DE2322858A1 - DEVICE FOR CHANGING THE INJECTION QUANTITY OF INJECTION PUMP AND INJECTION PUMP - Google Patents

Description

SOCIETE IM) USiCRIELEE GElCERAIiE BE MEOAHIQUE APPLIQÜEE SIff.MA, 89, Boulevard Irdne Joliot-Curie
69 Yenissieux, France

Device for changing the injection quantity of a Injection pump and injection pump

The invention relates to a device for changing the injection quantity per revolution of an injection pump and an injection pump for an internal combustion engine, the injection pump having a fixed base body and a distributor rotatably mounted in the base body, which is supplied by means of one of the motor supplied by the pump, driven shaft is driven, and wherein the pump further comprises at least one pump piston which is slidably mounted in a transverse recess parts formed in one of the of the fixed base body and the drive shaft is disposed, and wherein the piston under aex action is one of the other component accommodated cam is displaceable, and wherein in the fixed base body leading to the injection nozzles of the engine distributor carcasses are provided, which overflow with arranged in the rotatably mounted distributor and interact with the transverse recess, and these overflows opposite to

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the longitudinal axis of the distributor are inclined in such a way that a longitudinal displacement of the distributor leads to a change in the injection rate per pump rotation, and a controller responsive to the speed of the drive shaft is provided to control the longitudinal displacement of the distributor and the latter on the one hand. Influence of the controller is exposed to Druckirdttel and on the other hand the; counteracting influence of an elastic restoring device via a pressure bearing device cooperating with the distributor, and wherein a second elastic restoring device is arranged between the distributor and the pressure means.

The invention relates particularly, but not exclusively, to a device for varying the injection rate per revolution an injection pump for an injection pump of a Kraftf ahrseuges.

The invention is particularly directed to the device to change eier injection quantity per revolution in such a way to design that it reacts better than before to the various load cases occurring in practice and especially in a certain range of rotational speed a change in the injection volume per revolution of the Puir.pe depending on the Rotatlonsgescrv./inuigkeit of the drive shaft allows, according to OaP, in particular one about the nominal torque of the motor lying liotordrehrr.oment can be achieved without that smoke is generated at low speeds.

According to the invention is a device for changing the Injection volume per revolution of an injection pump of the aforementioned type, characterized in that a connecting device is arranged between the distributor, the pressure means and the pressure bearing device in such a way that a

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Shifting the Druckraittel in the longitudinal direction compared to the Druckla .'- fireinrichtung a longitudinal shift dos distributor g3nüb2r der Dru ei: position in a pure direction.

In general, the pressure means are arranged at one end of the distributor, while the pressure bearing device is arranged at the other end of the divider, wherein the connecting device can advantageously have a rod which is at least displaceably connected to the pressure means and is in a longitudinal bore of the distributor can extend to the pressure bearing device and can protrude beyond the distributor in such a way that the rod can cooperate with rolling elements arranged between the pressure bearing device and the adjacent end of the rod, the rolling elements bearing axially against the distributor.

The pressure bearing device is preferably made up of a bearing shell formed, which is freely slidably mounted in a cylinder liner, which in turn is freely rotatable in the manifold is arranged, and this cylinder liner can be connected in the longitudinal direction to the distributor, and the bearing shell can rest against one end of a lever, the other end of which together with the resilient return device of the distributor; Tircenv,? irkt, wherein the bearing shell can have a threatening surface inclined with respect to the distributor axis, while the on at least the end of the rod adjoining the shell a rotating surface inclined with respect to the longitudinal direction aufveis π can, and where the inclined surfaces of the rod and approach the bearing shell in the transverse direction to the distributor axis when they are parallel to the longitudinal direction of the Be moved.

The surfaces of rotation are preferably tapered surfaces and the

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Rollform balls. In addition, the with respect to the axis of the distributor inclined rotational surface of the bearing shell preferably point towards the distributor.

