EP2618939B1 - Regner - Google Patents

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Publication number
EP2618939B1
EP2618939B1 EP10757206.7A EP10757206A EP2618939B1 EP 2618939 B1 EP2618939 B1 EP 2618939B1 EP 10757206 A EP10757206 A EP 10757206A EP 2618939 B1 EP2618939 B1 EP 2618939B1
Authority
EP
European Patent Office
Prior art keywords
turbine
wall
sprinkler according
sprinkler
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10757206.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2618939A1 (de
Inventor
Michael Kistler
Thomas Renner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Husqvarna AB
Original Assignee
Husqvarna AB
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Publication date
Application filed by Husqvarna AB filed Critical Husqvarna AB
Priority to PL10757206T priority Critical patent/PL2618939T3/pl
Publication of EP2618939A1 publication Critical patent/EP2618939A1/de
Application granted granted Critical
Publication of EP2618939B1 publication Critical patent/EP2618939B1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
    • B05B3/02—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements
    • B05B3/04—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet
    • B05B3/0409—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements
    • B05B3/0418—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine
    • B05B3/0422—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine with rotating outlet elements
    • B05B3/0431—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine with rotating outlet elements the rotative movement of the outlet elements being reversible

Definitions

  • the invention relates to a sprinkler.
  • Sprinklers as garden irrigation devices typically have a sprinkler head forming a water outlet with a nozzle arrangement which is pivotable about a pivot axis relative to a body containing a water inlet.
  • the pivot axis is typically vertical, horizontally aligned with square sprinklers.
  • the pivoting of the sprinkler head is usually carried out via a rain gear, which is driven by a turbine wheel.
  • the turbine is preferably reversibly rotatable in two opposite directions of rotation, for which the drive water flow two separate supply ducts and a switching means arranged upstream of the channels, which switchably connects one of the supply ducts to the water inlet, are provided.
  • a water flow from the water inlet to the water outlet flows at least partially as a drive water flow across the turbine and typically as a bypass water flow via a spring-loaded valve, the bypass water flow being mostly greater than the drive water flow.
  • Such arrangements are well known.
  • Such a sprinkler with a turbine driven by a turbine is known.
  • the individual turbine blades form pocket-shaped cavities which open with narrow radial slots to a cavity surrounded by the ring of the turbine blades.
  • Two supply channels lead with round, parallel to the turbine axis first sections of a switching device upwards and open into narrower second sections, which arcuately surround the turbine in opposite angular segments. Of the second sections each have a plurality of narrowing nozzle channels angled away in the direction of the turbine.
  • a problem with such sprinklers is that, due to the system, the force exerted on the turbine by the drive water flow is small and therefore there is a risk that the turbine will not start up during a restart or one of the numerous switchover operations. Since the sprinklers for garden irrigation in the production should be inexpensive, the design options are limited.
  • the present invention has for its object to provide a sprinkler with a turbine driven by a rain gear, in which the startup behavior of the turbine is further improved with little effort.
  • the measures according to the invention significantly improve the flow properties of the water path through which the drive water flow flows.
  • the inventors have recognized that by the described measures a reduction of vortices can be achieved and thereby the energy losses of the drive water flow can be greatly reduced, so that a higher proportion of energy remains for acting on the turbine forces and causes a higher starting torque can be.
  • a first significant improvement results from redesigning a deflection region, in which the course of a supply channel from a first channel portion with substantially parallel flow to the turbine axis flow into a second channel section, wherein the flow direction of the second channel section extends substantially in a direction perpendicular to the turbine axis plane ,
  • the second channel section advantageously extends arcuately around the space in which the turbine is arranged.
  • the deflection region is designed to be streamlined and low-turbulence, so that at least one outer wall delimiting the outer path of the channel in the region of the deflection with respect to the flow direction change is formed curved.
  • a fictitious deflection axis can be assumed.
  • the first outer wall is with respect to such a deflection axis radially outer boundary of the supply passage in the region of the deflection.
  • the curvature radius of the first outer wall may vary over the course of the deflection and is advantageously not less than 30%, in particular not less than 60% of the height of the supply duct in the region of the deflection.
