• 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 centrifugal pump (1), in particular water pump, which is designed as a radial pump or Halbaxialpumpe, with a in a housing (2) about an axis (8) rotatably mounted and with a drive shaft (7) connected impeller (3) which Impeller (3) having an impeller blades (6) having impeller main body (4) and an impeller cover body (5), wherein impeller main body (4) and impeller cover body (5) relative to each other via an adjusting device (22) are axially displaceable. In order to achieve an active and reliable control of the centrifugal pump (1) with very low drive power over the entire speed and temperature range, it is provided that the impeller main body (4) axially displaceable on the drive shaft (7) or the impeller cover body (5) is, wherein the adjusting device (22) with the impeller main body (4) is operatively connected.
    公开号:AT517163A1
    申请号:T50398/2015
    申请日:2015-05-13
    公开日:2016-11-15
    发明作者:Gerald Feichtinger
    申请人:Bitter Eng & Systemtechnik Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a centrifugal pump, in particular water pump, which is designed as a radial pump or Halbaxialpumpe, with a rotatably mounted in a housing about an axis and connected to a drive shaft impeller, which impeller has a rotor blades having impeller main body and a Laufraddeckscheibe, wherein for adjusting the impeller outlet width the impeller of the impeller main body and the impeller cover body are axially displaceable relative to each other via an adjusting device.
    Particularly when used as coolant pumps of internal combustion engines for driving vehicles, there is the demand for low minimum coolant flow in the warm-up phase of the internal combustion engine and a needs-based control according to the operation of the internal combustion engine.
    Centrifugal pumps, which can be regulated by impeller outlet width adjustment, are known. The regulation of the impeller outlet width has the advantage of lower losses and a higher efficiency compared to a throttle control over split ring valves, as is known for example from EP 1 657 446 A2, since no energy is destroyed, but only the energy required in each case Fluid is transferred.
    In EP 2 299 120 A1, the impeller blades are connected to a drive and pressure-side impeller support disk. The adjustment of the impeller outlet width between an idle position and a pumping position is effected by a suction-side control disk which has slots corresponding to the impeller blades and co-rotates with the impeller support disk.
    US 4,798,517 A discloses a pump having an impeller-carrying impeller whose exit width is variable by a suction-side control disk, the control disk having slots corresponding to the impeller blades to be slid over the impeller blades. A similar variable geometry centrifugal pump is also known from US 5,169,286 A or US 4,828,455 A, respectively.
    The disadvantage is that in operating areas of the pump, in which the unneeded impeller blade outlet width through the slots of the control disk through in the
    Water space protrudes, relatively high flow losses occur, whereby the efficiency of the pump is deteriorated in these operating areas. A further disadvantage is that this concept only for two-dimensional blade contours, but not for three-dimensional, so spatially curved impeller blade shapes, as known for example from AT 506 342 Bl, DE 100 50 108 A or JP S59-165895 A, can be inserted. With three-dimensionally curved impeller blades, the pump efficiency of centrifugal pumps can be significantly improved.
    Another variable geometry centrifugal pump wherein the impeller vane width is varied by a control disk which is slid over the impeller vanes of the axially immovable impeller is known from US 4,828,454 A. The solution described in this publication differs from the described above all in that the unneeded impeller blade outlet width does not protrude into the water space, but into grooves of the suction-side control disk, which are covered at the impeller suction and impeller outer diameter. Again, flow losses occur, albeit slightly less than in the above publications. The cover plate is moved hydraulically in the axial direction and reset mechanically by means of spring, the impeller blade outlet width is the lower the higher the pump delivery pressure. Therefore, only a flow limitation is possible, but the demands for low minimum flow of coolant in the warm-up phase and needs-based control according to the operation of the internal combustion engine is not feasible. Due to the space requirement of the adjusting mechanism and the return springs in the cover plate open impeller designs can only be used on the suction side, the flow channel can not be optimally designed. A similar solution is also known from US 2005/118018 A, but here an eccentrically mounted adjusting device is provided.
