CA1036445A - Liquid fuel injection pumping apparatus - Google Patents
Liquid fuel injection pumping apparatusInfo
- Publication number
- CA1036445A CA1036445A CA231,480A CA231480A CA1036445A CA 1036445 A CA1036445 A CA 1036445A CA 231480 A CA231480 A CA 231480A CA 1036445 A CA1036445 A CA 1036445A
- Authority
- CA
- Canada
- Prior art keywords
- valve
- pressure
- cylinder
- piston
- valve element
- 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
Links
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
- F02M41/1416—Devices specially adapted for angular adjustment of annular cam
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Abstract
ABSTRACT OF DISCLOSURE
A fuel injection pumping apparatus includes an injection pump driven in timed relationship with an assoc-iated engine and a resiliently loaded fluid pressure operable member for controlling the timing of delivery by the injection pump. Means is provided for generating pressure responsive to the speed of the associated engine and this pressure is applied to the aforesaid member so that the timing of delivery of fuel is variable. The apparatus also includes a piston movable to adjust the force exerted by the resilient means on the member and valve means is provided for controlling the application of fluid pressure to said piston, the valve means being respon-sive to the speed of operation of the associated engine.
A fuel injection pumping apparatus includes an injection pump driven in timed relationship with an assoc-iated engine and a resiliently loaded fluid pressure operable member for controlling the timing of delivery by the injection pump. Means is provided for generating pressure responsive to the speed of the associated engine and this pressure is applied to the aforesaid member so that the timing of delivery of fuel is variable. The apparatus also includes a piston movable to adjust the force exerted by the resilient means on the member and valve means is provided for controlling the application of fluid pressure to said piston, the valve means being respon-sive to the speed of operation of the associated engine.
Description
~ID36445 This invention relates to liquid fuel injection pumping apparatus for supplying fu~l to internal combustion en~ines, and of the l~ind comprising an injection pump adapted to be driven in timed relationship with an associated engine, a resiliently loaded fluid pressure operable member for control-ling the timing of delivery of fuel to the associated engine and means for generating a pressure responsive to the speed of the associated engine, said pressure being applied to saiid member wh~reby the timing of the delivery of fuel will be dependent upon the speed of the associated engine.
Fuel pumping apparatus of the kind set out above is well known in the art one such example being described in United States Patent speci~ication 2910975. Other e~amples are l{nown in which the fluid pressure operable member is also . ,, - responsivc to the load on the associated engine. In the example described in the aforesaid United States P~ent the ~orce exerted by the resilient means which biases the valve ¦ member can be adjusted by means of a special piston. In ! this manner it is possible to alter the speed/timer charac-j teristic of the apparatus. Th~ pressure applied to the piston is controlled by a simple valve which is responsive to th~
pressure appl~d to the pressure o~rable member. The form of valve described in the United States Patent specification 2910975 is unfortunately not susceptible of modification to ~, i any appreciable extent whereby different operating charac-~"~.,' teriistics can be obtained.
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64~5 According to the invention a liquid fuel injection pumping apparatus for supplying fuel to an inte~nal combus-tion engine comprises an injection pump adapted to be driven in timed relationship with an associatad engine, a fluid pressure operable member for controlling the timing of delivery of fuel to the associated engine, means for generating a fluicl pressure responsive to an operating characteristic . of the associated engine, conduit means through which said ,- pressure is applied to said member, resilient means loading said member against the action of the fluid pressure, a pressure responsive piston forming an abutment for said ¦ resilient means, said piston being movable from a first to . a second position when pressure is applied thereto so as to vary the force exerted by said resilient means on said member, a pressure responsive valve for controlling the application of : pressure to said piston, said valve comprising a va~e cylinder, j a valve element movable in said cylinder, a port in the wall.
.```j of saicl valve cylinder, further conduit means for communicating . the pressure at said port to said pressure responsive piston,, . . .