  • the respective smallest radial distance of the outer wall of a supply duct radially inner first inner wall is limited, wherein in parallel to the fictitious deflection axis not constant cross section of the supply duct in the region of the deflection Consideration should be made at the centroid of the cross section of the supply channel in the region of the deflection.
  • the first inner wall of the supply channel extends in the region of the deflection kink-free and step-free, in particular monotone curved, wherein the optionally varying radius of curvature of the inner wall is advantageously not less than 20%, in particular not less than 40% of said height of the supply duct.
  • the supply channel is limited in the region of the deflection by surfaces of a lower part and a lid attached thereto, wherein the first channel section is formed between a switching device and the region of the deflection in the lower part.
  • the first inner wall is advantageously formed on the lower part and the first outer wall on the lid, resulting in an advantageous design of injection molds for lower part and lid for the curved course of the boundary of the supply duct in the region of the deflection.
  • the third channel section Another significant improvement results from the streamlined and low-Verwirklebarmen design of an ending at the Anströmdüse last channel section, hereinafter referred to as the third channel section, for which an angular extent of at least 30 ° was assumed around the turbine axis.
  • the design provides that a relative to the turbine axis radially outer lying, the supply channel limiting outer wall, which is also referred to below as the third outer wall, kink-free continuously curved.
  • the radius of curvature of the third outer wall is advantageously not less than 15%, in particular not less than 25% of the radius of the turbine, by which the outer radius of the annular arrangement of the turbine blades is understood.
  • the radius of curvature may vary in the course of the third channel section.
  • the third channel section advantageously extends with the constriction towards the continuous constriction, which increases with a towards the Anströmdüse Speed of the drive water flow is connected. Due to the crease-free continuously curved course of the third channel section results in a lack of or low turbulence low flow resistance and a high exit velocity of the drive water flow from the Anströmdüse in the direction of the turbine blades and an advantageous high torque to the turbine.
  • the inner wall of the third channel portion advantageously also runs kink-free and step-free, in particular also monotonically curved.
  • baffles such that they are inclined at the radial inner end edge with an outflow angle against a radial line, when flowing out of water from a currently acted upon by the Anströmdüse space between each other assigning baffles in a surrounded by the ring of the turbine blades Intermediate space one outflow direction of the water with one of the respective direction of rotation of the turbine opposite tangential flow component, which provides a power contribution to the starting torque of the turbine.
  • the fins are concaved away from the gap.
  • the turbine blades advantageously each have two guide surfaces facing away from each other and each associated with one of the two directions of rotation of the turbine and are preferably narrower in their radially outer ends than at the radially inner ends.
  • the gaps existing at the radially inner ends of the turbine blades between two guide surfaces to be oriented, through which water flows out of the intermediate space at said outflow angle, have a width in the circumferential direction which is advantageously between 30% and 200%, preferably between 50% and Is 150% of the distance of successive gaps.
  • the distance between successive gaps is usually equal to the maximum width of the turbine blades at their radially inner ends.
  • Fig. 1 shows in a slightly inclined oblique view of a partially cut rain gear whose housing has a lower part UT and an upper part OT, which are made as separate components, in particular as injection molded parts and then joined together in the manner shown.
  • the housing is shown partially cut and gives in particular the view into two supply channels. Only indicated by a broken line is a switching device UE, by means of which one of two supply ducts can be connected to the water inlet of the sprinkler.
  • a sprinkler head can be connected to a nozzle arrangement, such a connected sprinkler head being bidirectionally and bidirectionally pivotable about a rotation axis DA by means of the water-flowed sprinkler mechanism.
  • the axis of rotation DA is vertical for sector sprinklers in the regular operating position, horizontal for square sprinklers.
  • Fig. 1 can be seen as part of the lower part of two first channel sections K11 a first supply channel and K21 a second supply channel, which continue via deflection, which are described in detail, continue in second channel sections K12 of the first supply channel and K22 of the second supply channel.
  • the two supply channels are substantially mirror-symmetrical with respect to a center plane containing a turbine axis.
