EP0309797B1 - Soupape magnétique - Google Patents

Soupape magnétique Download PDF

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Publication number
EP0309797B1
EP0309797B1 EP88114822A EP88114822A EP0309797B1 EP 0309797 B1 EP0309797 B1 EP 0309797B1 EP 88114822 A EP88114822 A EP 88114822A EP 88114822 A EP88114822 A EP 88114822A EP 0309797 B1 EP0309797 B1 EP 0309797B1
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EP
European Patent Office
Prior art keywords
piston slide
space
bore
annular
electromagnetic valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88114822A
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German (de)
English (en)
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EP0309797A3 (en
EP0309797A2 (fr
Inventor
Ernst Dipl.-Ing. Linder
Helmut Dipl.-Ing. Rembold
Manfred Dipl.-Ing. Ruoff
Walter Schlagmüller
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0309797A3 publication Critical patent/EP0309797A3/de
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Publication of EP0309797B1 publication Critical patent/EP0309797B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means

Definitions

  • the invention is based on a solenoid valve according to the preamble of the main claim.
  • a solenoid valve known from DE-A-3 302 294
  • the two end sides of the piston slide have surfaces of different sizes and each of these end faces encloses a pressure chamber.
  • Both pressure chambers are connected to each other via an axial bore in the piston valve and are each connected to the high-pressure side and to the relief side by throttling play of the adjacent piston guide. Due to the uneven volume change of these pressure chambers during the piston slide stroke, a piston slide movement can only take place if pressure medium also flows in or out via the above-mentioned play.
  • both pressure spaces fill up to the high pressure level.
  • the solenoid valve according to the invention with the features of the characterizing part of claim 1 has the advantage over the prior art that the closing element of the solenoid valve, the piston slide, is pressure-balanced not only in the closed state but also in the opening movement.
  • pressure differences at the spool due to time differences of pressure waves, which are triggered on the fluid to be controlled during the opening and closing process of the spool, are avoided by the relief and reduced in a metered manner at the throttle.
  • FIG. 1 shows the first embodiment of the Invention with coaxial, relieving throttle in the wall of the space enclosed by the second cylindrical part
  • Figure 2 shows a second embodiment of the solenoid valve with a piston valve provided with a longitudinal through-bore, from whose through-bore a relief throttle leads radially to the annular recess
  • Figure 3 shows a third embodiment of the invention Solenoid valve with a piston slide, the second cylindrical part of which forms a throttle gap with the connection bore
  • FIG. 1 shows the first embodiment of the Invention with coaxial, relieving throttle in the wall of the space enclosed by the second cylindrical part
  • Figure 3 shows a third embodiment of the invention Solenoid valve with a piston slide, the second cylindrical part of which forms a throttle gap with the connection bore
  • FIG. 1 shows the first embodiment of the Invention with coaxial, relieving throttle in the wall of the space enclosed by the second cylindrical part
  • Figure 3 shows a third embodiment of the invention Solenoid valve with a piston slide, the second cylindrical part of which forms a
  • FIG 4 shows a fourth exemplary embodiment of the solenoid valve according to the invention, in which only a part of the guide part is exposed to the fluid pressure and the remaining end face is connected to the ambient air via a throttle and
  • Figure 5 shows a fifth embodiment in which the piston valve is sealed by sealing rings and the two front spaces on the piston valve are connected to the ambient air via a throttle.
  • Figure 1 shows the first embodiment of the solenoid valve according to the invention.
  • This has a valve housing 1, which contains a two-stage axial stepped bore with a first stepped bore part 2, which merges with a shoulder 3 lying in a radial plane into the second, middle stepped bore part 4, which in turn merges into the third stepped bore part 5.
  • the transition has a shoulder tapering with a first cone angle ⁇ 1 to the third stepped bore part, which serves as valve seat 7.
  • the third stepped bore part is closed at the end by a plate 8 and has a passage coaxial as a throttle 9.
  • the second stepped bore part 4 serves as a guide bore of a guide part 11 of a piston slide 12, which is connected to the guide part Adjacent has a transition part in the form of an annular recess 14, which forms a sharp sealing edge 15 with the guide part with a diameter corresponding to the guide part diameter, with which the piston slide comes into contact with the valve seat 7 in the closed position.
  • the annular recess 14 extends into the third stepped bore part 5, which forms a connecting bore with a reduced diameter coaxial to the guide bore, and merges there into a second cylindrical part 16 of the piston slide sliding in the coaxial connecting bore.
  • the piston slide has a conical lateral boundary wall of the recess 14 with a second cone angle ⁇ 2 which is greater than the first cone angle ⁇ 1.
  • the sealing line 15 thus always determines the narrowest opening cross section of the solenoid valve.
  • An annular space 17 is formed directly adjacent to the valve seat 7 on the guide bore side, in which the lateral boundary wall forming the valve seat 7, which extends conically with the cone angle 1, and into which the guide bore 4 opens.
  • a connecting line 18 leads radially into the annular space 17 and leads from a high-pressure space, not shown here, which is at least temporarily brought to a high fluid pressure.
