WO2020064062A1

WO2020064062A1 - Pump assembly for an internal combustion engine

Info

Publication number: WO2020064062A1
Application number: PCT/DE2019/200084
Authority: WO
Inventors: Walter Janker
Original assignee: Continental Automotive Gmbh
Priority date: 2018-09-27
Filing date: 2019-07-22
Publication date: 2020-04-02
Also published as: DE102018216582A1

Abstract

The invention relates to a pump assembly for an internal combustion engine, which pump assembly has: a pump casing (101) having a longitudinal axis (102), which can be coupled to the internal combustion engine (103), wherein the pump casing (101) has a contact surface (131) for the placement of the pump casing (101) on the internal combustion engine (103) and for the alignment of the pump casing (101) relative to the internal combustion engine (103), a flange (105), which has a fixing region (106) for fixing the flange (105) to the pump casing (101) and which has a coupling region (107) for coupling the pump assembly (100) to the internal combustion engine (103), wherein a main extension direction (108) of the coupling region (107) extends transversely with respect to the longitudinal axis (102), and the fixing region (106) projects beyond the coupling region (107) along the longitudinal axis (102).

Description

description

Pump arrangement for an internal combustion engine

There is a pump arrangement for an internal combustion engine, in particular a high-pressure fuel pump for an internal combustion engine of a motor vehicle.

Pump assemblies or pumps are used in motor vehicles, for example, to fuel in

To be able to inject combustion chambers of an internal combustion engine at high pressure. Pumps of this type are set up to apply a pressure to the fuel, which in gasoline internal combustion engines is, for example, in a range from 150 bar to 600 bar and can be up to 3000 bar or more in diesel internal combustion engines. The pump is attached to the internal combustion engine, for example, and is driven by it.

It is desirable to provide a pump arrangement that is reliable and variable.

According to one embodiment, a pump arrangement for an internal combustion engine has a pump housing with a longitudinal axis. The pump housing can be coupled to the internal combustion engine. The pump housing has a bearing surface for the pump housing to rest on the internal combustion engine. In addition, the support surface serves to align the pump housing relative to the internal combustion engine. The pump arrangement has a flange. The flange has a fastening area for fastening the flange to the pump housing. The flange has a coupling area for coupling the pump arrangement to the internal combustion engine. A main direction of extent of the coupling region extends transversely to the longitudinal axis. The fastener range protrudes along the longitudinal axis over the coupling area.

By means of the bearing surface, the pump arrangement on the internal combustion engine can be aligned precisely and in particular vertically. The relative alignment between the pump housing and the internal combustion engine is determined via the pump housing, which is manufactured with comparatively small tolerances, for example by means of a turning process. The relative orientation of the pump housing to the internal combustion engine is in particular not determined by means of the flange, which, for example, has greater manufacturing tolerances than the pump housing.

The flange has the projecting fastening area. This has better balancing behavior during manufacture and operation than a flat flange. Forces occurring during manufacture and during operation can be well balanced by the projecting fastening area. The cylindrical fastening area can compensate for existing radial forces, since the fastening area is made thinner than the coupling area, in particular transversely to the longitudinal direction.

On the formed metal sheet that forms the flange, the fastening area is located at the interface to the pump housing and is designed in the manner of a raised collar. The flange is fastened offset to the bearing surface by a few tens of millimeters in order to enable the pump arrangement to be preloaded on the internal combustion engine. The, for example, cylindrical fastening area is designed to better compensate for the radial forces that arise than a flat flange. Radial forces arise, for example, when the flange is pressed onto the pump pen housing and / or when welding. Thermal effects can also cause forces that can be compensated for by the fastening area. Thus larger diameter tolerances are possible when forming the recess.

According to one embodiment, the pump arrangement has a welded connection for fastening the fastening region to the pump housing. The welded joint has a weld seam. The weld seam extends transversely to the longitudinal axis in such a way that one end of the weld seam is arranged in the pump housing. The weld seam extends radially through the fastening area into the pump housing. The weld seam extends through the fastening area above the coupling area. The weld seam is thus arranged at a distance from the contact surfaces of the pump arrangement 100 to the internal combustion engine 103. This prevents contaminants such as welding spatter from welding from affecting the assembly of the pump arrangement on the internal combustion engine.