The connection device can be arranged such that a longitudinal displacement of the distributor relative to the thrust bearing device takes place in the opposite direction or in the same direction to the displacement of the pressure medium.

If Iran wants the longitudinal shift of the distributor in relation to the pressure bearing device is to take place in the opposite direction with the displacement of the pressure medium, then the on; approximation of the inclined rotating surfaces, the rod and the bearing shell in the sense of a longitudinal movement away from the distributor.

If the surfaces of rotation are shaped like a truncated cone, what la the previous paragraph has already been mentioned, then that of the horizontal lines of the cone-istuir.pfffläche of the bearing shell formed apex angle greater than that of the generatrix of the truncated cone surface of the adjacent rod end of the rod formed apex angles.

The invention relates also one injection pump, the 1st characterized in that they rJ.t the Brfindungsgernäßen device is provided for varying the injection confinement.

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For more! Ferfcir.ale, details and advantages of the invention result from the following description of an exemplary embodiment using the drawing. Show in it:

Fig. J. an axial section through an injection pump, the wit a compensation device according to the invention fitted

2, 3 and 4 show a part of the compensating device according to the invention in various working positions;

Fig.5 shows the delivery curve per revolution as a function of the rotational speed, which with the compensation device according to the invention according to Figure 2 can be achieved?

6 shows a further exemplary embodiment for the configuration the end of the rod shown in Fig.l to 4;

7 shows a delivery curve per revolution as a function of the speed of rotation that can be achieved with the embodiment shown in FIG is;

8 shows a further embodiment for the in the figures 1 to 4 shown rod and

Finally, FIG. 0 shows the conveying curve per revolution as a function of the rotational speed, which can be achieved with the embodiment of the rod shown in FIG.

In Fig.l it can be seen that the in this embodiment

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Example shown injection pump constructed in a known manner is, e.g. 3. as in DT-PS 1 303 637,.

The pump has a rigid body, which is preferably consists of two coaxially arranged parts la and Ib, and a rotatably mounted distributor or Slide 2, which is in a derr. Base body arranged bore 3 is mounted and driven by a coaxial shaft 4, which in turn is driven by the motor (not shown), which the pump supplies, is driven.

In the bores 6, which have the same diameter and have a common axis, two pump pistons 5 are slidably supported opposite one another, the axis is arranged to the axis of the shaft 4 substantially perpendicular. The sliding movement of the pistons 5 is controlled by a ring cam 7 controlled, which has just as many internal projections as the üotorzyllnder owns, which supplies one after the other should. The pump bushing 6 is with the injection nozzles (which are not shown in the figure) of the motor are correspondingly connected to channels 8 arranged in the base body 1. The pistons 5 are controlled by the squat 7 via rollers 9 and tappets 10 against the action of a return spring 11. This squat can be attached to a protruding, truncated cone trained r] to be flange-mounted part 4a, which forms part of the shaft 4, and the cam can be in one Housing 12 be arranged, through whose bottom part the // all 4 reach through, whereby in the bottom a seal 13 and a ball bearing 14 for supporting the shaft 4 are arranged.

The fuel delivery circuit from the pump bore 6 has a Main pump 15 on, ζ · Β · with a corresponding inner profile, the suction side of which on an inlet flange 16

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connected. The return of this Purape 15 is with the Housing interior 12 connected via a channel 17. Bores 18 arranged in the cone-shaped flange part 4a allow a passage of the pump 15 to the metering bores 22, the number of which corresponds to the number of cylinders of the engine, pumped liquid, the metering bores in a region of a first elongated metering groove 23 in the Bore 3 open, and the metering groove 2 3 in a circumferential Recess. 24 opens, which is arranged in your slide 2 in such a way that it is permanently connected to the pump bores 6 in Connection.