  • Such a high-pressure chamber is, in particular, a pump work chamber of a fuel injection pump, in which the high-pressure delivery phase to injectors is controlled by not relieving the pressure on the pump work chamber during the delivery stroke of the pump piston of the fuel injection pump.
  • a pump work chamber of a fuel injection pump in which the high-pressure delivery phase to injectors is controlled by not relieving the pressure on the pump work chamber during the delivery stroke of the pump piston of the fuel injection pump.
  • a relief chamber which can be, for example, the pump suction chamber which is often provided in an injection pump and is located at a low pressure level.
  • the connecting line can also lead to a fluid storage container, in the exemplary embodiment mentioned above to a fuel storage container or to the suction side of a pre-feed pump provided in such fuel injection pumps.
  • the piston slide 12 also has on its guide part 11 an axial threaded bore 20 into which an actuating rod 21 is screwed, to the end of which a flat armature 22 is fastened.
  • the magnetic core 23 with winding 24 of the electromagnet 29, which acts on the armature 22, is inserted in the first stepped bore part adjacent to the shoulder 3.
  • the first stepped bore part is finally sealed by a cover 25.
  • the actuating rod is provided with an axial bore 26, through which a transverse bore 27 leads, which opens in the area of the magnetic core and connects the first stepped bore part 2 and the space 28 delimiting on the end face from the adjacent piston slide 12 with a through channel 30 in the piston slide 12.
  • the through channel opens into the space 31 enclosed by the second cylindrical part 16 in the connection bore 5 and, together with the axial bore 26 or the transverse bore 27, represents a connecting channel between the spaces 31 and 28.
  • a return spring 32 designed as a compression spring, clamped, which moves the spool in the open position of the solenoid valve when the electromagnet is not energized.
  • the open position of the piston slide is limited by a stop 33 formed on the cover 25, against which the actuating rod 21 or the armature 22 comes to rest.
  • the spool is pressure-balanced in its closed position, since the high pressure supplied by the connecting line 18 does not find any axial contact surface in the annular space 17. Since the two end faces of the piston slide are connected to one another by the connecting channel 26, 27, 30, pressure compensation also prevails here.
  • the excited electromagnet 29 therefore only needs to overcome the force of the return spring 32. Moves the return spring 32 den Piston slide in the opening direction, fuel quantities are displaced by the piston slide, which can flow over the connecting channel 26, 30. Since the spaces 31 and 28 are relieved of pressure, no hindering pressures are built up here, but pressure waves are compensated at the throttle 9 provided, so that the piston slide can move continuously into the open position without uncontrolled adjusting movements taking place.
  • a further advantage is that the mass of the solenoid valve which is moved can be kept small with the aid of the through-channel 30 of the axial bore 26. By using the actuating rod, the mass is further reduced and the magnetic core can overlap radially inward, the piston slide 12, which leads to an elongated, compact shape of the solenoid valve.
  • Figure 2 shows a modified solenoid valve with essentially the same parts.
  • the space 31 is no longer relieved of the throttle lying coaxially to the axis of the piston slide but via a throttle 9 ', which is located in the wall of the piston slide 12' and connects the through-channel 30 with the annular recess 14.
  • the actuating rod 21 ' is also formed as a tube with only a slightly smaller diameter than the diameter of the guide member 11.
  • This actuating rod like that of FIG. 1, is made from non-magnetic material in order to prevent sticking to the stop 33.
  • the actuating rod 21 ' has a transverse bore 27 which defines the space 28 with the through-channel 30 or the wide axial bore 26 'connects.
  • the operation of this valve is otherwise the same as in the embodiment of Figure 1.
  • FIG. 3 A more modified form of the solenoid valve is shown in FIG. 3.
  • a two-stage stepped bore is likewise provided in a valve housing 51, the middle or second stepped bore part 54 being designed analogously to the second stepped bore part 4 of FIG. 1. Only here this second stepped bore part is not at the same time the guide part of the spool.
  • the second stepped bore part 54 in turn merges by means of a cone-shaped shoulder, which is designed as a valve seat 57, into a third stepped bore part which, analogously to FIG. 1, forms the coaxial connecting bore 55.
  • this also opens into an adjoining, front-side space 61, which, however, in a departure from the exemplary embodiment according to FIG. 1, is now closed by the housing of an electromagnet 62 with a magnetic core 63 and winding 64.
  • the piston slide 65 in this embodiment has a diameter which is interrupted by an annular recess 66 and thereby separates the piston slide into the guide part 67 and the lower second cylindrical part 68.
  • the guide part 67 is mounted in a bushing 69 which is inserted into the first stepped bore part 52 and projects far into the second stepped bore part 54 with a reduced diameter.
  • the edge between the guide part 67 and a tapered axial boundary of the recess 66 also works together with the valve seat as a sealing edge 70.
  • the piston slide has a part 71 with a reduced diameter which protrudes from the guide bore 73 provided with the inner bore of the bush 69 and carries a spring plate 74 at its end.
  • a return spring 75 is supported on this, which on the other hand rests on the valve housing, especially one supported on the bush 69 stop plate 76, which in turn is held by a cover cap 60 that encloses the valve housing and encloses the space 28 of FIG.
