KR20070086257A - Delivery unit - Google Patents

Abstract

In prior art, delivery units comprise a running wheel which is arranged in a pump chamber and which can be driven in a rotated manner by means of an actuator and comprise two front sides whereby a front wall of the pump chamber is arranged opposite thereto, and also comprises several recesses for storing, in a hydrodynamic manner, in both front sides of the running wheel. One disadvantage of the delivery unit is that dirt particles can collect in the recesses. When the dirt particles are flushed out from the recesses, they produce, in the region between the recesses which are arranged in a circular manner, increased friction and also stress marks and the axial gap between the running wheel and the pump chamber is smaller than in the region of the recesses. The inventive delivery unit reduces the friction acting upon the running wheel and increases efficiency. According to the invention, at least two adjacent recesses (38) of the at least one front side (28,29) and/or the at least one front wall (15,16) are connected together by, respectively at least one groove (42).

Description

Feed unit {DELIVERY UNIT}

The present invention relates to a supply apparatus according to the preamble of the independent claim.

A feeder having an impeller arranged in the pump chamber, including two front faces, each of which is rotated and driven by an actuator and facing the front wall of the pump chamber, and a plurality of recesses for hydrodynamic mounting in the two front surfaces of the impeller The device is already known from EP 1 091 127 A1. It is undesirable that dust particles can accumulate in the recess. When the dust particles are removed from the recesses, since the axial gap between the impeller and the pump chamber is smaller than in the region of the recesses, it creates increased friction and thus wear marks in the region between the recesses arranged in a circular shape. Cause.

The feeding device according to the invention with the representative features of the independent claims is improved in a simple manner in which at least two adjacent recesses of the at least one front face and / or the front wall are connected to each other through each at least one groove. Has an advantage. In this way the axial gap in the area between the recesses is widened, so that the dust particles cannot cause any increased friction and wear marks.

The arrangements described in the dependent claims enable further preferred constructions and improvements of the feeder described in the independent claims.

According to a preferred embodiment, the recesses and grooves are arranged in a circle shape and extend in an arc shape, a partial circle shape, a slot shape and the like. The recesses and grooves are preferably arranged on a common circle.

It is also preferred when the recess has a greater depth than the groove, since in this way an inclined surface can be formed in which hydrodynamic support of the impeller is achieved.

In particular, it is preferred that each recess comprises at least one inclined surface for hydrodynamic support of the impeller with respect to the front face and / or the front wall, in which the axial position of the impeller is two between the impeller and the front wall of the pump chamber. This is because the axial gap is adjusted to be at least about the same size. Accordingly, the friction acting on the impeller is reduced, and the efficiency of the feeding device is improved. At least one slope of the recess is provided at the subsequent end of the recess in the direction of rotation of the impeller when arranging the recess in the impeller, and at the downstream end of the recess when arranging the recess in the front wall of the pump chamber. .

In addition, the recess preferably has a lowest position each extending parallel to the at least one front face and / or the front wall.

The recesses of the front face of the impeller are also located opposite the recesses of the other front face of the impeller symmetrically with respect to the central plane, and the recesses located symmetrically facing are connected to each other by pressure compensation channels. In this way it is achieved that the pressures in the two recesses connected by the pressure compensation channels are each balanced.

Embodiments of the present invention are described in more detail in the figures shown in simplified form and in the description which follows.

1 shows a partial cross section of a supply apparatus according to the invention.

2 shows an impeller of a feeding device.

3 is a cross-sectional view of the impeller along the line III-III of FIG.

4 is a cross-sectional view of the supply apparatus along line IV-IV of FIG.

FIG. 5 is a cross-sectional view of the supply apparatus along the line VV of FIG. 1. FIG.

6 is a cross-sectional view of the recess and the impeller arranged in the front wall of the pump chamber according to the second embodiment.

1 shows a supply apparatus according to the invention.

The supply device according to the invention is used for supplying a fluid, for example fuel, from a storage tank, for example via a high pressure tube to an engine.

The supply device according to the invention is formed as a flow pump, for example a vortex pump or a side channel pump, and has a pump housing 1 comprising a pump part 2 and a motor part 3.

