• 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 rotor machine and an impeller, the rotor machine of which is intended to operate as a liquid pump or as a stirrer in a fluid such as a liquid or a colloid, the rotor machine having a pump housing (1) with an impeller (2) rotatably mounted about an axis (X). and which rotor machine has three main flow passages comprising; an axial inlet opening (4) with a defined opening area (Ain), - a radially oriented outlet opening (5) with the fi aligned opening area (Aut), and - a series of radially extending blades (3) distributed along the circumference of the impeller forming a number of flow channels (22: 1-22). In order to achieve improved working capacity, the opening area (Ain) of the inlet opening (4), the opening area (Aut) of the outlet opening (5) and the combined effective opening area (22: 1-22) extending through the impeller are so mutually designed that the rotor machine three main passages are filled and emptied of said fluid in a substantially uniform manner. cmoocumenis and seuingsvegmesktopvninau1oso2 P411o2o1ssEoo 1 10509 besk.docx
    公开号:SE1150409A1
    申请号:SE1150409
    申请日:2011-05-09
    公开日:2012-11-10
    发明作者:Ola Eriksson；Daniel Marjavaara
    申请人:Luossavaara Kiirunavaara Ab；
    IPC主号:
    专利说明:

    The object underlying the invention is that problems usually arise due to dimensional and area variations in transitions at flow crossings and that low efficiency is usually caused by flow separation due to rapid deceleration or rapid pressure increase in flow currents to and from a inlet and outlet respectively. In accordance with the invention, this is solved by giving the area of the inlet opening, the area of the outlet opening and the total effective opening area of the flow channel through the impeller such a mutual shape that the rotor machine fills and empties three main passages of liquid in a uniform manner.
    The invention will be described in more detail below with reference to the accompanying drawings, in which; Fig. 1 shows a longitudinal section through a rotor machine according to the invention with an impeller accommodated therein, which device is shown with partially broken away parts, Fig. 2 shows a graphical view of one of an imaginary flow channel formed by adjacent blades on the impeller, the flow channel shape varying between its inlet opening and outlet opening but where the two respective openings have constant cross-sectional areas, Fig. 3 is a perspective view of a piece of an impeller included in the rotor machine illustrating the flow profiles of the medium through the channel delimited between adjacent blades of the impeller, and Fig. 4 shows a cross section through the rotor machine according to the line lV - lV in Fig. 1. Fig. 1 shows a rotor machine of the centrifugal type which in the embodiment described here is intended to operate as a liquid or fluid pump but which in a slightly modified design could function as a stirrer. The rotor machine comprises a helical pump housing 1, i.e. and s.k. diffuser with a worm housing having an inner boundary wall 1a which expands radially outwards relative to the outer periphery 2a of an impeller 2 operating in the pump housing. This impeller 2 is provided along its circumference 2a with blades 3 or wings. Starting from a starting point 1b to a predetermined point 1c of the boundary wall 1a, the shell housing deviates in both axial and radial direction to increase the cross-sectional area A-flow of the fluid path in the direction of a discharge point. The worm-shaped chamber of the pump housing 1 has a suction inlet 4 and a pressure outlet 5 for the fluid. the impeller 2 has a radially extending cover plate which forms a bearing surface 6 for the blades 3. the impeller 2 is rotatably mounted on a shaft 7 and is driven by a drive unit not shown in more detail in the direction of the arrow and in a direction of rotation X. As a result of the impeller 2 rotation, a fluid is sucked in the axial direction, ie. in the longitudinal direction of the shaft via the suction inlet 3 into the helical pump housing and is discharged in the radial direction via the pressure outlet 4. the blade 3 of the impeller 2 has a contoured backwardly curved profile in the direction of rotation. The suction fluid sucked through the suction inlet 4 to the impeller 2 is transported through the blades of the impeller in the radial direction and inside the helical pump housing 1 towards the pressure outlet 5 through which the fluid leaves the rotary machine. 10 cmoocumens and seuingsuegoeskiopvninau1oso2 P411o2o1ssEoo 1 10509 besk.docx 10 15 20 25 30 35 3 denotes the thickened hub with which the impeller 2 is attached to the shaft 7. Drawing indications are in the following made relative to this axis of rotation X unless otherwise stated. The flow through the rotor machine is defined as the volume of fluid per unit time (ms / s), and the flow rate is the velocity of the flow and is given in meters per second (m / s).