  • the space 61 is connected to the radial recess 79 provided again in the connection bore 55 via a slight reduction in the diameter of the spool to form an annular gap 78. From this an outlet opening 80 of the connecting line 18 leads to the relief space.
  • this connecting line comes from the high-pressure chamber into the second stepped bore part 54, which together with the bush 69 forms the annular space 17 according to the exemplary embodiment according to FIG. 1.
  • the spaces 61 and 72 are still connected to one another by a connecting channel 82, just as the piston slide finally has a through channel 83, which here serves more to reduce the moving mass than the fuel guide and which can be closed on one side, for example.
  • This configuration has the advantage that the piston slide is of very slim design and that the piston slide can be produced from rod material with a few machining steps.
  • FIG essentially a training course from Figure 2 is, only one of the rooms with fuel.
  • a flat recess 86 is provided in the end piece of the guide bore 4 ', in which a round cord ring 87 is mounted, which comes with its inner contour to the actuating rod 21 ⁇ , which is carried out analogously to that of Figure 2.
  • the space 89 enclosed between the round cord ring 87 and the remaining, annular end face 88 between the actuating rod 21stange and the outer circumference of the guide part 11 is relieved via the transverse bore 27 branching off here to the axial bore 26 ⁇ , which merges into the through-channel 30 of the piston slide 12 ⁇ .
  • the space 31 enclosed by the second cylindrical part 16, into which the through hole 30 opens, is relieved via opening 90.
  • the armature-side end of the actuating rod 21 ⁇ is sealed by a likewise non-magnetic disc 92.
  • the space 28 'adjoining the round cord ring 87 on the armature side is relieved of ambient air via a throttle 93 in the cover 33'. If necessary, a filter 94 can be connected upstream.
  • This configuration has the advantage that the large-area armature 22 is no longer moved in a hydraulically damped manner in fluidic medium but in air, so that substantially lower restoring moments act on the piston slide and its actuating speed can be increased.
  • the round cord ring 87 provided for sealing is easily movable in the flat recess 86. Because of its free support, it can perform a flexing movement during the axial stroke of the piston valve, from which only slight counter-forces result, which therefore do not impair the movement of the piston valve. This type of installation is possible because there are practically no high pressures at the installation location.
  • a further development of the training according to FIG. 4 is shown.
  • the Round cord ring 87 is provided on the guide bore 4 'and the space on the armature side is relieved thereof via the throttle 93.
  • This measure of making one end-side space 28 "air-filled and relieving the atmosphere is carried on in the exemplary embodiment according to FIG. 5 at the other end of the piston valve 12"".
  • an annular flat recess 96 is also provided at the end of the connection bore 5" , into which a second round cord ring 97 is fitted, which here lies with its inside at the end of the second cylindrical part 16 in a sealing manner.
  • the disk 92 "which closes the axial bore 26" in the exemplary embodiment according to FIG.
  • the spool has a very low moving mass and can be brought into its end positions very quickly in conjunction with the low displacement forces.
  • part 71 of the piston slide has a plate-shaped stop 104 which, like the spring plate 74, can be screwed onto part 71 and is adjustably fixed there.
  • the stop 104 is between the Arranged spring plate and the end of part 71 and projects radially beyond spring plate 74.
  • the cover cap 60 has a cylindrical inner circumferential wall 105 which is provided with a thread 106 into which an adjustable annular stop 103 is screwed. At this stop, a second spring plate 101 comes into contact on the guide bore side, between which and the stop plate 76 a second compression spring 100 is clamped.
  • the piston slide is in the open position when the magnet is not energized. It is held in this by the return spring 75, a shoulder 108 between the guide part 67 and part 71 coming to rest against the stop plate 76.
  • the piston slide is displaced axially against the force of the return spring 75 in the closing direction until it comes to rest against the spring plate 101 with the adjustable stop 104.
  • This position brings about a partial closing position of the solenoid valve, in which, in a throttled manner, fluid can flow away via the connecting line 18 for partial relief. From a second excitation level of the magnet, the biasing force of the second spring 100 is then overcome and the piston slide is brought into the closed position.
  • This embodiment has the advantage that a large relief cross-section of the connecting line 18 during the suction and control phase z. B. a pump workspace is available. This results in quick relief and, when used with fuel injection pumps, also by relieving the pressure on the pump workspace, an exact end to the high-pressure delivery phase. If the connecting line also serves as a filling line for the pump work area, the large connecting cross-section with the solenoid valve fully open provides a large overflow cross-section that ensures good filling of the Pump work space guaranteed. At the beginning of the delivery stroke of the pump piston of an assigned fuel injection pump, the connecting line can initially be partially closed for the start of injection and then closed completely to determine the actual start of the high-pressure delivery phase of the pump piston.
  • the connecting line 18 can be switched very large, since it is not the total stroke of the piston slide that is used to determine the start of the high-pressure delivery phase. Because of the large overflow cross sections, the connecting line can advantageously also be used in principle as a filling line.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (11)

