EP0546459B1 - Interrupteur de pression d'huile - Google Patents

Interrupteur de pression d'huile Download PDF

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Publication number
EP0546459B1
EP0546459B1 EP92120688A EP92120688A EP0546459B1 EP 0546459 B1 EP0546459 B1 EP 0546459B1 EP 92120688 A EP92120688 A EP 92120688A EP 92120688 A EP92120688 A EP 92120688A EP 0546459 B1 EP0546459 B1 EP 0546459B1
Authority
EP
European Patent Office
Prior art keywords
oil
control slide
pressure
pressure switch
slide 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
EP92120688A
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German (de)
English (en)
Other versions
EP0546459A1 (fr
Inventor
Max Lüftl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Motorenfabrik Hatz GmbH and Co KG
Original Assignee
Motorenfabrik Hatz GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Motorenfabrik Hatz GmbH and Co KG filed Critical Motorenfabrik Hatz GmbH and Co KG
Publication of EP0546459A1 publication Critical patent/EP0546459A1/fr
Application granted granted Critical
Publication of EP0546459B1 publication Critical patent/EP0546459B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/18—Indicating or safety devices
    • F01M1/20—Indicating or safety devices concerning lubricant pressure
    • F01M1/22—Indicating or safety devices concerning lubricant pressure rendering machines or engines inoperative or idling on pressure failure