    In the feed pump described in DE 103 44 309 A1, the flow rate change is effected by an axially displaceable control disk arranged on the drive and pressure sides. On the drive shaft, in a region remote from the drive side, conveying blades are arranged which delimit pump delivery spaces with an axial conveying wall. The pump chambers are axially limited on the axial conveying wall side by the end face of the control disk.
    US 6,074,167 A discloses a variable geometry centrifugal pump wherein the impeller has an inner disk and an outer ring between which two-dimensional helically-curved impeller blades are interposed. Between the inner disc and the outer ring is an axially displaceable control disc, which has spiral slots for the impeller blades. By axially displacing the control disc between the inner disc and the outer ring of the impeller by means of an actuator, the impeller blade length can be switched between short impeller blade for low flow rates and long impeller blades for high flow rates.
    Furthermore, from US 2010 006 044 A a variable capacity water pump is known, wherein not the impeller width, but the axial position of the impeller is adjusted. The control is carried out by increasing or reducing the gap losses, whereby the pump must be operated with relatively poor efficiency.
    The invention is therefore based on the object, in centrifugal pumps - especially with spatially curved impeller geometry - over the entire speed and temperature range to ensure an active and reliable control with very low drive power.
    According to the invention, this takes place in that the impeller main body is arranged axially displaceably on the drive shaft, wherein the adjusting device is operatively connected to the impeller main body.
    Under runner main body is here to understand that first part of the multi-part impeller, which carries the impeller blades, so with which the impeller blades are firmly and immovably connected. The second part of the impeller, which closes off the blade channels on the end face facing away from the impeller main body, is referred to here as an impeller cover body. The impeller cover body can deviate from a purely cylindrical disc shape. In particular, the front side of the impeller cover body facing the impeller main body may have an area which is concavely curved, for example, which is designed in accordance with the optimum flow conditions in the vane passages.
    Actively connected means that the adjusting device physically communicates with its function for adjusting the impeller main body with the impeller main body. Depending on the design of the adjustment, this compound may be mechanical, hydraulic, pneumatic or electromagnetic type.
    Preferably, the impeller cover body is rigid, ie non-rotatable and non-displaceable, connected to the pump shaft. The impeller cover body is thus immovably and non-rotatably drivably connected to the drive shaft.
    It is particularly advantageous if the impeller cover body has groove-shaped pockets for receiving the impeller blades on the front side facing the impeller main body, the pockets preferably being closed on the rear side of the impeller cover body facing away from the impeller main body. The depth of the pockets of the impeller cover body is dimensioned so that the pockets when the axial displacement of the impeller main body the impeller blades completely or - up to a defined minimum impeller outlet width - predominantly can accommodate.
    In a particularly advantageous embodiment of the invention, it is provided that the impeller blades-at least within the diameter of the suction mouth-are curved three-dimensionally. This allows particularly good efficiencies of the centrifugal pump. If the spatial curvature of the impeller blades goes beyond the diameter of the suction mouth, then the pockets corresponding to the three-dimensional impeller blade shape can also be curved three-dimensionally. In this case, the impeller main body should be pivotable relative to the impeller cover body about the axis of rotation by at least a defined angular range, to allow a displacement of the impeller blades in and out of the pockets. The angle range is defined by the pitch of the three-dimensionally curved impeller blades. In an axial adjustment of the impeller main body so this is rotated according to the pitch of the impeller blades relative to the angular position of the impeller cover body.
    Apart from this slight relative Ververbewegung during displacement of the impeller main body of the impeller main body is drivingly connected to the impeller cover body and is therefore driven by this, that is rotated about the axis of rotation. This drive connection is most easily done directly by acting in the direction of rotation positive connection between the impeller blades and the pockets. In order to avoid an independent adjustment of the impeller outlet width due to the rotational movement of the impeller, it is favorable if the axial position of the impeller main body can be fixed by the adjusting device in each adjustment position.
