KR102216495B1 - Fuel pump for fueling an internal combustion piston engine - Google Patents

Abstract

The present invention relates to a fuel pump 10 for supplying fuel to an internal combustion piston engine, the fuel pump 10 having a body 18 and a cylindrical space 30 having a central axis 32 within the body, And a piston member (28) arranged to reciprocate within the cylindrical space (30), wherein the piston member includes a sleeve member (46) having a closed end arranged in the second space section (30''). Provided, wherein an annular space is provided between the sleeve member 46 and the piston member 28, wherein the pump comprises an annular gap at least partially surrounding the piston member 28, the sleeve member being annular Arranged to extend into the gap, the third space section 60 is arranged bounded by a sleeve member 46, and the third space section 60 is provided with a lubricant supply channel 62 and a lubricant discharge channel 64. Connected.

Description

Fuel pump for fueling an internal combustion piston engine

The present invention relates to a fuel pump for supplying fuel to an internal combustion piston engine, the fuel pump comprising a body and a cylindrical space having a central axis within the body, and a piston member arranged to reciprocate within the cylindrical space. Wherein the cylindrical space comprises a first space section having a first diameter, wherein the wall of the cylindrical space and the wall of the piston member are relative to each other so that the wall of the cylindrical space guides the piston member within the body. A first end of a piston member arranged to provide a first sealing gap, wherein the first space section forms a first pumping chamber of a pump configured to pump the fuel as the piston reciprocates within the cylindrical space. Bounded by

Internal combustion piston engines need to be provided with one or more fuel pumps. In particular, fuel injection into the engine's fuel chamber in so-called common rail systems requires the ability to pump fuel even at high pressures in excess of 250 MPa. As the pump is typically lubricated by the engine's lubricating oil, the presence of both fuel and lubricating oil in the pump may require special attention, particularly with regard to preventing or minimizing mixing of fuel and lubricant in the pump.

Document EP 0976926 B1 discloses an integrated pump and tappet unit for supplying fuel to an internal combustion engine such as a large diesel engine, wherein the unit is a tappet in which the axial movement is influenced by the movement of the cam surface provided on the camshaft, etc. A body portion surrounding the member, and a piston member operatively connected to the tappet member and arranged to pump fuel under high pressure from a fuel chamber arranged within the body portion. The body portion is a single member accommodating both the tappet member and the fuel chamber, and the tappet member and the piston member are connected to each other by tappet arms sealed to the flange member fixed to the body portion, so that the fuel from the fuel chamber contacts the tappet member. Is prevented.

Document DE 102015002304 A1 discloses a high pressure fuel pump. The literature does not mention the possible leakage of fuel into the lubricating oil, but shows the lubrication system of the pump. The pump includes a pump housing having an inner space, a pump plunger having a guide surface guided from the inner space of the pump housing, a lubricant line open to the inner space opposite the guide surface of the pearlunger, and ventilation through which the lubricant can be discharged from the spring chamber. A pipe, wherein the inner space and the pump plunger define a spring chamber of the high pressure fuel pump.

Document DE 102008042067 A1 discloses a drive shaft with an eccentric cam, and a pump with a piston housed in the cylinder. The document discloses a circular membrane seal used to separate fuel and lubrication systems from each other.

Document DE 102006059333 A1 discloses a fuel pump comprising at least one wiper element incorporated in the pump piston for removing leaking fuel collected between the pump piston and the pump cylinder from the cylinder wall. The wiper element is a scraper ring that removes leaking fuel that accumulates in the wall of the pump cylinder and guides it to at least one leaking groove.

US 7308849 defines a working chamber and is also driven indirectly by the drive shaft in a reciprocating motion against the force of the restoring spring. The pump piston is braced at least indirectly to the drive shaft through a sleeve such as a tappet, and a restoring spring engages at least the pump piston. The support element in the tappet braces the pump piston towards the drive shaft and is also at least indirectly braced at the drive shaft. The restoring spring engages the pump piston and tappet via a spring plate. The spring plate is elastically deformable in the direction of motion of the pump piston such that, as a result of the elastic deformation, the deviation in the position of the contact surface on the pump piston and on the tappet is compensated.