Definitions

  • the present invention relates to an oil pressure switch for oil-lubricated engines with a hydraulic work space that can be hydraulically connected to the pressure oil system via a pressure oil inlet, a work element that is biased by means of a spring against the pressure in the hydraulic work space, and a switching element that is coupled to the work element (see DE-A-1115523).
  • Such oil pressure switches are used to switch off the engine when the pressure in the lubricating oil system drops below a permissible value, or at least to indicate the pressure drop via a control lamp.
  • known pressure oil switches are constructed in such a way that the hydraulic working space limited on one side by the working element, in particular a membrane or a piston, is connected to the pressure side of the pressure oil system via the pressure oil inlet. The same pressure is therefore present in the hydraulic work space as at the outlet of the lubricating oil pump.
  • the oil pressure switch, in particular the spring for biasing the working element against the Pressure in the hydraulic work space is designed so that the work element is displaced against the force of the spring when the pressure in the hydraulic work space exceeds a predetermined limit pressure.
  • the movement of the working element is transmitted to the switching element coupled to it; in the event that a fuel shut-off valve is provided as the switching element, it is open when the pressure in the hydraulic work space exceeds the predetermined limit pressure, whereas the fuel valve is closed as long as the pressure in the hydraulic work space is below the predetermined limit pressure.
  • known oil pressure switches are unsatisfactory, especially when used on engines which are operated over a wide speed range. Because while on the one hand the pressure and the throughput in the pressure oil system increase with increasing speed of the pressure oil pump and on the other hand the minimum pressure in the pressure oil system, which is required for damage-free operation of the engine, also depends on the engine speed, known oil pressure switches always switch at the same pressure in the pressure oil system. After the known Oil pressure switch can therefore not take into account the fact that the oil pressure that arises in the damage-free pressure oil system increases with increasing engine speed, the limit pressure at which the oil pressure switch switches must be set so low that the engine is not yet switched off even at minimum speed.
  • the limit pressure of the oil pressure switch is set so that it is below the pressure that is set in a damage-free pressure oil system at the minimum engine speed.
  • the minimum pressure in the lubricating oil system which is required for damage-free operation of the engine at high speeds, is greater than the normal operating pressure in the pressure oil system when the engine is idling, the engine can be damaged if the pressure in the engine is damaged at high engine speeds Pressure oil system drops below the minimum pressure required for damage-free operation at the corresponding speed, but without falling to the set limit pressure. Because in this case the oil pressure switch does not respond.
  • Known oil pressure switches are therefore not able to reliably protect oil-lubricated engines in all operating states Protect damage caused by a drop in the lubricating oil pressure.
  • the present invention is therefore based on the object of providing a generic oil pressure switch which, in all operating states of the engine, prevents its damage as a result of a drop in the lubricating oil pressure.
  • US-A-3 176 672 is also concerned with this task
  • a flow channel through which pressure oil can flow is provided, into which the pressure oil inlet of the hydraulic working space opens, and in the flow channel, between a rest position and a working position, a flow-through control slide is accommodated, which has a bore running in the longitudinal direction an inflow-side inflow opening and an outflow-side outflow opening which is smaller than the inflow opening and has a connecting opening on its circumference, the connecting opening of the control slide connecting the bore to the pressure oil inlet in its working position, and that the control slide by means of a Control spool spring is biased against the direction of flow of the pressure oil flowing through the bore of the control spool, so that in its rest position it releases a hydraulic connection of the pressure oil inlet with the flow channel in the flow direction behind the control spool.
  • the oil pressure switch according to the invention thus has an inlet with which it can be connected to the pressure side of the lubricating oil system, and an outlet through which the oil flowing through the oil pressure switch flows into an unpressurized area, especially into the sump. Since the oil flow through the oil pressure switch depends on the speed of the oil pump, the flow conditions within the oil pressure switch also depend on the oil pump speed and thus on the engine speed. In particular, the pressure conditions within the flow channel and within the bore of the control slide change depending on the oil throughput through the oil pressure switch as a result of the pressure losses dependent on the flow speed.
  • the characteristic curve of the oil pressure switch according to the invention depends in particular on the cross-sectional ratio of the inflow and outflow opening of the control slide and the characteristic of the control slide spring and is designed in individual cases depending on the characteristic which indicates the minimum lubricating oil pressure over the engine speed.
  • the oil pressure switch according to the invention works in such a way that the control spool is moved against the force of the control spool spring as the pressure in the pressure oil system rises as a result of the engine and the lubricating oil pump starting up until the connection opening sweeps over the pressure oil supply to the hydraulic work space and thus the hydraulic work space with the bore of the control spool hydraulic connects.
  • the hydraulic pressure prevailing in the bore of the control slide is acted upon by the hydraulic working chamber, and the working element is moved against the force of the spring that biases it and switches the switching element coupled to it. In this case, the spool takes up its working position.
  • the control slide moves due to the action of the control slide spring in the direction of its rest position until it assumes a new equilibrium state.
  • the equilibrium position of the control spool resulting from the prevailing pressure upstream of the oil pressure switch depends, as already explained, on the throughput of pressure oil through the oil pressure switch, in particular through the control spool, and is therefore a consequence of the engine speed. If the pressure in the pressure oil system falls below the limit pressure dependent on the throughput, the new equilibrium position is so far in the direction of the idle position of the control slide that the connection opening is no longer hydraulically connected to the pressure oil supply.
  • the distance between the connecting opening of the control slide and its end face on the outflow side is approximately the same size as the diameter of the pressure oil inlet. This ensures that the hydraulic working chamber is depressurized almost simultaneously with the interruption of the connection between the hydraulic working chamber and the bore of the control slide, by connecting the pressure oil inlet to the flow channel in the flow direction behind the control slide. This measure promotes the sudden response of the oil pressure switch; a flutter it is surely avoided.
  • the sudden switching of the oil pressure switch can be further promoted by the fact that, in the rest position of the control slide, its bore is connected to the rear of the working element via the connection opening and via a connection channel; as a result, the residual pressure in the lubricating oil system acts on the rear of the working element (piston, membrane or the like) and supports the spring when the working element is displaced in order to actuate the switching element.
  • the space behind the work item i.e. opposite the hydraulic working space is expediently connected to the flow channel in the flow direction behind the control slide via a relief channel.
  • a connection allows the volume enclosed on the rear side of the working element to be compensated for when the working element is displaced as a result of displacement of the oil present there.
  • a control sleeve is preferably provided, in which the flow channel runs and which receives the control slide and the control slide spring. With such a control sleeve the required openings and bores can be produced with less effort than directly in the housing of the oil pressure switch.
