DE7001414U - DEVICE FOR REGULATING THE FUEL SUPPLY TO AN COMBUSTION MACHINE DEPENDING ON THE PRESSURE CONDITIONS OF THE PRESSURE CIRCULATING LUBRICATION. - Google Patents

Description

Patent attorneys
Dr. Ing.Waller Abitz Dr. Dieter V-. M ort
Dr. H ar. cA. Era .s

8 Munich S6, Pieiuenauerstr.ae

January 16, 1970 P-

SENTINEL DISTRIBUTORS, INC. 7815 West I6th Avenue, Denver, Colorado, V.St.A.

Device for regulating the supply of fuel to a Internal combustion engine as a function of the pressure conditions of the pressure circulation lubrication of the same

The invention relates to safety devices for parking of internal combustion engines under abnormal pressure conditions in the lubrication systems of such machines and in particular a protective device that serves to control the fuel supply to switch off an engine automatically when the pressure of the oil lubrication of the engine or one driven by the engine Machine drops to an undesirably low value.

The invention consists in a device for regulating the fuel supply to an internal combustion engine as a function of the pressure conditions, dia in pressure circulating lubrication

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prevail, and has a cylindrical body with an axially extending bore and radially extending Fuel inlet and outlet ports leading into the bore open to a valve in the bore to regulate the flow of fuel arranged between the inlet and outlet channels is, a piston which is arranged in the bore for axial movement therein and <* has a piston rod which attack the valve and open it when de *. ' Piston is moved in one direction, which piston has a bottom in a part of the bore that is the valve is turned away, is axially movable, means by which the piston head is exposed to the pressure existing in the lubrication system what pressure acts on the piston head in such a direction that the piston is moved into a position in which the piston rod opens the valve, and a spring arrangement, by means of which an elastic force is exerted on the piston against the force exerted by the lubricant pressure exerts on the piston crown, with dif> invention differs from the known in that a device is provided through welc.ie an area within the piston is exposed to the pressure of the fuel that passes through the bore between the fuel inlet and fuel outlet ducts flows, which area is arranged so that the fuel pressure exerted on this the spring 'in their Counteraction against the force that is exerted on the piston crown by the lubricant pressure is supported.

A number of pressure dependent engine fuel shut-off devices of this general type have been developed in the past, of which those described in U.S. Patent 3,202,143 come closest to the present invention. In these Dekannten devices of the fuel flow to the engine is controlled by a valve that _s v.ird normally held by a piston in a Offenetellung that in the Ventilöffnungeriohtung n by d 'movable pressure

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that prevails in the lubrication system and in the opposite Direction to allow the valve to close, by springs of best in under constant, their Strength is chosen so that the basic setting of the oil pressure level is achieved at which the fuel shut-off valve closes.

Although the valve piston described in the aforementioned patent are shown to be exposed to the pressure of the fuel against the oil pressure to a lesser extent, so that if the fuel pressure increases, the oil pressure level at which the fuel shut-off takes place, slightly higher than the The basic setting is by the springs, the structural and dimensional restrictions do not allow that known by these Devices the desired change in the oil pressure cut-off point in relation to the changes in the fuel pressure is achieved, especially in the case of the newer models of diesel engines with the low Oil pressure at idle speeds.

The invention solves this problem by providing a surface within the valve control piston against which the fuel pressure is exerted against the force exerted against the piston by the oil pressure. To this Way can get the desired relationship between oil pressure and fuel pressure at the time of fuel cut can be achieved without the external design or the external dimensions of the piston and that associated therewith Elements need to be changed.

For a better understanding of the invention, it is illustrated by means of the accompanying drawings using several embodiments described in more detail v * nd indeed seigon?

1 shows a schematic side view in elevation of an internal combustion engine with fuel injection or

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P-251 » ⁽ J.

of the diesel type with an inventive oil pressure-dependent engine shut-off device;

Figure 2 is a front view, partly in elevation and partly in vertical section, a preferred embodiment of an inventive pressure-controlled, piston-operated, Liquid fuel ball valve that opens on its seat or in its closed position is shown;

3 is a view in vertical section of the valve according to FIG Fig. 2 with certain parts shown in full lines and the valve in its fully open Position is shown;

H shows a side view on an enlarged scale and partially in section, the piston and the piston rod for the valve shown in Figures 2 and 3;

FIG. 5 is a view in horizontal section of the piston with piston rod according to FIG. 4, the section being essentially is guided according to the line 5-5 in Fig. U, and

Fig. 6 is a side view, partly in section, of a ♦ Another embodiment of the piston according to the invention with piston rod.

