EP1687524B1 - High pressure feed pump for internal combustion engines - Google Patents

Abstract

The invention relates to a high pressure feed pump (10) comprising a number of pump cylinders (12.1, 12.2) that are fixed to a housing and provided with a cylinder body (16) and admission valves (40.1, 40.2) and discharge valves arranged in the cylinder head (14). The admission valves (40.1, 40.2) of respectively two pump cylinders (12.1, 12.2), in the case of a radial piston pump, or three pump cylinders, in the case of an axial piston pump, that are respectively provided with two plungers (18.1, 18.2) moving out-of-phase in relation to each other about 180 DEG , or about 120 DEG for respectively three plungers, are mechanically interconnected by means of a pivotable rocker (42.1). The position of the rocker (42.1) is controlled by a single actuator (44.1). During the delivery stroke of a plunger (18.1, 18.2), the admission valves (40.1, 40.2) associated with the rocker (42.1) and located in an open position are closed by means of a pulse-type excitation of the actuator (44.1) and a resulting displacement of the rocker (42.1).

Description

The invention relates to a high-pressure feed pump, in particular for an injection system for internal combustion engines, according to the preamble of claim 1.

In CH-A-689 281 discloses a fuel injection system for an internal combustion engine, in particular for a diesel engine, and a method for monitoring the same disclosed. The fuel injection system has for each combustion cylinder at least one controlled by a control unit injection element, which has a leading into the cylinder, closable by this injection port and a pressure chamber arranged in front of the latter. The pressure chamber is connected to a supplied by a fuel pump in response to engine speed, load and load change high pressure part. The injection quantity of the fuel into the combustion cylinder can be supplied by means of a quantity metering device which is preferably connected upstream of the fuel pump and actuated by the control unit. The metering device has a valve which is assigned to a pump piston of the fuel pump.

In the EP-A-1101931 a high-pressure scribe system is described with common rail, which has a provided with at least one outlet channel channel element with opposite end faces. On the front sides are on high-pressure sealing surfaces on the one hand a plunger cylinder of a high-pressure pump and on the other hand connected to a common rail, so that the high-pressure pump via an inlet valve suck in a pumped medium and can introduce with increased pressure through the outlet channel of the channel element and an outlet valve via a drain channel in the space provided in the common rail pressure chamber. The flow rate of the pumped medium to the pump cylinder is controlled by a suction throttle valve projecting into a transfer channel.

The present invention is based on the object to provide a high pressure pump with a precise, reliable and very cost effective flow control.

This object is achieved by means of a high-pressure pump according to claim 1. Particularly preferred embodiments of the invention are specified in the dependent claims.

The high-pressure feed pump according to the invention, which is provided in particular for use in an injection system for internal combustion engines, has at least two delivery chambers delimited by a respective pump cylinder and a driven plunger. The two delivery chambers communicate with a low pressure inlet port via single actuator controlled intake valves and a high pressure exhaust port with a pressure controlled exhaust port. In a preferred embodiment, valve members of the intake valves are connected to each other by means of a rocker pivotally mounted on an actuator shaft of the actuator. Upon energization of the actuator, the actuator shaft is displaced and those intake valves located in an open position closed at where the associated plunger is in a delivery stroke.

The precision of the delivery quantity metering of the high-pressure delivery pump according to the invention corresponds to that of known high-pressure delivery pumps. In the subject invention, however, this is achieved by a smaller number of required actuators with significantly lower material and cost. In addition, the actuator requirements are reduced by operating in a pulsed mode and thus being in an energized state only for a short time. Another factor for reducing costs is the modular design of a preferred embodiment, in which form cylinder heads, cylinder body and a housing for receiving an eccentric shaft stand-alone mounting units, which are pressed tightly by means of bolts by screw. Furthermore, in one embodiment, the housing and the eccentric shaft are designed such that a simple assembly by inserting the eccentric shaft from an end face of the housing is possible in the same.

Fig. 1

einen Längsschnitt durch eine erfindungsgemässe Hochdruckförderpumpe;

Fig. 2

einen Ausschnitt aus der in Fig. 1 gezeigten Hochdruckförderpumpe mit zwei um 180° gegeneinander phasenverschobenen Plungerstellungen und einer Einlassventilsteuerung für beide Pumpzylinder mittels einer Wippe, deren mittlere Auflageposition von einem Aktuator gesteuert ist; und

Fig. 3

einen Querschnitt durch die in Fig. 1 gezeigte Hochdruckförderpumpe entlang der in Fig. 2 angegebenen Schnittebene A.