    Particularly small adjusting forces for the impeller outlet width adjustment are required when the axially displaceable main impeller body forms the suction port of the centrifugal pump. Especially with three-dimensionally curved impeller blades with closed blade channels, calculations and tests have shown that the impeller exit width adjustment by displacement of the impeller main body brings particular advantages compared to a known from the prior art displacement of a control disk, since much lower adjustment forces are needed. The reason for this is that the compressive forces acting on both sides of the impeller main body at least approximately cancel each other in the suction side arrangement of the impeller main body, so that the resultant axial force acting on the impeller main body is very small or even almost zero.
    In a preferred embodiment it is provided that the impeller main body is arranged on the side facing away from the drive side of the impeller. The impeller cover body is conveniently arranged on the side facing away from the suction mouth drive side of the impeller.
    In order to keep pressure and flow losses as small as possible in each displacement position of the impeller main body, it is particularly advantageous if the impeller main body is sealed on the side facing away from the impeller cover body relative to the housing via at least one labyrinth seal. It is particularly advantageous if in each case a labyrinth seal between the impeller main body and the housing of the pump is arranged both in the region of the suction mouth of the impeller, as well as near the exit from the impeller. The labyrinth seal consists in a known manner of intermeshing elements of the impeller main body and the housing, in the simplest case of an annular projection of the one part which engages in a corresponding shaped and dimensioned annular groove of the other part.
    The adjustment of the impeller main body can be done in various ways mechanically, electromagnetically, pneumatically, hydraulically or thermally.
    Mechanical adjustments can be realized for example by helical or thrust gear.
    In a first embodiment of the invention with a helical gear, the adjusting device can have an actuator verdreh bare threaded spindle and a spindle nut, wherein the threaded spindle is rotatably mounted within the drive shaft designed as a hollow shaft and the spindle nut is in contact with the impeller main body, and wherein the spindle nut and the Impeller main body in the axial direction immovable, preferably rotatable relative to each other, are connected together.
    In a second variant of the invention with a thrust mechanism, the adjusting device may comprise a sliding gear with a push rod which is displaceable via an actuator, which is connected to a push sleeve, wherein the push rod is mounted axially displaceable within the drive shaft designed as a hollow shaft and the push sleeve is connected to the impeller main body , and wherein the thrust sleeve and the impeller main body in the axial direction immovable, preferably rotatable relative to each other, are interconnected.
    In a third embodiment according to the invention with an electromagnetic actuator, it is provided that the electromagnetic actuator has at least one electromagnet fixed to the housing and at least one preferably annular permanent magnet fixedly connected to the impeller main body, wherein preferably the at least one permanent magnet is in the region of an impeller main body and the housing sealing labyrinth seal is arranged.
    The invention will be explained in more detail below with reference to the non-limiting exemplary embodiments.
    Show it
    1 shows a centrifugal pump according to the invention in a first embodiment in a longitudinal section,
    1 shows a centrifugal pump according to the invention in a second embodiment in a longitudinal section, and
    1 shows a centrifugal pump according to the invention in a third embodiment in a longitudinal section.
    Functionally identical parts are provided in the embodiments with the same reference numerals.
    The figures each show a centrifugal pump 1 with a two-part housing 2, in which a multi-part impeller 3 is arranged. The impeller 3 is composed of an impeller main body 4 and an impeller cover body 5, wherein a plurality of three-dimensionally curved impeller blades 6 are fixedly connected to, for example, integral with the impeller main body 4. The impeller cover body 5 is non-rotatably and also non-displaceably connected to a drive shaft 7, which is mounted by means of shaft bearings 9 in the housing 2 rotatably about the axis 8. The drive shaft is driven, for example via a pulley 7a via a traction means not further shown.
    The impeller main body 4 is mounted in each case axially displaceable on the impeller cover body 5. A direct connection between the drive shaft 7 and impeller main body 4 is not provided in the examples. The impeller main body 4 is disposed on the suction side 10 of the centrifugal pump 1 and forms the suction port 11. The impeller cover body 5 is arranged on the drive side 12 and has a front side 13 facing the impeller main body 4 which, together with the impeller blades 6 and the inner side 14 of the impeller main body 4, spans closed blade channels 15. The impeller cover body 5 has on the front side 13 groove-like pockets 16, which are formed according to the three-dimensional curvature of the impeller blades 6. The pockets 16 are designed to be closed towards the rear wheel 17 of the wheel cover body 5 facing away from the wheel main body 4 and designed so that the wheel blades 6 can be inserted at least predominantly.