; resilient means biasing said valve element to o~e end of said1~
, cylinder, a pair of axially spaced grooves on said valve element, a pair of passages through which said grooves commun-icate with the opposite ends of the valve cylinder respectively, passage means communicating the other end of said valve cylinder with the means generating said fluid pressure so that the valve ;' element moves in response to variations in said fluid pressure, and further passage means through which said one end of the cylinder communicates with a drain, said valve element acting ¦" depending on its position, to place said port in communication with one or the other end of said valve cylinder.
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An example of an apparatus in accordance with the inventio~ ~ill now be described with reference to the accompr-lnying drawing which shows the apparatus in diagrammiatic form, individual parts being in sectional side elevation.
Referring to the drawings, the apparatus comprises a rotary distributor member now shown, which in use, is driven in timed relationship with the associated engine. rhe distr~-butor member is mounted within a body part, and formed in the distributor member is a transversely extending bore in which are mounted a pair of pumping plungers. The plungers are adapted to be moved inwardly as the distributor member rotates, by m~ans of cam lobes formed on the internal periphery of an angularly adjustable cam ring 13 which is mounted in the body part of the apparatus. Conveniently rollers carried by shoes are provided between the plungers and the cam lobes. The portion of the bore which lies between the plungers constitutes the pumping chamber of ~ e injection pump, and in known manner, fuel displaced from this bore during inward movement of the plungers is delivered through a passage formed in the distri-butor member, to a delivery passage which is ln register with a deliver~ port formed in the body part, during the time when the plungers are being moved inwardly.
,`lj;~ During the filling stroke of the injection pump, fuel is delivered to the bore containing theplungers and conven-iently this fuel is obtained from a feed pump 14, the quantity of fuel being determined by a throttle valve including a manually adjustable member so that the speed of the associated ~i .
engine can be varied as required by the operator. Associated with the ~eed pump 14 is a valve 26 which provides a fuel pres~
sure which varied in accordance with the square of the speed , , i, .. .
~ .,, .. ,.;, I .
~36445 at which the engino is driven, Moreover, the output pressure of the feed pump i is controlled by a valve 80 that it varies in accordance with the speed at which the associated engine is operating In some instances, it also is arranged to vary in accordance with the square cf speed.
The angular setting of the cam ring 13 determines the timing of delivery of fuel to the associated engine~ and for ad~usting the angular setting a piston 17 is provided and which is contained within a cylinder 18. The piston 17 is provided wi$h a cylindrical bore in which is located a fluid pressure operable member in the form of a servo valve 19, one end of the servo valve is exposed to the pressure pro~ided by the valve 26, whilst the other end of the servo valve is contacted by resilient means in the forn~ of a coiled compression spring 20. The other end of the spring 20 engages with a piston 21 which is mounted within an e~tension of the cylinder 18.
Moreover~ intermediate the cylinder and the extension thereof, is a stop whereby the ~xtent of movement of the piston 21 ls limited.
Formed within the piston 17 is a passage 22 which extends to the end of the piston 17 remote from the piston 21, and the passage 22 opens into a port 23 positioned to be covered by a land of the v~l~e 19. The valve 19 is provided with a further land, a~d the annular groove defined between the two lands is in communication with the outlet of the feed pump 14 by way of an anti-shock valve 24. In operation9 as the pressure applied to the servo valve varies, the position of the valve 1g will also vary and if for instance the pressure increases, the valve will move against the action of the spring 20. The port 23 will be exposed to the groove on the valve 19 and fuel under pressure from the outlet of the feed pump will flow along the passage 22. As a result, the piston 17 will move in the same direc$ion, tLereby effecting anti-clcokwise movement of the .
: `
.... _ _ . _ . _ _ .... . ...... .. ..