Reference is first made to FIG. 1, in which the illustrated motor protection device is an oil pressure-controlled device Motor Abscellvorrichtung or a valve A has, with the • an internal combustion engine E of the Dieeelbauart with a conventional fuel pump F and an oil pump 0 is equipped. For the sake of simplicity, the security

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Device A hereinafter referred to as the oil monitor.

According to the invention, the inlet side of the oil monitor A is with the pressure side of the fuel pump F through a line 4 connected and connected to the pressure side of the oil pump 0 through a line 5. Fuel is supplied to the pump F by a not shown Fuel tank is supplied via a line 6 and arrives from the oil monitor A via a line ~ to the injection nozzles of the engine, which are generally designated by v, The oil pump 0 sucks oil from the sump 9 of the engine E and conveys this to the inlet side of the oil monitor A via the line 5, whereby the oil outlet channel of the oil monitor A through a plug 10 is closed when it is without a temperature controlled shut-off device or a heat monitor according to U.S. Patent 3,202,113 is used.

With regard to FIGS. 2 and 3, the oil pressure-controlled fuel shut-off valve according to the invention or the oil monitor according to the invention is essentially of the same design as shown in FIGS. and piston rod assembly. As shown, the oil monitor has a cylindrical metal body 11, preferably made of anodized aluminum, of very sturdy construction and provided with an axially extending bore of varying diameter. The upper part 12 of the bore is slightly longer and of nsm generally smaller diameter than the lower part 13, which extends to the lower end of the body 11 and forms a chamber I ¹ * of relatively large cross-section. Jas upper end of the bore portion 12 opens into a arweiterts counterbore, which has approximately the same diameter as the chamber 1 ^ ¹ and is provided with an internal thread 15 °. The lower end of the chamber Ik is countersunk in a similar manner and has an internal thread 16 of the same diameter.

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P-254 ι!

knife and the same pitch as the thread 15 provided so that the two ends of the body 11 by two similar Threaded caps 17, 17 can be completed. Each cap 17 is provided with a suitable sealing element 18, for example provided with a rubber or neoprene ring.

The upper part of the bore is indicated generally at 12 and is further divided into three communicating chambers of shorter length. The uppermost chamber is a combined fuel inlet and fuel valve chamber 19, the lower end of which has a conical or conical valve seat 20 which serves to accommodate a metallic or neoprene ball check valve 21 which is held elastically on its seat by a compression spring 22. The spring 22 is preferably made of stainless steel to the adverse effect of a chemical attack egg contaminated fuels ¹ turn on this. The valve body 11 is formed adjacent its upper end with a radially extending and threaded fuel inlet channel 23 which is in communication with the chamber 19. Immediately below the fuel inlet and valve chamber 19 is an intermediate fuel channel and a fuel outlet chamber 24 of smaller diameter than the chamber 19, the body 11 being provided with a radially extending and threaded fuel outlet channel 25, which is provided with the aforementioned chamber

24 communicates. The inlet and outlet channels 23 and

25 are preferably diametrically aligned in a common vertical plane but offset horizontally, as in FIG Fig. 2 and 3 shown. A third chamber 26 “that forms the lower end of the bore part 12 and serves as a piston chamber, as will be described below, is with both the lower part of the chamber 2 · * as well as with the enlarged one Chamber 14 at the lower end of the valve body in connection.