Particularly preferred embodiments of the inventive high-pressure feed pump are explained below with reference to the drawing. It shows purely schematically:

Fig. 1

a longitudinal section through a high-pressure pump according to the invention;

Fig. 2

a section of the in Fig. 1 shown high-pressure pump with two 180 ° against each other phase-shifted plunger positions and an intake valve control for both Pump cylinder by means of a rocker whose center support position is controlled by an actuator; and

Fig. 3

a cross section through the in Fig. 1 shown high pressure pump along in Fig. 2 specified section plane A.

In Fig. 1 is a longitudinal section of an inventive high-pressure pump 10 in the embodiment of a radial piston pump with four pump cylinders 12.1, 12.2, 12.3, 12.4 shown in a series arrangement. The high-pressure pump 10 is provided for internal combustion engines, in particular for diesel engines with a common rail. Each of the pump cylinders 12.1, 12.2, 12.3, 12.4 has a similar structure and has one of the inner walls of all pump cylinders 12.1, 12.2, 12.3, 12.4 common cylinder head 14, a cylinder body 16 and a plunger 18.1, 18.2, 18.3, 18.4 limited delivery space 20 on. The inner walls of the hollow cylindrical cylinder body 16 are designed as tight sliding fits (2μm to 10μm) for the plunger 18.1, 18.2, 18.3, 18.4. The cylinder body 16 are sandwiched between the cylinder head 14 and the housing 22 by means of bolts 24 and pressed tightly together.

The plungers 18.1, 18.2, 18.3, 18.4 are supported on them by compressive springs 26 against the cylinder body 16 and sit with their Plungerfüssen 27 on a lubricant film sliding on two-piece rolling elements 28. The rolling body 28 surround cylindrical crank bearing 30, which is connected to a drive of the plunger 18.1, 18.2, 18.3, 18.4 serving eccentric shaft 32 rotatable are stored. The two-part crank bearings 30 in turn surround eccentric, which are formed eccentrically offset from the longitudinal axis of the eccentric shaft 32. The eccentric shaft 32 is rotatably mounted on shaft bearings 31 in the housing 22. In the arrangement shown with four pump cylinders 12.1, 12.2, 12.3, 12.4 are each two shaft bearings 31 at the front end portions of the housing 22 and a third shaft bearing between the pumping cylinders 12.2 and 12.3. The eccentric shaft 32 tapers on one side to a protruding from the housing 22, conically shaped drive pin 33. Between the Abwälzkörpern 28 and the crank bearings 30 are also located to reduce friction lubricant films. The lubricant is supplied by a located within the eccentric shaft 32, arranged centrally to its longitudinal axis channel 34 with radial outlets 34 'to the rolling elements 28 and shaft bearings 31. The lubricant collects after lubrication in a lubricant sump 35, from which it in a known manner a not shown lubricant supply is returned.

The plungers 18.1, 18.2, 18.3, 18.4 of the pump cylinders 12.1, 12.2, 12.3, 12.4 differ in their in Fig. 2 illustrated stroke position: the designated 18.1 plunger is located at a bottom dead center at the beginning of the delivery stroke, designated 18.2 at a top dead center at the beginning of the suction stroke, so moved by 180 ° against the stroke position of the plunger 18.1, the designated 18.3 plunger in the middle Förderhubposition, ie 90 ° ahead of the stroke position of the plunger 18.1, and the designated 18.4 plunger in the middle suction stroke position, so moved by 180 ° against the stroke position of the plunger 18.3.

A cylinder head body 36 of the cylinder head 14 has four identical intake valves 40.1, 40.2, 40.3, 40.4, each associated with one of the four pump cylinders 18.1, 18.2, 18.3, 18.4, each having a valve member movably arranged in a cylindrical recess in the form of a valve stem 38.1, 38.2, 38.3 , 38.4 on. For a better overview are in Fig. 1 all intake valves 40.1, 40.2, 40.3, 40.4 shown in their closed position

Two inlet valves 40.1 and 40.2 and 40.3 and 40.4, which are associated with the plungers 18.1 and 18.2 and 18.3 and 18.4, are each actuated via a respective pivotable rocker 42.1 or 42.2. The middle support position of the rocker 42.1, 42.2 is controlled by an actuator 44.1, 44.2.