WO 2011160908 A1 discloses a pump comprising at least one pump element having a pump piston driven at least indirectly in stroke movement by a drive shaft. A plunger with a plunger body is arranged between the drive shaft and the pump piston, and is also movably guided in the receiving device in the direction of stroke movement of the pump piston, and is also supported on the drive shaft by a support element. The lubricant is supplied to the receiving device via a supply line, and the lubricant is also guided to the support element via a discharge line from the receiving device to the plunger body. An annular gap filter is provided between the plunger body and the receiving device, and is further arranged between a supply line for supplying lubricant to the receiving device and a discharge line for discharging lubricant to the plunger body.

It is an object of the present invention to provide a fuel pump for supplying fuel to an internal combustion piston engine, the performance of which is significantly improved over prior art solutions.

The objects of the present invention can be fulfilled substantially as disclosed in the independent claims and in other claims which set out the details of different embodiments of the invention.

A fuel pump for supplying fuel to an internal combustion piston engine includes a body and a cylindrical space arranged in the body and having a central axis, and a piston member arranged to reciprocate within the cylindrical space, the cylindrical space having a first diameter A first space section having a first space section, wherein the wall of the cylindrical space and the wall of the piston member are arranged relative to each other such that the wall of the cylindrical space guides the piston member within the body to provide a first sealing gap, And the first spatial section is bounded by a first end of the piston member forming a first pumping chamber of the fuel pump configured to pump fuel as the piston member reciprocates within the cylindrical space. . The piston member is provided with a sleeve member extending toward the first end of the piston member, so that an annular space is provided between the sleeve member and the piston member, and the annular space extends to the first end of the piston member. The inner wall of the second spatial section and the radial outer wall of the sleeve member are arranged relative to each other so that the inner wall of the second spatial section guides the sleeve member within the second spatial section Providing a gap, and an annular third spatial section arranged into the fuel pump, the third spatial section being arranged to extend into the annular third spatial section and to the inner wall of the second spatial section and the sleeve member And a lubricant supply channel and a lubricant discharge channel are connected to the third space section.

According to an embodiment of the present invention, in the second space section, a second pumping chamber of the fuel pump configured to pump fuel material from the second space section as the piston member reciprocates within the cylindrical space. Is provided.

According to an embodiment of the invention, the second space section is provided with a second pumping chamber of the pump configured to pump fuel from the second space section as the piston member reciprocates within the space, The pump includes a ventilation flow path connecting the second spatial section to the outside of the body to allow gas inflow into the second spatial section driven by the reciprocating motion of the piston member, and from the second spatial section. An exhaust flow path is provided connecting the second space section to the outside of the body for transporting fuel material away.

According to an embodiment of the invention, the vent flow path is provided with a one-way valve that allows flow towards the second space section.

According to an embodiment of the invention, the discharge flow path is provided with a one-way valve that allows flow away from the second spatial section.

According to an embodiment of the present invention, the annular gap in the second spatial section comprises at least partially forming the first spatial section such that the annular gap and the first spatial section overlap each other in the direction of the central axis of the cylindrical space. Surround

According to an embodiment of the present invention, the pump is provided with a cylindrical extension coaxial with the first space section forming an annular gap surrounding the piston member, and the sleeve member comprises an inner wall of the second space section and the cylindrical extension Arranged to extend into the annular gap between the parts.

According to an embodiment of the present invention, the cylindrical extension is a bushing removably attached to the body of the pump.

The present invention is suitable for use as a high pressure pump in a common rail fuel system.

The exemplary embodiments of the invention presented in this patent application should not be construed as limiting the applicability of the appended claims. The verb "comprises" is used in this patent application as an open limitation that does not exclude the presence of features not also presented. Features set forth in the dependent claims are freely combinable with each other unless otherwise specified. New features considered as features of the invention are set out in particular in the appended claims.

In the following, the present invention will be described with reference to the accompanying exemplary and schematic drawings.

1 shows a fuel pump unit according to an embodiment of the present invention.
2 shows a fuel pump according to another embodiment of the present invention.
3 shows a fuel pump according to a further alternative embodiment of the invention.
4 shows a fuel pump according to a further alternative embodiment of the invention.