  • the first channel sections K11, K21 run between the switching device UE downstream in the direction of the deflection regions substantially vertically and parallel to a turbine axis of a turbine of the sprinkler gear, wherein the turbine axis typically and in the illustrated embodiments is parallel to the axis of rotation DA.
  • the second channel sections K12, K22 run as shown in the illustration Fig. 2 can be seen, arcuately about a turbine TR, which is rotatably mounted about a turbine axis TA.
  • the second channel sections merge into third channel sections K13, K23, which terminate at an inflow nozzle AD and extend in the flow direction in front of it over an angular range W3 of at least 30 °.
  • the second channel sections and the third channel sections with continuous curvature pass continuously and without kinking into one another.
  • the flow of the drive water flow is deflected from an initially vertical main flow direction in the first channel section K11 to a horizontal one with respect to the turbine axis when entering the second channel section TA approximately tangential main flow direction, so that the change of the main flow direction over the region of the deflection is about 90 °.
  • An arrow MS represents the center of the flow.
  • Such a deflection by 90 ° can be assigned a fictitious deflection axis whose direction is perpendicular to both the first and to the second main flow direction and which lies in the inner angle of the two main flow directions and with respect to which a radially outer boundary of the supply channel and a radially inner boundary of the Supply ducts in the area of the deflection exists.
  • the radial with respect to such a fictitious deflection axis The outer boundary of the supply channel is given by a first outer wall AU1, the inner boundary by a first inner wall IU1.
  • the first outer wall AU1 is curved away from the interior of the supply channel, wherein the radius of curvature in the course of the outer wall AU1 in the flow direction can also vary. For a location of the outer wall, a radius of curvature RA is drawn.
  • the first inner wall IU1 is curved toward the interior of the supply passage in the region of the deflection.
  • a radius of curvature RI is likewise drawn for one point.
  • the distance of the first inner wall IU1 from the first outer wall AU1 is referred to as the height UH of the supply duct in the region of the deflection.
  • the radii of curvature RA and RI and the height UH can vary over the course of the deflection region.
  • the depth of the supply channel measured as a cross-sectional dimension in the direction of the fictitious deflection axis UA, advantageously remains substantially unchanged during the deflection from the end of the first channel section K11 to the beginning of the second channel section K12. If the cross section of the supply duct deviates from a rectangular shape in the region of the deflection, the depth of the supply duct, the height UH of the supply duct and the radii RA of the first outer wall AU1 and RI of the first inner wall IU1 are in each case going through the flow center and substantially perpendicular to measured in these directions.
  • the radius of curvature RA is advantageously not less than 30%, in particular not less than 60% of the maximum height UH of the supply duct in the area of the diversion.
  • the radius of curvature RI of the first inner wall IU1 is advantageously not less than 20%, in particular not less than 40% of the height UH.
  • the curvature of the first outer wall surface AU1 and the first inner wall surface IU1 having radii of curvature having minimum values advantageously results in a flow deflection in which turbulences of the flows at typical flow rates of the drive water flow are avoided or at least greatly reduced compared with known designs.
  • energy losses of the drive water flow can be advantageously avoided at this point and a higher drive power of the drive water flow to the turbine can be achieved, resulting in a higher start-up torque and improved start-up characteristics of the turbine.
  • the first inner wall surface IU1 of the supply duct is advantageously formed on the lower part UT and the first outer wall AU1 on the upper part OT.
  • This results in an advantageous embodiment of injection molding tools by injection molding tools for both the lower part and the upper part can be designed so that each mold halves in the direction of the axis of rotation relative to each other movable and no additional, the cost of a tool and the injection molding production increasing tool components such as slide or the like are required.
  • the upper part OT forms in the illustrated example, a downwardly open pot shape, which engages around the lower part with its outer wall outside, as a lid on the lid surface DE in the direction of the lower part, as an extension VD projecting the first outer wall AU1 is formed.
  • the extension VD forming the first outer wall AU1 of the cover surface DE engages closely the vertical wall of the supply channel formed in the lower part in continuation of the first channel section K11.
  • Other transitions with complementary steps at the transition from the lower part to the upper part in the region of the first outer wall AU1 in the region of the deflection are likewise possible. Small disturbances of uniform continuous curvature at such transitions are not taken into account for the radii of curvature mentioned.