  • Such a control sleeve can also serve at the same time to fasten the oil pressure switch to the crankcase of the engine or at another suitable location, in that the control sleeve has an external thread on the portion protruding from the housing of the oil pressure switch, which screwed into an internal thread provided on the crankcase or the like becomes.
  • the same oil pressure switch housing can also be used in this case for different engines with different characteristics of the minimum lubricating oil pressure over the speed, and only the unit comprising the control sleeve, control slide and control slide spring, which is relevant for the characteristic of the oil pressure switch according to the invention, is adapted to the respective engine.
  • the oil pressure switch according to FIGS. 1 and 2 has a housing 1, comprising an upper part 1a and a lower part 1b. Both parts of the housing are connected to one another in that an edge 2 of the upper part is flanged in a manner that overlaps a peripheral edge 3 of the lower part.
  • a membrane 4 is arranged in the parting plane of the upper part and lower part. It is clamped along its circumference between opposing flat surfaces of the upper part and the lower part.
  • the hydraulic working space 5 is located above the membrane, ie bounded by the membrane 4 and the upper part 1a of the housing.
  • the upper part 1 a of the housing is penetrated by the control sleeve 6.
  • This has an inlet 7 and an outlet 8 for the pressure oil, the pressure of which is to be monitored.
  • the control sleeve 6 On the inlet side, the control sleeve 6 has an external thread 9 and on the outlet side a collar 10.
  • the housing of the oil pressure switch can thus be mounted on a crankcase (not shown) by means of the control sleeve.
  • Two seals are provided for sealing, a first seal 11 between the upper part 1a of the housing and the crankcase (not shown) of the engine and a second seal 12 between the upper part 1a of the housing and the collar 10 of the control sleeve 6.
  • the control sleeve 6 is in the area which lies within the hydraulic working space 5, provided with a transverse bore 13 to form a pressure oil supply which connects the hydraulic working space 5 with the interior of the control sleeve 6, ie connects the flow channel for the pressure oil.
  • the control slide 14 is mounted inside the control sleeve 6 so as to be displaceable in the axial direction. It has a bore 15 running in its longitudinal direction with an inflow opening 16 and an outflow opening 17.
  • the inflow opening 16, measured in terms of its area, is approximately 4 times as large as the outflow opening 17.
  • the control slide 14 is pierced transversely to form two connecting openings 18 in the peripheral surface of the control slide.
  • the distance between the connecting openings 18 and the end face 19 of the control slide on the outflow side is slightly smaller than the diameter of the bores 13 in the control sleeve which represent the pressure oil inlet.
  • the control slide spring 21 is tensioned between the downstream face 19 of the control slide 14 and a shoulder 20 inside the control sleeve 6. Falling out of the control slide 14 from the control sleeve at its inlet end is prevented by the projections 22 provided in the inlet 7.
  • the control slide is secured against rotation about its longitudinal axis, so that the bores 13 of the control sleeve and the connecting openings 18 of the control slide are always in the same plane.
  • the working position (Fig. 2) of the control slide (14) is defined by a corresponding stop.
  • a pressure plate 23 is provided, which is fastened on a plunger 24, which is guided in a vertically displaceable manner in the lower part 1b of the housing.
  • the stamp serves to couple the membrane 4, which represents the working element, to the switching element, which is designed as a fuel cut-off valve.
  • an inlet connection 25, an outlet connection 26 and a valve chamber 27 are formed in the lower part 1b of the housing.
  • a pressure ring 28 is provided on the tappet 24, which presses the valve sealing ring 29 against the seat 30 in the locked position of the valve.
  • a compression spring 32 is clamped between the pressure ring 28 and the plug 31 closing the valve chamber 27.
  • This compression spring serves both to close the fuel valve and to bias the membrane 4 against the pressure in the hydraulic working space 5; the characteristic of the compression spring 32 is such that the pressure plate 23 and the plunger 24 are moved downward against the action of the compression spring 32 as soon as the pressure in the hydraulic working space exceeds 0.5 bar.
  • FIG. 1 shows the control spool 14 in its rest position, in which the hydraulic working space is connected via the bores 13 to the region of the flow channel which is behind the control spool 14 and is depressurized
  • FIG. 2 shows the control spool 14 in its working position, in which the hydraulic working chamber 5 is connected to the bore 15 of the control slide via the bores 13 of the control sleeve forming the pressure oil inlet and the connection openings 18 of the control slide.
  • the pressure prevailing in the bore of the control slide thus also acts in the hydraulic working space and presses the diaphragm 4, the pressure plate 23 and the tappet 24 down against the force of the compression spring 32 and opens the fuel valve.
  • the basic construction of the oil pressure switch according to FIGS. 3 and 4 corresponds to that according to FIGS. 1 and 2.
  • a housing 1 is penetrated by a control sleeve 6, which receives a control slide 14 and a control slide spring 21.
  • the hydraulic work space 5 not around the control sleeve 6, but rather it is arranged in the housing 1 at a distance from the bore which receives the control sleeve 6.
  • the pressure oil supply which connects the hydraulic working chamber 5 with the flow channel inside the control sleeve, includes both the transverse bore 13 through the control slide and the bore 33 through the housing.
  • the working element is designed as a piston 34 which is guided in a cylindrical bore 35 in the housing 1.
  • the piston 34 is sealed against the bore 35 by a sealing ring 36.
  • the compression spring 32 acting on the piston 34 is arranged on the rear side thereof and is supported on the end wall 37 of the housing.
  • the space delimited by the piston 34, the cylindrical bore 35 and the end wall 37 of the housing on the rear side of the piston 34 is hydraulically connected to the flow channel downstream of the control slide regardless of the position of the control slide 14, specifically via the holes 38, 39 and 40, the annular groove 41 on the control sleeve, the bores 42, 43 and 44, the circumferential annular groove 45 on the Control sleeve 6 and the transverse bore 46 through the control sleeve.
  • the ends of the bores in the housing are each blocked, the plugs 47 and 48 which block the bores 39 and 43 being visible in FIGS. 3 and 4.
  • the flow path formed by the bores 38, 39 and 40 and the annular groove 41 also connects, in the rest position of the control slide shown in FIG.
  • valve housing 50 In the housing 1, the valve housing 50 is inserted, into which the feed connector 25 and the outlet connector 26 for the fuel opens. Inside the valve housing 50, two sealing sleeves 51 and 52 and a guide 53 for the tappet 24, which is connected to the piston 34, are arranged.
  • the Shut-off valve interrupts the fuel flow through the supply nozzle 25, the valve chamber 27 and the outflow nozzle 26 when the tappet 24 bears against the sealing sleeve 51 due to a drop in pressure in the hydraulic working chamber 5 and the action of the compression spring 32.
  • a start-up device can also be seen from FIGS. 3 and 4, by means of which the fuel shut-off valve can be opened briefly manually in order to flood the injection pump.
  • a release lever 54 is provided in the hydraulic working space, which acts on the end face 55 of the piston 34.
  • the release lever 54 is connected in a rotationally fixed manner to the external actuating lever 56 via a shaft (not shown) which extends through the housing 1.
  • the actuating lever 56 is biased by a spring 57 into the position in which the piston 34 can move freely.
  • control slide 14 While the control slide 14 is in its rest position in FIG. 4 and thus releases a connection between the pressure oil inlet and the flow channel in the flow direction behind the control slide, so that the hydraulic working chamber 5 is depressurized, the control slide is in its working position according to FIG. 4.
  • the bore 15 in the interior of the control slide 14 is connected to the hydraulic working chamber 5 through the housing via the connecting openings 18 and the bores 13 in the control sleeve 6, the circumferential groove 58 and the bore 33 forming the pressure oil inlet.
  • the piston 34 is displaced to the left by the pressure in the hydraulic working space against the force of the compression spring 32, and the tappet 24, which is also displaced to the left, enables fuel to pass through the fuel shut-off valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Hydraulic Motors (AREA)