    The drawing figures denote a fluid which is sucked in via the suction inlet to the pump housing 1 by the flow arrow Ws, the cross-sectional area of the suction inlet being denoted by Ain. The widest central central part of the impeller 2 at its periphery 2a is slightly smaller than the inner diameter of the pump chamber 1 and said parts are so mutually formed that a successively widening annular gap 12 is formed whose cross-sectional area A-flow, viewed in radial direction, increases gradually in the medium flow direction. Said annular gap 12 thus forms a fluid path which surrounds the impeller 2 along a part of its periphery 2a and which cross-section A-flow of the fluid path increases stepwise in the direction of the pressure outlet 5 of the pump housing 1 (see in particular Fig. 4). The pressure outlet 5 is radially oriented to the chamber 4 and forms part of the pressure side and pressure outlet of the rotary machine, marked with the flow arrow Wd. The cross-sectional area of the pressure outlet 5 is denoted by Aut. As mentioned above, via the suction inlet 4 a fluid is sucked into the pump housing 1, as marked by the arrow Ws. Fig. 3 shows the impeller 2 in a perspective view in which it appears that the bearing surface 6 is radially extended and oriented in a plane perpendicular to the axis of rotation X. From the bearing surface 6 the blades 3 extend both axially upwards with a height denoted by (h) and radially out against the annular gap 12 substantially circumferential in the pump housing 1, the length of the blades being denoted (1).
    Said blade 3 extends perpendicularly from the main surface of the support surface 6 and in radial direction, more precisely between an end 21a facing the rear towards the hub 10 and a front peripheral end 21b.
    The blades 3 are evenly distributed along the circumference of the support surface 6 to form a series of a number of flow channels 22: 1-22 therebetween, each such flow channel having an inlet 23a at the rear end 21a and 21, respectively, of the adjacent blades facing the axis of rotation X. an outlet 23b at the radially leading or free end 21b of the adjacent blades. The cross-sectional area is denoted by A0 for said inlet 21a while the cross-sectional area for said outlet 21b is denoted by A1. Each flow channel 22: 1-22 has a nominal cross-sectional area denoted by Avs. In the following, nominal refers to the respective effective area of a respective flow channel 22: 1-22, ie. the cross section of a respective flow channel 22: 1-22 on the impeller 2 where the flow area is smallest.
    Consequently, it should be understood that the total flow area through the impeller 2, designated A-impl, is obtained as the product of Avs x the number of flow channels (n). Fig. 2 schematically illustrates a flow channel 22: 1 of the impeller 2, wherein said cross-sectional areas A0 and A1, respectively, are hereby defined for simplicity as the product of the distance (b) between adjacent blades 3 and their height (h) in the axial direction, i.e. A0 = b1xh1 and A1 = b2xh2, respectively. The nominal cross-sectional area Avs is here regarded as an infinitely thin volume segment which can be located at any point along the flow channel cmoocuments and settingsuegmesktopvn: nan1o5o2 P411o2o15sEoo 1 10509 besk.docx 10 15 20 25 30 35 4 see also fig. . As described above, the rotor machine forms a centrifugal pump in that during the rotation of the impeller 2 fluid is thrown from the flow channels 22: 1-22 towards the annular gap 12, to flow from there further out of the pump housing via the pressure outlet 5. The outgoing flow from the flow channels 22: 1 -22 gives rise to a negative pressure which sucks in liquid through the suction inlet 4 to the impeller 2. The term blade 3 in the following means a platform or curved which is rotatable about an axis to produce a pressure difference which brings a gaseous or liquid medium to be redistributed and change direction. The blades 3 are suitably tapered with their thickest part adjacent to the center of rotation or hub 10 of the impeller 2 and are in this case single curved, i.e. exhibiting a curvature in only one plane. As an alternative, the blades 