In the cylinder head body 36 is a longitudinally rectilinear, tubular inlet channel 46, which is connected to the recesses for the inlet valves 40.1, 40.2, 40.3, 40.4 and the supply of a pumped medium 48 is used. The delivery medium 48 is already in the inlet channel 46 under a pressure between 100 kPa and 600 kPa, which has been generated by a not shown prefeed pump.

As for better clarity only in Fig. 3 shown, the cylinder head 14 further per per pump cylinder 12.1, 12.2, 12.3, 12.4 depending on a pressure-controlled outlet valve 50.1, 50.2, 50.3, 50.4 in a corresponding recess. The recesses are connected to a high-pressure outlet channel 52, whose volume forms a pressure accumulator.

In Fig. 2 is an enlarged section of Fig. 1 with two jointly controlled intake valves 40.1, 40.2 shown. Based on Fig. 2 will describe further details of the structure and the operation of the high-pressure pump 10 below. Due to the similar structure, these details as well as their function can be transferred to the not shown part of the high-pressure pump 10.

The delivery chamber 48 of the pump cylinder 12.1, 12.2, 12.3, 12.4 narrows in the direction of the inlet valve 40.1, 40.2, 40.3, 40.4 to a valve seat 56 of the valve stem 38.1, 38.2, 38.3, 38.4 cooperating inlet valve seat 54.1, 54.2, 54.3, 54.4. The valve stem 38.1, 38.2, 38.3, 38.4 is biased at its, the valve plate 56 opposite end portion by means of a compression spring 58 against the cylinder head body 36 in its closed position. In the closed position, the valve plate 56 sits tightly on the inlet valve seat 54.1, 54.2, 54.3, 54.4. and prevents the discharge of the pumped medium 48 from the delivery chamber 20 into the inlet channel 46 or optionally the inlet from the inlet channel 46 into the delivery chamber 20. A on the valve stem 38.1, 38.2, 38.3, 38.4 the valve plate 56 formed opposite hemispherical valve stem 60 is in a cup-shaped valve stem 62 of the rocker 42.1, 42.2 stored. The rocker 42.1, 42.2 has on the same side in the opposite end region a second valve stem receptacle 62 for receiving the associated second valve stem 38.1, 38.2, 38.3, 38.4 of the second inlet valve 40.1, 40.2, 40.3, 40.4. In the center, on the side opposite the valve stem receptacles 62, a hemispherical actuator receptacle 64 is formed on the rocker 42.1, 42.2.

The actuator shaft 66 presses into the actuator receptacle 64.

A positional shift of the rocker 42.1, 42.2 in the direction of the longitudinal axis of the Aktuatorschafts 66 is controlled by the actuator 44.1, 44.2. The actuator shaft 66 is biased against the actuator 44.1, 44.2 in the direction of the open position of the associated intake valves 40.1, 40.2 or 40.3, 40.4 by means of an actuator shaft spring 67 designed as a compression spring. The bias of the Aktuatorschaftfeder 67 is greater than the sum of the oppositely acting biases of the respective associated compression springs 58 of the intake valves 40.1, 40.2 and 40.3, 40.4. The actuator 44.1, 44.2 preferably has an electromagnet; a piezoelectric element would also be conceivable. In the case of an electromagnet, the actuator shaft 66 is formed as an extension of an actuator armature. The actuator 44.1, 44.2 and thus the position of the Aktuatorschafts 66 is influenced by a not shown, preferably electronic control. The actuator 44.1, 44.2 is mounted on a cylinder head cover 68 fastened to the cylinder head 14. The cylinder head cover 68 has centrally a recess through which the actuator shaft 66 is movably passed. The cylinder head cover 68 spans a recess in the cylinder head body 36, in which the valve stem heads 60 emerge with the compression springs 58 and the bearing on the valve stem heads 60 rocker 42.1, 42.2 is located.

Within the pump cylinder 12.1, 12.2, 12.3, 12.4 circumferential, to the plungers 18.1, 18.2, 18.3, 18.4 out open grooves 70 are incorporated with a semicircular cross section. You are with a in Fig. 3 shown return channel 72 and serve to return leakage quantities of the pumped medium 48, which by the close sliding fit of pump cylinders 12.1, 12.2, 12.3, 12.4 and Plungers 18.1, 18.2, 18.3, 18.4 have passed, to a reservoir, not shown, for the pumped medium 48th

On a housing cover 74 with a passage for the drive pin 33, a thrust washer 78 is mounted opposite an outer circumferential shoulder of the eccentric shaft 32. On the opposite side of the housing 22, a further thrust washer 78 supports the end face of the eccentric shaft 32 directly against a further housing cover 74, which is provided with a passage for the supply of lubricant from. The thrust washers 78 are used for the transverse guidance of the eccentric shaft 32 in the housing 22. On the side of the drive pin 33, a circumferential lip seal 80 is connected to the housing cover 74, which prevents leakage of lubricant from the housing 22 by their concerns on the drive pin 31.