~g364~5 ring 13 9 ther~by servingr to advance the tirning of delivery o~ fuel to the engine Conversely, if the pressure ~hould fall, then the valve 19 mov0s ln *he opposite direction and the port 23 is exposed to a drain and in -this case~ the reaction of the cams and rollers will effect clockwise movement of the ring 13 and movement of the plston 17 towards the left. Such movement occurs until the port 23 is again coversd by the land of the valve, Also provided is a valve 27 which determines the pressure applied to the piston 21. The valve 27 comprises a valve body 28 in uhich is defined a cylindrical chamber, one end of which communicates with the outlet of the valve 26 whilst the other and enlarged end of the chamber communicates with a drain. Slidably mounted within the narrower portion of the chamber, is a valve member 29 and a coiled compression spring 3O is provided in the enlarged portion o~ the chamber, and acts upon the valve member 29.
~ ormed in the valve member 29 are three axially spaced grooves 31, 32 and 33, the groove 32 being the central groove and being connectod by way o~ a passage within the valvs member, with the end o~ the chamber containing the spring 3O. The other two grooves are interconnected with each other, and with the narrower end of the chamber. Moreover, formed in the bod~ 28 is a port 34 with which the grooves can register, and the port 34 is connected to the cylinder containing the piston 21. When the pressure applied to the valve member 29 is such that the force is less than the preload of the spring 3O, the groove 33 will be in register with the port 34 so that fuel under pressure from the valve 26 will be applied to the piston 21 and the piston will assume the po~ition in which it is shown~ As the pressure increases, however, the valve member 29, will move against the action of the spring 3O, and the groove 32 brought into register with the port 34O When this occurs, the ~' . .
103G4~5 pressure to which the piston 21 i~ expos~d is a drain pre~sure so that the pi.ston 21 wlll mov0 under the ection of the force exerted by the spring disposed between the piston 21 and the valve 19, so that it assumes the dotted position shown in ~i.gure 2. As the pressure further incr~ases, the groove 31 will be brought into register with the port 34, and the position of the piston 21 will revert to that which is shown in full outli.ne in Figure 2. If desired~ however, the groove 31 may be omitted 90 that there will be no reversion of the position of the piston 21.
In an alternative arrangement the grooves 31 and 33 are connected to the drain whilst the groove 32 is connected to the outlet of the valve 26, but again the groove 31 may be omitted.
With this arrangement, the piston 21 will remain in the dotted outline position until the valve member 29 has moved sufficiently to bring the groove 32 in register with the port 349 and it will stay in this position until further movement of the valve 29 occurs.
By UBillg the valve and piston as described an appreciable modification can be made to the timing characteristic over a narrow range o~ engine speeds the various examples described illustrate that such modification can be achieved in a very simple manner.
, . . .
Fuel pumping apparatus of the kind set out above is well known in the art one such example being described in United States Patent speci~ication 2910975. Other e~amples are l{nown in which the fluid pressure operable member is also . ,, - responsivc to the load on the associated engine. In the example described in the aforesaid United States P~ent the ~orce exerted by the resilient means which biases the valve ¦ member can be adjusted by means of a special piston. In ! this manner it is possible to alter the speed/timer charac-j teristic of the apparatus. Th~ pressure applied to the piston is controlled by a simple valve which is responsive to th~
pressure appl~d to the pressure o~rable member. The form of valve described in the United States Patent specification 2910975 is unfortunately not susceptible of modification to ~, i any appreciable extent whereby different operating charac-~"~.,' teriistics can be obtained.
'`!
.~ I
, ' ' , !'~, - 2 i ,. i~
1;` ` 1 ~7~, ~, . ~ , . .. ... . . ~ :
64~5 According to the invention a liquid fuel injection pumping apparatus for supplying fuel to an inte~nal combus-tion engine comprises an injection pump adapted to be driven in timed relationship with an associatad engine, a fluid pressure operable member for controlling the timing of delivery of fuel to the associated engine, means for generating a fluicl pressure responsive to an operating characteristic . of the associated engine, conduit means through which said ,- pressure is applied to said member, resilient means loading said member against the action of the fluid pressure, a pressure responsive piston forming an abutment for said ¦ resilient means, said piston being movable from a first to . a second position when pressure is applied thereto so as to vary the force exerted by said resilient means on said member, a pressure responsive valve for controlling the application of : pressure to said piston, said valve comprising a va~e cylinder, j a valve element movable in said cylinder, a port in the wall.
