GB1579711A - Fuel injection pumper for internal combustion engine - Google Patents
Fuel injection pumper for internal combustion engine Download PDFInfo
- Publication number
- GB1579711A GB1579711A GB516278A GB516278A GB1579711A GB 1579711 A GB1579711 A GB 1579711A GB 516278 A GB516278 A GB 516278A GB 516278 A GB516278 A GB 516278A GB 1579711 A GB1579711 A GB 1579711A
- Authority
- GB
- United Kingdom
- Prior art keywords
- pump
- valve
- cylinder
- bore
- delivery
- 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
- 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
- F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
- F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/462—Delivery valves
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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)
Description
(54) FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINE
(71) We, ROBERT BOSCH GMBH, a
German company of Postfach 50, 7 Stuttgart 1,
Federal Republic of Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:
The invention concerns a fuel injection pump.
A fuel injection pump is already known (US Patent Application No. 3 759 235), whose delivery valve is arranged as a complete valve unit in a longitudinal bore of a valve holder. A valve spring abutment member in the form of a threaded member is inserted into this longitudinal bore, and is therefore subject to the high compressive and impact stresses created during operation at high injection pressures, which may result in premature damage to, or undesirable disalignment of, the spring abutment member.High-pressure sealing of the pump working chamber is effected by means of sealing surfaces and counter surfaces, in the form of metallic gaskets, about the valve holder and the pump cylinder, which necessitates extremely strong clamping forces between the pump cylinder and the valve holder, since the maximum pressures created in the pump working chamber tend to force the two members apart. The substantial clamping and pumping forces result, disadvantageously, in stress corrosion and metal fatigue in the components concerned, which may lead to serious damage.Owing to the substantial tension forces necessary in order to maintain a perfect seal, there is a danger of deformation of the upper portion of the cylinder bore in which the pump piston is guided, and, in consequence, owing to the magnitude of the fitting tolerance between the pump piston and the cylinder bore amounting to only several thousandths of a millimetre, seizing of the piston, and consequent damage, may occur. A cylindrical portion of the valve holder is accommodated in the receiving bore of the respective clamping member, and serves only to centre the valve; an additional high-pressure seal is necessary also in the region of this cylindrical portion.
In a fuel injection pump, already known from US Patent Application No. 2 282 562, high pressure sealing of the pump working chamber is improved by the fitting of a guide spigot in the cylinder bore in a manner to provide a high-pressure seal; moreover, the construction of the holder is integral with a pipe connector leading to the fuel delivery line to the injection nozzle and the spigot so that the sealing problems of the first mentioned known fuel injection pump are avoided; however, the disadvantages of the delivery valve being mounted in the longitudinal direction of the valve holder and having a spring abutment member in the form of a threaded element, still remain.If such a pump is to be provided with a delivery valve in the form of a pressure balancing valve, the disadvantages described become more marked, since either installation difficulties arise, or, if a pressure balancing valve opening in a direction towards the pump working chamber is used, there is an increased danger that the respective spring abutment member, or corresponding support ing members, may be damaged and get into the pump working chamber, thus causing immediate failure of the pump, quite apart from damage to important components.
According to the present invention, there is provided a fuel injection pump for an internal combustion engine, the pump having a piston axially and rotationally movable in a cylinder provided in a housing, and having a delivery valve arranged between a working chamber of the pump and a delivery line connectible to the injection nozzle, the valve being housed within a valve holder which has a cylindrical surface at least partially fitted into the cylinder end and forming a sealing surface co-operating with a cylindrical counter surface defined by the wall of the cylinder, to provide a high pressure seal for the cylinder, said valve being arranged in a bore in the holder, which bore extends generally transversely of the cylinder axis, from said cylindrical surface, and which bore is connected to the working chamber and to the delivery line by respective portions of a delivery passage.
This pump has the advantage that, in the event of e.g. a spring abutment member becoming loose, it still remains in its assembly position, and operation of the delivery valve is not impaired. In the case of an injection pump wherein the working chamber is defined between an end face of the piston and an end face of a cylindrical spigot, which is inserted with a pressure-tight fit in the cylinder and which comprises a portion of the valve holder accommodating at least that portion of the delivery passage which connects the valve to the working chamber and providing a portion of the sealing surface, a very compact form of construction, reliable retention of the delivery valve, and perfect sealing of the pump working chamber are advantageously achieved.Moreover, the respective member clamping the valve holder is subject only to the pressures acting upon the end face of the spigot, so that the necessary clamping and retaining forces are correspondingly small.