In the connecting surfaces between the housing 22 and the cylinder body 16, between the cylinder body 16 and the cylinder head 14 and between the cylinder head body 36 and the cylinder head cover 68 sealing rings 82 are inserted into correspondingly shaped grooves. Due to the strong pressure of the said parts on each other, a tight closure of the high-pressure feed pump 10 is ensured and prevents leakage of the pumped medium 48 or of the lubricant.

The discharge of the pumped medium 48 during the delivery stroke of the plunger 18.1, 18.2, 18.3, 18.4 takes place through the pressure-controlled outlet valves 50.1, 50.2, 50.3, 50.4 in the outlet channel 52. As in Fig. 3 shown, the exhaust valves 50.1, 50.2, 50.3, 50.4 are designed as ball valves known type. A ball 84 is in Pressed their closed position by a biased Auslassdruckfeder 86 in their Auslassventilsitz 88 and closes the high-pressure outlet channel 52 tightly against the delivery chamber 20. If the pressure of the pumped medium 48 in the delivery chamber 20 exceeds the pressure in the outlet channel 52 by one of the bias of the Auslassdruckfeder 86 dependent, in usually very small amount, so the ball 84 lifts from its exhaust valve seat 88 and the fluid 48 escapes into the high pressure exhaust passage 52. The ball 84 is in a cylindrical recess conically narrowing toward the exhaust valve seat 88 between its exhaust valve seat 88 and a conveying-space-side end face of a Ausdruckdruckfeder 86 bearing pin 90 out. The outlet channel 52 is connected to this recess. A plate-like widening 92 of the pin 90 rests on a shoulder 93 in the recess of the housing 22. An Allen screw 94 presses the widening 92 against the shoulder 93 and closes the recess in the housing 22.

The following is the operation of the in Fig. 1 to Fig. 3 Describe high-pressure pump 10 shown. A first plunger 18.1 of a pump cylinder 12.1 is initially in its suction stroke, the associated outlet valve 50.1 in its closed position and the actuator 44.1 in a non-excited state. The associated first inlet valve 54.1 is in the open position during the suction stroke due to the dominant bias of the actuator stem spring 67.

The conveying medium 48, which is already below the pressure generated by an upstream, not shown prefeed pump, is moved from the low-pressure inlet channel 46 through the opened inlet valve 40 Suction chamber 20 sucked. The plunger 18.1 reaches the bottom dead center at the end of its suction stroke. In this, in Fig. 3 shown position of the plunger 18.1, the volume of the conveying space 20 is maximum. In the subsequent delivery stroke, the delivery chamber volume is reduced by the movement of the plunger 18.1 and delivery medium 48 is pushed back through the open inlet valve 40.1 into the inlet channel 46 until the delivery chamber volume corresponds to the desired delivery quantity. By a pulse-like excitation of the actuator 44.1, the actuator shaft 66 is attracted along its longitudinal axis against the bias of the Aktuatorschaftfeder 67 and closed the inlet valve 40.1 at this time. The rocker 42.1 follows this movement due to the bias of the pressure spring 26 mounted on the valve stem 38.1 and the pressure increase subsequently occurring in the pumping chamber 20 as a result of the movement of the plunger 18.1 in the direction of the inlet valve 40.1. As a result, the valve plate 56 of the valve stem 38.1 is pressed against its inlet valve seat 54.1, so that no pumped medium 48 can leave the delivery chamber 20 through the inlet valve 40.1. A second, associated with the same rocker 42.1 inlet valve 40.2 remains in spite of the excitation of the actuator 44.1 in its open position, since the 180 ° out of phase with the first plunger 18.1 moving second plunger 18.2 is in the suction stroke and because of the pressure difference between the low-pressure inlet port 46 and the delivery chamber 20 the valve stem 38.2 while doing in the direction of the conveyor 20 holds open.