For example, the welded joint has two welds. The two welds are spaced apart along the longitudinal axis. A reliable connection can thus be formed between the flange in the pump housing. The distance between the two weld seams avoids double welding and thus a reduction in the cross-section of the connection.

According to one embodiment, the flange has a recess which is surrounded by the fastening region and the coupling region. The fastening area surrounds the recess with a first inner diameter. The coupling area surrounds the recess with a second inner diameter. The first inner diameter is smaller than the second inner diameter. Thus, the flange is only in contact with the pump housing at the fastening area. The coupling area is spaced from the pump housing. Forces are thus transmitted between the pump housing and the flange at the fastening area, which can compensate for them well. Radial forces in particular can be introduced in a defined manner in the fastening area above the coupling area.

According to one embodiment, the sheet thickness of the fastening area is thinner than the sheet thickness of the coupling area. As a result, the welded connection can be formed simply and reliably and, at the same time, a coupling with the internal combustion engine can be implemented reliably.

According to one embodiment, the flange is designed to preload the pump housing against the internal combustion engine in a fastened state. For example, the fastening area and the coupling area enclose an angle of less than 90 °. For example, the angle is less than 90 ° and greater than 80 °. Alternatively or additionally, the coupling area has an inward curvature.

When attaching the flange to the pump housing, the fastening area is pressed in the direction of the pump housing. As a result, the pump housing is biased against the internal combustion engine.

According to one embodiment, a contact surface of the coupling region for contact with the internal combustion engine is arranged at least in regions along the longitudinal axis offset from the bearing surface. When attaching the pump housing to the internal combustion engine, the coupling area is initially spaced apart from the internal combustion engine and is then pressed against the internal combustion engine. As a result, the pump housing is biased against the internal combustion engine. In addition, the set arrangement ensures that the pump assembly 100 is aligned by means of the pump housing 101 relative to the internal combustion engine 103 and the flange does not undesirably affect the alignment even with larger manufacturing tolerances.

According to one embodiment, the pump housing has an inclined flank adjacent to the support surface, so that the coupling area is spaced apart from the pump housing. The sloping flank is provided as an alternative or in addition to the larger second inner diameter on the coupling area. Similar to the larger second inner diameter, the inclined flank realizes a distance between the flange and the pump housing at the coupling area. The inclined flank is designed such that a contact between the flange and the pump housing is only formed on the fastening area.

According to one embodiment, the flange is produced by means of a non-machining process. The flange is made in particular by means of forming, pressing and stamping. This makes the flange simple, inexpensive, material-saving and flexible to manufacture. A high stability of the flange can also be achieved.

Further advantages, features and further developments result from the following examples explained in connection with the figures. Identical, similar and identically acting elements are seen in all figures with the same reference numerals.

Show it:

FIG. 1 shows a schematic illustration of a pump arrangement according to an exemplary embodiment, FIG. 2 shows a schematic sectional view of a pump arrangement according to an exemplary embodiment,

FIGS. 3 to 6 steps for producing a flange according to an exemplary embodiment,

FIG. 7 shows a schematic illustration of a flange according to an exemplary embodiment,

FIG. 8 shows a schematic illustration of a flange according to an exemplary embodiment,

FIG. 9 shows a schematic illustration of a pump arrangement according to an exemplary embodiment,

FIG. 10 shows a schematic illustration of a pump arrangement according to an exemplary embodiment,

FIG. 11 different configurations of the flange according to exemplary embodiments,

FIG. 12 shows a schematic illustration of a pump arrangement according to an exemplary embodiment,

FIG. 13 shows a schematic illustration of a pump arrangement according to an exemplary embodiment, and

Figure 14 is a schematic representation of a flange according to an embodiment.

FIG. 1 shows a schematic illustration of a pump arrangement 100. The pump arrangement is, for example, a high-pressure gasoline pump for an internal combustion engine 103 (with for example Figure 9) of a motor vehicle. The pump arrangement 100 is in particular designed to provide pressures of 300 bar or more.

The pump arrangement 100 has a pump housing 101. The pump housing surrounds a cylinder space in which a piston 125 (FIG. 12) can be moved along a longitudinal axis in order to draw in fluid and to apply pressure to it.

The pump arrangement 100 has a flange 105. The flange 105 extends in regions transverse to the longitudinal axis 102 and serves as a mounting interface for fastening the pump connection 100 to the internal combustion engine 103.