The return circuit from these pump bores 6 is through ei — Ä ne second elongated groove or distribution groove 25 is formed, which starts from a circumferential recess 24 in order to enter the distribution merge channels 8. The metering bores 22 are used at the same time to conduct the fuel and to relieve the Pump and it can be seen from the Pig. 1 that an injection begins at the moment when the connection between a metering bore 22 and the second elongated groove 25 interrupted is, this case occurs when the subsequent metering bore 22 with the first elongated metering groove 23 is connected.

The elongated grooves 23 and 25 are at an angle with respect to the longitudinal direction of the slide 2 according to a helical line arranged in such a way that an elongated displacement of the slide leads to a change in the injection duration so / ie to a change in the injection quantity per revolution of the injection pump.

A centrifugal governor 26, the speed of rotation the drive shaft 4 responds, is to control the longitudinal

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displacement j of the slide 2 is provided, the slide 2 on the one hand the influence of the governor 27 via pressure medium P is exposed and on the other hand the opposite action of a resilient return device R via a Thrust bearing B, the slide 2 ralt interacts. Between a further elastic device 27 formed by a helical spring is provided for the slide 2 and the pressure means P.

The centrifugal governor 26 has flyweights 28 which are pivotably mounted about axes 29 and by means of claws, not shown in the drawing, which cooperate with a recess of a bushing 31, the longitudinal displacements control this socket 31, this socket belonging to the pressure means P. The socket 31 is in a blind hole in the shaft 4 arranged coaxially to the slide 2, one end 2b of the slide engaging in the blind hole of the shaft. The socket 31 has on its inner side a surface 31a which is arranged perpendicular to the socket axis and which during operation opposes the end face f of the slide end 2b comes to rest, as will be explained later.

When the speed of rotation increases, the flyweights 28 move away from the shaft axis 4 and shift the socket 31 and the slide 2 in FIG. 1 from left to right.

The pressure means P with the bushing 31 furthermore have a ring (or a rotor stem) 32 which is inserted between the bushing 31 and the slide is arranged and rotatably fixed to the shaft 4 connected is. In the ring 32 a split pin 33 is arranged perpendicular to the axis of the shaft 4, the ends of which engage in holes, which are provided in the ring. The cotter pin 33 is

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fixed in the longitudinal direction and in the direction of rotation with the ring 32 tied together. The end 2b of the slide 2 is hollow and provided with diametrically opposed Lärigsnuten 34, which preferably run helically and are closed at their ends lying in the longitudinal direction. Through this The cotter pin 33 engages grooves 34.

The outer diameter of the slide end 2b is smaller than the outer diameter of the rest of the slide 2, so that a Shoulder 2c is formed at the junction of these two parts. The spring 27 is between this shoulder 2c and a shoulder is clamped, which is provided on the inside of the ring 32.

The resetting device R is made up of several coil springs formed, which are mounted displaceably between two on a guide rod 37 arranged parallel to the slide 2 Bearing shells 35 and 36 are clamped. The spring tension of the springs R can be adjusted by means of a cam 38, which is rotatably connected to the operating device for the acceleration. The bearing shell 35 supported by the springs R is loaded, rests against the thrust bearing B by means of a cover 35a and a lever or rocker arm 40, which is around an axis 41 arranged between the slide 2 and the spring group R is rotatably mounted. The movement of the bearing shell 35 is delimited by a shoulder 37a of the guide rod 37. The cover 35a can slide on the bearing shell 35, and a spring s, i.e. an overload spring, is arranged between the bearing shell 36 and the cover 35a.

A connection L is arranged between the pressure means P and the pressure bearing B. This connection L has a rod

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42 or a cylindrical tappet, which extends along an elongated cavity 43, which runs through the entire slide 2. The rod 42 ends on the side of the bush 31 in a part 44 which has a larger diameter and through which the cotter pin 33 engages so that the rod 42 is connected to the ring 32 in the longitudinal direction and in the direction of rotation. The part 44 is arranged in the cavity of the sight end 2b.