1 schematically shows a fuel pump 10 configured to supply fuel to an internal combustion piston engine. More specifically, the pump is a high pressure pump configured to deliver fuel at a pressure in excess of 200 MPa. The pump 10 is provided with a supply rail 12 and a high pressure rail 14, and both the supply rail 12 and the high pressure rail 14 are a first pump arranged in the body 18 of the pump 10 It is connected to the chamber 16. The body 18 comprising the pump chamber 16 may also be referred to as the barrel of the pump 10. The supply rail 12 is connected to the pump chamber 16 via an intake conduit 20. The high pressure rail is connected to the pump chamber 16 via an outlet conduit 22. The intake conduit 20 is provided with a one-way valve 24 configured to allow fuel to flow only from the supply rail 12 to the pump chamber 16. Respectively, the outlet conduit 22 is provided with a one-way valve 26 configured to allow fuel to flow only from the pump chamber 16 to the high pressure rail 14. In the embodiment shown in FIG. 1, the supply rail 12 and the high pressure rail 14 are integrated into the body 18, but it is conceivable that the rails are outside the body 18.

In addition, the pump 10 is provided with a piston member 28 arranged into a cylindrical space 30 arranged into the body 18. The cylindrical space 30 has a central axis 32 and the cylindrical space 30 is substantially rotationally symmetric with respect to the central axis 32. Therefore, the piston member 28 is also rotationally symmetric about the central axis 32. The external shape of the body can also be designed as required. The piston member 28 is arranged into the space in a reciprocable manner. The piston member 28 has a first end 28', at its end, abutting a cylindrical space 30 forming the first pumping chamber 16. The piston also has a second end 28 ″ opposite the first end 28 ′. The piston member 28 is configured to reciprocate and pump fuel within the space 30 provided for the piston member 28. The reciprocating movement of the piston member together with the one-way valves 24 and 26 in this way provides a pumping effect of the fuel pump. The piston member 28 is advantageously an assembly of several parts, which is shown here such that the first end 28 ′ and the second end 28 ″ are separate parts removably connected to each other.

The cylindrical space 30 comprises a first space section 30' having a first diameter D1. In the first space section 30 ′, the wall of the space section and the wall of the piston member 28 are arranged relative to each other to provide a first sealing gap 34 between the walls, which also provides a piston in the body 18 Guide member 28. Additionally, the walls of the first space section guide the piston member within the body 18 while it reciprocates in the space. The piston member 28 comprises a first portion arranged in the first space section 30' and also has a diameter substantially equal to the first diameter so that the desired guidance and sealing is provided.

The cylindrical space 30 also comprises a second space section 30'' having a second diameter D2 that is larger than the first diameter D1. The second spatial section 30 ″ is on the same central axis as the first spatial section 30 ′. The piston member 28 comprises a second portion arranged in the second spatial section 30 ″ so that the desired guidance and sealing is provided. In the second spatial section 30 ″, the wall of the second spatial section and the wall of the piston member 28 are arranged relative to each other to provide a second sealing gap 35 between the walls, respectively. Additionally, the wall of the second space section guides the piston member in a second portion within the body 18 while the piston member reciprocates in the space.

There is a second pump chamber 16 ′ arranged on the body 18 of the pump 10. The second pump chamber 16' is connected with the second space section 30 ″ such that the second pump chamber 16 ′ is configured to use the empty space of the second space section 30 ″ as a pump chamber. And arranged. The piston member 28 is arranged to be in contact with both the first pump chamber 16 and the second pump chamber 16'.

The piston member 28 and the first pump chamber and the second pump chamber are arranged in such a way that, while the piston member moves in one direction, the volumes of the first pump chamber and the second pump chamber increase or decrease in the same way, i.e. It is configured in the pump shown in FIG. 1 to be changed.