  1. Soupape électromagnétique pour commander le passage d'une conduite de liaison (18) entre un volume à haute pression qui est au moins mis de temps à autre à haute pression du fluide, notamment d'une chambre de travail d'une pompe d'injection de carburant et d'une chambre basse pression, avec un boîtier de soupape (1) contenant un alésage de guidage (4, 73) qui débouche dans un volume annulaire (17) dont la paroi limite latérale opposée à l'alésage de guidage (4, 73) et dirigée dans la direction axiale, est réalisée sous la forme d'un siège de soupape (7) qui se rétrécit suivant une forme conique avec un premier angle de cône alpha 1 vers un perçage de raccordement (5), coaxial par rapport à l'alésage de guidage (4, 73) et dont le diamètre est réduit par rapport à celui de l'alésage de guidage, un tiroir rotatif (12, 67) dont le diamètre présente des gradins et qui sert d'organe d'obturation de la soupape, ce tiroir étant coulissé par un électro-aimant (29) contre la force développée par un ressort de rappel (32) et comporte une pièce de guidage (11) guidée dans l'alésage de guidage et une pièce cylindrique (16) pénétrant dans le perçage de raccordement, en étant séparée de la pièce de guidage (11) par une cavité annulaire (14), la paroi limite latérale de la cavité étant inclinée de façon tronconique vers la pièce de guidage (11) et arrive avec un second angle de cône alpha 2 supérieur au premier angle de cône alpha 1 et la ligne de jonction entre la pièce de guidage (11) et la paroi limite latérale de la cavité (14) forme l'arête d'étanchéité (15) par laquelle le tiroir rotatif vient dans sa position de fermeture en appui contre le siège de soupape (7), la face frontale de la pièce cylindrique (16) délimitant un volume (31) dans le boîtier de soupape (1) qui est relié par un canal de liaison (30, 26) à un volume (28, 72) délimité frontalement par la pièce de guidage (11) et qui est relié à un volume de décharge par un organe d'étranglement (9, 9', 78, 93), avec en outre un orifice d'entrée de la conduite de liaison (18) venant de la chambre de haute pression dans la paroi du volume annulaire (18) et un orifice de sortie de la paroi du perçage de raccordement (5, 55) dans la zone de recouvrement de celui-ci avec la cavité annulaire (14, 66) et une butée axiale (33) contre laquelle peut venir le tiroir rotatif en position d'ouverture lorsque l'arête d'étanchéité (15) est dégagée du siège de soupape (7, 57), caractérisée en ce que les volumes (31, 28, 61, 72, 31, 28") délimités par les faces frontales du tiroir rotatif dans le boîtier de soupape (1) sont déchargés en pression et le tiroir à piston est sollicité vers la position d'ouverture par des ressorts de rappel (32).
  2. Soupape électromagnétique selon la revendication 1, caractérisée en ce que le tiroir rotatif comporte un canal traversant (30, 26) qui relie les faces frontales du tiroir rotatif et l'organe d'étranglement (9) est réalisé comme perçage d'étranglement dans la fermeture frontale du perçage de raccordement (5) (figure 1).
  3. Soupape électromagnétique selon la revendication 1, caractérisée en ce que les volumes (61, 69) sont reliés par un intervalle annulaire (78) qui forme l'organe d'étranglement entre la seconde partie cylindrique (68) et le perçage de raccordement (55) avec la cavité annulaire (66) (figure 3).
  4. Soupape électromagnétique selon la revendication 1, caractérisée en ce que le tiroir rotatif comporte un canal traversant (30, 26) qui relie entre elles les faces frontales du tiroir rotatif et l'organe d'étranglement (9') est prévu dans un perçage de liaison entre le canal traversant (30) et la cavité annulaire (14) (figure 2).
  5. Soupape électromagnétique selon la revendication 2, caractérisée en ce que le ressort de rappel ( 32) est logé dans une cavité axiale (30) de la seconde partie cylindrique (16), entre cette partie et un élément de fermeture (8) frontal du perçage de raccordement (5) (figures 1, 2, 4, 5).