At the remote from the socket 31 longitudinal end of the Rod 42 this is provided with a lug 45, e.g. is screwed onto the rod and has a larger diameter than the rod and the ineeiher to the bore 43 coaxial Hole in the appropriate end of the slide 2 is provided. This approach 45 runs out into a frustoconical part 46, the rotating surface opposite the longitudinal axis of the slide 2 is inclined, the surface lines of this surface in the extension of the slide 2 converge * The cone-shaped end of the shoulder 45 lies outside d3S slider 2.

The thrust bearing device B is arranged on the side of the slide end 2 which is remote from the bushing 31 and has a bearing shell or a funnel 47 (see FIGS. 2 to 4) against which the end of the lever 40 remote from the springs R rests. On the side facing the slide, this bearing shell 47 has a rotating surface 47a which is inclined with respect to the axial direction of the distributor or slide 2, from which point it is turned.

The bearing shell 47 is freely displaceable in a cylinder liner 48 stored on the adjoining Enae des Schie-

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Ber 2 is freely rotatably mounted by means of a ball bearing 49. In. the bore of the cylinder liner 48, in which the bearing shell 47 can slide, a locking device on one side is provided, which is formed by a snap ring 50 (see FIGS. 2 to 4). This snap ring 50 is inserted into a groove which is arranged in the cylinder liner 48 at the end facing the lever 40. The cylinder liner 48 is firmly connected to the slide 2 in the axial direction ».

Between the bearing shell 47 and the shoulder 45 of the rod 42 For example, roller bodies formed by the balls 51, for example, are arranged in such a way that they open against the truncated cones Surfaces 46, 47a and the front end 2d of the slide 2 run up against. A limit lever 52 acts via a tongue iii with the cylinder liner 48 together.

As can be seen from the following description, works according to the invention, shown in the figures Compensation device such that a longitudinal displacement of the rod 42 by means of the bearing shell or the funnel 47 an opposite displacement of the slide 2iin with respect to the bearing shell 47 causes.

Of course, the approach 45 (or the end of the rod 42) and / or the bearing shell 47 can be arranged differently than described above, namely such that a displacement of the rod 42 relative to the bearing shell 47 is a displacement of the slide effected in the same sense.

In FIG. 6, a projection 45a can be seen which has two frustoconical parts 46a and 46b which converge as an extension of the slide 2. These two frustoconical parts are in the longitudinal direction of a cylinder part 46c

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divided, on the one hand due to the large cross-section
of part 46a and on the other hand to the small cross-section the part 46b. If the balls 51 interact with one of the keo-jtli-tur.pfförriiqen surfaces 46a by 46b, then a longitudinal displacement of the rod and the shoulder 45a with respect to the bearing shell 47 occurs an opposite displacement of the slide 2. If the balls 51 cooperate with the cylinder part 46c, then the slide 2 is not displaced in the longitudinal direction with a longitudinal displacement of the extension 45a with respect to the bearing shell 47.

In Figure 8, an approach 45b can be seen, which differs from
the approach 45a essentially differs in that
the frustoconical part 46b of the projection 45a is replaced by a frustoconical part 46d, the inclination of which is reversed. The surface lines of the frustoconical part 46b thus converge in the direction of the slide 2. The part 46d is extended by a cylinder part 46e like the part 46c in FIG. this cylinder part 46e is in turn extended by a frustoconical part 46f, the surface lines of which converge as the surface lines of the part 46a in FIG.
The extension 45b is therefore barrel-shaped. When the balls 51 interact with the surface 46d, a displacement of the rod 42 with respect to the bearing shell 47 causes a displacement of the slide 2 in the same direction.

The end of the rod 42, which has the approach cooperating with the balls 51, can also have other shapes according to requirements, in particular the eleventh double-cone shape, which is achieved by the
8 reverses slopes of the frustoconical parts of the approach, or such a shape that is achieved thereby

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incea one reverses the slope of the conical shape part 4i> shown in FIGS.