A particularly advantageous elaboration of the invention may be achieved in a fuel injection pump wherein the valve holder is provided, in addition to the spigot, with a pipe connector providing connection to the delivery line, and with an upper body clamped within a bore of a clamping flange attached to the pump housing.
By incorporating the delivery valve in the upper body of the valve holder, the invention may be used even in relatively small pumps, since the spigot no longer serves to accommodate the valve. A valve arrangement, which is cheap and simple and also very economical of space, can be provided owing to both the movable valve member and the spring abutment member being in the form of balls.
The invention is described further, by way of example, with reference to the accompanying drawings, wherein :
Figure 1 is a section through the first embodiment of the invention;
Figure 2 is a corresponding section through the second embodiment of the invention; and
Figure 3 is a section along the line 111-111 in Figure 2;
Figure 4 is a section through the third embodiment of the invention
In the fuel injection pump 10, shown as a first embodiment in Figure 1 , a pump cylinder 13 is inserted in a bore 11 of a pump housing 12, which is only partially shown, a pump piston 15 being guided axially and rotationally movably in the cylinder bore 14.The pump cylinder 13 is supported via an annular shoulder 16 on a step 17 of the housing 12, and is rigidly clamped against this step 17 by means of a clamping flange 19 via a pipe connector 21 and a valve holder 22. The pipe connector 21 is fitted in an enlarged portion I la of the bore 11, and the suction chamber 24 of the injection pump is externally sealed by means of a sealing ring 23, fitted in an annular groove 20 in the pipe connector 21.
A guide spigot 25, in the form of a cylindrical portion of the valve holder 22, is lapped, in order, like the piston 15, to provide a highpressure seal, in a portion 14a of the cylindrical bore 14 adjacent to the pump working chamber, and is inserted in this bore. Inside the spigot 25, a delivery valve 28 is mounted in a transverse bore 27, extending perpendicularly to the longitudinal axis of the pump cylinder 13 and the valve holder 22, the delivery valve 28, which is inserted as a complete unit into this transverse bore 27, comprising a valve seat 29, in the form of a portion of the transverse bore 27, a movable valve member 31, a valve spring 32, and a spring abutment member 33, the movable valve member 31 and the spring abutment member being formed by balls, The spring abutment member 33 is pressfitted into the transverse bore 27, its assembly position being delimited by the wall of the receiving bore 14a surrounding the spigot 25.
It is also possible to insert the spring abutment member 33, in the form of a ball, loosely and without the use of pressure into the transverse bore 27, since the wall of the receiving bore 14a determines its assembly position, and the spigot 25 of the valve holder 22 is fitted by lapping into the portion 14a of the cylinder bore 14 so as to provide a high-pressure seal.
Fuel, which may leak between the spigot 25 and the wall of the portion 14a of the bore, flows via a groove 34 and a clearance between the outer diameter of the pump cylinder 13 and the enlarged portion 1 la of the bore to the suction chamber 24. The groove 34 is formed in an annular shoulder 35 of a flangelike portion 22a of the valve holder 22.
Tile transverse bore 27, housing the valve seat 29 and serving as a spring compartment of the delivery valve 28, is connected via a portion 36 of the delivery passage to the pump working chamber 26, antI, via a portion 37 of the delivery passage in the valve holder 22, and a bore 38 in the pipe connector 21, to the delivery line 39, shown notionally only, connected to the injection nozzle.
Parallel with the delivery valve 28, fitted as a complete unit in the transverse bore 27, a second valve unit 41, operating as a by-pass valve, is inserted in a further transverse bore 42 provided in the spigot 25 of the valve holder 22. This valve unit 41 is connected via a throttling bore 43 to the portion 37 of the delivery passage, and its movable valve member 44 is arranged so as to open in a direction towards the pump working chamber 26, so that, on the cessation of injection, damped pressure balancing of the pressure line 39 with respect to the pump working chamber 26 can take place via the throttling bore 43, owing to the portion of the transverse bore 42 serving as the spring compartment being connected by means of a connecting bore 45 to the portion 36 of the delivery passage. The two valves 28 and 41 are identical in construction, each having a ball as movable valve member and spring abutment member respectively, which makes for compact construction, the two valves serving jointly as a pressure balancing valve.