The fuel β inlaßkanuner ¹ 19, which are used to absorb power

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P-2 514 / '//

Fuel from the fuel pump F via the inlet channel 23 and the hose or flexible pipe 4, which is connected to this by a connecting piece 28, serves as the fuel from the chamber 2 "* via the outlet channel 25 via a similar line or hose 7 and a connecting piece 30 is fed to the injection nozzles 8 of the engine E, to which the tflwächter A is assigned. The fuel flow from the inlet channel 2 3 to the outlet channel 2 5 via the chambers 19 and 24 is regulated by the action of a ball valve 21 which can be moved upward into the open position by the piston rod 31 of an actuating piston 32 which is located in the lowest chamber 26 of the Bore part 12 is slidably disposed therein for vertical axial movement under the influence of oppositely directed forces, as will be described below. Since ^a ball valve 21 is pushed untnn in the closed position on its seat 20 by the spring 22 _f when the piston 32 at the bottom. The end of its stroke is, as shown in Fig. 2, whereby a communication between the chambers 19 and 24 is prevented and thereby the fuel flow to the engine E is shut off. The piston rod 31 has a much smaller diameter than the fuel channel chamber 24, so that the fuel can flow freely from the inlet channel 23 to the outlet channel 25 when the piston is moved upwards to lift the ball valve 21 from its seat

With the lower end of the piston 32, an enlarged piston head 33 is connected, which in the chamber 14, which through the lower bore portion 13 is formed, is slidably disposed. For lifting the piston and opening the valve 21, the underside of the piston head 33 is the pressure of the. the chamber 14 through the lubricating oil pump 0 (Fig. 1) over «inside Inlet channel 34 exposed to a connection piece 35 and an oil supply line 5 connected to it.

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P-25U., "

Although the oil line 5 in any suitable manner with the pressure circulating lubrication of the engine E, which with the oil monitor A, it can also be connected to the lubrication system of a motor-driven auxiliary device, for example a compressor, as in 8 of U.S. Patent 3,202,143. In the latter case, the oil pressure supplied to the chamber IU is the same as that existing in the last-mentioned lubrication system of the auxiliary device.

In order to elastically resist the upward valve opening movement of the ball valve 21 caused by the oil pressure in the chamber It and that to support the self-actuated renewed closing of the valve, if the oil pressure drops to an undesirably low value, the compression spring 22 is provided, as mentioned, their lower end presses against the ball valve 21, while its upper end in a recess or depression 38 in the · Cap part 17 is seated. The force exerted on the ball valve 21 can be varied by using springs of various kinds Strength can be adjusted.

A second compression spring 39 surrounds the piston rod 31 of the piston 32, is supported at its upper end against a constricted shoulder UO, which divides the chambers 2U and 26, and presses at its lower end against the actuating piston 32, as shown in FIGS. The force exerted on the actuating piston 32 by the spring 39 can also by using springs of different strengths can be adjusted. The compression spring 39 is supported by the pressure of the fuel * in the chamber 2U, as follows described, to move the piston 32 forcibly downwards so that the spring 22 can close the valve, when the oil pressure in the chamber IU drops below the desired target point. The piston 32 and the piston crown 33

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P-254 , ff- : I. * 1 - m »*» Sealing rings 41 are with Krafts ¹ * and oil-resistant and 42 provided.

From the above and from the description below it results that the fuel valve 21 in a raised Position is held that a free flow of fuel from the inlet channel 23 through the chambers 19 and 24 to the outlet channel 25, as long as the oil pressure in the lubrication system of the Motor (or the associated driven auxiliary device) and is held in the mentioned chamber 14 at the value or above the value which is caused by the joint force of the Springs 22 and 39 and is determined by the fuel pressure in the chamber 24.

The fuel valve of the oil monitor A can be partially opened by hand when the oil pressure in the chamber 14 is insufficient to raise the valve to its fully open position. Such a hand-operated organ is particularly advantageous if the safety device according to the invention is used in conjunction with an engine with a compressor is used because it is often desirable to operate the engine with the compressor switched off, among which Conditions where the oil pressure in the compressor's lubrication system does not hold the ball valve 21 in its open position and the fuel supply to the engine would be cut off would,

As shown in FIGS. 2 and 3, the manually operable member for opening the fuel valve 21 has an eccentric one Cam disk 43, which is arranged in the chamber 14 below the piston head 33 at the inner end of a shaft 44 is. The shaft 44 extends from the valve body 11 through a bushing 46 radially outward, which in the aforementioned Body at a point approximately in the middle between the oil inlet & channel 34 and a diametrically opposite oil outlet

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Channel 48 is screwed in, the latter being closed as shown by a plug 10, when the Ülwüchter are used in conjunction with one or more temperature-controlled shutdown devices or heat guards, as shown in Figs. 1 and 9 of US Pat. No. 3,202,143 should, the plug 10 can be replaced by a suitable connector to which an oil line is connected.