The function of the compensation device according to FIG. ₉ I will now be explained with reference to Έχ <% * 2 to 4 and to the curve shown in FIG. 5. This curve shows the changes in the amount of energy per revolution Q atif the ordinate as a function of the reduction in the speed K of the drive shaft 4 on the abscissa, the speed iam corresponding to a constant factor dox the rotational speed of the motor supplied by the pump.

X ^? For the following explanations, it should be assumed that the cam 38 is rotated counterclockwise and that the bearing shell 36 is pressed against the bearing shell 35 to the extent that it is glued. This state corresponds to full load.

When the engine is started, the cover 35a moves away from the bearing shell 35 by means of the overload spring s # and the lever 40 pushes the slide 2 with maximum force with respect to the ELg.1 to the left. The grooves 23 and 25 provided in the slide 2 are arranged in such a way that the injection quantity per revolution Q 'of the pump also corresponds to a maximum. The point on the curve corresponding to FIG. 5, which shows this operating state of the pump, corresponds to point a, the ordinate value CU corresponding to the injection quantity for the maximum load.

When the rotation speed of the pump increases and the Flyweights 28 move away from slide axis 2, then

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If the slide 2 is a testimony to oils Fig.2 '«rbii liaks aiach right verschc & ren, Me spring 27 has' a larger spring - stiffness than the SfoerlaHtfeder s * so that e'er ring 32, the slide 2, the jam 42 iind the pressure bearing arrangement 3 move * © hme da © a ¥ schiebefo.e> y © giing thisir individual parts against each other, ibis the corner 35a against the bearing shell 35 sur Ajulage teoitant, with the ^ bearing shell given a shoulder 37a of the TührüHgsstaaage 37 with simultaneous Koiripression flar springs R is applied.

f this! 'Teise τ-iorden the slide 2, 42 _# AEIE crate of Hing 32 and the Doacklagereiiiridtitung B from the position shown ia Figure 1 position 5mdie in FIG. 2 shifted dargesfcellteii Ijage. The corresponding operating f> iinks the Feiope in Fig. 5 is the point h with the ordinate value © -, which is under the folder CL, i / o in the "shift of the slide 2 itoü left to right a terrain change is £ ' iii3prit2n: close pra -Uiaäreiung derPöKpe causes * the iibszis-

se: i «- / ert to point h is U ,.

ι ■

If the rotational speed of the pump increases continuously, then the pressure transmitted by the centrifugal governor to the ruckle bush 31 causes the input 32 to be displaced with respect to the thrust bearing unit 3, because the spring 27 has a smaller capacity than the springs R The bearing sheep 47 thus remains immobile in the axial direction until the ring 32 approaches the bearing shell through the spring 27. This displacement of the length 32 causes a Versehiebrjig uer rod 42 and the projection 45 through which these parts also approach the bearing shell 47. The approach 45 and in particular the conical unpiförmlge surface 46 cause the approach to üie

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Bearing shell 47, the balls 53 rise on the tapered flies 47a of the bearing shell 47. During this cleat, the balls 51 press against the face 2c of the slide 2 in such a way that it moves away from the bearing shell 47 by aer. immovable lever 40 is held.

There is therefore a shift of the slide 2 from right to left with respect to the base body 1 and thus about the amount of injection per revolution of the pump. This sewegunc of the slide 2 with respect to the bearing shell 47 is possible until the surface 31a of the bushing 31 corrms against the surface of the slide 2 to abut, as shown in FIG. The corresponding operating point of the pump is-fc ALSC the funct c in Figure 5, the Q of the Oräinaterwert corresponds to _0, which lies between the ordinate values of Q and Q_ and. Since the AbsziEsenwsrt N-, which is larger than the Msscisfcen Vei- "t K ₁ , is assigned. As can be seen in FIGS. 3 and 4, a mirror is present between the ring 50 and the bearing shells 47, Aufgangsspiel j can be seen in Fig. 2.