As mentioned above, in the first spatial section 30 ′, the walls of the spatial section and the walls of the piston member 28 are arranged relative to each other to provide a first sealing gap 34 between the walls. The first sealing gap 34 separates the first pump chamber 16 and the second pump chamber 16', which is of an annular shape. Since the first pump chamber 16 operates as a high-pressure pump configured to deliver fuel at a pressure in excess of 200 MPa, the fuel in the first pump chamber tends to flow into the first sealing gap 34, and furthermore, the sealing gap. (34) tends to flow through. Although not shown here, the first sealing gap 34 between the pump chambers 16, 16' is for collecting fuel material flowing from the first pump chamber 16 to the first sealing gap 34. Means may be provided. Such means may comprise a groove arranged in the wall of the first space section provided with a conduit for guiding the fuel material to further processing. Since the second pump chamber 16 ′ is in the second spatial section 30 ″, it may be referred to generally below.

The pump 10 is provided with means for conveying the fuel material away from the second pump chamber 16'. Therefore, firstly, the pump 10 is provided with a vent flow path 36. The ventilation flow path 36 connects the outside of the body 18 with a second pump chamber 16 that extends through the body 18 of the pump and is also formed into the second space section 30 ″. The vent flow path 36 is configured to allow gas inflow into the second space section 30 ″ driven by the reciprocating motion of the piston member. In addition to the pump 10, the fuel material introduced into the second pump chamber 16 ′ or the second space section 30 ″ is supplied to the second space section 30 ″, i.e., through the sealing gap 34. A discharge flow path 38 is provided connecting the second pump chamber 16 ′ configured to convey away from the two pump chamber 16 ′ to the outside of the body 18.

The vent flow path 36 is provided with a one-way valve 40 that allows gas flow in the vent flow path 36 in a direction towards the second space section 30 ″, and also prevents backflow of fluid. The vent flow path 36 has an inlet that opens around the pump 10. Respectively, the discharge flow path 38 is provided with a one-way valve 42 configured to allow flow away from the second space section 30 ″ through the discharge flow path 38. During the compression stroke, the volume of the second pump chamber 16' is reduced, whereby it is pressurized. Gases and liquids in the second pump chamber 16' are forced out from the second pump chamber 16' through the discharge one-way valve 42. Further, during the suction stroke of the pump, the second pump chamber 16' expands to cause suction through the ventilating one-way valve 40.

In FIG. 1, the piston member 28 is in a first extreme position in which the first pump chamber 16 has its minimum volume. The piston member 28 is movable by an external force, indicated by arrow 44, which may be provided directly by the actuation of the engine.

The piston member 28 is provided with a sleeve member 46 connected to the second end 28 ″ of the piston member 28 and also having a closed end, ie a bottom 58. The bottom 58 of the sleeve member 46 extends radially to the piston member 28. The sleeve member 46 may be integral to or be a separate part of the sleeve member 46 and/or the second end 28 ″ of the piston member 28. Therefore, the bottom 58 of the sleeve member 46 is common with the piston member 28, which serves to receive the force required to reciprocate the piston member 28 within the pump 10. The sleeve member is arranged such that an annular space is provided between the sleeve member 46 and the piston member 28, which forms a second pump space 16' from now on. The sleeve member 46 opens toward the first end 28' of the piston member 28. The sleeve member is inserted into the second spatial section 30 ″ such that the radial inner wall of the second spatial section 30 ″ and the radial inner wall of the sleeve member 46 face each other to provide a second sealing gap 35. Are arranged. The wall of the second space section 30 ″ guides the sleeve member 46 of the piston member 28 within the body 18 when the piston member 28 and the sleeve member move along the central axis 32. .

The body 18 of the pump 10 is provided with a cylindrical extension 48 facing the second end of the piston member 28, which extension is coaxial with the first space section 30'. The cylindrical extension 48 has an axial length in the direction of the central axis 32 and an outer diameter smaller than the second diameter D2. The cylindrical extension 48 extends axially into the second spatial section 30 ″. In this way, the cylindrical extension 48 forms an annular gap 47 in the radial direction between the cylindrical extension 48 of the body and the inner wall of the body. The annular gap 47 defines the first spatial section at least partially so that the annular gaps of the second spatial section 30 ″ and the first spatial 30 ′ section overlap each other in the direction of the central axis 32 of the cylindrical space. Surround The sleeve member 46 is arranged to extend into the annular gap 47. The end face of the cylindrical extension 48 abuts the second pump chamber 16' together with the piston member 28 and sleeve member 46. The fitting of the sleeve member 46 extending into the annular gap between the cylindrical extension 48 and the second spatial section 30'' is the radial inner wall of the annular gap, i.e. the cylindrical outer wall and the sleeve of the extension 48 The radial inner walls of the member 46 are adapted to oppose each other to provide a third sealing gap 37.

