• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a coolant pump (4) for an internal combustion engine (1), with a housing (5) having a housing cover (6) in which an impeller (8) rotatable about an axis of rotation (7) is arranged which is coaxial with the axis of rotation (Fig. 7) has a suction mouth (19), wherein the housing (5) forms at least one inlet channel (19) formed substantially normal to the rotation axis (7), to coolant from one of the axis of rotation (7) spaced lateral pump inlet (15) to the suction mouth (19), and wherein the inlet channel (18) has at least one flow-influencing element (20, 21). In order to take up little space and to allow a homogeneous flow of the impeller, it is provided that - viewed in the direction of the axis of rotation (7) - at least one flow-influencing element (20, 21) in the region of a preferably normal to the axis of rotation (7) and / or by the axis of rotation (7) extending longitudinal center axis (18 ') of the inlet channel (18) is arranged.
    公开号:AT517125A1
    申请号:T50375/2015
    申请日:2015-05-07
    公开日:2016-11-15
    发明作者:Robert Dr Pöschl
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a coolant pump for an internal combustion engine, having a housing cover having a housing, in which a rotatable about a rotation axis impeller is arranged, which coaxially to the axis of rotation has a suction port, wherein the housing forms at least one substantially normal to the rotational axis formed inlet channel to Lead coolant from one of the rotational axis spaced side pump inlet to the suction port, wherein the inlet channel has at least one flow-influencing element. Coolant pumps are usually attached to the front side of internal combustion engines and equipped with cantilever feed channels to the wheels in order to achieve the most homogeneous possible flow of the wheels and good efficiencies. The drive is effected, for example, mechanically via a traction means by a crankshaft or a camshaft. Extensive inlet channels have the disadvantage that in the direction of the axis of rotation of the impeller of the coolant pump relatively much space is needed.
    The publications CN 101 782 081 A and CN 103 267 018 A each disclose a coolant pump with a lateral pump inlet, wherein between the pump inlet and the suction port of the impeller of the coolant pump is formed a substantially in a normal plane extending on the axis of rotation of the impeller inlet channel. In this case, a flow-influencing element formed by a guide rib is provided in the area of the suction mouth. Although such pumps have a smaller axial extent, but a homogeneous flow of the wheels is not guaranteed.
    The object of the invention is to develop a coolant pump, which on the one hand requires little space and on the other hand allows a homogeneous flow of the impeller.
    According to the invention, this is achieved in that at least one flow-influencing element is arranged in the region of a longitudinal center axis of the inflow channel, which is preferably designed to run normally on the axis of rotation and / or through the axis of rotation.
    By at least one flow-influencing element, for example, as a cross-sectional reduction device, flow divider or
    Flow homogenization device is carried out, the flow is evenly distributed in the inlet channel over the entire available flow cross-section. As a result, a homogeneous, uniform flow of the suction and high-efficiency operation of the impeller is achieved. At the same time only a small extension of the water pump in the axial direction of an internal combustion engine is possible in the assembled state, whereby space can be saved.
    It is advantageous if - viewed in the direction of the axis of rotation - at least one flow-influencing element is formed symmetrically to the longitudinal center axis of the inlet channel.
    A particularly good homogenization of the flow can be achieved if at least one first flow-influencing element is arranged in the inlet channel between the pump inlet and the suction mouth. In this case, the first flow-influencing element can have, for example-viewed in the direction of the axis of rotation-the shape of a flow divider or an arrowhead facing the flow direction. In a variant of the invention, an embodiment with two adjacent arrow or flow sub-elements, which are arranged symmetrically to the longitudinal center axis, possible
    The first flow-influencing element, which is arranged in the region of the longitudinal central axis, homogenizes the flow through the inlet channel by passing part of the coolant flow sucked through the pump inlet from the region of the longitudinal central axis to the remote outer channel walls. The shape of the flow divider or the arrowhead favors this flow guidance.
    The first flow-influencing element thus has the task of achieving a fanning out of the main flow, so that a part of the flow is forced outwards and distributed around the circumference of the suction mouth.