3 can be double-curved like blades, ie. The above-described nature constitutes a substantially known technique and as such does not relate to the present invention. Again with reference to Fig. 1 and Fig. 4, as mentioned above, the first generally axially directed suction inlet 4 of the pump housing 1 has been given a defined area Ain and the second generally radially directed pressure outlet 5 of the pump housing has been given a specific area Aut. According to the present invention, these two apertures are equal, Ain = Aut, i.e. Ain / Aut is preferably equal to 1.0 or said ratio is in the range 0.9-1.1. During the rotational movement of the impeller 2 inside the worm-shaped working chamber of the pump housing 1, a hydrodynamic transfer is effected, the fluid leaving the rotor machine via a flow out of the pump housing 1 as illustrated by the arrow Wd. Fig. 4 shows the impeller 2 in a plan view, wherein in this illustrated example the impeller 2 has six blades 3 which are directed backwards in relation to the direction of rotation of the impeller. Between adjacent blades 3, six (n) flow channels 22: 1-22 are thus defined, the width of which denoted b can, but does not necessarily have to be constant. According to the invention, the total flow area of the rotor machine Atot-imp for fluid through the impeller 2 is obtained as the product of the nominal cross-sectional area Avs and the number (s) of flow channels 22: 1-22 over the bearing surface 6 of the impeller 2. An important feature of the present invention is inlet area Ain and outlet area Aut are substantially equal, the feature that the total passage area of the impeller 2, Atot-impl = nx Avs is equal to said inlet outlet areas Ain, Aut of the pump housing 1. Similarly, the cross-sectional area A-flow, for the fluid path is delimited between the outer periphery 2a of the impeller 2 and the circumferential inner boundary wall 1a of the worm-shaped pump housing 1, selected to expand in the radial direction in a certain manner so that a soft successively widening fluid path is delimited. More specifically, the outer wall of the pump housing body or the so-called the coil radially outwards from the periphery of the impeller 2 in such a way that the cross-sectional area A-flow increases stepwise so that the starting point from a starting point 1b of the coil continuously expands so that the cross-sectional area A-cmoocuments and settmgaieguuesktoynm: nan1oso2 P411o2o 109 The flow at each given point 1c of the cross-sectional area A-flow of the flow path along the inside 1a of the screw corresponds to the throughput area Avs for the effective number (n-eff) of the flow channels A-impl of the impeller 2 located between said starting point 1b and a given point 1c along the inside 1a of the screw. That is, ie. A-flow = n-eff x Avs where n-eff consists of the actual number (n) of effective feed channels which are located between said starting point 1b and a given step (n) at a certain end point 1c of the coil.
    Thus, a rotor machine of the present type must carefully consider the dimensioning of the following four flow passages and areas in the constructive design of the machine, namely; - the suction inlet 4 and the area Ain, - the pressure outlet 5 and the area Aut, - the impeller's total opening area A-impl for the sum of the flow channels 22: 1-22 through the impeller calculated as A-impl = nx Avs where the expression Avs refers to the nominal area of each flow channel , and - the radial expansion of the coil with the cross-sectional area A-flow, where A-flow = n-eff x Avs and n-eff consist of the actual number (n) of effective feed channels located between the coil start point 1b and a given end point 1c of the coil.
    Taken together, the present invention is based on the conclusions that the efficiency of the rotor machine can be improved by ensuring that the ratio between Ain, Aut and A-impl is substantially equal to one or that the ratio between any of these parts is in the range 0.9-1.1.
    Fig. 2 schematically shows a profile through an exemplary flow channel 22: 1 of the impeller 2 in which it should be understood that this type of flow channel can have any shape.