    The impeller blades 6 and the pockets 16 form a positive locking in the direction of rotation, so that the impeller main body 4 is driven via this form fit by the impeller cover body 5, while the impeller cover body 5 is driven directly by the drive shaft 7.
    In the area of the pressure side 18, the housing 2 of the centrifugal pump forms an outlet spiral 2a.
    The suction-side impeller main body 4 is mounted axially displaceably in the hub 5a of the impeller cover body 5. The impeller blades 6 of the impeller main body 4 can dip in the pockets 16, whereby the impeller vane outlet width b between a minimum value and a maximum value can be adjusted by displacing the impeller main body 4. A smooth sliding of the impeller main body 4 on the impeller cover body 5 can be achieved when the impeller material is modified with lubricants. The pockets 16 in the rotor cover body 5 can be covered with a cover 5b forming the rear side 17 of the rotor cover body 5 in order to avoid pressure-side flow losses.
    In order to avoid flow losses in each position of the impeller main body 4 by short-circuit flows between pressure side 18 and suction side 10, labyrinth seals 20, 21 are arranged between the impeller main body 4 and the housing 2, wherein an inner first labyrinth seal 20 in the region of the suction mouth 11 and an outer second labyrinth seal 21 in the region of the pressure side 18 facing outer diameter 4 b of the impeller main body 4 is provided. Each labyrinth seal 20, 21 consists of intermeshing elements 20a, 20b; 21a, 21b of the impeller main body 4 and the housing 2, that is, for example, an annular projection 20a, 21a of the one part, for example, the impeller main body 4, which engages in a corresponding annular groove 20b, 21b of the other part, for example, the housing 2. The cylindrical projections 20a, 21a form, together with the corresponding annular grooves 20b, 21b of the housing 2, the labyrinth seals 20, 21.
    The impeller main body 4 is displaced via an adjusting device 22 in the axial direction along the axis 8 of the drive shaft 7 against the force of a restoring force formed by a return spring 23.
    The adjustment of the impeller main body 4 can be effected in various ways mechanically, electromagnetically, pneumatically, hydraulically or thermally. In FIGS. 1 and 2, a mechanical adjustment, in Fig. 3, an electromagnetic adjustment is provided.
    Fig. 1 shows a first embodiment of the invention, wherein the adjusting device 22 has a helical gear 24 with a rotatable via an actuator 25 threaded spindle 26 and a spindle nut 27, wherein the threaded spindle 26 and the spindle nut 27 are formed as a coarse thread drive. The threaded spindle 26 is rotatably supported within the formed as a hollow shaft drive shaft 7 via slide bearings 19 and secured axially. Between the threaded spindle 26 and the drive shaft 7, a seal 19 a is arranged. The spindle nut 27 is connected to the impeller main body 4, wherein the spindle nut 27 and the impeller main body 4 are non-slidably and rotatably connected with each other in the axial direction.
    The threaded spindle 26 can be rotated via the actuator 25 clockwise or counterclockwise. The spindle nut 27 is in unregulated operation, for example in case of failure of the actuator 25, of the bearing in the impeller cover 5, designed as a compression spring return spring 23, the hub 4a of the impeller main body 4 and a thrust bearing 28 moves against a stop 29 on the threaded spindle 26, thereby Fail-safe sets the maximum impeller blade outlet width bmax. In controlled operation, the spindle nut 27, depending on the required function, via the actuator 25 and the threaded spindle 26 against the thrust bearing 28, the hub 4a of the impeller main body 4 and the return spring 23 moves and thus set the desired impeller blade outlet width b. The actuator 25 may be formed by a stepper motor 30 and a spur gear 31, for example.