    In an advantageous embodiment of the invention is further provided that a second flow-influencing element is arranged in the inlet channel in the region of the suction mouth of the impeller. The second flow-influencing element is preferably rotationally symmetrical and arranged coaxially to the axis of rotation. For example, the second flow-influencing element-viewed in the direction of the rotational axis of the impeller-may have the shape of a circle whose diameter preferably corresponds to at least one hub diameter of the impeller and / or at least the diameter of the suction mouth. The flow-influencing element protrudes into the inlet channel as a circular disk lying opposite the suction mouth. The inlet channel ends outside of the circular disk in an annular channel extending through an opening angle of more than 180 °, which is flow-connected in the radial direction to the suction mouth via an annular gap formed by the second flow-influencing element. The annular gap is formed by the distance between the second flow-influencing element and the suction mouth.
    The inlet channel has at least one first inlet channel wall which includes access to the suction mouth and a second inlet channel wall which runs opposite the first inlet channel wall and a third inlet channel wall which connects the first and the second inlet channel wall.
    A particularly effective and simple embodiment of the invention provides that at least one flow-influencing element is formed by a protruding in the direction of the axis of rotation in the inlet channel bulge of a feed channel wall. Conveniently, this is the first or second inlet channel wall, wherein preferably the bulge is formed by the housing, particularly preferably by the housing cover. The second inlet channel wall is part of the housing cover. The first flow-influencing element can be formed by a first bulge and the second flow-influencing element by a second bulge. Conveniently - viewed in a plane defined by the axis of rotation and the longitudinal central axis of the inlet channel cutting plane - between the bulge (or the maximum formation of the bulge) and the opposite inlet channel wall - formed in a direction parallel to the rotation axis -ermost smallest distance, which preferably at least 10% of the width of the inlet channel measured in the direction of the axis of rotation is immediately adjacent (eg downstream or upstream) of the bulge. Furthermore, it is advantageous if - in a normal plane to the axis of rotation - between a flank surface of the first flow-influencing element (or the outer edge of the bulge to the maximum formation of the bulge) and at least one opposing Zulaufkanalwand (eg the first and second Zulaufkanalwand connecting third Inlet channel wall) a measured in a normal plane to the inlet channel wall second smallest distance is formed, which is preferably at least 40% of the diameter of the suction mouth.
    In the direct connection between the pump inlet or the housing feed line and the suction mouth of the impeller - the inlet opening in the impeller of the coolant pump - so at least one flow-influencing element is provided. This flow-influencing element can be embodied as a bulge projecting into the flow of the inflow channel, which reduces the flow in direct connection, but two or more such bulges or indentations are also possible. The aim is to create a flow resistance and to distribute the flow of the coolant pump from one side to the entire circumference. The impression or
    Bulge of the first flow-influencing element preferably does not extend all the way to the opposite channel wall of the inlet channel, but can also be underflowed, wherein between the bulge and the opposite channel wall, a first smallest distance is formed. This first distance below the bulge of the remaining inlet channel is related to the second smallest distance which is measured in a projection in the direction of the axis of rotation on a normal plane of the axis of rotation between the first bulge and the suction mouth of the impeller: the smaller the first distance, the larger the second distance must be in order to allow after the underflow of the first bulge, a convergence of the coolant and a uniform flow around the suction mouth of the impeller.
    In addition, the housing above the suction mouth of the impeller may have a second flow-influencing element designed as a circular bulge, which causes a deflection of the cooling liquid in the direction of the impeller. If the second flow-influencing element has a diameter corresponding to the hub diameter of the impeller, a particularly good and largely swirl-free flow of the impeller of the coolant pump can be achieved.
    In a further variant flow-influencing guide walls, for example baffles, guide ribs or the like, may be provided in the flow path, which feed the flow to the suction mouth in a targeted manner. These baffles can be arranged in a variant of the invention also directly on the edge of the suction mouth. For example, at least one baffle can be arranged directly in the region of the circumference of the suction mouth of the impeller and be straight or slightly helical in order to achieve a corresponding deflection of the cooling liquid. Additionally or alternatively, at least one guide wall can also be arranged in the region between the suction mouth and the pump inlet in the inlet channel.
