• 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:

    公开号:AT510072A1
    申请号:T0118110
    申请日:2010-07-13
    公开日:2012-01-15
    发明作者:Johann Kalkgruber
    申请人:Solarfocus Holding Gmbh；
    IPC主号:
    专利说明:

    • * • * «I» ·
    turbine
    description
    The invention relates to a turbine, as well as a device in which the turbine according to the invention is used.
    The turbine according to the invention can be used particularly advantageously wherever another device is to be driven to move by the turbine and the speed of the movement of this other device should be proportional to the flow through the turbine.
    In a particularly advantageous application of the turbine according to the invention, the turbine drives a pump.
    It should be preceded that the term "turbine" in the sense of this text means a device which converts the kinetic energy of a fluid into the rotational energy of a solid.
    The combination of turbine according to the invention and driven by this pump is particularly advantageous for the transfer of heat from a hotter liquid medium in a second, originally cooler liquid medium using a heat exchanger.
    Pelton turbines have a kind of water wheel, wherein the blades of the water wheel are curved shell-like and a water jet as tangential as possible reaches the shell surface and is deflected at the shell. Ideally, the velocity of the impinging jet of water is twice the peripheral velocity of the blade and the velocity of the water flowing away from the blade is approximately zero. Except for the area illuminated directly by water, the blades of the Pelton turbine are exposed to air. Pelton turbines are commonly used to drive generators. Their speed is constant; As the flow through the turbine changes, the velocity of the jet impinging on the blades is controlled to be as nearly as twice the peripheral speed of the blades as possible. For a general
    Seito 1 ι · · · · · I · · »· · ·
    Turbine construction is adjusted over the entire size range of the possible flow (volume flow) through the turbine, the area of the flow cross-section through the nozzle, in which the water jet driving the impeller is formed, proportional to the flow of water. Since the flow velocity through a cross-sectional area is the quotient of flow through cross-sectional area, it is therefore constant.
    AT 505 704 A1 and EP 578 126 A2 deal with an advantageous method for transferring heat from a hot water circuit to service water by flowing both media through a water / water heat exchanger. In this case, the flow of service water caused by the pressure in the cold water supply line when opening a faucet drives a turbine which drives a pump which moves the hot water through the heat exchanger. Thus, without requiring electrical control and without the need to supply electrical energy, the hot water flow through the heat exchanger is approximately proportional to the flow of service water through the heat exchanger. At a constant inlet temperature of hot water and hot water so that the temperature of the extracted, heated in the heat exchanger process water, almost regardless of how strong the flow of hot water.
    In practice, this seemingly advantageous approach has not been enforced, since the desired proportionality between the two rivers is not given sufficiently well with small flow of process water. As soon as the flow of warm process water falls below a certain threshold, the flow of hot water through the heat exchanger decreases disproportionately and the process water remains approximately or completely cold.
    The object underlying the invention is to provide a device consisting of turbine and driven by this pump, the turbine by a flowing through
    Page 2
    Turbine f I ·· ** ♦
    Medium is driven, the turbine drives the pump and the pump drives another liquid medium. Compared to previous implementation proposals to, the device to be created at relatively small flow through the turbine to provide better pumping power. The device must be so robust, durable, low maintenance, low noise and low cost that it can be used as part of domestic hot water installations. For solving the problem, it is proposed according to the invention to use a waterwheel as the turbine and the flow cross section for the fluid medium flowing at the turbine at the inflow to the waterwheel within the permissible size range of the flow of the turbine driving medium, only for small flows of this medium relative to the flow cross section to constrict on larger rivers.
    With "waterwheel" For the purposes of this document, it is meant a wheel provided on its circumference with radially projecting blades and rotatably mounted on its axis, which can be driven to rotate by the pulse of liquid medium flowing in the circumferential direction of the wheel against the blades. In this sense, the wheel of a Pelton turbine is also regarded as a waterwheel.
    With "flow" In this document, the physical quantity is the quotient of the volume of a liquid medium flowing through a flow cross-section through the time required for the flow of this volume. One unit of measure for the flow is, for example, cubic meters per second.
    By narrowing the flow cross-section of the water wheel driving medium only in small rivers, only with small rivers, the flow rate of the medium is increased relative to the flow, so that only for small rivers, the flowing medium relative to the flow has an increased speed, so related to the river also has an increased pulse and
    Page 3
    Turbine • * · · so that the water wheel drives disproportionately in relation to the river.
    This ensures that the waterwheel only stops at much smaller flows due to inevitably always existing friction, as it would do with a constant large flow cross-section.
    The invention is illustrated by means of drawings:
    Fig. 1: shows in a sectional view stylized an example according to the invention turbine including a structurally associated pump.