The pump part 2 comprises a pump chamber 4 in which the impeller 5 rotates around the pump shaft 8 which is rotationally symmetrical. The impeller 5 is driven by an actuator 9 provided in the motor part 3. The actuator 8 is for example an electric motor and is arranged in the motor chamber 7 of the motor unit 3.

The upstream region of the pump chamber 4 is described as the suction side, and the downstream region of the pump chamber 4 is described as the pressure side of the unit.

The pump chamber 4 includes a pump chamber inlet 11 and a pump chamber outlet 12. The pump chamber 4 is limited by two axial facing front walls, namely the first front wall 15 and the second front wall 16, in which the pump chamber inlet 11 is located within the first wall 15. A pump chamber outlet 12 is provided in the second wall 16 radially with respect to the pump axis 8 of the ring wall 17.

The impeller 5 comprises a plurality of impeller blades 5.1, with one blade chamber 5.2 formed therebetween. The blade chamber 5.2 opens towards the front walls 15, 16 and is arranged at a radially outward end of the impeller blade 5.1 in a radially outward direction, for example with respect to the pump axis 8. It is sealed by). However, the blade chamber 5.2 is clearly open radially outward and may not have a ring 5.3.

The circular transmission channels 14 arranged in the radial region of the impeller blades 5.1 are arranged in the front walls 15, 16.

The first front wall 15 is for example a part of the suction cover 18 and the second front wall 16 and the ring wall 17 are for example a part of the pressure cover 19. An inlet channel 22 is provided in the suction cover 18 through the pump chamber inlet 11 to the pump chamber 4, and the supply fluid of the supply device leaves the pump chamber 4 through the pump chamber outlet 12. For example, the pump chamber 4 is in fluid communication with the motor chamber 7 via an outlet channel 23 provided in the pump chamber outlet 12 and the pressure shroud 19.

The pressure shroud 19 includes a through opening 24. The drive shaft 10, which is mechanically coupled to the actuator 9, protrudes from the motor chamber 7 and proceeds into the pressure chamber 4 through the through opening 24 of the pressure cover 19.

The axial width of the pump chamber 4 is greater than the axial width of the impeller 5, so that each axial gap 20 of about 10 to 30 μm between the impeller 5 and the front walls 15, 16. ) Exists. The difference between the width of the pump chamber 4 and the width of the impeller 5 is defined as the total axial gap.

The impeller 5 is fixed on the drive shaft 10, for example, protruding into the pump chamber 4, for this purpose the impeller 5 comprises an impeller opening 25, the drive shaft 10 being formally coupled and / or At least extend into the impeller opening 25 to engage the impeller forcefully. The impeller 5 is for example supported on the drive shaft 10 to move axially between the first front wall 15 and the second front wall 16.

The impeller 5 has a first front face 28 facing the first front wall 15 of the pump chamber 4 and a second front face 29 facing the second front wall 16 of the pump chamber 4. ).

A plurality of recesses 38 for hydrodynamic mounting of the impeller 5 on at least one of the front faces 28, 29 of the impeller 5 and / or at least one of the front walls 15, 16 of the pump chamber 4. ) Is provided. In FIG. 1 a recess 38 is arranged, for example, on the front faces 28, 29 of the impeller 5. However, this may be provided on the front walls 15, 16 of the pump chamber 4 according to the second embodiment. The recess 38 is formed to act like a hydrodynamic bearing, in this way an axial position of the impeller 5 between the first front wall 15 and the second front wall 16 of the pump chamber 4. Is adjusted so that two equally sized axial gaps 20 appear between the impeller 5 and the front walls 15, 16. Thereby, only a small frictional force acts on the impeller 5, so that the efficiency of the feeding device is improved.

The supply device for example transfers fluid from the storage tank 32 to the inlet channel 22, the pump chamber inlet 11, the pump chamber 4, the pump chamber outlet 12, the outlet channel 23 and the motor of the pump housing 1. Suction through the negative motor chamber 7 supplies fluid, for example fuel, to the engine 34 through the high pressure tube 33. The high pressure pipe 33 is provided, for example, with a check valve 35 in order to maintain the assigned pressure in the high pressure pipe 33 after switching off the supply device.