FIG. 2 shows a sectional view of the pump arrangement 100. The flange 105 has two holes 122. A screw 126 is arranged in each of the holes 122. The pump arrangement 100 can be fixed on the internal combustion engine 103 by means of the screws 126.

The flange 105 has a fastening area 106 and a coupling area 107. The coupling region 107 extends along a main direction of extent 108. In the illustration in FIG. 2, this corresponds, for example, to a horizontal. The longitudinal axis 102 runs transversely and in particular perpendicularly to the main direction of extent 108. In the illustration in FIG. 2, the longitudinal axis 102 runs, for example, along a vertical.

The fastening region 106 runs transversely to the coupling region 107 at least in regions along the longitudinal axis 102.

The flange 105 is connected to the pump housing 101 at the fastening region 106. The connection between the Pump housing 101 and the flange 105 is formed on the fastening supply area 106 of the flange 105, which runs along the longitudinal axis 102 and jumps over the coupling area 107 before. The flange 105 is attached to the internal combustion engine at the coupling region 107, which is aligned along the main direction of extension 108 transversely to the fastening region 106.

The manufacture of the flange 105 according to an exemplary embodiment is described below in connection with FIGS. 3 to 6. FIGS. 3A, 4A, 5A and 6A each show a sectional view and FIGS. 3B, 4B, 5B and 6B each show a perspective view.

First, a metal sheet 109 is made available, as shown in FIG. 3. The metal sheet 109 is, for example, a stainless steel sheet with a thickness of approximately 3 mm. For example, the metal sheet 109 is punched out of a larger metal sheet. The metal sheet 109 extends in cross-section along the main extension direction 108 or along a main extension plane.

As shown in FIG. 4, a recess 110 is made in the metal sheet 109. For example, the recess 110 is made in the metal sheet 109 by means of stamping or stamping or drilling. The recess 110 is in particular round and is completely surrounded by the metal sheet 109.

The metal sheet 109 is subsequently formed, in particular in a forming area 135. The forming area 135 directly adjoins the recess 110 and delimits the recess As shown in FIG. 5, the forming area is drawn transversely to the main direction of extent 108 along the longitudinal direction 102. The protruding fastening area 106 is thereby formed. The orientation of the metal sheet 109 in the forming area 135 is changed by means of tensile and pressure forming of the metal sheet 109, in particular in the forming area 135, in order to form the fastening area 106. Adjacent to the recess 110, the metal sheet 109 has a projection 123. This is subsequently removed, as shown in Figure 6.

After the projection 123 has been removed, an inner side 112 of the fastening region 106 has a predetermined inner diameter 113. The inner diameter is specified in particular as a function of an outer diameter of the pump housing 101. The inside 112 faces the recess 110 and delimits it.

In addition, the two holes 122 are made in the coupling region 107.

The free end of the fastening area 106 is reworked, for example, after the projection 103 has been removed in order to make it easier to press the flange 105 onto the pump housing 101. For example, post-processing is carried out by means of embossing, pressing or pressing.

The inner diameter 113 is also post-processed, for example, by pressing, pressing and / or stamping in order to realize the given inner diameter 113 within predetermined tolerances.

The raised fastening area 106 is thus located on the flange 105 in the area of the large, central recess 110 at the interface to the pump housing 101. Cleaning area 106 arises from material that is present in the metal sheet 109 anyway.

The available material in the forming area 135 is drawn out of the perforated metal sheet 109 (FIG. 4) in a pot-shaped manner by the forming process (FIG. 5).

Then the projection 123 is punched out and the inner diameter 113 is calibrated. The calibration is carried out, for example, by means of a stamp or other pressing or pressing.

A material flow occurs through the forming process and the drawing process for forming the fastening region 106. In addition, thinning of the metal sheet 109 occurs in the fastening area 106. For example, the fastening area 106 has a thickness of approximately 50% of the original thickness of the metal sheet 109. As a result, a welding of the flange 105 to the pump housing 109 is subsequently simplified.

The deformation of the metal sheet 109 in the deformation region 135 strengthens the material in the fastening region 106 and in the transition to the coupling region 107. The pre-jumping fastening area 106 acts to reinforce the flange 105 against deformations like a rib. There is no need for a raised outer edge of the coupling region 107, which is formed, for example, in the case of conventional flanges for reinforcement.