    It is particularly favorable if two guide walls facing away from one another form a double spiral and are arranged on the side of the suction mouth facing away from the pump inlet such that the two partial flows of the coolant flowing in the circumferential direction on both sides of the suction mouth are led to the suction mouth. The double spiral diverts the coolant, which flows tangentially past the suction mouth of the impeller, in the direction of the suction mouth. Depending on the desired twist, this double spiral can be embodied substantially symmetrically with respect to a plane spanned by the longitudinal central axis of the inlet channel and the axis of rotation or asymmetrically.
    The coolant is first fanned out by the first flow-influencing element in the direction of the jacket of the housing and then radially, so swirl-free fed radially to the suction mouth before it flows axially through the suction mouth in the blade channels of the impeller. In this case, it is particularly advantageous if the inlet channel has a flow cross-section extending widening between an inlet-side first end and a suction-mouth-side second end. The flow cross-section thus increases steadily or continuously from the pump inlet to the suction mouth. Due to the widening cross section, the flow velocity is reduced, which supports the homogenization of the flow. A particularly uniform inflow to the suction mouth can be achieved if - viewed in the direction of the rotation axis - the suction mouth side second end of the inlet channel is designed as a circular sector concentric with the suction mouth, preferably extending the circular sector by an angle of about 180 °. The circular sector-shaped second end of the inlet channel forms a flow-calming collecting space in which turbulence and swirl components in the coolant flow are reduced.
    Compared to known from the prior art embodiments, the invention allows both a reduction in the axial extent of the coolant pump, as well as an optimal efficiency homogenous supply of the cooling liquid to the suction mouth of the impeller. Since the supply of the cooling liquid is not carried out in the direction of the axis of rotation, but normal thereto, smaller space requirements can be met.
    Due to the homogeneous supply of the coolant to the suction mouth, a largely swirl-free flow of the impeller of the coolant pump is achieved. This in turn allows a uniform performance at different operating ranges. Due to the uniform distribution of the coolant mass over the entire circumference of the water pump geometry all pump blades of the coolant pump are simultaneously operated in terms of vibration and pump efficiency in the optimum range.
    The invention is explained in more detail below with reference to the non-limiting figures. Show in it
    1 shows a part of an internal combustion engine with a coolant pump according to the invention in an oblique view,
    2 shows the internal combustion engine in a front view,
    3 shows the drive of the coolant pump of FIGS. 1 and 2,
    4 shows the coolant pump according to the invention in a front view,
    5 shows the coolant pump in a plan view,
    6 shows the coolant pump in a section along the line VI - VI in Fig. 4,
    6a, the coolant pump in a section analogous to FIG. 6, in a variant,
    Fig. 7, the coolant pump in a section along the line VII - VII in Fig. 5 in a first embodiment of the invention and
    Fig. 8, the coolant pump in a section along the line VII - VII in Fig. 5 in a second embodiment of the invention.
    Functionally identical parts are provided in the embodiment variants with the same reference numerals.
    Fig. 1 shows an internal combustion engine 1 with a cylinder head 2 and a cylinder block 3. On the front side of the cylinder head 2 designed as a radial pump according to the invention coolant pump 4 is attached. The coolant pump 4 has a housing 5 with a housing cover 6, in which an impeller 8 designed as a radial impeller or semi-axial impeller and arranged rotatably about a rotation axis 7 is arranged. The drive 13 of the impeller shaft 9 of the impeller 8 takes place in the present case by a camshaft 10 via a toothed belt 11, as shown in FIG. 3 can be seen. Reference numeral 12 denotes the cover of the drive.
    The coolant flows via a supply line 14 into the pump inlet 15, and flows through the coolant pump 4 and is conveyed by the latter through an overflow channel 16 into the cylinder head 2. If appropriate, a thermostatic valve can be arranged in the region of the pump inlet 15. After flowing through the cooling chambers of the cylinder head 2, not shown, the coolant leaves the cylinder head 2 via a drain 17 and is directed to a not further illustrated radiator.