There is a third space section 60 arranged radially into the annular gap between the inner wall of the body and the cylindrical extension 48, and a sleeve member 49 abutting the third space section. The third space section is used for the purpose of lubrication of the pump 10. The pump 10 is provided with a lubricant supply channel 62 and a lubricant discharge channel 64. The minimum volume of the third space section 60, and the location and volume of the lubricant supply channel 62 and the lubricant discharge channel 64 are configured to allow the formation of a pond of lubricant within the third space section, but made with lubricant. 3 Prevents filling of the space section as a whole. In particular, the lubricating oil supply channel 62 and the lubricating oil discharge chamber 64 are dimensioned so that the flow rate of the lubricating oil coming out of the third space section 60 is at least eventually greater than the flow rate of the lubricating oil into the third space section 60. do.

The ventilation flow path 36 extends through the body 18 to the inner wall of the second space section 30 ″ in which the outlet 50 is arranged. The vent flow path 36 continues in the sleeve member 46 which opens through the outlet 52 of the vent flow path into the second pump chamber 16'. In the transition region between the body 18 and the ventilation flow path 36 in the sleeve member 46, a rectangular space 54 extending in the direction of the central axis 32 is provided, into which the ventilation flow path opens. . In this way, the flow path is opened in all operating positions of the piston member 28 and sleeve member 46. The vent flow path and the discharge flow path may be realized by providing bores, grooves or otherwise provided channels suitable for the material of the pump 10. In the embodiment of FIG. 1, the rectangular space 54 is provided as an indentation as the outer wall of the sleeve member 46, but it is also conceivable to arrange it with the inner wall of the body 18. The discharge flow path 38 is provided with a similar rectangular space 54 to cause a flow connection between the piston member 28 and the discharge flow path 38 in the body 18.

Now, when installed in an internal combustion engine, an external force 44 is advantageously caused by the engine's power system. Therefore, the piston member 28 is, typically indirectly, in a mechanical force transmission connection with the crankshaft of the engine. In practice, this means that the mechanical force transmission is lubricated by the engine lubricant. The pump 10 is provided with means for conveying the fuel material away from the second pump chamber 16', and any fuel material exiting through the sealing gap 34 will not enter the engine's lubricating oil.

In FIG. 2, the pumping effect in the second pump chamber 16 ′ is one-way valves by the inlets and outlets of the suitably positioned vent flow path 36 and discharge flow path 38 to the piston member and body. An embodiment of the invention that is achieved without is shown. The rectangular spaces 54 are positioned such that the vent flow path 36 opens when the piston portion is in a suction stroke capable of balancing the underpressure formed in the second pump chamber 16'. The inlets and outlets of the vent flow path 36 and the discharge flow path 38 are closed when the piston member moves toward the first end 28 ′ and the pressure is reduced in the second pump chamber 16 ′. Are arranged to increase in At a specific position of the piston member 28, the discharge flow path 38 is open and the second pump chamber is discharged.

In FIG. 3, a pump unit 10 is shown in which the structure of the second pump chamber 16 ′ differs from that shown in FIGS. 1 and 2. Here, the piston member 28 extends from the first end through the guide flange 56 to the cam drive system (not shown) of the pump 10. The piston member 28 is provided with a bottom 58 as a radial extension in contact with the second pump chamber 16'. In this case, there is no sleeve member 46 provided in connection with the bottom 58. The radially distal end of the bottom 58 is properly sealed against the inner wall of the second space section 30 ″ so that a pumping effect can be obtained by the second pump space 16 ′. A feature common to all of FIGS. 1 to 3 is that the discharge flow path 38 opens to a portion abutting the second pump chamber 16 ′ furthest from the first end of the piston member. When the pump is in the same position as that shown in FIGS. 1 to 2 (the central axis 32 is positioned vertically and the first end 28' of the piston member is oriented upward), the discharge flow path ( 38) opens to the lowest position in the second pump chamber 16'. In practice, the central axis 32 need not be exactly vertical, but the pump may be tilted as long as the discharge flow path is arranged in a substantially lowest position into the second pump chamber 16'.