Claims (10)

  1. Interrupteur à pression d'huile pour des moteurs lubrifiés par de l'huile sous pression, comportant un espace de travail hydraulique (5) apte à être connecté hydrauliquement par une arrivée d'huile sous pression (13,33) à un système à huile sous pression, un élément de travail (4,34) précontraint contre la pression dans l'espace de travail hydraulique (5) au moyen d'un ressort (32) et un élément de commutation couplé avec l'élément de travail (4,34), caractérisé en ce qu'il est prévu un canal d'écoulement (7,8) apte à être traversé par l'huile sous pression, dans lequel débouche l'arrivée d'huile sous pression (13,33) de l'espace de travail hydraulique (5), en ce qu'une vanne-pilote (14) apte à être traversée est reçue de façon mobile longitudinalement dans le canal d'écoulement (7,8) entre une position de repos et une position de travail, ladite vanne-pilote comportant un alésage (15) s'étendant longitudinalement, pourvue d'une ouverture d'afflux (16) aménagée du côté de l'amenée, et d'une ouverture de reflux plus petite (17) aménagée en face de l'ouverture d'afflux, et sur son pourtour une ouverture de liaison (18), l'ouverture de liaison de la vanne-pilote reliant dans sa position de travail l'alésage (15) avec l'arrivée d'huile sous pression (13,33), et en ce que la vanne-pilote (14) est précontrainte au moyen d'un ressort de vanne-pilote (21) en sens opposé à la direction d'écoulement de l'huile sous pression passant à travers l'alésage (15) de la vanne-pilote, de sorte qu'elle libère dans sa position de repos une liaison hydraulique entre l'arrivée d'huile sous pression (13,33) et le canal d'écoulement (8) dans la direction d'écoulement derrière la vanne-pilote (14).
  2. Interrupteur selon la revendication 1, caractérisé en ce que l'espace du côté arrière de l'élément de travail est hydrauliquement relié au canal d'écoulement en direction de l'écoulement derrière la vanne-pilote (14).
  3. Interrupteur selon la revendication 1, caractérisé en ce que la distance entre l'ouverture de liaison (18) et la surface extérieure (19) du côté du reflux de la vanne-pilote (14) correspond pratiquement au diamètre de l'amenée d'huile sous pression dans sa zone avoisinant la vanne-pilote.
  4. Interrupteur selon la revendication 1, caractérisé en ce qu'en position de repos de la vanne-pilote (14), l'alésage (15) aménagé dans sa partie intérieure est hydrauliquement relié par l'ouverture de liaison (18) de même que par d'autres chemins d'écoulement, avec l'espace situé du côté arrière de l'élément de travail.
  5. Interrupteur selon la revendication 1, caractérisé en ce que pour l'élément de travail, un piston (34) guidé dans une ouverture cylindrique (35) est prévu.
  6. Interrupteur selon la revendication 1, caractérisé en ce que l'élément de travail est prévu sous la forme d'une membrane (4).
  7. Interrupteur selon la revendication 1, caractérisé en ce que pour l'élément de commutation est prévue une soupape de blocage de carburant.
  8. Interrupteur selon la revendication 1, caractérisé en ce que pour l'élément de commutation un interrupteur électrique est prévu.
  9. Interrupteur selon la revendication 1, caractérisé en ce qu'une douille de guidage (6) est prévue, dans laquelle s'étend le canal d'écoulement et qui reçoit la vanne-pilote (14) et le ressort de vanne-pilote (21).
  10. Interrupteur selon la revendication 9, caractérisé en ce la douille de guidage (6) passe complètement à travers le boîtier de l'interrupteur et comporte à son extrémité d'afflux, sur le tronçon dépassant du boîtier (1) de l'interrupteur à pression d'huile, un filetage extérieur (9), et à son extrémité opposée un écoulement (8) d'huile sous pression.
EP92120688A 1991-12-11 1992-12-04 Interrupteur de pression d'huile Expired - Lifetime EP0546459B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4140749 1991-12-11
DE4140749A DE4140749C2 (de) 1991-12-11 1991-12-11 Öldruckschalter