    The profile AO defines the cross-sectional area of the inlet opening 22a and the cross-sectional area of the outlet opening A1 22b. The sides of the illustrated flow channel 22: 1 are delimited by two adjacent opposing blades 3, the bottom of the flow channel 22: 1 is delimited by a part of the support surface 6 and its upper surface by a part of an end cap 1d included in the pump housing. The nominal volume of the flow channel 21: 1 is calculated as, length (I) x nominal cross-sectional area (Avs). Opposite upper and lower surfaces 1d, 6 and opposite side surfaces 3, which delimit the specific flow channel 22: 1, can diverge or converge towards or from each other in the flow direction of the flow channel. In the following, the terms "diverging channel" and "converging channel", respectively, mean that two of the opposite delimiting surfaces of the channel diverge and converge from parallelism in an axial direction, however, according to the present invention it is essential that any deformation of the flow channel is achieved with a constant cross-sectional area. That is, regardless of the geometric cross-sectional shape of the flow channel 22: 1, the mutual distance between opposite surfaces and how they converge and diverge relative to each other in the flow channel, it is essential that cmpocumens and seuingsvegweskropnminan1o5o2 10 The flow channel 22: 1 is designed so that the ratio AO / A1 is always substantially equal to 1, where A0 is the outlet area of the flow channel and A1 is the inlet area of the flow channel, so the ratio between A0 and A1 should be equal to one or in each cases are in the range 0.9-1.1, ie the area ratio AO / A1 is for retreating close to or equal to one. In Fig. 3, Avs denotes the nominal cross-sectional area of an infinitely thin volume segment located at an arbitrary point along the specified flow channel 22: 1, the total volume or actual flow capacity of the flow channel being defined by a number of consecutive volume segments. That is, the flow capacity of the flow channel 32: 1 is the sum of any number of such volume segments Avs across the channel where the integration boundaries are constituted by the radial length of the flow channel 31. The ratio between a nominal predetermined area and the volume segment Avs which is moved along a flow section between the inlet opening 22a of the flow channel 22: 1 and the outlet opening 22b, respectively, must according to the invention be equal to one (1), or at least be in the range 0.9 - 1.1, ie. . only deviate about 10% from the nominal value of the Avs of the cross-sectional area. The relationship between a volume segment with nominal cross-sectional area Avs which is moved between the inlet opening 22a of the flow channel 22: 1 and the outlet opening 22b, respectively, should thus partly have the same cross-sectional area along the entire integration distance (channel length) and the same cross-sectional area / said inlet. That is, measured the deviation from the nominal cross-sectional area Avs in the flow channel, ie. Delta Avs (AAvs) should be in the range 0.9 - 1.1. That is, the cross-sectional shape of the flow channel 22: 1 can be varied, but the nominal cross-sectional area Avs of an infinitely thin volume segment moving between inlet / outlet should according to the invention be substantially constant.
    One of the major advantages of the present embodiment of the flow channel 22: 1, i.e. more specifically, the total flow channels 22: 1-22 of the impeller 2, with a constant nominal cross-sectional area Avs along its length is that the flow channel will be filled and emptied uniformly. This is despite the fact that the flow channel 22: 1 at its inlet opening 22a located against the axis of rotation X suitably has a substantially axially extended surface area and that the outlet opening 22b at its peripheral end facing away from the axis of rotation X has a radially extended surface area. From the dimensioning and flow point of view, the mentioned surface area for inlet and outlet, respectively, is of significant advantage. By axially extended shape is meant that the inlet 22a of the flow channel 22: 1 has an axially higher height (h) than the outlet 22b. Similarly, the inlet 22a of the flow channel 22: 1 is narrower and has a smaller width (b) than the outlet 22b.