Owing to the parallel, coplanar arrangement of the two valve units 28 and 41, a relatively simple line arrangement is possible, each requiring only a respective portion 36, 37 of the delivery passage.
The pump piston 15 has a control surface 47, delimited in a known manner by an angular control edge 46, the control surface 47 cooperating, together with the end face 48 of the pump piston 15, with two control ports 49 arranged in the wall of the cylinder bore 14 and each serving simultaneously as a suction bore and a return-flow bore.
In this embodiment of the invention shown in Figure 1, the cylindrical surface of the spigot 25, in the form of a cylindrical portion of the valve holder 22, serves as a sealing surface, and the wall of the portion 14a of the cylinder bore 14, serving as a receiving bore for this spigot 25, serves as a counter surface of the high-pressure seal between the pump working chamber 26 and the suction chamber 24. The valve holder 22 is subjected to the full fuel pressure in the pump working chamber 26 only at its end adjacent to the pump working chamber 26, so that the force required to clamp the valve holder 22 need not be very great.
In the case of the fuel injection pump 51, shown in Figures 2 and 3 as a second embodiment of the invention, components corresponding to the first embodiment are denoted by the same reference numerals, or an index mark is attached to the numeral in cases where they differ substantially in form or position.
In contrast to the separate arrangement in the case of the pump 10 of the first embodiment, in the case of the injection pump 51, the valve holder denoted by the reference numeral 22', in addition to being formed integrally with the spigot 25', is also integral with a pipe connector 21' for connection of the delivery line 39, and with an upper body 53, arranged between the spigot 25' and the pipe connector 21 ', and having a clamping flange 52.The upper body 53, like the spigot 25', is in the form of a cylindrical portion of the valve holder 22' and is shrink-fitted rigidly in a bore 54, serving as a receiving bore, of the clamping flange 52, which is attached by means of screws 18 to the pump housing 12. The clamping flange 52 is centrally located by means of a cylindrical collar 55 in the portion 1 la of the receiving bore 11 of the pump housing 12.
In contrast to the arrangement shown in
Figure 1, wherein the bores 27 and 42 are approximately parallel to each other and lie in planes so spaced as to leave a minimum wall thickness between these bores, the valves 28' and 41' (see Figure 3) are arranged so that when viewed in the longitudinal direction of the cylinder they are perpendicular to each other in the spigot 25. Also the portions of the cylindrical surface of the spigot 25' broken by the transverse bores 27' and 42', are situated as low as possible, that is, adjacent to the pump working chamber 26. This has the advantage that a sufficiently long unbroken sealing surface remains between the spigot 25' and the portion 14a of the cylinder bore 14 in order to provide a perfect high-pressure seal.The portion of the delivery passage of the delivery valve 28'leading to the pump working chamber is denoted by the reference numeral 36', and the corresponding portion of the delivery passage leading to the delivery line 39 is denoted as 37'. The by-pass valve 41' (see Figure 3) comprises a portion 56 of the delivery passage leading to the pump working chamber 26, and a portion 57 of the delivery passage connecting the valve 41' to the delivery line.
This arrangement of the two valves permits not only improved high-pressure sealing between the spigot 25'and the portion 14a of the bore, but also very compact construction of the valve arrangement and advantageous utilisation of the space available, so that, if required, spring retainers (not shown), for supporting the balls serving as movable valve members, may also be incorporated.
In contrast to the pump cylinder 13, the pump cylinder here denoted as 13' is mounted floatingly on the spigot 25', its axial position relative to the pump piston 15 being adjustable by means of an adjusting device 58, an actuating lever 59 of which engages in a groove 61 in the periphery of the pump cylinder 13, By means of this adjustment it is possible to vary the commencement of fuel delivery, as is desirable in the case of high-speed diesel engines, and in the case of many engines in order to comply with the stricter exhaust emission regulations.This variability of the commencement of fuel delivery, or the retardation of the commencement of injection thereby achievable, is effected by variation, by means of the adjusting device 58, of the position of the control ports 49 relative to the control edge formed by the end face 48 of the pump piston 15.
Since, owing to the high-pressure seal formed between the spigot 25' and ;the portion 14a of the bore, no axial forces act upon the pump cylinder 13', the adjusting forces required to be supplied by the adjusting device 58 are also small, which is a great advantage compared with other devices for adjusting the timing of the commencement of fuel injection.