Since the grooves 34 in which the cotter pin 33 engages, helical are formed, the relative displacement of the Rod 42 and the slide 2 a rotation of the slide et— witness, which is equilateral with its longitudinal displacement er-fo.l ^ t. It follows from it that? not just the amount of injections. pt © Pump rotation is changed, but also the forward shift oöer Rücknahnse of the injection time.

Of course, in the case in which straight grooves 3 H * were used, ie grooves running parallel to the axis of the slide 2, the injection quantity could be changed

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achieve a certain rotation of the slide.

It can be seen that the value Q depends on the position of the metering rod 37 in the longitudinal direction and that the value Q ₂ depends on the; HuId or the shape of the parts 46 or 47a depends. The value Hy depends on the characteristics of the spring s. The difference between the fourth GL and the value Q. i3t depends on the amount of longitudinal displacement JJ ₁ (see FIGS. 2 and 3) that is possible between the bearing shell 47 and the slide 2. The difference between N- and N is essentially dependent on the characteristics of the spring 27 and the shape of the surfaces 46 and 47a. All of these values can be selected or adjusted as required by setting or adjusting the various aforementioned parameters accordingly.

The arcuate course of the curve between points b and σ depends on the shape of the inclined or rising surfaces 46 and 47a. When the speed of rotation of the wool 4 reaches the value IT- (see fig. 5), at which the flyweights 28 transmit a greater force to the slide 2 than the springs R, then the slide 2, the rod 42, the ring move 32 and the bearing shell 47 in a longitudinal view and the injection per revolution of the bottle is reduced until the slide 2 assumes its position, which has been displaced furthest to the right, as shown in FIG. The curve d to e in Fig.5 the Bevecung of the slider 2 from the corresponding in Flg _s position shown in the 3 to represent Fici., Position shown in Figure 4.

7 shows the course of the curve for different injection rates per revolution Q as a function of the change in speed N to be recognized, this curve progression

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can be achieved with a compensating device, the extension 45a of which is designed as shown in FIG. The individual abscissa and ordinate points of this curve shape have the same meaning as the abscissa and ordinate points of the curve described in connection with FIG. It can be seen that the curve sections a ¹ , b ¹ , c ¹ and d ¹ in FIG. 7 are analogous to the curve sections a, b, c, and d of the curve shown in FIG Balls 51 correspond to the surfaces 46a and 46c shown in FIG. The abscissa value of the point d * is denoted by Um.

The curve section d'-k of the curve shown in FIG. 7 means an increase in the injection quantity per revolution as a function of the rotational speed and corresponds to an interaction of the balls 51 with the tapered surface 46b shown in FIG. The ordinate value belonging to the point k is Q. ¹ -, which lies above the ordinate value Qf ₂ · At the speed ^ ' ₃ r that of the abscissa value of the point k. corresponds to «the Iinjection quantity drops.

FIG. 9 shows the course of the curve for different Einoritzr:! Enc; s per revolution, which can be achieved with a compensating device, the extension 45b of which is designed as shown in FIG. The various abscissa and ordinate points of this curve have the same meaning as the abscissa and orcinate points of the curve described in connection with FIG. 5 and are provided with the same reference numerals with two lines. The portions of a ¹ ',' b, c ¹ 'and d ¹ * of the curve geir.äß Fig.9 correspond to the Abfchnitten a, b, c and the curve d in FIG. 5. The portion

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d ^lf -l indicates a decrease in the injection rate per revolution as a function of the speed of rotation and corresponds to a functional interaction of the balls 51 with the surface 4Gd, the slope of which is reversed with respect to the slope of the surface 46 £. The abscissa value of point d '· is N- and the abscissa value of point 1 is N "-, this fourth being above the abscissa _{value N 5.} The ordinate value of point 1 is Q ¹¹ 3 and is below the value Q ¹ * ₂ ·

The compensation device according to the invention, which at the same time forms a device for automatic injection adjustment by the screw-shaped grooves 34 and the cotter pin 33 during the displacement of the ring 32 with respect to the slide cooperate, as well as the other features described above the injection pump, in particular the limiting lever 52 and the device to achieve an overload when starting of the engine, enable at least a certain rotation changes in the injection rate

quantity per pump revolution and, in particular, thanks to an injection quantity above the N'enneinneinritzmenrn, an engine torque which is above the * nominalmor.ent, without the correction shown by the curve bc in FIG. 5 _{at the low rotational speeds between N. and N 3} and the reduction in the injection volume per pump revolutions at these low rotational speeds, smoke is generated.