  • Fig. 2 narrowed in an advantageous embodiment of the feed channel in the second channel section K11 kink-free and stepless continuously and goes continuously into a third channel section K13, which leads up to the Anströmdüse AD.
  • the second channel section K12 can also be designed with a constant cross section.
  • the third channel section K13 is continuously narrowed in its course to the Anströmdüse AD, whereby the flow rate of the water of the drive water flow to the Anströmdüse AD increases.
  • the third channel section K13 is advantageously a continuously curved outer wall A3 and / or a continuously curved inner wall I3. Outer wall A3 or inner wall I3 may also have a straight course on the Anströmdüse AD.
  • the radius of curvature of the outer wall A3 is advantageously not less than 20%, in particular not less than 40% of the radius RT of the turbine TR.
  • the radius of curvature of the inner wall 13 is advantageously not less than 15%, in particular not less than 25% of the radius RT of the turbine TR.
  • the following as inflow angle (EW in Fig. 5 ) designated angle between the main flow direction of the exiting from the Anströmdüse AD ES water relative and the tangential direction of the turbine at the Anströmdüse is advantageously not more than 45%.
  • the second and third channel sections which are not clearly separated in a continuous transition, are for the purposes of explanation of the invention in FIG the manner delimited against each other that the third channel section over an angular segment W3 of at least 30 ° to the turbine axis TA before the Anströmdüse AD extend.
  • a third channel section defined in this way is also at an in Fig. 3 sketched variant with more complex structure of the supply channel given.
  • the second channel section K12 is continued not only into the third channel section K13, but also into an additional auxiliary channel KH which leads to an additional turbine nozzle facing upstream of the inlet nozzle AD.
  • the motive water flow flows from the on-air nozzle AD to the turbine blades of the turbine TR and applies thereto a force or a torque.
  • the drive water flow is passed in an advantageous embodiment in an area surrounded by the annularly arranged turbine blades interior IR.
  • the bypass water flow which is quantitatively larger in most cases than the drive water flow, passed through the interior IR, wherein a spring-loaded bypass valve in the bypass path upstream of the interior IR is arranged, so that the previously recombine separate flow paths in the interior IR and continue in the direction of the connection GA or the water outlet of a nozzle arrangement connected thereto.
  • Fig. 4 shows a preferred embodiment of a turbine TR with a plurality of turbine blades TS, which are arranged in a regular array about a turbine axis TA annular and formed as axial projections of a common carrier ring SR.
  • the turbine blades have in this advantageous embodiment, a shape of the guide surfaces, which in reference to the Fig. 5 described in more detail advantageous effect an additional contribution to the torque acting on the turbine, in particular for the start-up of the turbine.
  • the turbine blades TS are mirror-symmetrical with respect to mirror planes extending through the turbine axis TA, whereby such a mirror symmetry also applies to the intermediate spaces ZR between successive turbine blades with respect to mirror symmetry planes extending through the intermediate spaces and containing the turbine axis TA due to the regular arrangement of the turbine blades.
  • Such mirror symmetries are common in bidirectionally driven turbines of rain gearboxes.
  • a drive water flow emerging from the drive nozzle AD has a main flow direction ES at the exit from the flow nozzle AD, which is inclined by an angle EW against the tangential direction of the turbine rotation circle by an inflow angle EW, such an inflow angle advantageously not being greater as 45 °.
  • Out of the onflow nozzle AD in the space between two adjacent turbine blades inflowing water is displaced water from this gap ZR at the same time, which flows through a gap LU between the relative to the turbine axis TA radially inner end edges of the gap ZR standing opposite limiting vanes in the interior IR.
  • the guide surface acted upon by the water flow from the onflow nozzle AD can advantageously be curved concavely away from the intermediate space ZR.
  • the guide surface acted on by the drive water flow from the onflow nozzle AD runs at its end, which is located inside the turbine axis TA, at an outflow angle AW, inclined towards the radial line into the interior space.
  • Water displaced from the intermediate space ZR therefore has, as it leaves the intermediate space ZR, a flow direction AS through a gap LU between adjacent turbine blades which is directed counter to the radial direction against the direction of rotation DR of the turbine assigned to the inflow nozzle AD.
  • the exit angle AT is advantageously at least 15 °, in particular at least 25 °.
  • the outflow angle is advantageously not greater than 50 °.
  • the width LL of the gaps LU is advantageously between 30% and 200%, preferably between 50% and 120% of the distance LS of adjacent gaps.