    Fig. 2: shows on the basis of a flow chart a possible use of the device of FIG. 1 for the heating of process water by heat transfer from a hot water circuit run.
    Fig. 3: shows with reference to a diagram an exemplary inven tion proper dependence of the flow cross-section and the velocity of the driving medium at the inlet to the water wheel of the flow of the medium.
    Simplified in FIG. 1 are parts of the turbine 2, which are not moved during operation, as a single entire part 30 outlined.
    The water wheel 25 is arranged in a turbine chamber 26. Preferably, the waterwheel 25 is designed as a Pelton wheel, since this is a particularly good energy transfer from the driving medium to the waterwheel achievable. The driving medium flows through an inlet 20 into a cylinder space 21 and through a flow channel narrowed to a nozzle 24 at an end face of the cylinder into the turbine chamber 26 into the blades of the water wheel 25. Via the outlet 27 the medium leaves the turbine chamber 26 again. The part of the turbine chamber 26 not occupied by the waterwheel 25 is completely filled with the liquid medium
    Page 4 · «» i ···· * »····« · * · «« < · * «· · · Μ · #» * * · · ·
    Turbine • · · · · · · * * · * * * (· filled, so that the blades of the water wheel move throughout in liquid medium.
    The cylinder chamber 21 is bisected by a two-sided control piston 22. On the side of the nozzle 24 protrudes from the control piston 22, a rod-shaped, slightly tapered at its end nozzle needle 23 on or in the nozzle 24. When the control piston is moved toward the nozzle, this nozzle needle projects into the nozzle 24 and thus narrows the flow cross-section of the medium flowing through the nozzle.
    On the side facing away from the nozzle, a compression spring 28 acting between the control piston 22 and the end face of the cylinder chamber is arranged in the cylinder chamber 21. Unless other forces act more strongly, it pushes the control piston in the direction of the nozzle-side end face of the cylinder chamber 21 and thus the nozzle needle 23 in the nozzle 24, so that thus the flow cross-section is narrowed in this. A compression spring 28 is not mandatory. Also by the difference of the effective piston surfaces on both sides of the control piston 22 is formed at pressure equality on both sides of a resulting, directed to the nozzle 24 toward the force on the control piston. In addition, you could also apply the weight on the control piston to suitably inclined or vertical orientation to push the control piston 22 to the nozzle 24 out.
    The pressure of the medium flowing through the inlet 20 into the nozzle-side part of the cylinder space "seeks". to push the control piston 22 away from the nozzle-side end face of the cylinder chamber. In the remote from the nozzle side of the cylinder chamber can be pumped through the inlet 29 also a medium. The pressure of this medium "strives " after that, move the control piston 22 towards the nozzle 24 and thus narrow the flow cross-section.
    Significant advantages of this design will be apparent from the exemplary application outlined in FIG.
    Page b 4 * * * «4 * 94 * I · * * * * * 4 Φ»
    Turbine * 4 4 4 4 4 M («4 * 4» ♦ *
    The device according to the invention shown in Fig. 2 in a flow diagram consists of a turbine 2 and a pump 6, wherein the pump 6 is driven directly by the turbine 2. In an advantageous, because simple, robust and low-loss construction, the pump 6 can be designed as a flow pump, the rotor is arranged with the water wheel of the turbine 2 on a common shaft.
    2, with the faucet 10 open, cold service water 1 flows through the inlet 20 into the turbine 2, through the turbine, driving the turbine, out of the turbine, through a heat exchanger 3, and through a domestic hot water 4 Faucet 10 to the outside.
    A stub 5 leads that pressure, which prevails after the pressure reduction in the turbine in the hot water, to the second inlet 29 of the turbine 2. For this purpose, you can already realize the line 5 in the turbine housing or on the turbine housing; Typically, the inlet is in the line 5 in the area of the outlet 27 from the turbine chamber 26. It would also be possible to place the starting point of the line 5 between the turbine 2 and the heat exchanger 3 or after the heat exchanger. 3
    When the faucet 10 is wide open, the pressure in the service water on the side of the inlet '20 to the turbine 2 is much higher than - seen in the flow direction - behind the turbine chamber 26. Thus, the pressure at the inlet 29 is much lower than at the inlet 20 in the two-part cylinder chamber 21 (Fig. 1) of the turbine. The control piston 22 is thus pressed away from the nozzle 24 so that the nozzle has the maximum flow cross-section.
