GB2295463A - Governor mechanism having independent active coil adjustment and pre-stressing - Google Patents

Governor mechanism having independent active coil adjustment and pre-stressing Download PDF

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Publication number
GB2295463A
GB2295463A GB9423582A GB9423582A GB2295463A GB 2295463 A GB2295463 A GB 2295463A GB 9423582 A GB9423582 A GB 9423582A GB 9423582 A GB9423582 A GB 9423582A GB 2295463 A GB2295463 A GB 2295463A
Authority
GB
United Kingdom
Prior art keywords
governor
spring
screw
governor spring
adjustment
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.)
Withdrawn
Application number
GB9423582A
Other versions
GB9423582D0 (en
Inventor
David Stanley Waterman
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.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Priority to GB9423582A priority Critical patent/GB2295463A/en
Publication of GB9423582D0 publication Critical patent/GB9423582D0/en
Publication of GB2295463A publication Critical patent/GB2295463A/en
Withdrawn legal-status Critical Current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
    • F02M41/14—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 rotary distributor supporting pump pistons
    • F02M41/1405—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • F02M41/1427—Arrangements for metering fuel admitted to pumping chambers, e.g. by shuttles or by throttle-valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/04—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors
    • F02D1/045—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors characterised by arrangement of springs or weights

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Abstract

A governor mechanism for a rotary fuel pump in an engine comprises an adjustment mechanism 20 which adjusts the number of active coils and prestresses, independently, a governor spring 18. Mechanism 20 adjusts the number of active coils via screw 28 which is in threaded engagement with outer screw 22 and has on one end helical grooves 38 having a pitch equal to that of spring 18. When locking screw 30 is released the screw 28 is rotated, relative to outer screw 22, resulting in a change in the number of active coils. Releasing lock nut 24 allows the outer screw 22 to rotate relative to housing 12, thereby adjusting the pre-stressing of spring 18 independently. Sealing rings 26, 32 (or 52, fig 2) are provided to restrict leakage. Spring 18 acts on one end of lever 10 the other end of which acts against a centrifugal weight mechanism 14. The lever 10 is further connected to fuel control member 16. Spring rotation, when adjusting, is restricted by leg 40 bearing against the housing 12. <IMAGE>