.```j of saicl valve cylinder, further conduit means for communicating . the pressure at said port to said pressure responsive piston,, . . .
; resilient means biasing said valve element to o~e end of said1~
, cylinder, a pair of axially spaced grooves on said valve element, a pair of passages through which said grooves commun-icate with the opposite ends of the valve cylinder respectively, passage means communicating the other end of said valve cylinder with the means generating said fluid pressure so that the valve ;' element moves in response to variations in said fluid pressure, and further passage means through which said one end of the cylinder communicates with a drain, said valve element acting ¦" depending on its position, to place said port in communication with one or the other end of said valve cylinder.
!~";
( - 3 ~
.',~ '. ~
:~ i ~136~4~;
An example of an apparatus in accordance with the inventio~ ~ill now be described with reference to the accompr-lnying drawing which shows the apparatus in diagrammiatic form, individual parts being in sectional side elevation.
Referring to the drawings, the apparatus comprises a rotary distributor member now shown, which in use, is driven in timed relationship with the associated engine. rhe distr~-butor member is mounted within a body part, and formed in the distributor member is a transversely extending bore in which are mounted a pair of pumping plungers. The plungers are adapted to be moved inwardly as the distributor member rotates, by m~ans of cam lobes formed on the internal periphery of an angularly adjustable cam ring 13 which is mounted in the body part of the apparatus. Conveniently rollers carried by shoes are provided between the plungers and the cam lobes. The portion of the bore which lies between the plungers constitutes the pumping chamber of ~ e injection pump, and in known manner, fuel displaced from this bore during inward movement of the plungers is delivered through a passage formed in the distri-butor member, to a delivery passage which is ln register with a deliver~ port formed in the body part, during the time when the plungers are being moved inwardly.
,`lj;~ During the filling stroke of the injection pump, fuel is delivered to the bore containing theplungers and conven-iently this fuel is obtained from a feed pump 14, the quantity of fuel being determined by a throttle valve including a manually adjustable member so that the speed of the associated ~i .
engine can be varied as required by the operator. Associated with the ~eed pump 14 is a valve 26 which provides a fuel pres~
sure which varied in accordance with the square of the speed , , i, .. .
~ .,, .. ,.;, I .
~36445 at which the engino is driven, Moreover, the output pressure of the feed pump i is controlled by a valve 80 that it varies in accordance with the speed at which the associated engine is operating In some instances, it also is arranged to vary in accordance with the square cf speed.
The angular setting of the cam ring 13 determines the timing of delivery of fuel to the associated engine~ and for ad~usting the angular setting a piston 17 is provided and which is contained within a cylinder 18. The piston 17 is provided wi$h a cylindrical bore in which is located a fluid pressure operable member in the form of a servo valve 19, one end of the servo valve is exposed to the pressure pro~ided by the valve 26, whilst the other end of the servo valve is contacted by resilient means in the forn~ of a coiled compression spring 20. The other end of the spring 20 engages with a piston 21 which is mounted within an e~tension of the cylinder 18.
Moreover~ intermediate the cylinder and the extension thereof, is a stop whereby the ~xtent of movement of the piston 21 ls limited.