    The invention is not limited to what is described above and that shown in the drawings, but can be changed and modified in a number of different ways within the scope of the inventive concept stated in the appended claims. cmoocuments and seuingsvegunesktomminau1o5o2 P411o2o1ssEoo 1 10509 besk.docx
    权利要求:
    Claims (1)
    [1]
    A rotary machine intended to operate as a liquid pump or as a stirrer in a fluid such as a liquid or a charcoal, the rotor machine having a pump housing (1) with an impeller rotatably mounted about an axis (X). 2) and which rotor machine has three main flow passages comprising; an axial suction inlet (4) with a defined opening area (Ain), - a radial pressure outlet (5) with a defined opening area (Aut), and - a series of radially extending blades (3) distributed along the circumference of the impeller forming a number flow channels (22: 1-22) with a total opening area (A-impl), characterized in that the opening area (Ain) of the suction inlet (4), the opening area (Aut) of the pressure outlet (5) and the opening through the impeller (2) the total nominal cross-sectional area (Avs) of the extending flow channel (22: 1-32) is so mutually designed that the rotor machine fills three main passages and empties on said fluid in a substantially uniform manner. A rotor machine according to claim 1, wherein the total nominal opening area of a volume segment (Avs) located at any point along a flow distance between the inlet (22a) and the outlet (22b) of each of said flow channels (22: 1-22) : n), is equal to the opening area (Ain) of the suction inlet (4) and the opening area (Aut) of the pressure outlet (5). . Rotor machine according to one of Claims 1 to 2, in which the opening area (Ain) of the suction inlet (4) = the opening area (Aut) of the pressure outlet (5) = A-impl defined as the total nominal opening area (Avs) of all the flow channels (22: 1) of the impeller (2) -22: n). . A rotor machine according to any one of claims 1-3, comprising a combination of any of the following conditions; - that Ain / Aut is in the range 0.9 - 1.1, - that A-impl / Ain is in the range 0.9 - 1.1, - that A-impl / Aut is in the range 0.9 - 1.1, - that A-flow / A-impl ( n-eff) is in the range 0.9 - 1.1. - that AO / A1) is in the range 0.9 - 1, - that AAvs for a flow channel (22: 1-22) is in the range 0.9 - 1.1, where where Ain is the opening area of the suction inlet (4) where Aut is the pressure outlet (5 ) opening area where A-impl is the sum of the nominal cross-sectional area (Avs) of the flow channels (22: 1-22), cxoocumenis and set veg ngsvegvneskiopmirian 1oso2 P411o2o1ssEoo 1 10509 besk.docx 10 15 20 25 30 35 8 8 in the coil annulus formed cross-sectional area and n-eff is the number (n) of effective flow channels (22: 1-22: n) between a start point (1b) and end point (1c) at the coil, where AO is the opening area of an inlet (22a) and A1 is the outlet area of an outlet (22b) of a flow channel (22: 1-22), where AAvs is the deviation from a nominal cross-sectional area (Avs) of a volume segment which is moved between inlets (22a) and outlets (22b) of a flow channel (22: 1-22). An impeller for a rotor machine intended to operate as a liquid pump or as a stirrer in a fluid such as a liquid or a colloid and which impeller (2) is rotatably mounted in a pump housing (1) included in the rotor machine for rotation about an axis (X) and comprising a radially extending support surface (6) as oriented in a plane perpendicular to the axis of rotation carries a series of radially extending blades (3) which distributed along the circumference of the base part between them form a series of flow channels (22: 1-22) where each flow channel has a opening (22a) facing the axis of rotation with an opening area (A0) and a radially outwardly directed opening (22b) with an outlet area (A1), characterized in that each flow channel (22: 1-22) is designed so that it with respect to a volume segment with a nominal cross-sectional area (Avs) which can be located at any point along a flow section between the inlet (22a) and the outlet (22b) of the flow channel, respectively, has a substantially constant cross-sectional area along the entire channel length. Impeller according to claim 5, wherein the deviation AAvs for a flow channel (22: 1-22) with respect to volume segments with a nominal cross-sectional area (Avs) which is moved along a flow section between the inlet (22a) and the outlet (22b) of the flow