Fuel which may leak between the spigot 25'and the portion 14a of the cylinder bore 14 flows via the intermediate chamber between the pump cylinder 13'and the clamping flange 52, and the portion l la of the receiving bore 11, into the suction chamber 24, and, right up to the connection point of the pres sure line 39 not a single high-pressure external seal is provided, whereby a high degree of reliable, leakproof operation of this pump is ensured.
The pump cylinder 13', whose one end is mounted on the spigot 25', is guided at its other end on the pump piston 15, which preferably is centred by means of a pivot in the pump rod (not shown). Sealing of the suction chamber 24 with respect to the spring compartment (not shown) of the pump is effected by means of a sealing arrangement 62.
As in the case of the second embodiment shown in Figures 2 and 3, the fuel injection pump 71, shown in Figure 4 as a third embodiment of the invention is provided with a valve holder 22", which, like the valve holder 22', is an integral unit comprising a pipe connector 21", a spigot 25", and an upper body 72, arranged between the two latter. The upper body 72, in the form of a cylindrical portion of the valve holder 22", is rigidly shrink-fitted, and also high-pressure sealed, in a bore 73, serving as a receiving bore for the valve holder 22", in a clamping member 74 in the form of a clamping flange, and accommodates a parallel arrangement of the two valves 28" and 41", as in the first embodiment shown in Figure 1.
The portion 36" of the delivery passage, which connects the delivery valve 28 ' to the pump working chamber 26, extends through the spigot 25", and, as in the first embodiment, is connected via a connecting bore 45 to the by- pass valve 41' The other portion 37" of the delivery passage connects to both the spring compartment of the delivery valve 28" and the portion 43, in the form of a throttling bore, of the second transverse bore 42 pertaining to the valve 41", which portion 43 is closable by means of the valve member 44 of the second valve assembly 41".
Since, in the case of this embodiment, the valves are not housed in the spigot 25", the latter, and hence also the pump piston 15 arranged axially thereof, may be as small as desired so that the arrangement here shown may be used in particular for smaller sizes of pumps. The pump cylinder 13", which is mounted floatingly on the pump piston 15 and the spigot 25', is clamped in its position shown in the drawing by clamping means (not shown) against a flange 76 of the valve holder 22". Fuel, which may leak between the spigot 25", and the cylinder bore 14 of the pump cylinder 13", flows via grooves 77 in the end face of the pump cylinder 13" into the suction chamber 24.
In the case of all three embodiments of the invention shown in Figures 1 to 4, the pump cylinder 13, 13,13', 13"is prevented from rotating by means of a pin 82 of a screw 83, serving simultaneously as an impact screw, the pin 82 engaging in a groove 81 in the periphery of the pump cylinder, whereby the position of the control ports 49 relative to the control edge 46 of the pump piston 15 is determined.
In the embodiments shown in Figures 2, 3 and 4, in which the pump cylinders 13', 13" are floating cylinders, for basic adjustment of the fuel feed, or in order to achieve controlled adjustment of the fuel feed rate, the pump cylinder 13', 13" can be rotated by means of an eccentrically arranged pin 82 on a correspondingly modified screw 83, or by means of a special adjusting device. In order to permit this rotation, the groove 61 shown, in the periphery of the pump cylinder 13' in
Figure 2, must be correspondingly formed as an annular groove or at least as a portion of an annular groove.
By virtue of the press fit of the spring abutment member 33, which is maintained by the wall of the respective receiving bore and requires no additional securing means, all the embodiments shown provide a realiable highpressure seal, suitable for very high injection pressures, between the pump working chamber 26 and the suction chamber 24, and, in the case of the injection pumps 51 and 71 shown in Figures 2 to 4, except at the connection to the pressure line 39, no other external high-pressure sealing is employed.
For this reason injection pumps according to the present invention are usable for very high injection pressures of over 1000 bar.
WHAT WE CLAIM IS:
1. A fuel injection pump for an internal combustion engine, the pump having a piston axially and rotationally movable in a cylinder provided in a housing, and having a delivery valve arranged between a working chamber of the pump and a delivery line connectible to the injection nozzle, the valve being housed within a valve holder which has a cylindrical surface at least partially fitted into the cylinder end and forming a sealing surface cooperating with a cylindrical counter surface defined by the wall of the cylinder, to provide a high pressure seal for the cylinder, said valve being arranged in a bore in the holder, which bore extends generally transversely of the cylinder axis, from said cylindrical surface, and which bore is connected to the working chamber and to the delivery line by respective portions of a delivery passage.