    The housing 5 of the coolant pump 4 forms an inlet channel 18 which extends at least between the pump inlet 15 and the suction mouth 19 of the impeller 8. The inlet channel walls 18a, 18b, 18c of the inlet channel 18 in this case have access to the suction mouth 19 comprehensive first inlet channel wall 18b, one of the first inlet channel wall opposite extending second inlet channel wall 18c and the first 18b and second inlet channel wall 18c connecting third inlet channel wall 18a. These are formed by the housing jacket 5a, by the housing bottom 5b (third inlet channel wall 18a) and by the housing cover 6 (second inlet channel wall 18c). Between an inlet-side first end 181 and a suction-mouth-side second end 182 of the inlet channel 18, the flow cross-section of the inlet channel 18 expands (or continuously continuously). Viewed in the direction of the axis of rotation 7, the suction mouth side second end 182 of the inlet channel 18 as
    Circular sector 182 'concentric with the suction mouth 19 carried out, which circular sector 182' extends through an angle α of about 180 °, as can be seen well in Fig. 4.
    In the inlet channel 18, a first flow-influencing element 20 formed by a first protrusion 20a of the second inlet channel wall 18c of the housing cover 6 is formed, which-when viewed in the direction of the axis of rotation 7-substantially has the shape of a counter to the coolant flow S in the inlet channel 18 directed arrowhead. The first bulge 20a is formed by the housing cover 6 in the exemplary embodiments.
    Between the first flow-influencing element 20 and the opposite first inlet channel wall 18b, a first distance h is measured, measured in the direction of the axis of rotation 7, which at least 10% of the width b of the inlet channel 18, measured in the direction of the axis of rotation 7, immediately adjacent, e.g. downstream or upstream of the first flow-influencing element 20 (Figures 6, 6a). The first distance h extends between the maximum shape of the bulge 20a and the first inlet channel wall 18b. Between a flank surface 20b of the first flow-influencing element 20 and at least one opposing inlet channel wall (here, for example, the third inlet channel wall 18a, the housing shell 5a) is further formed in a normal plane Ei on the inlet channel wall 18a measured second distance k, which is at least 40% of the diameter D of the suction mouth 19 is (Fig. 4). Here, as the flank surface 20b, the region from the outer edge of the bulge 20a and the first flow-influencing element 20 for maximum molding is e.g. the bulge 20a.
    The first flow-influencing element 20 is spaced from the suction mouth 19, (or arranged between pump inlet 15 and suction mouth 19), wherein a - measured in a normal plane ε2 on the axis of rotation 7 - third distance x between the first flow-influencing element 20 and the suction mouth 19 at least the double diameter D of the suction mouth 19 is.
    Furthermore protrudes into the flow S of the inlet channel 18 as a second recess 21a of the channel wall 18c of the inlet channel 18 formed second flow-influencing element 21, which here also by the
    Housing cover 6 is formed. The second flow-influencing element 21 has - viewed in the direction of the axis of rotation 7 of the impeller 8 - the shape of a circular disc whose diameter D2i at least the hub diameter d of the impeller 8 corresponds. In particular, it is favorable if the diameter D2ib of the dome 19 facing the dome 21b of the second bulge 21a is approximately equal to the hub diameter d. The inlet geometry formed by the housing bottom 5b to the impeller 8 has in the region of the suction mouth 19 a defined radius r for the flow-favorable axial deflection of the radial inlet flow S. As shown in FIG. 6 a, the region of the housing bottom 5 b surrounding the suction mouth 19 can form an annular bead 51 narrowing the radial flow cross-section, which is arranged between the surrounding annular space 183 in the outer region of the second end 182 of the inlet channel 18 and the suction mouth 19. The bead 51 may be formed circumferentially, or have radial interruptions or projections, which serve as the suction port 19 directed radial flow guide. The bead 51 increases the freedom of design for the outer contour of the housing 5. In place of the bead 51 and individual local radial dents can be provided. Of course, it is also possible to additionally or instead of the bead 51, the interruptions, projections or indentations provide radial guide ribs 52 or vanes, which guide the flow from the surrounding annular space 183 to the suction port 19. Individual such guide ribs 52, which are indicated only schematically in FIG. 4, can be distributed uniformly over the circumference around the suction mouth 19.
    The first flow-influencing element 20 is also at a distance from the second flow-influencing element 21, wherein the fourth distance y between the first flow-influencing element 20 and the second flow-influencing element 21 measured in a normal plane ε2 on the rotation axis 7 is at least 40% of the diameter D of the suction mouth 19 (Fig. 6.6a).