As shown in FIG. 7, the forming and forming of the fastening region 106 does not interrupt a material structure 124 in the metal sheet 109. The material structure 124, also called the fiber course, corresponds to one, for example Lattice structure or other microscopic material properties of the metal sheet 109, which form during the production of the metal sheet 109. Since the flange 105 is produced by means of a non-machining process, these material structures 124 are not interrupted. This leads to a comparatively stable flange.

FIG. 8 shows the inside 112 of the flange 105 according to an exemplary embodiment in a detailed illustration.

In the projecting fastening area 106, the inner side 112 surrounds the recess 110 with the inner radius 113. A contact area 129 is thus formed on the fastening area 106. The contact area 129 serves for the direct contact of the flange 105 with the pump housing 101. In the fully assembled state, the flange 105 contacts the pump housing 109 with the contact area 129. For example, the flange 105 does not touch the pump housing 101 outside the contact area 129.

A recessed area 114 is formed next to the contact area 129. The contact area 129 and the recessed area 114 jointly delimit the recess 110. The area to be reset is set back transversely to the longitudinal axis 102 with respect to the contact area 129. The recessed area 114 has a larger inner diameter 130 than the contact area 129. The inner diameter 130 is larger than the inner diameter 113. For example, the inner diameter 130 is between 0.01 mm and 1 mm larger than the inner diameter 113.

The inner diameter 130 is in particular so much larger that the recessed area 114 is at a distance 115 (FIG. 10) from the pump housing 101 in the fully assembled state. This causes tensions and during production and operation Forces between the flange 105 and the pump housing 101 primarily on the fastening area 106.

The fastening area 106 has a smaller sheet thickness 133 than the coupling area 107, which has a larger sheet thickness 134. In particular, the extent of the coupling area 107 transversely to the longitudinal axis 102 is significantly greater than the extent of the fastening area 106 transversely to the longitudinal axis 102. As a result, the fastening area 106 can more easily compensate for occurring forces than the coupling area 107. Because of the recessed area 114, the coupling area 107 is spaced apart arranged by the pump housing 101. A power transmission between the pump housing 101 and the flange 105 takes place in particular only at the contact area 129 of the fastening area 106.

Figure 9 shows the pump assembly 100 in one with the

Internal combustion engine 103 coupled state.

The pump housing 101 has a support projection 104 which projects transversely to the longitudinal axis 102. A support surface 131 is formed on the support projection 104. On the support surface 131, the pump housing 101 is in contact with the internal combustion engine 103, for example with the cylinder head of the internal combustion engine 103. The support surface 131 is oriented transversely to the longitudinal axis 102.

The support projection 104 with the support surface 131 serves to support the pump housing 101 on the internal combustion engine 103. The support projection 104 with the support surface 131 also realizes an alignment of the pump housing 101 relative to the internal combustion engine 103. The alignment of the pump housing 101 relative to the internal combustion engine 103 is in particular not realized by means of the flange 105, but rather by means of the pump housing 101 itself. The pump housing 101 is manufactured, for example, by means of a turning process and therefore has comparatively low tolerances due to the manufacturing process. Therefore, the pump housing 101 is reliably aligned within narrow tolerances relative to the internal combustion engine 103, even if the flange 105 has larger manufacturing tolerances.

The flange 105 is in direct contact with the pump housing 101 at the contact region 129 of the fastening region 106. Outside the contact region 129, the flange 105 is spaced apart from the pump housing 101. In particular at the recessed region 114, a distance 115 (FIG. 10) is transverse to the longitudinal direction 102 between the pump housing 101 and the flange 105. The recessed area 114 is, for example, already formed during the shaping of the shaping area 135 and possibly reworked, for example by pressing and / or pressing or another non-cutting method.

The flange 105 is fastened to the pump housing 101 by means of a weld connection with the weld seams 118, 119. More than two weld seams 118, 119 or only a single weld seam 118 can also be provided. The weld seams 118, 119 are formed in the fastening area 106.