  6. Soupape électromagnétique selon l'une des revendications 1 à 4, caractérisée en ce que le ressort de rappel (75) s'appuie sur une coupelle à ressort (74) prévue à l'extrémité d'une partie (71) de l'alésage de guidage (67) du tiroir rotatif, sortant de l'alésage de guidage (73) et en ce que l'extrémité opposée du tiroir rotatif subit l'action de l'induit (77) de l'électro-aimant (figure 3).
  7. Soupape électromagnétique selon l'une des revendications 1 à 4, caractérisée en ce que l'extrémité de l'alésage de guidage (4') non tournée vers le volume annulaire (17) comporte une cavité (86) aplatie, annulaire recevant une bague de rétreint (87) qui peut s'y déplacer alternativement dans la direction axiale avec une légère déformation, et qui s'applique par ailleurs par son diamètre intérieur contre une partie cylindrique (21") sortant de l'alésage de guidage et appartenant au tiroir rotatif, cette partie ayant un diamètre réduit par rapport à la partie de guidage (11) du tiroir rotatif, et comporte un canal de liaison (27) entre l'appui de l'anneau de rétreint (87) et la pièce de guidage (11), canal qui part du volume (31) délimité par la face frontale du tiroir rotatif tournée vers le perçage de raccordement (figures 4 et 5).
  8. Soupape électromagnétique selon la revendication 7, caractérisée en ce que le tiroir rotatif comporte une cavité (30, 26) traversante axialement, la partie cylindrique (21") en saillie étant reliée à l'induit (22) de l'électro-aimant (13) en étant fermée à sa face frontale et le volume (28") qui reçoit l'induit (22) et les électro-aimants est relié à l'air ambiant par un organe d'étranglement (93) (figure 4).
  9. Soupape électromagnétique selon la revendication 1, caractérisée en ce que l'extrémité de l'alésage de guidage (4') non tournée vers le volume annulaire (17) comporte une cavité (6) aplatie, annulaire qui reçoit un anneau de rétreint (87) mobile axialement de façon alternative avec une faible déformation et qui s'applique par ailleurs par son diamètre intérieur contre une partie cylindrique (22") du tiroir rotatif, partie qui sort de l'alésage de guidage, cette partie ayant un diamètre réduit par rapport à la partie de guidage (11) du tiroir rotatif, et comporte un canal de liaison entre l'appui de l'anneau de rétreint (87) et la pièce de guidage (11), canal qui conduit à un volume d'évacuation et l'extrémité du perçage de raccordement (5") opposée au volume annulaire (17) présente une cavité aplatie (96) annulaire qui reçoit un second anneau de rétreint (97) mobile axialement de façon alternative avec une légère déformation et qui par ailleurs s'applique par son diamètre intérieur contre l'extrémité de la seconde partie cylindrique (16) coulissante dans le perçage de raccordement (5") et le volume (98) emprisonné par l'anneau de rétreint du côté du volume annulaire est relié au volume d'évacuation par un canal de liaison (figure 5).
  10. Soupape électromagnétique selon la revendication 9, caractérisée en ce que le tiroir rotatif comporte une cavité axiale traversante (30, 26") et l'induit (22) de l'électro-aimant est fixé à la partie cylindrique (21"), le volume (28") qui reçoit l'induit et l'aimant étant relié à l'air extérieur par un organe d'étranglement (93) (figure 5).
  11. Soupape électromagnétique selon l'une des revendications précédentes, caractérisée en ce qu'en plus du ressort de rappel (32), il est prévu un second ressort (100) monté entre une pièce fixe (76) du boîtier de la soupape électromagnétique et une coupelle à ressort (101) qui s'appuie sur le boîtier de la soupape électromagnétique par une butée (103) réglable, et qui à partir d'une certaine course partielle du tiroir rotatif dans le sens de la fermeture vient en appui contre une butée (104) du tiroir rotatif et qui peut se soulever de la partie fixe pour la partie restante de la course de fermeture du tiroir rotatif.
EP88114822A 1987-09-26 1988-09-09 Soupape magnétique Expired - Lifetime EP0309797B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873732553 DE3732553A1 (de) 1987-09-26 1987-09-26 Magnetventil
DE3732553 1987-09-26