    Fig. 7 shows a coolant pump without additional guide surfaces. The housing cover is removed, therefore, first and second flow-influencing elements are not apparent. The impeller 8 is indicated schematically by dashed lines. The partial flows Si, S2 formed by the flow-influencing elements 20, 21 flow along the circumference of the suction mouth 19.
    The embodiment of the invention shown in FIG. 8 differs from FIG. 7 in that in the area of the suction mouth-side second end 182 of the inlet channel 18, two guide walls 22a, 22b facing away from one another and forming a double spiral 22 on the side of the suction mouth 19 facing away from the pump inlet 15 are arranged so that the two in the circumferential direction on both sides of the suction mouth 19 flowing partial flows Slr S2 of the coolant to the suction port 19 are performed. By the double spiral 22, the tangentially flowing past the suction mouth 19 of the impeller 8 coolant in the direction of the suction mouth 19 is redirected. The guide walls 22a, 22b are formed in the exemplary embodiment substantially symmetrical to a plane defined by the longitudinal central axis 18 'of the inlet channel 18 and the axis of rotation 7 ε3. The longitudinal central axis 18 'can - viewed in the direction of the axis of rotation 7 - form an axis of symmetry of the inlet channel 18. If an input twist is desired on entering the suction mouth 19, the guide walls 22a, 22b may also be designed asymmetrically.
    The coolant is first fanned out by the first flow-influencing element 20 in the direction of the housing jacket 5a and then supplied to the suction mouth 19 substantially radially with respect to the axis of rotation 7, ie homogeneously, ie without swirling or at least with little twist. Thereafter, it flows axially, ie in the direction of the axis of rotation 7, through the suction mouth 19 into the blade channels of the rotor 8. The circular sector-shaped second end 182 of the inlet channel 18 forms a flow-calming collecting space in which turbulence and swirl components in the coolant flow are reduced.
    The coolant pump 4 according to the invention allows both a reduction of the installation space in the direction of the axis of rotation 7, as well as an optimal homogeneous homogenous supply of the cooling liquid to the suction port 19 of the impeller eighth
    Due to the homogeneous supply of the coolant to the suction port 19, a largely swirl-free flow of the impeller 8 of the coolant pump 4 is achieved. This in turn allows a uniform performance at different operating ranges. Due to the uniform distribution of the coolant mass over the entire circumference of the water pump geometry all pump blades of the coolant pump 4 are simultaneously operated in terms of vibration and pumping efficiency in the optimum range.
    权利要求:
    Claims (16)
    [1]
    1. Coolant pump (4) for an internal combustion engine (1), with a housing cover (6) comprising a housing (5) in which a about an axis of rotation (7) rotatable impeller (8) is arranged, which coaxial with the axis of rotation (7) a suction mouth (19), wherein the housing (5) at least one substantially normal to the rotation axis (7) formed inlet channel (19) is formed to coolant from one of the rotation axis (7) spaced side pump inlet (15) to the suction mouth (19 ), and wherein the inlet channel (18) at least one flow-influencing element (20, 21), characterized in that at least one flow-influencing element (20, 21) in the region of a preferably normal to the axis of rotation (7) and / or by the axis of rotation (7) extending longitudinal center axis (18 ') of the inlet channel (18) is arranged.
    [2]
    Second coolant pump (4) according to claim 1, characterized in that at least one flow-influencing element (20, 21) is formed symmetrically to the longitudinal central axis (18 ') of the inlet channel (18).
    [3]
    3. Coolant pump (4) according to claim 1 or 2, characterized in that at least one first flow-influencing element (20) in the inlet channel (18) between the pump inlet (15) and the suction mouth (19) is arranged.
    [4]
    4. coolant pump (4) according to one of claims 1 to 3, characterized in that at least a second flow-influencing element (21) in the inlet channel (18) in the region of the suction mouth (19) is arranged.
    [5]
    5. coolant pump (4) according to claim 4, characterized in that the second flow-influencing element (21) is rotationally symmetrical and coaxial with the axis of rotation (7) is arranged.
    [6]
    6. Kühlmittepumpe (4) according to claim 4 or 5, characterized in that - viewed in the direction of the axis of rotation (7) - the second flow-influencing element (21) has the shape of a circle, wherein preferably the diameter (D2i) of the circle at least one Hub diameter (d) of the impeller (8) corresponds.