Landscapes

  • Hydraulic Turbines (AREA)
  • Nozzles (AREA)
EP10757206.7A 2010-09-24 2010-09-24 Regner Active EP2618939B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10757206T PL2618939T3 (pl) 2010-09-24 2010-09-24 Zraszacz

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/064108 WO2012037979A1 (de) 2010-09-24 2010-09-24 Regner

Publications (2)

Publication Number Publication Date
EP2618939A1 EP2618939A1 (de) 2013-07-31
EP2618939B1 true EP2618939B1 (de) 2016-02-10

Family

ID=44064916

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10757206.7A Active EP2618939B1 (de) 2010-09-24 2010-09-24 Regner

Country Status (5)

Country Link
EP (1) EP2618939B1 (ru)
CN (1) CN103118794B (ru)
PL (1) PL2618939T3 (ru)
RU (1) RU2527780C1 (ru)
WO (1) WO2012037979A1 (ru)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106824580A (zh) * 2017-01-23 2017-06-13 慈溪市博捷金属制品有限公司 一种摇摆式洒水器
US11919013B2 (en) * 2018-07-12 2024-03-05 Water Pik, Inc. Tangential oscillating massage engine
CN111448971A (zh) * 2020-06-03 2020-07-28 温州大学 一种农业灌溉装置

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4417691A (en) * 1976-11-08 1983-11-29 Anthony Manufacturing Corp. Turbine drive water sprinkler
US4253608A (en) * 1979-05-21 1981-03-03 The Toro Company Part-circle sprinkler with reversible stator
IL96546A (en) * 1990-12-05 1994-06-24 Lego Lemelstrich Ltd Sector watering rotary sprinkler
RU2032317C1 (ru) * 1994-03-28 1995-04-10 Смирнов Александр Борисович Дождевальная установка
DE10142144A1 (de) * 2001-08-29 2003-03-20 Gardena Kress & Kastner Gmbh Beregnungsvorrichtung
WO2003020431A1 (de) * 2001-08-29 2003-03-13 Gardena Manufacturing Gmbh Beregnungsvorrichtung
RU2262991C1 (ru) * 2004-05-17 2005-10-27 Федеральное государственное образовательное учреждение высшего профессионального образования Ставропольский государственный аграрный университет Распылитель жидкости турбинного типа
CN101048234B (zh) * 2004-07-16 2010-12-22 雷鸟有限公司 冲击洒水装置驱动系统
PT2086690E (pt) * 2006-11-21 2014-08-26 Clever Water Sprinkler Technologies Ltd Aspersor rotativo
RU2347624C1 (ru) * 2007-10-10 2009-02-27 Открытое акционерное общество Научно-производственное объединение "Искра" Батарейный циклон
RU2371256C1 (ru) * 2008-04-25 2009-10-27 Владимир Васильевич Шаршков Разбрызгивающая установка
CN101486020B (zh) * 2008-11-04 2010-11-10 张成良 一种全地形灌溉用自动喷水器
CN201361591Y (zh) * 2009-02-25 2009-12-16 丘新贵 一种用于喷淋系统上的旋转式供水装置
CN201431936Y (zh) * 2009-05-07 2010-03-31 张柏明 一种自旋式喷洒器

Also Published As

Publication number Publication date
CN103118794A (zh) 2013-05-22
CN103118794B (zh) 2015-11-25
PL2618939T3 (pl) 2016-07-29
RU2527780C1 (ru) 2014-09-10
EP2618939A1 (de) 2013-07-31
WO2012037979A1 (de) 2012-03-29

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