In FIG. 4, the pump 10 is configured to be installed such that the first end 28 ′ of the piston member 28 is horizontal below the second end 28 ″ of the piston member 28. An embodiment is shown. The basic configuration of the pump 10 is similar to that shown in Fig. 1, but these features, which are influenced by the starting orientation, are designed differently. In FIG. 4 it is shown that the first sealing gap 34 is provided with a fuel scraper ring 68 in an annular space arranged to minimize the flow of fuel to the second space section 30 ″. There is also another annular space 67 close to the first pump chamber 16 in which the fuel discharge channel 66 extends outside the body 18. Although not shown, a similar fuel scraper ring 68 and fuel discharge channel 66 may be arranged in the pumps shown in FIGS. 1 to 3. This arrangement reduces the amount of fuel flow to the second pump space 16' through the first sealing gap 34, but the fuel to the fuel discharge channel 66 is still quite high pressure.

In the pump 10 shown in FIG. 4, a bushing 70 is provided in the second space section 30 ″. The bushing is a generally cylindrical part with an outwardly extending shoulder at its first end. It is attached at the first end to the inner surface of the second spatial section 30'', in which an annular space 60 is provided between the bushing 70 and the inner surface of the second spatial section 30''. A section is provided having a diameter smaller than the second spatial section 30 ″, if possible. The bushing 70 is attached to the body 18 on the side of the first end 28' of the piston member 28 at its first end. The piston member 28 comprises a sleeve member 46 arranged in the second spatial section 30 ″ to correspond to FIGS. 1 and 2 provided with the desired guidance and sealing. In the second spatial section 30 ″, the inner wall of the second spatial section and the wall of the sleeve member 46 are arranged relative to each other to each provide a second sealing gap 35 between the walls. The sleeve member 46 is arranged to extend into the annular gap 60 formed by the bushing 70 and the wall of the second spatial section 30 ″. In this way, the bushing 70 abuts the second pump chamber 16' together with the sleeve member 46 and the piston member 28. The fitting of the sleeve member 46 extending into the annular gap between the bushing 70 and the wall of the second spatial section 30'' is the radial inner wall of the annular gap, i.e. the radial outer wall of the bushing 70 and the sleeve The radial inner walls of the member 46 are adapted to oppose each other to provide a third sealing gap 37.

In FIG. 4 there is a third space section 60 arranged radially into the annular gap between the bushing 70 and the inner wall of the body, and a sleeve member 49 abutting the third space section 60. The third space section 60 is used for the purpose of lubrication of the pump 10. The pump 10 is provided with a lubricant supply channel 62 and a lubricant discharge channel 64. The lubricant supply channel 62 is arranged at a position for supplying oil to the second sealing gap 35. The lubricant discharge channel 64 is arranged to open to the third space section 60.

The pump 10 is provided with means for conveying the fuel material away from the second pump chamber 16'. Therefore, firstly, the pump 10 is provided with a vent flow path 36. The ventilation flow path 36 extends through the body 18 of the pump and connects a second pump chamber 16 which is also formed as a second space section 30 ″ with the outside of the body 18. The vent flow path 36 is configured to allow gas inflow into the second space section 30 ″ driven by the reciprocating motion of the piston member 28. In the pump 10, a second pump chamber 16' is connected to the outside of the body 18 to seal the fuel material introduced into the second pump chamber 16' or the second space section 30'. A discharge flow path 38 is provided which is configured to convey through the gap 34 away from the second spatial section 30 ″, ie the second pump chamber 16 ′.