    [7]
    7. coolant pump (4) according to one of claims 1 to 6, characterized in that at least one flow-influencing element (20, 21) by a in the direction of the axis of rotation (7) in the inlet channel (18) protruding bulge (20a, 21a) of a Inlet channel wall (18c) is formed.
    [8]
    8. Coolant pump (4) according to claim 7, characterized in that - viewed in a plane defined by the axis of rotation (7) and the longitudinal center axis (18 ') of the inlet channel (18) cutting plane (ε3) - between the first flow-influencing element (20) and the opposite inlet channel wall (18b) has a first smallest distance (h) measured in a direction parallel to the axis of rotation (7), which is preferably at least 10% of the width (b) measured in one direction parallel to the axis of rotation (7) Inlet channel (18) immediately adjacent to the first flow-influencing element (20).
    [9]
    9. coolant pump (4) according to claim 7 or 7, characterized in that - viewed in a normal plane (ε2) on the axis of rotation (7) - between a flank surface (20b) of the first flow-influencing element (20) and at least one opposite inlet channel wall ( 18a) a in a normal plane (ει) on the inlet channel wall (18a) measured zerer smallest distance (k) is formed, which is preferably at least 40% of the diameter (d) of the suction mouth (19).
    [10]
    10. The coolant pump (4) according to any one of claims 1 to 9, characterized in that the first flow-influencing element (20) from the suction port (19) and / or from the second flow-influencing element (21) is spaced.
    [11]
    11. The coolant pump (4) according to claim 1, characterized in that a third smallest distance (x) between the first flow-influencing element (20) and the suction mouth (19) in a normal plane (ε2) on the rotation axis (7) ) is at least twice the diameter (d) of the suction mouth (19).
    [12]
    12. The coolant pump (4) according to one of claims 1 to 11, characterized in that measured in a normal plane (ε2) on the axis of rotation (7) a fourth smallest distance (y) between a first flow-influencing element (20) and a second flow-influencing Element (21) is at least 40% of the diameter (d) of the suction mouth (19).
    [13]
    13. Coolant pump (4) according to one of claims 1 to 12, characterized in that in the inlet channel (18) at least one coolant in the direction of the suction mouth (19) directing guide wall (22a, 22b) is arranged.
    [14]
    14, coolant pump (4) according to claims 13, characterized in that two mutually remote guide walls (22a, 22b) form a double spiral (22) and on the pump inlet (15) facing away from the suction mouth (19) - preferably substantially symmetrically one through the longitudinal center axis (18 ') of the inlet channel (18) and the axis of rotation (7) of the impeller (8) spanned plane (ε3) - are arranged.
    [15]
    15. coolant pump (4) according to one of claims 1 to 14, characterized in that the inlet channel (18) has an extending between an inlet-side first end (181) and a suction mouth second end (182) extending flow cross-section.
    [16]
    16, coolant pump (4) according to claims 15, characterized in that the suction mouth side second end (182) of the inlet channel (18) is designed as co-axial with the suction mouth (19) executed circular sector (182 '), wherein preferably the circular sector (182 ') by an angle (a) of about 180 °. 2015 05 07 Fu
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    引用文献:
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    DE102020116359A1|2020-06-22|2021-12-23|Man Truck & Bus Se|Device for conveying a coolant|GB180823A|1921-03-31|1922-06-08|George Ure Reid|Improvements in centrifugal pumps|
    DE19510812A1|1995-03-24|1996-09-26|Klein Schanzlin & Becker Ag|Centrifugal pump|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50375/2015A|AT517125B1|2015-05-07|2015-05-07|COOLANT PUMP FOR A COMBUSTION ENGINE|ATA50375/2015A| AT517125B1|2015-05-07|2015-05-07|COOLANT PUMP FOR A COMBUSTION ENGINE|
    PCT/AT2016/050133| WO2016176712A1|2015-05-07|2016-05-09|Coolant pump for an internal combustion engine|
    EP16736764.8A| EP3292311A1|2015-05-07|2016-05-09|Coolant pump for an internal combustion engine|
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