Description

GOVERNOR MECHANISM This invention relates to a governor mechanism for a fuel injection pumping apparatus for supplying fuel to an internal combustion engine.
One common type of governor mechanism comprises a pivotal lever which is coupled to a fuel control member arranged to control the quantity of fuel delivered to a pumping apparatus. The lever pivots under the influence of a centrifugal weight mechanism which is arranged to act against a governor spring. In use, at relatively low engine speed, the lever is moved under the influence of the governor spring to a position in which the fuel control member permits delivery of a relatively large quantity of fuel. At higher engine speeds, the centrifugal weight mechanism acts against the governor spring to move the lever to a position in which a smaller quantity of fuel is delivered.
Another type of governor mechanism does not include a pivotal lever, the centrifugal weight mechanism thereof acting against a slidable fuel control member, a governor spring acting against the action of the centrifugal weight mechanism.
It is desirable to be able to control the "droop" of the governor, i.e. the variation in engine speed which must take place in order to move from maximum fuel delivery to minimum fuel delivery. One technique for controlling droop is to employ means for controlling the number of active coils of the governor spring, such an adjustment in effect adjusting the rate of the governor spring.
Conventionally, adjustment of droop in this manner results in a change in the pre-stressing of the governor spring, and hence in a change in the operating speed of an associated engine. It is an object of the invention to provide a governor mechanism in which the level of droop can be adjusted independently of the pre-stressing of the governor spring.
According to the present invention there is provided a governor mechanism comprising a fuel control member operable under the influence of a centrifugal weight mechanism, a coiled governor spring acting against the centrifugal weight mechanism, means for controlling the number of active coils of the governor spring, and adjustable mounting means for the governor spring, adjustable independently of the controlling means.
It will be recognised that by controlling the number of active coils of the governor spring, the effective rate of the spring can be controlled. By reducing the number of active coils of the governor spring, the application of a force to the spring results in a smaller change in length of the spring than if a greater number of the spring's coils were active. It will thus be understood that by reducing the number of active coils, a greater force must be applied to the lever in order to move from a position in which maximum fuel delivery occurs to a position in which minimum fuel delivery occurs, and hence that a relatively large change in engine speed is required. By increasing the number of active coils, a smaller engine speed change is required.It will be recognised therefore that by adjusting the number of active coils of the governor spring, the droop of the governor mechanism can be adjusted. Further, the adjustable mounting means can be used to compensate for my change in the pre-stressing of the governor spring resulting from adjustment of the controlling means.
The means for controlling the number of active coils of the governor spring preferably forms part of the governor spring mounting, and preferably comprises a member an end of which is provided with a helical groove arranged to receive at least one of the coils of the governor spring.
The member is arranged such that angular adjustment thereof results in relative movement of the member and the governor spring, adjusting the number of coils of the governor spring received within the helical groove. It will be recognised that the spacing of the coil(s) within the helical groove is substantially fixed, and thus that these coils are substantially inactive, any increase in length of the spring due to the application of a load thereto occurring as a result of an increase in the separation of the active coils, i.e. those not received within the helical groove.
Preferably, the adjustable mounting means is arranged such that the axial position of the member can be adjusted independently of its angular position to permit adjustment of the pre-stressing of the governor spring without adjusting the number of active coils thereof.
The adjustable mounting means preferably comprises an adjustment member axially moveable with respect to a housing, the member of the controlling means being angularly moveable with respect to the adjustment member.
The adjustment member is preferably in screw-threaded engagement with the housing. The member of the controlling means is preferably axially fixed with respect to the adjustment member, or alternatively may be in screw-threaded engagement therewith.
The invention will further be described, by way of example, with reference to the accompanying drawings, in which like reference numerals denote like parts, and in which: Figure 1 is a cross-sectional view of a rotary fuel pump including a governor mechanism in accordance with a first embodiment; and Figure 2 is a view illustrating the governor mechanism of a second embodiment.
The rotary fuel pump illustrated in Figure 1 comprises a distributor member 60 rotatable within a sleeve 62 at a speed associated with engine speed. The distributor member 60 includes a through bore within which a pair of plungers 64 are reciprocable under the influence of the cam surface of a cam ring 66 including angularly spaced cam lobes. Fuel is delivered to the through bore by a fuel control member 16 under the control of a governor mechanism, through an inlet port 68 of the sleeve 62, inlet passage 70 of the distributor member 60 and axially extending passage 72. At this time, since the rollers carried by the plungers 64 are not aligned with the cam lobes, the fuel pushes the plungers 64 outwards.As the distributor member 60 rotates, the communication between the inlet port 68 and inlet passage 70 is broken, and a delivery passage 74 of the distributor member 60 registers with a delivery port 76 of the sleeve 62. Shortly thereafter, the rollers align with the cam lobes resulting in inward movement of the plungers 64, pumping fuel from the through bore through the axially extending passage 72 and delivery passage 74 to the delivery port 76 from where it is delivered to a respective cylinder of an associated engine. Such a rotary fuel pump is well known, see for example GB-A-218337.0, and will not be described in detail.
The governor mechanism comprises a lever 10 pivotally mounted to part of the housing 12 of the rotary fuel pump. A centrifugal weight mechanism 14 acts against a first end of the lever 10 to pivot the lever 10 with respect to the housing 12. A second end of the lever 10 is coupled in a conventional manner to the fuel control member 16 arranged to control the quantity of fuel delivered by the rotary fuel pump.
The second end of the lever 10 is further connected to a governor spring 18, the free end of which is adjustably mounted to the housing 12 by an adjustment mechanism 20.
The adjustment mechanism 20 comprises an outer cylindrical adjustment member 22 the inner and outer surfaces of which are both provided with screw- threads. The screw-thread provided on the outer surface of the cylindrical member 22 mates with the screw-thread of a threaded aperture provided in the housing 12. A lock nut 24 also engages with the screw-thread provided on the outer surface of the cylindrical member 22, the lock nut 24 being provided with a sealing ring 26 arranged to restrict leakage between the housing 12 and the cylindrical member 22.
An externally screw-threaded rod 28 extends within and mates with the screw-thread provided on the inner surface of the cylindrical member 22.
A second lock nut 30 also mates with the screw-thread of the rod 28, the lock nut 30 carrying a sealing ring 32 arranged to restrict leakage between the rod 28 and the cylindrical member 22. The outer end of the rod 28 is provided with a head 34 of hexagonal cross-section to facilitate rotation of the rod 28. A similar head 36 is provided at the outer end of the cylindrical member 22.
The end of the rod 28 opposite to the hexagonal head 34 is provided with a helical groove 38, the width of which may be slightly larger than the diameter of the wire from which the governor spring 18 is constructed. The pitch of the groove 38 is preferably equal, or at least similar, to the pitch of the coils of the governor spring 18.
As shown in Figure 1, an end portion of the governor spring 18 mates with the helical groove provided in the rod 28, a laterally extending leg 40 integral with an end of the governor spring 18 engaging with the housing 12 in order to prevent or restrict rotation of the end portion of the governor spring 18.
In order to adjust the droop of the governor mechanism, the lock nut 30 is released to permit angular adjustment of the rod 28 with respect to the cylindrical member 22. Angular adjustment of the rod 28 is then achieved using the head 34, such angular adjustment resulting in a change in the number of coils of the governor spring which are received within the groove 38 provided in the end of the rod 28. It will be recognised that rotation of the rod 28 in one direction results in more coils of the spring 18 being received within the groove 38, rotation in the opposite direction releasing part of the governor spring 18 from the groove 38.Whilst angular adjustment of the rod 28 is occurring, there is a tendency for the end portion of the governor spring 18 furthest from the lever 10 to rotate, and such rotation of the end of the governor spring 18 is restricted by the engagement of the leg 40 with the housing 12.
Once the desired level of droop has been achieved, the lock nut 30 is tightened so as to prevent further adjustment of the position of the rod 28, and hence to prevent a change in the number of active coils of the governor spring 18.
In addition to adjusting the effective rate of the governor spring 18 by adjusting the number of active coils thereof, the operator may also wish to adjust the level of pre-stressing of the governor spring 18. This can be achieved by adjusting the axial position of the rod 28 which is achieved by slackening the lock nut 24 and rotating the cylindrical member 22 with respect to the housing 12 using the head 36. It will be recognised that since the rod 28 is in screw-threaded engagement with the cylindrical member 22, such movement of the cylindrical member 22 will result in rotation of the rod 28, and hence in adjustment of the number of active coils of the governor spring 18 unless the rod 28 is held in the desired angular position.Hence, once the desired level of pre-stressing has been achieved, adjustment of the position of the rod 28 may be required in order to adjust the number of active coils of the governor spring 18. It may therefore be desirable to adjust the prestressing of the spring 1 8 before adjusting the effective rate thereof. It will further be recognised that in order to be able to achieve adjustment of the level of pre-stressing and of the number of active coils of the governor spring 18, the screw-thread provided on the outer surface of the cylindrical member 22 should be of different pitch to that provided on the inner surface thereof.
The governor mechanism illustrated in Figure 2 differs from that illustrated in Figure 1 in that the rod 28 is not in threaded engagement with the cylindrical member 22. Instead, the axial position of the rod 28 with respect to the cylindrical member 22 is fixed, angular adjustment of the rod 28 with respect to the cylindrical member 22 being possible in order to adjust the number of active coils of the governor spring 18. The end of the rod 28 remote from the governor spring 18 is provided with a short screw-threaded region with which a lock nut 50 engages, the lock nut 50 being arranged to engage against the head 36 of the cylindrical member 22 in order to restrict relative movement of the rod 28 and the cylindrical member 22. Seal rings 52 are provided between the rod 28 and the inner surface of the cylindrical member 22 in order to restrict leakage therebetween, no such sealing ring being required in the lock nut 50. Adjustment of the droop of the governor is achieved in the same manner as described above, and will not be described. It will be recognised, however, that adjustment of the pre-stressing of the spring 18 can take place independently of adjustment of the number of active coils thereof.
It will be recognised that other types of adjustment mechanism 20 could be used, and that it may be possible to arrange for the inactive coils of the governor spring 18 to be at the end closest to the lever 10 rather than at the end furthest from the lever 10 as described above. It may further be possible to arrange for the inactive coils of the governor spring to be provided at a mid-portion thereof.