2. A pump as claimed in claim I wherein the valve comprises a valve seat, a valve closure member, and a spring urging the closure member towards the seat, the spring being seated against an abutment member within the transverse bore, which abutment member is disposed adjacent to the said counter surface of the cylinder.
3. A pump as claimed in claim 1 or 2 wherein the valve holder is clamped directly or indirectly within the cylinder.
4. A pump as claimed in claim I, 2 or 3, in which the piston is provided with a control edge which is angled with respect to the longi
**WARNING** end of DESC field may overlap start of CLMS **.
Claims (17)
1. A fuel injection pump for an internal combustion engine, the pump having a piston axially and rotationally movable in a cylinder provided in a housing, and having a delivery valve arranged between a working chamber of the pump and a delivery line connectible to the injection nozzle, the valve being housed within a valve holder which has a cylindrical surface at least partially fitted into the cylinder end and forming a sealing surface cooperating with a cylindrical counter surface defined by the wall of the cylinder, to provide a high pressure seal for the cylinder, said valve being arranged in a bore in the holder, which bore extends generally transversely of the cylinder axis, from said cylindrical surface, and which bore is connected to the working chamber and to the delivery line by respective portions of a delivery passage.
2. A pump as claimed in claim I wherein the valve comprises a valve seat, a valve closure member, and a spring urging the closure member towards the seat, the spring being seated against an abutment member within the transverse bore, which abutment member is disposed adjacent to the said counter surface of the cylinder.
3. A pump as claimed in claim 1 or 2 wherein the valve holder is clamped directly or indirectly within the cylinder.
4. A pump as claimed in claim I, 2 or 3, in which the piston is provided with a control edge which is angled with respect to the longi
tudinal axis of the piston.
5. A pump as claimed in claim 1,2, 3 or 4, wherein the working chamber, is defined between an end face of the piston and, an end face of a cylindrical spigot, which is inserted with a pressure-tight fit in the cylinder and which comprises a portion of the valve holder accommodating at least that portion of the delivery passage which connects the valve to the working chamber and providing a portion of the sealing surface.
6. A pump as claimed in claim 5, wherein the delivery valve is arranged within the spigot
7. A pump as claimed in claim 5, wherein the valve holder is provided, in addition to the spigot, with a pipe connector providing connection to the delivery line, and with an upper body clamped within a bore of a clamping flange attached to the pump housing.
8. A pump as claimed in claim 7, wherein the delivery valve is arranged within the upper body.
9. A pump as claimed in claim 7 or 8, wherein the upper body is shrunk into the bore of the clamping flange.
10. A pump as claimed in claim 2, wherein the abutment member is a press fit in the transverse bore and is retained therein by the counter surface of the cylinder or is guided in the transverse bore and abuts the counter surface.
11. A pump as claimed in any preceding claim, wherein the valve holder is provided with a second valve arranged in a further transverse bore to provide a return by-pass around the delivery valve.
12. A pump as claimed in claim 11, wherein the axes of the two transverse bores lie in planes so spaced as to leave a minimum wall thickness between these bores.
13. A pump as claimed in claim 11 or 12, wherein the axes of the two transverse bores when viewed in the longitudinal direction of the cylinder are angularly spaced from each other and wherein the working chamber is connected to the delivery line by the delivery passage controlled by the delivery valve and by a further passage controlled by the second valve.
14. A pump as claimed in claim 11 or 12 wherein the axes of the two transverse bores are approximately parallel with each other, the two bores being connected by respective common portions of the delivery passage to the working chamber and to the delivery line.
15. A pump as claimed in claim 14 wherein a spring compartment of the second valve, and a portion of the first transverse bore forming the supply passage to the first valve are connected to the portion of the delivery passage connected to the pump working chamber, and wherein the spring compartment of the first valve, and a portion of the second transverse bore which is closable by means of the closure member of the second valve are connected to the other portion of the delivery passage.
16. A pump as claimed in any preceding claim, wherein the closure member and the spring abutment member of the delivery valve comprise balls.