As can be seen in more detail from FIG. 10, the weld seams 118, 119 each run obliquely or transversely to the longitudinal axis 102. The weld seams 118, 119 each run transversely to the fastening area 106. The weld seams 118, 119 are from outside the fastening area 106 in the direction toward the pump housing 101 brought in. One end 132 of the weld seams 118, 119 is arranged in the interior of the pump housing 101. The weld seams 118, 119 in particular do not run along an outer wall of the pump housing 101, but rather transversely thereto. The weld seams are arranged along the longitudinal direction 102 at one end of the flange 105 which faces away from a contact surface 111 of the coupling region 107. The contact surface 111 serves to rest on the internal combustion engine 103 in the assembled state.

Due to the arrangement of the

Welds 118, 119 from the contact surface 111 Ver dirt the contact surface 111 due to the welding can be avoided as well as possible. As a result, a reliable and precise attachment of the pump arrangement 100 to the internal combustion engine 103 is possible, and errors in the relative orientation of the pump arrangement 100 to the internal combustion engine 103 due to contamination that can arise from the welding can be avoided.

The same effect is achieved by arranging the ends 132 of the weld seams 118, 119 in the pump housing 101. Thus, no dirt can leave the pump housing 101 at the ends 132. No weld spatter or the like can occur at the ends 132, which can contaminate the contact surface 111, for example.

The welding to form the weld seams 118, 119 takes place radially through the fastening area 106 above the coupling area 107. The coupling area 107 shields the contact surface 111 from the influences of the welding process. Ver dirt, welding spatter and the like are thus removed from the contact surface 111. This eliminates the need for covering devices such as grooves or a housing collar at the assembly contact point. The weld seams 118, 119 arranged laterally and introduced radially into the pump housing 101 end in the pump housing 101, so that welding exits at the ends 132 is eliminated. This can be dispensed with a splash guard groove, which is conventionally provided.

Two weld seams 118, 119 are preferably used. This means that welding begins on both at the same time

Weld seams 118, 119 possible. The start is particularly offset by 180 °. This means that there is little warpage. Material stresses and changes that occur during welding occur symmetrically. Due to the formation of two weld seams 118, 119, a lower welding energy can be used than with a large seam. This means that less heat can be introduced and therefore a less heated assembly in the assembly process. For example, the two weld seams 118, 119 each have an extension along the longitudinal direction 102 of approximately 0.5 mm in cross section.

The two weld seams 118, 119 are at least a short distance apart and do not overlap. This prevents double welding, which would reduce the connection cross-section. For example, the two weld seams are spaced about 0.1 mm apart.

The weld seams 118, 119 each have only a single seam entry point, since the seam depth in the pump housing 101 runs out. The weld seams 118, 119 in particular have no seam exit point that is exposed.

As an alternative or in addition to the recessed area 114, the distance 115 between the flange 105 and the pump housing 101 on the inside 112 outside the contact area 129 can be realized by means of an oblique flank 117 on the pump housing 101. For example, the pump housing 101 has an increasing section along the longitudinal axis 102 Diameter, the diameter on the support surface 131 being small and increasing with increasing distance from the support surface 131. As a result, the distance 115 is realized in the assembled state between the contact area 129 and the contact surface 131. As an alternative or in addition to the flange 105, the pump housing 101 thus has, for example, a recessed area which is formed in particular by means of the oblique flank 117. As a result, stresses and forces between the flange 105 and the pump housing 101 occur primarily at the fastening region 106 during manufacture and operation.

FIG. 11 shows different configurations of the flange 105. The configuration of the flange 105 can be easily adapted to different interfaces of different internal combustion engines 103.

For example, a difference between the different configurations of the flange 105 is a distance between the holes 122, which can be, for example, 66 mm or 75 mm.

In addition, the diameter of the holes 122 can be adjusted as desired, for example depending on the screws 126 used. For example, the holes 122 have a diameter M8 or a diameter M6.

It is also possible to design the coupling region 107 asymmetrically. For example, the holes 122 on the left and right of the recess 110 are at a different distance from the recess.

In the independent versions of the flange 105, the tools for producing the recess 110 and the fastening area 106 can remain the same. For example, only the punches for the hole spacing of the holes 122 and the cutting of the outer contour adapted. It is thus possible to attach the pump arrangement 100 to a wide variety of internal combustion engines 103 by means of the flange 105. In this case, cost-effective production is possible because the flange 105 can be easily adapted to the different specifications of the internal combustion engine 103.