Claims (4)

1. A governor mechanism comprising a fuel control member operable under the influence of a centrifugal weight mechanism, a coiled governor spring acting against the centrifugal weight mechanism, means for controlling the number of active coils of the governor spring, and adjustable mounting means for the governor spring adjustable independently of the controlling means.
2. A governor mechanism as claimed in Claim 1, wherein the controlling means forms part of the governor spring mounting.
3. A governor mechanism as claimed in Claim 1 or Claim 2, wherein the adjustable mounting means comprises an adjustment member axially moveable with respect to a housing, the controlling means including a member which is angularly adjustable with respect to the adjustment member.
4. A governor mechanism substantially as hereinbefore described with reference to the accompanying drawings.
GB9423582A 1994-11-22 1994-11-22 Governor mechanism having independent active coil adjustment and pre-stressing Withdrawn GB2295463A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB9423582A GB2295463A (en) 1994-11-22 1994-11-22 Governor mechanism having independent active coil adjustment and pre-stressing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB9423582A GB2295463A (en) 1994-11-22 1994-11-22 Governor mechanism having independent active coil adjustment and pre-stressing

Publications (2)

Publication Number Publication Date
GB9423582D0 GB9423582D0 (en) 1995-01-11
GB2295463A true GB2295463A (en) 1996-05-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB9423582A Withdrawn GB2295463A (en) 1994-11-22 1994-11-22 Governor mechanism having independent active coil adjustment and pre-stressing

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1006268A2 (en) * 1998-12-05 2000-06-07 Lucas Industries Limited Governor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB548211A (en) * 1941-03-28 1942-09-30 Weyburn Engineering Company Lt Improvements in or relating to centrifugal governors
GB2154338A (en) * 1984-02-16 1985-09-04 Bosch Gmbh Robert Speed governor for fuel injection pumps

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB548211A (en) * 1941-03-28 1942-09-30 Weyburn Engineering Company Lt Improvements in or relating to centrifugal governors
GB2154338A (en) * 1984-02-16 1985-09-04 Bosch Gmbh Robert Speed governor for fuel injection pumps

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1006268A2 (en) * 1998-12-05 2000-06-07 Lucas Industries Limited Governor
EP1006268A3 (en) * 1998-12-05 2001-09-19 Lucas Industries Limited Governor
US6443127B1 (en) 1998-12-05 2002-09-03 Delphi Technologies, Inc. Governor

Also Published As

Publication number Publication date
GB9423582D0 (en) 1995-01-11

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WAP Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1)