Publications (3)

Publication Number Publication Date
EP0309797A2 EP0309797A2 (fr) 1989-04-05
EP0309797A3 EP0309797A3 (en) 1990-05-09
EP0309797B1 true EP0309797B1 (fr) 1992-05-06

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Family Applications (1)

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EP88114822A Expired - Lifetime EP0309797B1 (fr) 1987-09-26 1988-09-09 Soupape magnétique

Country Status (4)

Country Link
US (1) US4832312A (fr)
EP (1) EP0309797B1 (fr)
JP (1) JP2635717B2 (fr)
DE (2) DE3732553A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0580325A1 (fr) * 1992-07-23 1994-01-26 Zexel Corporation Dispositif d'injection de combustible
EP0588475A2 (fr) * 1992-07-23 1994-03-23 Zexel Corporation Dispositif d'injection de combustible
GB2285305A (en) * 1993-12-16 1995-07-05 Daimler Benz Ag Pressure-compensated solenoid valve
US5476245A (en) * 1993-12-13 1995-12-19 Mercedes-Benz Ag Pressure-compensated solenoid valve
EP0840004A1 (fr) 1996-11-04 1998-05-06 Robert Bosch Gmbh Soupape électromagnétique
AU709936B2 (en) * 1995-12-19 1999-09-09 Frank Stuart Curnow Shut-off valves
DE4238727C2 (de) * 1992-11-17 2001-09-20 Bosch Gmbh Robert Magnetventil

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4142998C1 (fr) * 1991-12-24 1993-07-22 Robert Bosch Gmbh, 7000 Stuttgart, De
GB9203636D0 (en) * 1992-02-19 1992-04-08 Lucas Ind Plc Fuel pumping apparatus
DE9202519U1 (de) 1992-02-27 1992-05-14 Lanny, Michael, 7547 Wildbad Ventil
US5386965A (en) * 1993-06-04 1995-02-07 Ber-Lo Manufacturing Company, Inc. High pressure flow valve with pressure assist valve seal
DE4322546A1 (de) * 1993-07-07 1995-01-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
GB9322850D0 (en) * 1993-11-05 1993-12-22 Lucas Ind Plc Control valve
JP3142038B2 (ja) * 1993-12-03 2001-03-07 株式会社デンソー 電磁弁
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US4832312A (en) 1989-05-23
JPH01113570A (ja) 1989-05-02
EP0309797A3 (en) 1990-05-09
EP0309797A2 (fr) 1989-04-05
JP2635717B2 (ja) 1997-07-30
DE3732553A1 (de) 1989-04-13
DE3870789D1 (de) 1992-06-11

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