FIG. 12 shows a cross section of the pump arrangement 100. The flange 105 was first pressed onto the pump housing by means of an interference fit. The weld seams 118, 119 were then introduced. The flange 105 is only in contact with the pump housing 101 in the area of the weld seams 118, 119. The defined introduction of the radial forces into the fastening area 106 above the coupling area 107 takes place on account of the diameter gradation between the inner diameter 113 of the fastening area 106 and the inner diameter 130 reset area 114. Alternatively or additionally, the inclined flank 117 is formed on the housing body 117. The inclined flank 117 on the one hand facilitates the pressing of the flange 105 onto the pump housing 101. The oblique flank 117 is also configured in accordance with exemplary embodiments such that the distance 115 between the recessed area 114 and the pump housing 101 is formed in the assembled state.

FIG. 13 shows the relative arrangement along the longitudinal axis 102 between the flange 105 and the pump housing 101. The pump housing 101 has the support projection 104 with the support surface 131. This defines the position of the pump housing 101 relative to the internal combustion engine 103. The flange 105 is fastened in particular along the longitudinal axis 102 relative to the pump housing as a function of the bearing surface 131. The flange 105 is fastened to the pump housing 101 in such a way that the contact area 129 is at a predetermined distance 136 from the Has bearing surface 131. For example, the distance is more than 4 mm or more than 5 mm.

The flange 105 is fastened to the pump housing 101 in such a way that the contact surface 111 is spaced apart from the internal combustion engine 103 before the screws 126 are tightened. An offset 127 is formed along the longitudinal axis 102 between the contact surface 131 and the contact surface 111. The offset is, for example, greater than 0.01 mm and less than 0.5 mm.

The offset ensures that the relative position of the pump housing 101 to the internal combustion engine 103 is always predetermined by the support projection 104 with the support surface 131 and, in particular, is not impaired by the contact surface 111 resting on the internal combustion engine 103. Thus, for example, an undesired inclination of the pump housing 101 relative to the internal combustion engine 103 can be avoided. In addition, flatness deviations of the coupling region 107 can be compensated for, so that even a not completely flat contact surface 111 is always spaced apart from the internal combustion engine 103 before the flange 105 is completely fixed to the internal combustion engine 103.

Plane deviations occur, for example, due to manufacturing reasons if the coupling region 107 is bent slightly upwards or downwards, for example. The tolerance for the press fit dimension of the flange 105 should be kept very low. For this, too, it is advantageous if deviations in the evenness of the flange 105 do not have to be taken into account in the press-on dimension. The size of the offset 127 is specified accordingly.

In addition, the offset 127 enables the pump housing 101 to be preloaded with respect to the internal combustion engine 103 when the pump arrangement 101 is completely on the internal combustion engine 103 is fixed. The screws 126 press the coupling region 107 against the internal combustion engine 103. This results in a spring force of the flange 105 which presses the pump housing 101 against the internal combustion engine 103.

FIG. 14 shows a further embodiment of the flange 105. The coupling region 107 is slightly inclined or curved toward the outside, so that the offset 127 increases from the center to the outside. For example, the offset 127 on the outside is between 0.1 and 0.5 mm. For example, the coupling region 107 has a curvature inwards, so that the offset 127 increases outwards.

The coupling region 107 has an angle 116 to the longitudinal direction 102 which is less than 90 ° and in particular greater than 70 °, in particular greater than 80 °.

Comparably, the coupling area 107 and the fastening area 106 have an angle 128 to one another which is less than 90 ° and greater than 70 °, in particular greater than 80 °.

Due to the inclination or curvature of the coupling area upward, the biasing force on the pump housing 101 can be realized and the offset 127 between the contact surface 131 and the contact surface 111 is reliably realized. The inclination results, for example, from the design of the flange 105, which is designed in such a way that the coupling region 107 is bent upwards after manufacture. As a result, the press-on dimension and / or the tension is ensured relative to the support surface 131.

The pump arrangement 100 is distinguished, inter alia, by the fact that the flange 105 is produced entirely as a stamped formed part in accordance with exemplary embodiments. According to exemplary embodiments, machining is completely dispensed with. The fastening area 106 can be produced with the reduced sheet thickness 133 by the reshaping. Interruptions in the material structure 124 of the metal sheet 109 are avoided.