After the end of the pulse-like excitation of the actuator 44.1, the first inlet valve 40.1 remains in its closed position until the next following suction stroke. The associated second inlet valve 40.2 is replaced by the Stopping the excitation of the actuator 44.1 is not affected and remains in its open position.

After the plunger 18.1 of the first pump cylinder 12.1 has passed through top dead center and has entered the suction stroke, the first inlet valve 40.1 is opened and the delivery medium 48 is sucked into the delivery chamber 20. The associated second plunger 18.2 passes through the bottom dead center and begins to push the medium 48 back into the inlet channel 46 until the inlet valve 40.2 is closed by means of a renewed pulse-like excitation of the actuator 44.1.

The described mode of operation continues periodically and, by controlling the time from opening to closing of the inlet valves 40.1, 40.2, 40.3, 40.4, makes it possible to control the quantity of the pumped medium 48 forced into the high-pressure outlet channel. The amount in this case ranges from a maximum, namely a delivery chamber volume per plunger period and pump cylinders 12.1, 12.2, 12.3, 12.4, to zero, in which case the inlet valves 40.1, 40.2, 40.3, 40.4 remain open during the entire plunger period. In the latter case, the high pressure pump 10 operates at idle.

In contrast to the above-described operation, in which the flow rate is determined by the closing of the inlet valves 40.1, 40.2, 40.3, 40.4 in the delivery stroke, in a further embodiment, the flow rate by closing the intake valves 40.1, 40.2, 40.3, 40.4 already in the intake stroke be limited. For this purpose, the preloads of the compression springs 58 of the inlet valves 40.1, 40.2, 40.3, 40.4 and the actuator shaft 66 must be adjusted accordingly. The bias of Compression springs 58 must be chosen such that the inlet valves 40.1, 40.2, 40.3, 40.4 can also be closed during the suction stroke. In addition, a modification of the actuators 44.1, 44.2, in particular with regard to longer holding times necessary.

In the Fig. 1 to Fig. 3 As shown, a series arrangement of radial piston pumps can alternatively also be replaced by a boxer arrangement or an arrangement with pump cylinders rotated at an angle about the longitudinal axis of the eccentric shaft.

It is also possible to control with an axial piston pump three pump cylinders with plungers, which are moved with a phase shift of 120 ° to each other, with a single rocker and an actuator. In this case, the rocker is preferably formed star or triangular. Three corresponding valve stem receptacles can be arranged, for example, evenly around a central actuator receptacle. However, the dosage of the flow rate is limited to a range between zero and about 2/3 of the maximum flow before an irregular promotion occurs. The maximum flow rate corresponds to the flow rate in the event that each of the inlet valves is closed at the exact time at which the respective associated plunger passes through its bottom dead center before the subsequent pressure stroke.

In embodiments as a radial or axial piston pump, of course, one or more pairs of pump cylinders or pump cylinder triplets each by means of a common rocker 42.1, 42.2 and a single actuator 44.1, 44.2 operated in the described arrangement.

The plungers 18.1, 18.2, 18.3, 18.4 can also be mounted in a floating manner by means of a pressure compensation for the extremely low-friction movement on the rolling bodies 28. For this purpose, the plunger 18.1, 18.2, 18.3, 18.4 are equipped with hollow shafts, in which stamps are guided freely movable. In a delivery stroke of the plunger 18.1, 18.2, 18.3, 18.4 of the punch is pressed in the direction of the rolling body 28 and located in the hollow shaft lubricant between the plunger 27 and the Abwälzkörper 28 is pressed.

The assembly of the high-pressure pump is particularly simple and inexpensive due to the modular structure of the separately manufactured assembly units cylinder head 14, cylinder body 16 and housing 22. In addition, the possibility for lateral insertion of the eccentric shaft 32 in the housing 22 contributes to ease of assembly.