The vent flow path 36 is provided with a one-way valve 40 that allows gas flow in the vent flow path 36 in a direction towards the second space section 30 ″, and also prevents backflow of fluid. The vent flow path 36 has an inlet that opens around the pump 10. Respectively, the discharge flow path 38 is provided with a one-way valve 42 configured to allow flow away from the second space section 30 ″ through the discharge flow path 38. During the compression stroke, the volume of the second pump chamber 16' is reduced, thereby being pressurized. Gases and liquids in the second pump chamber 16' are forced out from the second pump chamber 16' through the discharge one-way valve 42. During the suction stroke of the pump, the second pump chamber 16 ′ also expands to cause suction through the ventilated one-way valve 40.

The sealing effect of the aforementioned sealing gaps may be based on the surface and/or dimensional tolerances of the parts and/or the quality of separate sealing elements, such as o-rings or lip seals.

Although the present invention has been described by way of examples in connection with what is now considered the most preferred embodiments herein, the invention is not limited to the disclosed embodiments, but as defined in the appended claims, features of the present application It is to be understood that it is intended to cover various combinations or variations of these, and several other applications included within the scope of the present invention. The detailed description mentioned in connection with any of the above embodiments may be used in connection with other embodiments in which such combinations are technically possible.

Claims (7)

A fuel pump (10) for supplying fuel to an internal combustion piston engine,
A body 18 and a cylindrical space 30 arranged in the body and having a central axis 32,
A piston member (28) arranged to reciprocate within the cylindrical space (30)
Including,
The cylindrical space (30) comprises a first space section (30') having a first diameter (D1), the wall of the cylindrical space (30) holding the piston member (28) in the body (18). The wall of the cylindrical space and the wall of the piston member 28 are arranged relative to each other to guide to provide a first sealing gap 34, and
The first space section (30 ′) forms a first pumping chamber (16) of the fuel pump (10) configured to pump fuel as the piston member (28) reciprocates within the cylindrical space. The central axis (32) is bounded by a first end (28') of the piston member (28), the cylindrical space (30) having a second diameter (D2) greater than the first diameter (D1) Further comprising a second spatial section (30'') of the image,
The piston member is provided with a sleeve member (46) extending toward the first end (28') of the piston member (28), so that an annular space between the sleeve member (46) and the piston member (28) is Wherein the annular space opens toward the first end (28') of the piston member (28), and an inner wall of the second space section (30') is within the second space section (30''). In order to guide the sleeve member 46 in, the inner wall of the second spatial section 30 ″ and the radial outer wall of the sleeve member 46 are arranged relative to each other to provide a second sealing gap 35, , And
An annular third space section (60) is arranged into the fuel pump (10), and the third space section (60) is arranged to extend into the annular third space section (60). Is partially bounded by, and
A lubricant supply channel 62 and a lubricant discharge channel 64 are connected to the third space section 60, and
In the second space section 30 ″ of the pump configured to pump fuel from the second space section 30 ″ as the piston member 28 reciprocates within the space 30. A second pumping chamber (16') is provided, the pump (10) being driven by a reciprocating motion of the piston member, of the body to allow gas inflow into the second space section (30''). A vent flow path 36 connecting the second space section 30 ″ outward, and the second outside of the body for conveying fuel material away from the second space section 30 ″. Fuel pump, characterized in that an exhaust flow path 38 is provided connecting the space section 30 ″. The method of claim 1,
The pump (10) is provided with a cylindrical extension (48) coaxial with a first space section (30') forming an annular gap surrounding the piston member (28), the sleeve member (46) being Fuel pump, characterized in that it is arranged to extend into the annular gap between the cylindrical extension (48) and the inner wall of the two space section (30''). The method of claim 1,
Fuel pump, characterized in that the vent flow path (36) is provided with a one-way valve (40) which allows flow towards the second space section (30''). The method of claim 1,
Fuel pump, characterized in that the discharge flow path is provided with a one-way valve (42) which allows flow away from the second space section (30 ″). The method of claim 1,
The annular gap in the second spatial section (30 ″) is at least partially so that the annular gap and the first spatial section (30 ′) overlap each other in the direction of the central axis (32) of the cylindrical space. Fuel pump, characterized in that it surrounds one space section. The method of claim 2,
Fuel pump (10), characterized in that the cylindrical extension (48) is a bushing (70) that is removably attached to the body (18) of the pump (10). delete

Images