The amount of injections per pump rotation is limited by means of the lever 52 (niehe Fig.l) by opposing it is threatened clockwise, so that the displacement of the slide 2 in the direction of a limitation of the Einnritz crowd success.

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Claims (10)

Patent claims I, J Device for changing the injection quantity per revolution ^s - * ^/ hung of an injection pump for an internal combustion engine, the injection pump having a fixed base body and a distributor which is rotatably mounted in the base body and which is supplied as one from the engine and from the pump , driven shaft is driven, and v / obai the pump also has at least one pump piston which is slidably mounted in a transverse recess which is arranged in one of the components formed by the base body and the drive shaft, and the piston under the The action of a cam received by the other component is displaceable, and distribution channels leading to the injection nozzles of the motor are provided in the fixed base body, which overflows arranged in the rotatably mounted distributor and interact with the transverse recess, and these overflows gogon over the longitudinal axis of the distributor de are inclined so that a longitudinal displacement of the distributor leads to a change in the injection rate per Pimpcnundrehung, and a controller responsive to the speed of the drive shaft is provided to control the longitudinal displacement of the distributor and the latter - 19 - 309846/0532 copy on the one hand exposed to the influence of the regulator via pressure medium is and on the other hand the opposite acting In-flow of an elastic restoring device via a pressure actuator which interacts with the distributor, and wherein a second elastic restoring device is arranged between the distributor and the pressure means, characterized in that a connecting device L between the distributor (2) and the pressure bags P and the thrust bearing device B arranged in this way is that a displacement of the pressure means P in the longitudinal direction with respect to the pressure bearing device B is a longitudinal displacement of the distributor (2) opposite the thrust bearing device B evokes. 2. Device according to claim 1, at v / elcher the pressure means P are arranged at one end (2b) of the manifold, while the pressure valve B is arranged at the. other distribution menu c. is arranged, marked with # that the connecting device L has a rod (42), which are connected at least displaceably to the pressure means P, clon and located in a longitudinal bore (43) of the distributor extends up to the pressure bearing device B, and protrudes beyond the distributor in such a way that the rod with RcEkör- "pern (51), the z-./ischen the pressure bearing device B and the adjacent Jew of the rod, is arranged, can cooperate, the rolling body (51) axially against the Distributor (2) are in contact 3. Device according to claim 2, characterized in that that the pressure bearing device B is formed by a bearing shell (47) which is freely displaceable in a ' Cylinder liner | 43), which in turn can rotate freely 309846/0532 BAD OBlQiNAt. Jt bar is arranged in the distributor (2), and that this' uylincerbuchse (^ 8) rides in the longitudinal direction of your distributor is connected and the bearing shell (47) anliect against one end of a lever (4O), the other end of which itiit the resilient Resetting device R of the distributor interacts, wherein the bearing shell has a rotating surface (47a) inclined with respect to the distributor axis, while the the rod end adjoining the bearing shell likewise with at least one rotating surface inclined with respect to the longitudinal direction (46), and wherein the inclined surfaces (46,47a) of the rod (42) and the bearing shell (47) extend in the transverse direction approach each other to the distributor axis (2) if they are shifted parallel to the longitudinal direction of the distributor will. 4. Apparatus according to claim 3, characterized in that the inclined surfaces (46,47a) Truncated conical surfaces sine and the rolling bodies (41) of balls are formed. 