Claims (12)

1. High-pressure feed pump for an injection system for internal combustion engines, with at least two feed spaces (20) which are delimited by a pumping cylinder (12.1, 12.2, 12.3, 12.4) and by a driven plunger (18.1, 18.2, 18.3, 18.4) which are connected in each case to a low-pressure inlet duct (46) via an inlet valve (40.1, 40.2, 40.3, 40.4) controlled by means of an actuator (44.1, 44.2) and to a high-pressure outlet duct (52) via a pressure-controlled outlet valve (50.1, 50.2, 50.3, 50.4), characterized in that at least two inlet valves (40.1, 40.2, 40.3, 40.4) are controlled by means of a single actuator (44.1, 44.2).
2. High-pressure feed pump according to Claim 1, characterized in that during a suction stroke of the plunger (18.1, 18.2, 18.3, 18.4), with the inlet valve (40.1, 40.2, 40.3, 40.4) open, the feed space (20) is filled completely with a feed medium, and, in the subsequent feed stroke, the feed medium is pressed back again through the open inlet valve (40.1, 40.2, 40.3, 40.4) by the plunger (18.1, 18.2, 18.3, 18.4), until the feed-space volume of the feed space (20) corresponds to a desired feed quantity and the inlet valve (40.1, 40.2, 40.3, 40.4) is closed by means of a preferably pulse-like actuation of the actuator (44.1, 44.2).
3. High-pressure feed pump according to Claim 1 or 2, characterized in that the inlet valves (40.1, 40.2, 40.3, 40.4) and the outlet valves (50.1, 50.2, 50.3, 50.4) are arranged in a cylinder-head body (36) of a cylinder head (14).
4. High-pressure feed pump according to one of Claims 1 to 3, characterized in that the plungers (18.1, 18.2, 18.3, 18.4) assigned to the inlet valves (40.1, 40.2, 40.3, 40.4) controlled by means of the actuator (44.1, 44.2) are driven synchronously, but with a phase shift of preferably 180° or 120° with respect to one another.
5. High-pressure feed pump according to one of Claims 1 to 4, characterized in that each inlet valve (40.1, 40.2, 40.3, 40.4) has a valve member (38.1, 38.2, 38.3, 38.4) cooperating with an inlet-valve seat (54.1, 54.2, 54.3, 54.4), the valve members of the inlet valves (40.1, 40.2, 40.3, 40.4) controlled by means of the actuator (44.1, 44.2) are connected to one another by means of a rocker (42.1, 42.2) pivotable on an actuator stem (66) of the actuator (44.1, 44.2), and the actuator (44.1, 44.2) controls the position of the actuator stem (66).
6. High-pressure feed pump according to Claim 5, characterized in that the valve members (38.1, 38.2, 38.3, 38.4) are prestressed into their closing position.
7. High-pressure feed pump according to Claim 5 or 6, characterized in that the actuator stem (66) is prestressed in the direction of the open position of the valve members (38.1, 38.2, 38.3, 38.4).
8. High-pressure feed pump according to one of Claims 5 to 7, characterized in that, in the event of a displacement of the actuator stem (66) as a result of an excitation of the actuator (44.1, 44.2), the inlet valves (40.1, 40.2, 40.3, 40.4) which are assigned to the rocker (42.1, 42.2) and are in an open position are set into a closing position by pumping cylinders (12.1, 12.2, 12.3, 12.4), the plungers (18.1, 18.2, 18.3, 18.4) of which are in the feed stroke.
9. High-pressure feed pump according to one of Claims 5 to 8, characterized in that the high-pressure feed pump (10) is designed as an axial piston pump and two or three inlet valves (40.1, 40.2, 40.3, 40.4) are controlled by means of a single actuator (44.1, 44.2), in the case of three inlet valves (40.1, 40.2, 40.3, 40.4) the rocker (42.1, 42.2) having three rocker arms arranged in the form of a star.
10. High-pressure feed pump according to one of Claims 1 to 9, characterized in that, for the purpose of quantity metering, the inlet valves (40.1, 40.2, 40.3, 40.4) are set into their closing position during the feed stroke of the plungers (18.1, 18.2, 18.3, 18.4) belonging to them.
11. High-pressure feed pump according to one of Claims 1 to 10, characterized in that the high-pressure feed pump (10) is designed as a radial piston pump, and in each case two inlet valves (40.1, 40.2, 40.3, 40.4) are controlled by means of a single actuator (44.1, 44.2).
12. High-pressure feed pump according to Claim 1, characterized in that the actuator (44.1, 44.2) has an actuator stem (66), the position of which can be influenced and which presses into an actuator receptacle (64) of a pivotable rocker (42.1, 42.2) which is mounted on valve-tappet heads (60) of valve members (38.1, 38.2, 38.3, 38.4) of the inlet valves (40.1, 40.2, 40.3, 40.4) and which is predetermined in each case for actuating two inlet valves (40.1, 40.2; 40.3, 40.4), and in that the actuator (44.1, 44.2) controls a displacement in position of the rocker (42.1, 42.2).

Images