    FIG. 2 shows a second embodiment variant according to the invention, wherein the adjusting device 22 has a thrust mechanism 32 with a push rod 33 and a push sleeve 34. In this case, the push rod 33 is slidably mounted in the hollow drive shaft 7 via slide bearings 19 and sealed by at least one seal 19a. The push rod 33 protrudes centrally through the bearing 35 of the actuator 25, wherein at the first end 33 a of the push rod 33, a stop 29, which may be secured against rotation, is fixedly connected to the push rod 33. The push rod 33 can be moved via the actuator 25 in the direction of the pulley 7a. At the second end 33b of the push rod 33, the push sleeve 34 is fixedly connected to the push rod 33. In unregulated operation, for example in case of failure of the actuator 25, the push rod 33 is moved by the mounted in the impeller cover body 5 return spring 23, the hub 4a of the impeller main body 4 and the thrust bearing 28 in the suction side until the stop 29 on the bearing 35 of the actuator 25th is present, which fails to set the maximum impeller blade outlet width bmax. In controlled operation, the push rod 33, depending on the required function, is moved via the actuator 25 in the direction of the pulley 7a and thus deflected via the push sleeve 34, the thrust bearing 28 and the hub 4a of the impeller main body 4 against the spring formed as a compression spring 23 and thus the desired impeller outlet width b set. The actuator 25 may be, for example, a pneumatic, hydraulic or electric lifting element.
    FIG. 3 shows a third variant according to the invention, wherein the adjusting device 22 has an electromagnetic actuator 25. The adjusting device 22 has at least one permanently connected to the impeller main body 4 permanent magnet 36 and a fixedly connected to the housing 2 electromagnet 37. The permanent magnets 36 and corresponding electromagnets 37 can be arranged in the region of the outer labyrinth seal 21. In uncontrolled operation, for example, in the event of failure of the actuator 25, the impeller main body 4 is moved by the stored in the impeller cover body 5, formed for example as a compression spring return spring 23 and the hub 4a of the impeller main body 4 in the direction of the suction side 10 until the hub 4a of the impeller ha uptkörpers 4 is present at the arranged on the drive shaft 7 stop 29, wherein fail-safe adjusts the maximum impeller blade outlet width bmax. In controlled operation, by appropriate energization of the electromagnet 37, depending on the required function, the impeller main body 4 is moved against the return spring 23 in the direction of the drive side 12 and thus set the desired impeller blade outlet width b.
    In each of the embodiments, an active and reliable control of the centrifugal pump 1 with very low drive power can be achieved over the entire speed and temperature range.
    权利要求:
    Claims (14)
    [1]
    1. Centrifugal pump (1), in particular water pump, which is designed as a radial pump or Halbaxialpumpe, with a in a housing (2) about an axis (8) rotatably mounted and with a drive shaft (7) connected impeller (3), which impeller ( 3) has an impeller main body (4) and an impeller cover body (5), wherein for adjusting the impeller outlet width (b) of the impeller (3) the impeller main body (4) and the impeller cover body (5) relative to each other via an adjusting device ( 22) are axially displaceable, characterized in that the impeller main body (4) is arranged axially displaceably on the drive shaft (7) or the impeller cover body (5), wherein the adjusting device (22) with the impeller main body (4) is operatively connected.
    [2]
    Second centrifugal pump (1) according to claim 1, characterized in that the impeller cover body (5) is rigidly connected to the drive shaft.
    [3]
    3. Centrifugal pump (1) according to claim 1 or 2, characterized in that the impeller cover body (5) on the impeller main body (4) facing the front side (13) groove-shaped pockets (16) for receiving the impeller blades (6), wherein preferably the Pockets (16) on the rear of the impeller main body (4) facing away (17) of the impeller cover body (5) are formed closed.
    [4]
    4. Centrifugal pump (1) according to claim 3, characterized in that the impeller blades (6) - at least in the region of the suction mouth (11) are three-dimensionally curved, wherein preferably the pockets (16) are also three-dimensionally curved according to the three-dimensional impeller blade shape.
    [5]
    5. Centrifugal pump (1) according to claim 4, characterized in that the impeller main body (4) relative to the impeller cover body (5) about the axis (8) is arranged pivotably about at least one defined angular range.