    If the faucet 10 is closed so far that while still hot water flows through it, but only a much smaller amount per time than when the faucet completely open, so is the pressure level in the stub 5 and thus at the inlet 29 with respect to the previously discussed case , much closer to the printed
    Scite 6 • ··· «» * * * * * * * «· · (t · · · · · ·« »f» II * · *
    Turbine * · # * * * * * * · «··· * * 4 4» «* ·· ··· ** · veau at the inlet 20 in front of the turbine. The control piston is now - if necessary supported by a compression spring 28 - compared to the previously discussed case, moved closer to the nozzle 24, so that the nozzle needle 23 narrows the flow cross-section in the nozzle 24, which is intended, the flow rate of water through the nozzle is increased.
    The farther the faucet 10 is open, the lower the pressure at the inlet 29 and the farther the control piston is pushed away from the nozzle 24. When the faucet 10 is completely closed, the pressure at the inlet 29 is equal to the pressure at the inlet 20, and the nozzle needle 23 on the control piston is pushed against the nozzle 24 in abutment. If the nozzle 24 is completely closed, that does not bother, since no flow takes place anyway.
    By the turbine 2, the pump 6 is driven. In the example shown in FIG. 2, this hot water 7 pumps out of a store 8 through the heat exchanger 3 and back into the store 8 in a circle. The more warm service water 4 is removed, the stronger the turbine 2 is driven and the more pumps the pump 6 hot water 7 through the heat exchanger 3 for the purpose of heating the service water. Due to the described inventive design of the parts at the inlet to the turbine chamber, this advantageous, at least approximate proportionality up to very small rivers of the service water is maintained.
    It is advantageous to form the cross-sectional shape of the projecting into the nozzle 24 part of the nozzle needle 23 differently than the cross-sectional shape of the nozzle 24, so that the nozzle 24 can never be completely closed by the nozzle needle 23, as otherwise set at very small flow of the process water Swinging the control piston and thus may cause rattling in the water pipe.
    For example, the nozzle may have a circular cross-sectional area and the nozzle needle a square cross-sectional area
    Page 7 ► ♦ * · I * · 1
    Turbine ► · · 1 ** * * or also a circular cross-sectional area, which however is supplemented by one or more grooves or webs.
    It is urgently recommended to make the bias of the compression spring 28 adjustable, for example, by performing the lid on the cylinder chamber 21 at which the compression spring 28 abuts, as a bolt screwed sealingly into a nut thread.
    Good dimensioning of the individual parts compression spring, piston cross-section, nozzle cross-section, blade shape of the water wheel, etc., as well as specifications for the materials from which these parts can be formed under consideration of conditions such as maximum flow, temperature range, ingredients in the flow medium, etc. in the context of expert Action mainly by approximation and attempt to be found, which is why it will not be discussed further here.
    3 shows by way of a diagram an exemplary inventive dependency of the flow cross section A and the velocity v of the driving medium at the inflow to the water wheel from the flow Q of the medium in the size range of the flow Q permissible for the turbine.
    The cross-sectional area A (see its exemplary localization in FIG. 1) increases monotonically at the lower edge region of the permissible size range of the flow Q with the size of the flow Q, reaches its maximum value at a maximum of about 40% of the maximum flow and remains constantly high as the flow increases ,
    Preferably, the cross-sectional area A in the lower size range of the flow Q increases disproportionately with the size of the flow, as shown.
    The average flow velocity v of the medium through the area A is calculated as Q / A. In the upper part of the flow Q, therefore, the velocity v is proportional to the flow.
    Page 8 * · t # * · «
    * »·« «I *« * * *
    Turbines • For flows that are smaller than the lower limit Ql does not decrease with decreasing flow, but remains at least constantly high or - as shown - preferably even increases.
    For the purposes of the invention, it is important that the flow cross-sectional area at the inflow to the water wheel is narrowed only at low flow compared to the flow cross-sectional area at a larger flow.
    The discussed method to perform this narrowing by means of a injectable into the nozzle nozzle needle, which is arranged on a control piston on which the pressure difference between turbine to the flowing medium and away from the turbine medium flowing, is feasible without external energy supply and a simple, inexpensive and robust construction feasible.
    With the means of control engineering, of course, other coupling mechanisms between flow through the turbine and size of the cross-sectional area of the nozzle at the inlet to the water wheel are possible and certainly also useful in some cases. In particular, electrical and / or pneumatic and / or hydraulic measuring and adjusting elements are to be considered here.
    In the context of the invention, other possibilities of energy transfer between turbine 2 and pump 6 are conceivable as a common rotor shaft. For example, a gear ratio can be interposed and / or an energy transfer can take place in that a synchronous motor equipped with permanent magnetization drives a synchronous motor equipped with permanent magnetization through the turbine. Even with this construction, one is independent of external energy and electrical energy supply network; In addition, one is free in the spatial arrangements of turbine and pump relative to each other. All mentioned energy transfer mechanisms between turbine 2 and pump 6, where proportionality
    Page 9
    Turbine between the turbine and pump speeds prevail, can be run easily and robust and they can operate with low loss and self-sufficient.