The cam 43 is attached to the end of the shaft 44 by an adjusting screw 57 in such a position that it is located directly below the central part of the piston crown 33. The cam 43 is on the shaft 44 so directed that when the piston 32 is at the lower end of its stroke in the valve closing position, the is shown in Fig. 2, the underside of the piston head 33 rests on the deep part of the cam.

The outer end of the shaft 44 is provided with an actuating handle 50 which is guided through a diametrically extending opening in the shaft and is fastened in this in any suitable manner, for example by means of an adjusting screw (not shown). A clockwise rotation of the handle and the shaft through an angle of 180 ° has the consequence that the cam is rotated so that the flattened high part of the same comes into contact with the piston head 33, whereby the piston 32 counter to that exerted by the spring 39, downward elastic force is raised. It is not necessary that the stroke of the cam plate 43 will be adequate in size, in order to raise the piston 32 over its full stroke so that the ball valve is moved to its fully open position 21, as long as it is sufficient _s to open the valve part, since under such conditions the engine E is not fully loaded.

For the automatic return of the cam 43 in the

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tig. 2 and 3 indicated position in which they the valve closing filler of the piston 32, the shaft HH is surrounded by a torsion spring 52, one end of which is at a pin 53 is anchored, which is attached to the valve housing 11 and protrudes axially outward from this, while the other end is hooked around the handle 50 as shown at 54. The ends of the spring 52 are arranged and the spring is wound in such a direction that the spring is tensioned by turning the Welj.e 44 clockwise will. As a result, after the shaft 44 has been turned clockwise by 180 ° from that shown in FIG. 2 by the handle 50 Position has been rotated, the spring 52 is loaded so that, as soon as the oil pressure in the chamber 14 is sufficiently high, in order to lift the piston crown 33 out of contact with the flattened high part of the cam disk 43, the spring 52 itself actively rotates the shaft 44 counterclockwise to return the cam disk 43 to its normal position. In this context it should be mentioned that as long as the. downward force exerted on piston 32 is the upward force exerted on piston head 33 by the oil pressure in chamber 14 exceeds the friction One rotation of the shaft is sufficient between the underside of the piston crown and the high part of the cam and to prevent the cam under the influence of the torsion spring.

The rotational movement of the cam disk 43 and the shaft 44 is limited to the desired angle of 180 ° by a limiting pin 55 which is attached to the shaft 44 and protrudes transversely from this. The pin 55 is arranged so that when the cam 43 is in its normal position is located, the pin 55 ^ .η a lower stop pin SB is applied, which from the valve body 11 is substantially in a vertical Auefluohtvmg with the spring anchoring pin 53 radially sticks out. To lift the piston through the cam is

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it is only necessary to rotate the shaft 44 until the Limiting pin 55 comes to rest on pin 53, which a "\ ch serves as an upper stop pin.

The oil monitor described above in connection with FIGS. 2 and 3 is of the same design and mode of operation such as that described in U.S. Patent 3,202,143. However, as best shown in FIG. U - 6, the Piston 32 and the piston rod 31 of the inventive Device depends on the corresponding elements according to the said patent in a way that improved results and results in a more versatile mechanism «

From Fig. U and 5, in conjunction with Figs. 2 and 3, it follows that that the upper part of the piston 32 with a calibration axially extending Recess or depression 60 is provided, which can be drilled so that a conical base surface 61 is obtained which is opposite to the surface of the bottle bottom 33 on which the oil pressure is exerted. The piston rod 31 is formed from a steel tube and is provided with a slot 62 which runs the full length of the rod extends so that the C-shaped cross shown in Fig. 5 » cut results. The lower end of the rod 31 extends into the piston recess 60 in which it is press fit.

• With the training described, of course, the fuel, which flows through the chamber 24 between the fuel inlet and outlet channels 23 and 25, into the interior of rod 31 through slot 62, down to the bottom of recess 60 and against the base surface 61 exert a pressure that supports the springs 22 and 39, the piston 32 against the piston head 33 exerted oil pressure to push down «Since the pressure of the fuel flowing through the chamber 24 on its way to the Motor passes through, calibrate with the motor speed and load

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If this pressure is applied to the inner surface 61 of the piston 32, the oil pressure level is automatically changed changes j at which the fuel cut-off takes place, whereby this is raised above the primary switch-off point, which is determined by springs 2 2 and 39, so that the likelihood of damage to the engine is reduced if the oil pressure becomes undesirable low value drops.