Formed within the piston 17 is a passage 22 which extends to the end of the piston 17 remote from the piston 21, and the passage 22 opens into a port 23 positioned to be covered by a land of the v~l~e 19. The valve 19 is provided with a further land, a~d the annular groove defined between the two lands is in communication with the outlet of the feed pump 14 by way of an anti-shock valve 24. In operation9 as the pressure applied to the servo valve varies, the position of the valve 1g will also vary and if for instance the pressure increases, the valve will move against the action of the spring 20. The port 23 will be exposed to the groove on the valve 19 and fuel under pressure from the outlet of the feed pump will flow along the passage 22. As a result, the piston 17 will move in the same direc$ion, tLereby effecting anti-clcokwise movement of the .
: `
.... _ _ . _ . _ _ .... . ...... .. ..
~g364~5 ring 13 9 ther~by servingr to advance the tirning of delivery o~ fuel to the engine Conversely, if the pressure ~hould fall, then the valve 19 mov0s ln *he opposite direction and the port 23 is exposed to a drain and in -this case~ the reaction of the cams and rollers will effect clockwise movement of the ring 13 and movement of the plston 17 towards the left. Such movement occurs until the port 23 is again coversd by the land of the valve, Also provided is a valve 27 which determines the pressure applied to the piston 21. The valve 27 comprises a valve body 28 in uhich is defined a cylindrical chamber, one end of which communicates with the outlet of the valve 26 whilst the other and enlarged end of the chamber communicates with a drain. Slidably mounted within the narrower portion of the chamber, is a valve member 29 and a coiled compression spring 3O is provided in the enlarged portion o~ the chamber, and acts upon the valve member 29.
~ ormed in the valve member 29 are three axially spaced grooves 31, 32 and 33, the groove 32 being the central groove and being connectod by way o~ a passage within the valvs member, with the end o~ the chamber containing the spring 3O. The other two grooves are interconnected with each other, and with the narrower end of the chamber. Moreover, formed in the bod~ 28 is a port 34 with which the grooves can register, and the port 34 is connected to the cylinder containing the piston 21. When the pressure applied to the valve member 29 is such that the force is less than the preload of the spring 3O, the groove 33 will be in register with the port 34 so that fuel under pressure from the valve 26 will be applied to the piston 21 and the piston will assume the po~ition in which it is shown~ As the pressure increases, however, the valve member 29, will move against the action of the spring 3O, and the groove 32 brought into register with the port 34O When this occurs, the ~' . .
103G4~5 pressure to which the piston 21 i~ expos~d is a drain pre~sure so that the pi.ston 21 wlll mov0 under the ection of the force exerted by the spring disposed between the piston 21 and the valve 19, so that it assumes the dotted position shown in ~i.gure 2. As the pressure further incr~ases, the groove 31 will be brought into register with the port 34, and the position of the piston 21 will revert to that which is shown in full outli.ne in Figure 2. If desired~ however, the groove 31 may be omitted 90 that there will be no reversion of the position of the piston 21.
In an alternative arrangement the grooves 31 and 33 are connected to the drain whilst the groove 32 is connected to the outlet of the valve 26, but again the groove 31 may be omitted.
With this arrangement, the piston 21 will remain in the dotted outline position until the valve member 29 has moved sufficiently to bring the groove 32 in register with the port 349 and it will stay in this position until further movement of the valve 29 occurs.
By UBillg the valve and piston as described an appreciable modification can be made to the timing characteristic over a narrow range o~ engine speeds the various examples described illustrate that such modification can be achieved in a very simple manner.
, . . .