The press fit on the or the contact area 129 is in particular arranged exclusively on the fastening area 106 above the coupling area 107. This makes a greater tolerance acceptable, since possible widenings by the press fit are more tolerable in the fastening area 106 than in the case of a flat flange.

The two weld seams 118, 119 are formed all around the flange 105 on the fastening region 106. By welding along the longitudinal axis 102 from one side of the flange to the other side of the flange 105 is dispensed with. The weld seams 118, 119 each end in the pump housing 101. This prevents welding spatter from reaching the contact surface 111. In addition, for example, there is no need for further shapes which conventionally serve as welding spray protection.

The shaping of the shaping area 135 to the fastening area 106 leads to material hardening. This results in a flange with increased stability over flat flanges.

Different outer contours of the flange 105 and arrangements and diameters of the holes 122 are easily possible with the fastening area 106 remaining of the same design. As a result, many stages of the stamping tool can be reused for production with different variants of the flange design.

Due to the offset 127 of the flange 105 to the pump housing 101, a preload of the pump arrangement 101 can be variably adjusted and in particular in different internal combustion engines 103 without changing the design of the flange 105 or the pump housing 101 differently adjustable. The prestressing dimension or the prestressing force is defined during assembly by the press-on dimension, for example by means of a corresponding specification for the distance 136. In addition, the offset 127 ensures that the pump arrangement 100 is aligned relative to the motor by means of the support projection 104 and thus as accurate as possible, in particular vertical , Alignment is feasible.

The pump arrangement 100 thus enables good durability with comparatively simple, inexpensive and quick producibility. A sufficiently reliable pump arrangement 100 can thus be realized even with limited installation space requirements.

Claims

1. Pump arrangement for an internal combustion engine, comprising:

- A pump housing (101) with a longitudinal axis (102) which can be coupled to the internal combustion engine (103), wherein the pump housing (101) has a bearing surface (131) for placing the pump housing (101) on the internal combustion engine (103) and for aligning the pump housing (101) relative to the internal combustion engine (103),

- A flange (105) which has a fastening region (106) for fastening the flange (105) to the pump housing (101) and which has a coupling region (107) for coupling the pump arrangement (100) to the internal combustion engine (103), wherein a main direction of extension (108) of the coupling area (107) extends transversely to the longitudinal axis (102) and the fastening area (106) projects along the longitudinal axis (102) over the coupling area (107).

2. Pump arrangement according to claim 1, comprising a welded connection for fastening the fastening region (106) to the pump housing (101), which has a weld seam (118, 119) which extends transversely to the longitudinal axis (102), so that one end (132 ) the weld seam (118, 119) is arranged in the pump housing (101).

3. Pump arrangement according to claim 2, wherein the welded connection has two weld seams (118, 119), the two

Welds (118, 119) along the longitudinal axis (102) are spaced apart.

4. Pump arrangement according to one of claims 1 to 3, wherein the flange has a recess (110), the supply area from the fastening area (106) and the coupling area (107), the fastening area (106) including the recess (110) one surrounds the first inner diameter (113) and the coupling region (107) surrounds the recess (110) with a second inner diameter (130), the first inner diameter (113) being smaller than the second inner diameter (130).

5. Pump arrangement according to one of claims 1 to 4, in which a sheet thickness (133) of the fastening area (106) is thinner than a sheet thickness (134) of the coupling area (107).

6. Pump arrangement according to one of claims 1 to 5, in which the flange (105) is designed to clamp the pump housing (101) against the internal combustion engine (103) before in a fastened state.

7. Pump arrangement according to one of claims 1 to 6, in which the fastening region (106) and the coupling region (107) enclose an angle (128) of less than 90 ° or in which the coupling region has an arch toward the inside.

8. Pump arrangement according to one of claims 1 to 7, in which a contact surface (111) of the coupling region (107) for contact with the internal combustion engine (103) is at least partially offset along the longitudinal axis (102) to the support surface (131).

9. Pump arrangement according to one of claims 1 to 8, wherein the pump housing (101) adjacent to the bearing surface (131) has an oblique flank (117), so that the coupling region (107) is spaced from the pump housing (101).

10. Pump arrangement according to one of claims 1 to 9, in which the flange (105) is produced by means of a non-cutting process.