When doing this an inner surface of the piston the fuel pressure any desired ratio between the fuel pressure and the oil pressure shut-off valve can be achieved can be achieved without changing the external design or dimensioning of the piston and the piston rod will. Another advantage of the design shown is that the oil monitor from the US Pat. No. 3,202,113 disclosed type, which is already used, can be converted to obtain the desired results for For many purposes it is only necessary to featen theirs Replace piston rods with slotted ones without any further changes.

If desired, a larger area ---! for the fuel pressure application to achieve, as in the piston with the piston rods of FIG, U is provided by the base surface 61 of the recess 60 _9, the modified construction can of FIG. 6 are used as shown in Fig. 6, the piston 32 ° separately formed by the piston head 33 and provided with a countersunk recess 6 3 which is connected to the recess 60, the outer surface of the lower end of the piston 32 'having an A' male thread for releasable engagement with an internal thread 64 in the piston head 33 'is provided. Of? Fuel pressure is now exerted against the base 6 5 of the Eintis £ ing 63, the exposed area of which can be changed in order to achieve the desired fuel

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pressure / oil pressure ratio by changing the diameter the depression.

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Claims (1)

Device for regulating the fuel supply to an internal combustion engine as a function of the pressure conditions of the pressure circulating lubrication of the same, adt a »cylindrical body which has an axially extending bore and radially extending fuel inlet and outlet channels which open into the aforementioned bore, a valve which is arranged in the bore for regulating the fuel flow between the inlet and outlet channels, a piston which is arranged in the bore for axial movement therein with a piston rod, which the latter serves to grip the valve and to open this ₅ when the piston moves in one direction wi /> d, which piston has an axially movable head in a part of the bore facing away from the valve, means by which the piston head can be subjected to pressure, which consists in the lubrication system, which pressure acts on the piston crown in such a direction that the piston moves in an S position is moved, in which the piston rod opens the valve, and a spring arrangement, for exerting an elastic force on the piston which is opposite to the force which is exerted on the piston head by the lubricant pressure, characterized by means through which a surface (61, 65) within the piston (32, 32 ') is exposed to the pressure of the fuel flowing through the bore (19, 2t +) between the fuel inlet and outlet channels (2 3, 25), which surface is so arranged that the fuel exerted on them - 15 - 700141Ai8.11. 71 pressure causes the spring arrangement (22, 39) to be supported which the piston head (33, 33 '} through the force exerted against the lubricant pressure Device according to Claim 1, characterized in that the piston (32, 32) has a recess (60) with a base surface (61, 65) which is opposite to the surface of the piston crown (33, 33 ') on which the lubricant pressure is exercised, and the piston rod (31) has a passage (62) through the fuel from the BcVrung (19, 2U) between the fuel inlet and Outlet channels (23, 25) can flow to the deepening. Device according to Claim 2, characterized in that the piston rod (31) extends into the recess (60). stretches, whereby the pressure of the fuel in the bore between the fuel inlet and outlet channels (23, 25) through the passage t & 2) to the base surface (61, 65) the deepening is transferable. Device according to claim 2 or 3, characterized in that the passage (62) in the piston rod (31) has the shape of a longitudinal slot in the piston rod wall, one end of the piston rod being press fit into the recess (6o) of the piston. 5. Device according to claims 2 - H \ characterized in that the piston (32 ') has an inner recess (63) - 16 - 700141418.11.71 having which with the recess (60) in connection stands and has a larger diameter than this, which recess (63) has a base surface (6S), which is opposite to the surface of the piston crown (33 *) on which the lubricant pressure is exerted, into which recess (63) fuel from the bore between the fuel inlet and outlet channels (23, 25) flows. 6. Apparatus according to claim 5, characterized in that the part of the piston (32 *) in which the recess (60) and the inner recess (63) are formed, is detachably connected to the piston crown « - 17 - 700141418.11.71