2162285B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE8422046U DE8422046U1 (en) 1984-07-24 1984-07-24 Fuel injection pump

Publications (3)

Publication Number Publication Date
GB8515895D0 GB8515895D0 (en) 1985-07-24
GB2162285A true GB2162285A (en) 1986-01-29
GB2162285B GB2162285B (en) 1988-02-03

Family

ID=6769142

Family Applications (1)

Application Number Title Priority Date Filing Date
GB08515895A Expired GB2162285B (en) 1984-07-24 1985-06-24 Fuel injection pump

Country Status (3)

Country Link
JP (1) JPH061065B2 (en)
DE (1) DE8422046U1 (en)
GB (1) GB2162285B (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0369155A1 (en) * 1988-11-12 1990-05-23 Robert Bosch Gmbh Fuel injection pump
EP0499787A1 (en) * 1991-02-21 1992-08-26 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
WO2003042529A1 (en) * 2001-11-12 2003-05-22 Robert Bosch Gmbh Distributor injection pump comprising a pretensioned force transmission element

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6393465U (en) * 1986-12-10 1988-06-16
JPH09137468A (en) * 1995-11-13 1997-05-27 Chugoku Electric Power Co Inc:The Pall prevention device of hydraulic shovel

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60116853A (en) * 1983-11-26 1985-06-24 Diesel Kiki Co Ltd Distributor type fuel injection pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0369155A1 (en) * 1988-11-12 1990-05-23 Robert Bosch Gmbh Fuel injection pump
EP0499787A1 (en) * 1991-02-21 1992-08-26 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
WO2003042529A1 (en) * 2001-11-12 2003-05-22 Robert Bosch Gmbh Distributor injection pump comprising a pretensioned force transmission element

Also Published As

Publication number Publication date
JPS6138155A (en) 1986-02-24
GB2162285B (en) 1988-02-03
JPH061065B2 (en) 1994-01-05
DE8422046U1 (en) 1985-11-21
GB8515895D0 (en) 1985-07-24

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Legal Events

Date Code Title Description
PCNP Patent ceased through non-payment of renewal fee

Effective date: 19930624