Publications (2)

Publication Number Publication Date
EP0546459A1 EP0546459A1 (fr) 1993-06-16
EP0546459B1 true EP0546459B1 (fr) 1995-06-21

Family

ID=6446746

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92120688A Expired - Lifetime EP0546459B1 (fr) 1991-12-11 1992-12-04 Interrupteur de pression d'huile

Country Status (3)

Country Link
EP (1) EP0546459B1 (fr)
JP (1) JP3450021B2 (fr)
DE (2) DE4140749C2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102140947B (zh) * 2011-04-01 2013-12-04 关永友 发动机防烧瓦安全自动保险器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE424589C (de) * 1924-12-29 1926-01-26 Otto Michalk Stroemungsanzeiger, insbesondere fuer OElschmierleitungen
DE1115523B (de) * 1956-05-26 1961-10-19 Messerschmitt Boelkow Blohm Sicherheitsvorrichtung fuer die Schmierung von Brennkraftmaschinen, insbesondere Zweitakt-Otto-Maschinen mit Brennstoffeinspritzung
US3176672A (en) * 1961-11-02 1965-04-06 Gen Motors Corp Low oil pressure sensitive engine governor
DE1476112A1 (de) * 1965-12-30 1969-09-25 Sapp Harold Albert Sicherheitseinrichtung fuer Brennkraftmaschinen
GB2054101A (en) * 1979-07-17 1981-02-11 Prestcold Ltd Differential pressure valve

Also Published As

Publication number Publication date
DE4140749A1 (de) 1993-06-17
EP0546459A1 (fr) 1993-06-16
JP3450021B2 (ja) 2003-09-22
DE59202613D1 (de) 1995-07-27
DE4140749C2 (de) 1994-02-03
JPH05248339A (ja) 1993-09-24

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