Claims (3)
1. A liquid fuel injection pumping apparatus for supplying fuel to an internal combustion engine comprising an injection pump adapted to be driven in timed relationship with an associated engine, a fluid pressure operable member for controlling the timing of delivery of fuel to the associated engine, means for generating a fluid pressure responsive to an operating characteristic of the associated engine, conduit means through which said pressure is applied to said member, resilient means loading said member against the action of the fluid pressure, a pressure responsive piston forming an abutment for said resilient means, said piston being movable from a first to a second position when pressure is applied thereto so as to vary the force exerted by said resilient means on said member, a pressure responsive valve for controlling the application of pressure to said piston, said valve comprising a valve cylinder, a valve element movable in said cylinder, a port in the wall of said valve cylinder, further conduit means for communicating the pressure at said port to said pressure responsive piston, resilient means biasing said valve element to one end of said cylinder, a pair of axially spaced grooves on said valve element, a pair of passages through which said grooves communicate with the opposite ends of the valve cylinder respectively, passage means communicating the other end of said valve cylinder with the means generating said fluid pressure so that the valve element moves in response to variations in said fluid pressure, and further passage means through which said one end of the cylinder communicates with a drain, said valve element acting depending on its position, to place said port in communication with one or the other end of said valve cylinder.
2. An apparatus according to Claim 1, including an additional groove on said valve element, said additional groove being axially spaced on one side of said pair of grooves, and a further passage connecting said additional groove to the remote one of said pair of grooves.
3. An apparatus according to Claim 2, in which said passages and further passage are formed in the valve element.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB32019/74A GB1515288A (en) | 1974-07-19 | 1974-07-19 | Liquid fuel injection pumping apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1036445A true CA1036445A (en) | 1978-08-15 |
Family
ID=10331839
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA231,480A Expired CA1036445A (en) | 1974-07-19 | 1975-07-15 | Liquid fuel injection pumping apparatus |
Country Status (10)
| Country | Link |
|---|---|
| JP (1) | JPS5134328A (en) |
| AR (1) | AR205574A1 (en) |
| BR (1) | BR7504586A (en) |
| CA (1) | CA1036445A (en) |
| DE (1) | DE2532480A1 (en) |
| ES (1) | ES439573A1 (en) |
| FR (1) | FR2278929A1 (en) |
| GB (1) | GB1515288A (en) |
| IT (1) | IT1039927B (en) |
| ZA (1) | ZA754530B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4224916A (en) * | 1978-11-13 | 1980-09-30 | Stanadyne, Inc. | Timing control for fuel injection pump |
| US4365939A (en) * | 1979-07-06 | 1982-12-28 | Lucas Industries Limited | Fuel injection pumping apparatus |
| DE3201914A1 (en) * | 1982-01-22 | 1983-08-04 | Robert Bosch Gmbh, 7000 Stuttgart | Fuel injection pump for internal combustion engines |
| GB8619994D0 (en) * | 1986-08-16 | 1986-09-24 | Lucas Ind Plc | Fuel injection pump |
-
1974
- 1974-07-19 GB GB32019/74A patent/GB1515288A/en not_active Expired
-
1975
- 1975-01-01 AR AR259664A patent/AR205574A1/en active
- 1975-07-15 CA CA231,480A patent/CA1036445A/en not_active Expired
- 1975-07-15 ZA ZA00754530A patent/ZA754530B/en unknown
- 1975-07-17 JP JP50086740A patent/JPS5134328A/ja active Pending
- 1975-07-17 FR FR7522398A patent/FR2278929A1/en active Granted
- 1975-07-18 BR BR7504586*A patent/BR7504586A/en unknown
- 1975-07-18 IT IT25544/75A patent/IT1039927B/en active
- 1975-07-19 ES ES439573A patent/ES439573A1/en not_active Expired
- 1975-07-21 DE DE19752532480 patent/DE2532480A1/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| AU8304075A (en) | 1977-01-20 |
| ES439573A1 (en) | 1977-02-16 |
| JPS5134328A (en) | 1976-03-24 |
| BR7504586A (en) | 1976-07-06 |
| IT1039927B (en) | 1979-12-10 |
| AR205574A1 (en) | 1976-05-14 |
| FR2278929B1 (en) | 1980-05-23 |
| ZA754530B (en) | 1976-07-28 |
| FR2278929A1 (en) | 1976-02-13 |
| GB1515288A (en) | 1978-06-21 |
| DE2532480A1 (en) | 1976-01-29 |
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