17. A fuel injection pump constructed substantially as herein particularly described with reference to and as illustrated in Figure 1; Figures 2 and 3; or Figure 4 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19772705489 DE2705489A1 (en) | 1977-02-10 | 1977-02-10 | FUEL INJECTION PUMP FOR COMBUSTION MACHINES |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB1579711A true GB1579711A (en) | 1980-11-26 |
Family
ID=6000775
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB516278A Expired GB1579711A (en) | 1977-02-10 | 1978-02-09 | Fuel injection pumper for internal combustion engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS5399131A (en) |
| DE (1) | DE2705489A1 (en) |
| GB (1) | GB1579711A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2269426A (en) * | 1992-07-31 | 1994-02-09 | Bosch Gmbh Robert | Fuel injection pumps for internal combustion engines |
| US7114928B2 (en) | 2000-04-18 | 2006-10-03 | Toyota Jidosha Kabushiki Kaisha | High-pressure fuel pump and assembly structure of high-pressure pump |
| US7287967B2 (en) | 2000-04-18 | 2007-10-30 | Toyota Jidosha Kabushiki Kaisha | High-pressure pump having small initial axial force of a clamping bolt |
| EP2507505A1 (en) * | 2009-12-01 | 2012-10-10 | Stanadyne Corporation | Common rail fuel pump with combined discharge and overpressure relief valves |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3138409A1 (en) * | 1981-09-26 | 1983-04-21 | Robert Bosch Gmbh, 7000 Stuttgart | "FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES" |
| US4488857A (en) * | 1983-02-17 | 1984-12-18 | Ambac Industries, Incorporated | Mounting arrangement for injection barrel in housing of fuel injection pump |
| IT8553563V0 (en) * | 1985-07-02 | 1985-07-02 | Weber Spa | CONTROL DEVICE FOR FUEL INJECTION DEVICES FOR DIESEL CYCLE ENGINES |
| DE4008071A1 (en) * | 1990-03-14 | 1991-09-19 | Kloeckner Humboldt Deutz Ag | Valve for delivery outlet for fuel injection pump - has valve body which slides in close fitting bush |
| DE4225302C2 (en) * | 1992-07-31 | 2003-05-15 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines |
| DE102005024042A1 (en) * | 2005-05-25 | 2006-11-30 | Robert Bosch Gmbh | Outlet for a high-pressure pump |
| DE102012208106A1 (en) * | 2012-05-15 | 2013-11-21 | Veritas Ag | Pressure holding valve arrangement for a fuel line |
| DE102017211434A1 (en) * | 2017-07-05 | 2019-01-10 | Robert Bosch Gmbh | Connecting piece for a high-pressure fuel pump and high-pressure fuel pump |
| JP6681487B2 (en) * | 2019-02-08 | 2020-04-15 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
-
1977
- 1977-02-10 DE DE19772705489 patent/DE2705489A1/en not_active Withdrawn
-
1978
- 1978-02-08 JP JP1334478A patent/JPS5399131A/en active Pending
- 1978-02-09 GB GB516278A patent/GB1579711A/en not_active Expired
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2269426A (en) * | 1992-07-31 | 1994-02-09 | Bosch Gmbh Robert | Fuel injection pumps for internal combustion engines |
| GB2269426B (en) * | 1992-07-31 | 1995-08-30 | Bosch Gmbh Robert | Fuel injection pumps for internal combustion engines |
| US7114928B2 (en) | 2000-04-18 | 2006-10-03 | Toyota Jidosha Kabushiki Kaisha | High-pressure fuel pump and assembly structure of high-pressure pump |
| CN1298990C (en) * | 2000-04-18 | 2007-02-07 | 丰田自动车株式会社 | High-pressure pump and assembly structure of high-pressure pump |
| US7287967B2 (en) | 2000-04-18 | 2007-10-30 | Toyota Jidosha Kabushiki Kaisha | High-pressure pump having small initial axial force of a clamping bolt |
| CN100436809C (en) * | 2000-04-18 | 2008-11-26 | 丰田自动车株式会社 | High-pressure pump |
| EP2507505A1 (en) * | 2009-12-01 | 2012-10-10 | Stanadyne Corporation | Common rail fuel pump with combined discharge and overpressure relief valves |
| EP2507505A4 (en) * | 2009-12-01 | 2014-02-05 | Stanadyne Corp | Common rail fuel pump with combined discharge and overpressure relief valves |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5399131A (en) | 1978-08-30 |
| DE2705489A1 (en) | 1978-08-17 |
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| Date | Code | Title | Description |
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| PS | Patent sealed | ||
| PCNP | Patent ceased through non-payment of renewal fee |