Figure 2 shows an impeller of a feeding device with a recess according to the first embodiment of the feeding device according to the invention.

In the impeller according to FIG. 2 the parts which operate identically or identically as compared to the supply device of FIG.

The recess 38 is for example provided radially inward of the impeller blades 5.1 of the impeller 5 and arranged horizontally in a virtual ring. The ring is provided centrally with respect to the pump shaft 8, for example. For example, four recesses 38 are evenly distributed over the area of the ring. However, clearly any number of recesses 38 may be provided. The recess 38 extends in the form of an arc, a partial circle, a slot, or the like, for example. The recess 38 includes at least one face 39 inclined with respect to the front face 28 and 29 for hydrodynamic support of the impeller 5, respectively. The inclined surface 39 for hydrodynamic support is arranged adjacent to the next end of the recess 38 with respect to the direction of rotation 41 of the impeller 5. The recesses 38 each have a lowest position 40 running parallel to the front face 28, 29, for example. For example, the lowest position 40 of the recess 38 is adjacent to two inclined surfaces 39, that is, the leading and following. According to the first embodiment, the leading slope 39 has a shorter length, for example a shorter arc length, than the subsequent slope 39 in the direction of rotation. The leading slope 38 in the direction of rotation may be omitted and replaced by a stepped step because it does not contribute to hydrodynamic support.

According to the invention, at least two adjacent recesses 38 of at least one front face 28, 29 and / or at least one front wall 15, 16 are provided with each of the at least one groove 42. Are connected to each other through. According to the first embodiment, the recesses 38 are provided on the two front faces 28, 29 of the impeller 5. For example, each recess 38 is connected via an adjacent recess 38 and groove 42, respectively. The groove 42 extends in an arc shape, a circle shape or the like, for example, so that the recess 38 and the groove 42 together form a general ring. The recess 38 and groove 42 remain at least distinguishable because the depth of the groove 42 is smaller than the lowest position 40 of the recess 38 and the depth of the inclined surface 39 ( 3). The width Bn measured radially with respect to the pump axis 8 of the groove 42 is the same size as the width Bv measured radially with respect to the pump axis 8 of the recess 38, for example. However, others are possible.

The inclined surface 39 of the recess 38 is formed by, for example, continuously decreasing the depth of the recess 38 as it goes from the lowest position 40 to the adjacent groove 42.

FIG. 3 shows a cross section of the impeller along the line III-III of FIG. 2.

The recess 38 extends at least approximately parallel to the front face 28, 29, for example, in the region of the lowest position 40. As opposed to the direction of rotation 41, this extends on the subsequent inclined surface 39 and merges into the groove under a decrease in the depth of the next groove 42 in the direction of rotation 41. Viewed in the direction of rotation, the depth of the recess 38 is reduced through a stepped step 43 in the form of a staircase, shown by the dotted line, or the leading inclined surface 39, leading to the leading groove 42.

The recess 38 of the front face 28 of the impeller 5 is positioned facing the recess 38 of the other front face 29 of the impeller 5, for example symmetrically with respect to the center face 45. Thus, the symmetrically facing recesses 38 are connected to each other via a pressure compensation channel 46. In this way the same high pressure is formed in the two recesses 38 which are connected via the pressure compensation channel 46.

The fluid in the axial gap 20 is delivered together in the direction of rotation 41 upon rotation of the impeller 5 and has a relative velocity towards the impeller 5 as opposed to the direction of rotation 41. Accordingly, the fluid in the axial gap 20 flows through the recess 38 and the groove 42 as opposed to the direction of rotation 41. In the region of the subsequent inclined surface 39, the flow cross section narrows in the form of a wedge between the front surfaces 28, 29 of the impeller 5 and the front walls 15, 16 of the pump chamber 4, thus making it higher in the fluid. Increasing pressure is formed to affect each front face 28, 29 of the impeller 5, in this way adjusting the axial position of the impeller 5 to form axial gaps 20 of the same size. do.