channel, respectively, is in the interval 0.9 -1.1. Impeller according to one of Claims 5 to 6, in which a respective flow channel (22: 1-22:) has an opening (22a) directed towards the axis of rotation (X) with the opening area (AO) and its radially outwardly directed outlet (22b) with an outlet opening area (A1). ) are essentially the same, but have different geometric cross-sectional shapes. Impeller according to claim 7, wherein the ratio between the inlet area (A0) of a respective flow channel (32: 1-32) and its outlet area (A1) is in the range 0.9 - 1.1, independent of the selected respective cross-sectional shape of the inlet opening (22a) and the outlet opening (22a). 22b). cnoocumenis and seuingsvegvnesktopimman1oso2 P411o2o15sEoo 1 10509 besk.docx 9 9. An impeller according to any one of claims 5 - 8, wherein the blades (3) defining the flow channels (22: 1-22) with respect to their width ( b) in the main plane of the impeller perpendicular to the axis of rotation (X), diverge from each other in the flow direction of the flow channel so that each of said flow channels has a larger radial width i at its outlet (22b) than at its inlet (22a). caoocuments and seuingsuegunesktopvnina 1 1o5o2 P411o2o1ssEoo 1 10509 besk.docx
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    同族专利:
    公开号 | 公开日
    SE536929C2|2014-11-04|
    CA2833860A1|2012-11-15|
    AU2012254210A1|2013-11-07|
    US9546661B2|2017-01-17|
    BR112013028697A2|2017-01-24|
    AU2012254210B2|2016-02-25|
    US20140064947A1|2014-03-06|
    WO2012154118A9|2013-01-10|
    WO2012154118A1|2012-11-15|
    CA2833860C|2019-04-09|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2046226A|1934-12-13|1936-06-30|Cleveland Brass Mfg Company|Centrifugal pump|
    US4253798A|1978-08-08|1981-03-03|Eiichi Sugiura|Centrifugal pump|
    JPH03111697A|1989-09-22|1991-05-13|Jidosha Denki Kogyo Co Ltd|Small centrifugal pump|
    US5316440A|1991-05-10|1994-05-31|Terumo Kabushiki Kaisha|Blood pump apparatus|
    WO1994015102A1|1992-12-29|1994-07-07|Vortex Australia Pty. Ltd.|Pump impeller and centrifugal slurry pump incorporating same|
    AUPN715595A0|1995-12-14|1996-01-18|Warman International Limited|Improved centrifugal pump|
    US6398494B1|1999-05-14|2002-06-04|Argo-Tech Corporation|Centrifugal pump impeller|
    US6779974B2|2002-12-11|2004-08-24|Polyvane Technology Corp.|Device of a volute channel of a pump|
    DE102006003727A1|2006-01-26|2007-08-02|ENTEC GbR |Closed impeller for centrifugal pump operates for conveying homogeneous liquids, especially in cooling systems of motor vehicles|
    DE602006010075D1|2006-09-18|2009-12-10|Ihc Holland Ie Bv|Centrifugal pump and its application|
    US7896617B1|2008-09-26|2011-03-01|Morando Jorge A|High flow/high efficiency centrifugal pump having a turbine impeller for liquid applications including molten metal|
    US20100284812A1|2009-05-08|2010-11-11|Gm Global Technology Operations, Inc.|Centrifugal Fluid Pump|EP3359821B1|2015-10-06|2021-01-27|Nordic Heater AB|Fan assembly comprising fan wheel with inlet and outlet of equal cross section area|
    JP2018178820A|2017-04-10|2018-11-15|日本電産サンキョー株式会社|Pump device|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1150409A|SE536929C2|2011-05-09|2011-05-09|Rotor machine intended to work as a pump or stirrer as well as an impeller for such a rotor machine|SE1150409A| SE536929C2|2011-05-09|2011-05-09|Rotor machine intended to work as a pump or stirrer as well as an impeller for such a rotor machine|
    AU2012254210A| AU2012254210B2|2011-05-09|2012-05-08|Rotor machine intended to function as a pump or an agitator and an impeller for such a rotor machine|
    US14/116,116| US9546661B2|2011-05-09|2012-05-08|Rotor machine intended to function as a pump or an agitator and an impeller for such a rotor machine|
    BR112013028697A| BR112013028697A2|2011-05-09|2012-05-08|rotor machine intended to function as a liquid pump or as a stirrer in a fluid such as a liquid or colloid and impeller for a rotor machine intended to function as a liquid pump or as a stirrer in a fluid such as a liquid or a colloid|
    PCT/SE2012/050487| WO2012154118A1|2011-05-09|2012-05-08|Rotor machine intended to function as a pump or an agitator and an impeller for such a rotor machine|
    CA2833860A| CA2833860C|2011-05-09|2012-05-08|Rotor machine intended to function as a pump or an agitator and an impeller for such a rotor machine|
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