    Page 10
    权利要求:
    Claims (9)
    [1]
    Turbine, which has a arranged in a turbine chamber, driven by flowing medium water wheel and a control device through which for the turbine driving liquid medium, the flow cross-section at the inlet to the water wheel in dependence on the flow of the medium is contractible and expandable, characterized in that, within the admissible size range of the flow (Q) through the turbine, only in the case of small flows the flow cross-section (A) at the inflow to the water wheel (25) is narrowed compared to the flow cross-section for larger flows.
    [2]
    2. Turbine according to claim 1, characterized in that for rivers, which are greater than 40% of the permissible maximum flow ', the flow cross section (Ά) at the inlet to the waterwheel is constantly large.
    [3]
    3. Turbine according to claim 1 or claim 2, characterized in that the inflow to the water wheel (25) as a nozzle (24) is formed and that the flow cross-section in the nozzle (24) by a nozzle needle (23) is variable, which in this Nozzle is inserted.
    [4]
    4. Turbine according to claim 3, characterized in that the nozzle needle is attached to a two-sided control piston (22), wherein on one side of the two-sided control piston in the cylinder chamber (21) in which the control piston is movable, the pressure of the turbine chamber (26 ) flowing medium and on the second side of the control piston, the pressure of this medium after the pressure reduction at the turbine.
    [5]
    5. Turbine according to claim 4, characterized in that in the turbine chamber (26) flowing medium flows through the cylinder space (21) and that the nozzle (24) is arranged on an end face of the cylinder space (21). Page 11 • * * * I * * * * * «I ·» «* * I« · «» * * Turbine «· ·« · * ♦ * · · »· ··· · · *« * ψ ·
    [6]
    6. Apparatus comprising a turbine 2 according to any one of the preceding claims, characterized in that it further comprises a power transmission mechanism and a pump (6), wherein by the energy transmission mechanism mechanical energy from the turbine to the pump (6) is transferable.
    [7]
    7. The device according to claim 6, characterized in that the energy transmission mechanism is constructed such that it causes mutually proportional speeds to turbine (2) and pump {6}.
    [8]
    8. Apparatus according to claim 6 or claim 7, characterized in that the turbine (2) driving medium hot water (1, 4) which is guided in the course of its flow path through a heat exchanger (3) and that by the pump (6) driven medium hot water (7), which is also passed through this heat exchanger (3) in the course of its flow path.
    [9]
    9. Apparatus according to claim 8, characterized in that the heat exchanger (3) is adapted to heat process water. page 12
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE447985C|1923-03-25|1927-08-06|Hans Thoma Dr Ing|Electric voltage regulator for power generators operating by means of a liquid servomotor|
    EP0319464A1|1987-11-30|1989-06-07|GebràœDer Sulzer Aktiengesellschaft|Turbine with a control device, and its use|
    AT505704A1|2007-08-31|2009-03-15|Kalkgruber Johann|DEVICE FOR HEATING WATER IN PASSAGE|
    DE284200C|
    CH101875A|1922-02-03|1923-10-16|Gilbert Gilkes And Company Lim|Water turbine with a nozzle that can be regulated by a needle.|
    GB239796A|1925-04-07|1925-09-17|Percy Hector Pitman|Improvements in and relating to governing and other controlling devices of jet-impelled water turbines|
    US2976687A|1956-07-16|1961-03-28|Allis Chalmers Mfg Co|Control for multijet impulse turbine|
    US4355949A|1980-02-04|1982-10-26|Caterpillar Tractor Co.|Control system and nozzle for impulse turbines|
    WO1983000721A1|1980-02-04|1983-03-03|Bailey, John, M.|Control system and nozzle for impulse turbines|
    JPH02286881A|1989-04-28|1990-11-27|Fuji Electric Co Ltd|Nozzle switching method for pelton hydraulic wheel|
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    EP2950007B1|2014-05-28|2017-08-16|SOLARFOCUS Holding GmbH|Device for heating water|
    AT14883U1|2014-07-07|2016-08-15|Solarfocus Holding Gmbh|Turbine with control body|
    CN107620664A|2017-10-24|2018-01-23|广东银泽金属科技有限公司|A kind of environment protection energy-saving efficient water guide equipment|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1181/2010A|AT510072B1|2010-07-13|2010-07-13|TURBINE|ATA1181/2010A| AT510072B1|2010-07-13|2010-07-13|TURBINE|
    EP11005584.5A| EP2407663B1|2010-07-13|2011-07-07|Turbine and method of controlling a turbine|
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