    [6]
    6. centrifugal pump (1) according to one of claims 1 to 5, characterized in that the impeller main body (4) with the impeller cover body (5) is drive-connected and driven by this.
    [7]
    7. Centrifugal pump (1) according to one of claims 1 to 6, characterized in that the impeller main body (4) the suction port (11) of the centrifugal pump (1) is formed.
    [8]
    8. Centrifugal pump (1) according to one of claims 1 to 7, characterized in that the impeller cover body (5) on the suction mouth (11) facing away from the drive side (12) of the impeller (3) is arranged.
    [9]
    9. Centrifugal pump (1) according to one of claims 1 to 8, characterized in that between the impeller main body (4) and the impeller cover body (4) closed blade channels (15) are formed.
    [10]
    10. Centrifugal pump (1) according to one of claims 1 to 9, characterized in that the impeller main body (4) on the the impeller cover body (5) facing away from the housing (2) via at least one labyrinth seal (20, 21) is sealed.
    [11]
    11. Centrifugal pump (1) according to one of claims 1 to 7, characterized in that the adjusting device (22) has a helical gear (24) with a via an actuator (25) rotatable threaded spindle (26) and a spindle nut (27), wherein the threaded spindle (26) is rotatably mounted inside the drive shaft (7) designed as a hollow shaft, and the spindle nut (27) is connected to the impeller main body (4), and wherein the spindle nut (27) and the impeller main body (4) are immovable in the axial direction, preferably rotatable relative to each other, are interconnected.
    [12]
    12. Centrifugal pump (1) according to one of claims 1 to 7, characterized in that the adjusting device (22) has a thrust mechanism (32) with a via an actuator (25) displaceable push rod (33), which with a push sleeve (34) wherein the push rod (33) is axially slidably supported within the drive shaft (7) formed as a hollow shaft, and the push sleeve (34) is connected to the runner main body (4), and the push sleeve (34) and the runner main body (4) in the axial direction immovable, preferably rotatable relative to each other, are connected to each other.
    [13]
    13. Centrifugal pump (1) according to one of claims 1 to 9, characterized in that the adjusting device (22) comprises an electromagnetic actuator (25).
    [14]
    14. Centrifugal pump (1) according to claim 10, characterized in that the electromagnetic actuator (25) has at least one housing-fixed electromagnet (37) and at least one preferably annular permanent magnet (36) which is fixedly connected to the impeller main body (4), wherein Preferably, the at least one permanent magnet (36) in the region of the impeller main body (4) and the housing (2) sealing labyrinth seal (20, 21) is arranged.
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    同族专利:
    公开号 | 公开日
    EP3295034B1|2021-01-20|
    AT517163B1|2019-08-15|
    WO2016179619A1|2016-11-17|
    EP3295034A1|2018-03-21|
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    DE102014217489A1|2013-09-10|2015-03-12|Schaeffler Technologies Gmbh & Co. Kg|Axial, by a shaft extending actuator assembly|FR3071278B1|2017-09-18|2020-02-21|Sogefi Air & Cooling|VARIABLE FLOW PUMP DEVICE AND CIRCUIT COMPRISING SUCH A PUMP|
    CN108119395A|2017-12-10|2018-06-05|安徽银龙泵阀股份有限公司|A kind of centrifugation impeller of pump of variable leaf width|
    CN108302061B|2018-02-06|2019-12-13|宁波吉利罗佑发动机零部件有限公司|Variable flow formula water pump|
    CN111648965B|2020-06-01|2021-09-24|安徽凯润泵阀科技有限公司|Centrifugal water pump|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50398/2015A|AT517163B1|2015-05-13|2015-05-13|ROTARY PUMP|ATA50398/2015A| AT517163B1|2015-05-13|2015-05-13|ROTARY PUMP|
    EP16733866.4A| EP3295034B1|2015-05-13|2016-05-06|Centrifugal pump with sliding rotor|
    PCT/AT2016/050129| WO2016179619A1|2015-05-13|2016-05-06|Centrifugal pump with sliding rotor|
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