4 shows a cross section of the supply device according to line IV-IV of FIG. 1, and FIG. 5 shows a cross section of the supply device according to line V-V of FIG. 1.

In the feeding device according to FIGS. 4 and 5, the same or the same operating parts for the feeding device according to FIGS. 1 to 3 are referred to by the same reference numerals.

In the second embodiment according to FIG. 4, the recesses 38 are not arranged on the two front faces 28, 29 of the impeller 5, but on the two front walls 15, 16 of the pump chamber 4. It differs from the second embodiment according to Figs. The pressure compensation channel 46 is omitted. The recess 38 is arranged on the front walls 15, 16 of the pump chamber 4 and flows through in the rotational direction of the impeller 5, unlike the arrangement with respect to the impeller 5. Thus, inclined surfaces 39 for hydrodynamic support can be arranged at the downstream ends of the recesses 38 with respect to the flow direction in the axial gap 20, respectively.

The recess 38 is arranged radially inward of the feed channel 14 with respect to the pump chamber 8 in the second embodiment. The recess 38 extends at least approximately parallel to the front walls 15, 16, for example, in the region of the lowest position 40. Downstream, the recess 38 extends into the groove 42 and merges into the groove under reduced depth for hydrodynamic support on the inclined surface 39 rearward with respect to the flow direction in the axial gap 20. Along the upstream, the depth of the recess 38 gradually narrows through the stepped step 43 in the form of steps or through the inclined surface 39 upstream and merges into the groove 42 located forward in the flow direction.

The recesses 38 of the front wall 15 of the pump chamber 4 are symmetrical with respect to the central plane, for example, located in the center between the front walls 15, 16 and extending parallel to the front walls 15, 16. In order to face the recesses 38 of the other front wall 16 of the pump chamber 4.

Figure 6 shows a cross section of a recess arranged in the front wall of the impeller and the pump chamber according to the second embodiment.

In the supply device according to FIG. 6, the same or the same operating parts for the supply device according to FIGS. 1 to 5 are referred to by the same reference numerals.

Claims (10)

A supply device having an impeller disposed in the pump chamber, The impeller is rotationally driven by an actuator and the front wall of the pump chamber includes two facing surfaces, each of which has a plurality of hydrodynamic supports for at least one of the front wall of the impeller and / or at least one of the front wall of the pump chamber. A supply apparatus having a recess of Supply device characterized in that at least two adjacent recesses (38) of at least one front face (28, 29) and / or at least one front wall (15, 16) are connected to each other via respective grooves. 2. Apparatus according to claim 1, characterized in that the recesses (38) and / or grooves (42) are arranged in a circle. 2. Apparatus according to claim 1, characterized in that the recess (38) and / or groove (42) runs in the form of an arc, a partial circle, a slot or the like. 2. Apparatus according to claim 1, characterized in that the recess (38) and groove (42) form a common circle. 2. Apparatus according to claim 1, characterized in that the recess (38) has a greater depth than the groove (42). The recess 38 according to claim 1, wherein the recess 38 is inclined with respect to the front face 28, 29 and / or the front wall 15, 16, respectively, and at least one sloped face for hydrodynamic mounting of the impeller 5. 39). 6. The supply apparatus according to claim 5, wherein the at least one inclined surface 39 is provided adjacent to the next end of the recess 38 with respect to the direction of rotation of the impeller 5 when each arranges the recess. . 6. The at least one inclined surface (39) according to claim 5, characterized in that the at least one inclined surface (39) is provided at the downstream end of the recess (38) respectively when arranging the recess in the front walls (15, 16) of the pump chamber (4). Feeding device. 7. The recess (38) according to claim 6, characterized in that the recesses (38) each have a minimum position (40) extending parallel to at least one front face (28, 29) and / or front wall (15, 16). Feeding device. 2. The recess 38 of claim 1, wherein the recess 38 of the front face 28 of the impeller 5 is positioned opposite the other front face 16 of the impeller 5 symmetrically with respect to the center face 45 and is symmetrical. The recesses (38) which are located opposite each other are connected to each other via a pressure compensation channel (46).

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