5. Device according to one of claims 1 to 4, characterized characterized in that the turntables (47a.) of the bearing shell (47) inclined with respect to the distributor axis ζυπ distributor (?.) understands that the approach of the ganei-g- tpn flat (47a), the laying shell (47) and at least one inclined rotating surface (46,46a, 46h, 46f) of the rod (42) ira fjinn a longitudinal locomotion from the distributor, so that the L <m7f? shift the prescaler (2) compared to the pressure bearing device B against the longitudinal displacement of the pressure medium P takes place. - 21 - 309848/0532 BATH ORIGINAL 6. Device according to one of claims 1 to 4, characterized ge characterizing f _ff that the inclined with respect to the distributor axis Drehflciehe (47a) of the bearing shell (47) to the distributor (2) and that the approach of the inclined surface (47a) of the bearing shell ( 47) and at least one inclined rotating flange (4Sb) of the rod £ 42} in the sense of a longitudinal movement to the distributor, so that the longitudinal displacement of the distributor (2) with respect to the printing device § in the same sense as the longitudinal displacement the pressure medium P takes place » 7 · A device according to Ansprüdhsa 4 'and 5, Ge characterized of marking, et _P FCOS äeir Spitz enwinkel that of the generatrices of the Kagelcjtöapffläche C47a) of the cup {47) gebiIslet \ tixdg firög ©? Than that of cladding dea lines practice Kegelstür.ipffia ^ © C4 € _i 46a _# 46b) of the Angren ^ nd the Stance | 421 Spltsscnwinkel formed -1st 8. Device according to ©! .N & i » Um ^ -Ässsprüche I to 7 _t durch- g. & ■ kea px « rejects ₉ Φα & dia Driicksdttel @in «gi Ring-. (32) show "the in Lßsägosräditi ^ f nad in Drehrichtusig" with that of dfur Qruck! ® "p" iimgldfetim <§ B det ^ xaten Ende / ..,. (44) eier rod {A2) r.dtfesls sines splintes (33) vouch. the, the durcli in ä & m delimiting Verteiierende C2b) "UKjeeiräaefc · Länqsxii & k n (M) himäurdigs®lit, YND the" vf @ ite elastic Rüaksttili ^ terishtimg daft of © in @ r screws * £ ÜThe (27) is gebildüt, AT® swisdien dan ring C32) utaä dent distributor (2) is clamped in ^ bo daü der-Ei ^ g (32) and the distributes a © l @ l & tiwb © w®f £ mg in LMngssichtiaig. Ability to exit ^ BATH ORIGINAL 9. Apparatus according to claim 8, characterized in that the arranged in the distributor (2) Grooves (34) are helical. 10. Injection pump for an internal combustion engine with a - fixed base body and a rotatably mounted in the base body driven distributor, which by means of one of the>. Motor powered by the pump. Shaft is driven, and wherein the pump also has at least one pump piston which is slidably mounted in a transversely verlavforden recess which is arranged in one of the components formed by the fixed base body and the drive shaft, and wherein the piston under the action of one of the Another component accommodated cam is displaceable, and v / obei provided in the feston base body leading to the injection nozzles of the riot gate, the i;: it in the rotatably mounted manifold arranged overflows and cooperate with the transverse recess, and these overflows opposite to the longitudinal axis of the distributor are inclined in such a way that a longitudinal displacement of the distributor leads to a change in the fuel quantity per Pvarpenundrehung, and woboi a "". is intended to control the displacement of the distributor and the latter is on the one hand the influence of the regulator via pressure means and on the other hand it is. storage device <j, and a second elastic return device is arranged between the distributor and the ^β Druckrrdtteln, thereby geke η η - - 23 - 309846/0532 αν « draws that the injection pump with a balancing device; rj 9 ^ 1. "ß one of claims 1 to 9 aU3 <jG3tattGt. - 24 - 309846/0532 BATH ORIGINAL