• 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:
    To achieve a compact, simple and robust control valve for a hydrodynamic torque generator (31), which is linear over a wide range, the control channel (12) of the control valve is shaped such that upon rotation of the valve body (6) between a first, from the closed position different valve position (α1) and a second valve position (α2) with a larger flow (V.) than in the first valve position (α1) a substantially linear relationship between valve position (α) and flow (V.) is achieved.
    公开号:AT514248A2
    申请号:T50467/2014
    申请日:2014-07-04
    公开日:2014-11-15
    发明作者:Johann Dipl Ing Msc Eitzinger；Hannes Gruber；Martin Monschein
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    AV-3623 AT
    Linear control valve
    The subject invention relates to a control valve having a valve housing having an inlet opening and an outlet opening, which are connected by a flow channel, wherein in the flow passage a rotatably mounted cylindrical valve body is arranged and the axis of rotation of the valve body is arranged normal to the longitudinal axis of the flow channel and wherein in the valve body Recess is provided which forms a continuous through the valve body control channel which intersects the lateral surface of the valve body. Furthermore, the invention relates to a hydrodynamic torque generator with such a control valve at the outlet and a method for controlling a hydrodynamic torque generator with such a control valve at the outlet.
    In many applications, so-called water brakes are used as a resistor for generating a load torque for a drive unit, in particular as a load unit for testing such drive units or drive trains with drive units, such as an internal combustion engine, a drive train with an internal combustion engine, a hybrid powertrain, etc. Such water brakes are e.g. from US Pat. No. 5,834,654 A or US Pat. No. 4,020,684 A. WO 2012/175337 A1 describes a water brake as a load unit on a test bench for internal combustion engines.
    The load torque of such a hydrodynamic torque generator (water brake) is controlled by the torque generator essentially via the flow of the operating medium, usually water. For this purpose, normally an inlet valve and an outlet valve are arranged, via which the flow through the torque generator is regulated, see e.g. US 5,834,654 A.
    In the regulation of the discharge of the operating medium from the torque generator, the main problem is the application-based extremely low available pressure difference between the interior of the torque generator and the drain. Control valves for this application are typically called " Butterfly " Valves with rotatable throttle executed, as shown in US 5,834,654 A or US 4,020,684 A. Although this embodiment can be made very compact, the linear adjustment range of such valves, ie the area in which there is a linear relationship between adjustment of the valve body (rotation angle) and flow (characteristic), but by design is low, which is the control of such valves for adjustment makes a desired flow consuming. 2 / 2œ1
    AV-3623 AT
    Commercially available linear valves operate with a control orifice, which artificially reduce the maximum available opening cross-section and thus reduce the achievable flow characteristics or increase the required pressure difference, in order to obtain a linear characteristic. Such a valve is e.g. in EP 269 280 B1 or WO 2006/015220 A2. The disadvantage of valves with orifice plate is the increased flow resistance, which results from the use of the control panel. Thus, with a given (lower) pressure difference, less water can flow out than with a valve which completely opens. The use of a "correspondingly larger" valve would increase the required space, which is often not available. Also, the commercially available valves (e.g., a control ball valve) are completely sealed, which is not advantageous for the particular application to a hydrodynamic torque generator. The same applies essentially to commercially available, linear control valves which have a cylindrical throttle body.
    Valves with longitudinally adjustable throttle body, e.g. in the form of a valve plug, are typically less compact and usually require a mechanical conversion of a rotational movement (drive motor) in a linear movement of the throttle body. Pneumatic linear drives for such valves usually do not reach the required adjustment speed, or only with considerable effort. An electric linear drive for such applications typically consists of a servo motor with mounted spindle slide, which converts the rotary motion into a linear movement. This design is in addition to the increased space an additional service part, which is subject to wear and therefore an additional, undesirable cost factor. A linear drive without motion conversion would e.g. a coil with plunger armature, which is controlled in position. However, this type of linear drives is not as widespread on the market as classic servo drives and therefore not cost competitive.
    DE 10 2010 041 704 A1 discloses a control valve for controlling a volume flow, which has a cylindrical valve body arranged in a pipeline with a recess. By turning the valve body in the pipeline, the free flow cross-section in the valve and thus the volume flow through the control valve changes. Such control valves usually show a (highly) nonlinear behavior and are therefore suitable only for an accurate control of a volume flow or such a scheme is expensive.
    DE 43 19 015 A1 in turn shows a control valve with a throttle valve. To linearize the relationship between flow and position of the throttle valve here the inner shape of the valve housing in the throttle valve is specially shaped. However, this allows only a linearization at the beginning of the setting range, ie starting with the 3 / 2Ö2 '
    AV-3623 AT closed position up to a certain adjustment, realized, the possible linearisable adjustment range is very limited for design reasons.
    Hydrodynamic torque generators must, however, usually be able to set a large torque range, which requires a large adjustment range of the control valve 5. The interesting operating range of such torque generators is between a minimum, non-zero torque and a maximum torque. Thus, the measures for linearization as described in DE 43 19 015 A1 for a control valve for a hydrodynamic torque generator unsuitable or not effective. 10 It is an object of the subject invention to provide a compact, simple and robust control valve for a hydrodynamic torque generator, which is linear over a wide range.
    This object is achieved in that the control channel is formed in the valve body to a substantially linear upon rotation of the valve body between a first, different from the closed-15 sen position valve position and a second valve position with a larger flow than in the first position Relationship between valve position and flow to achieve. This makes it possible in the particularly interesting adjustment range, between a first valve position unequal to the closed position and a second valve position, to achieve a linear characteristic which greatly facilitates the regulation of the control valve. The fact that only the control channel has to be shaped accordingly, results in a simple, compact and robust control valve with few components. In addition, such a control valve is also very flexible, since the control valve can be easily and quickly adapted to different conditions, in particular different required flow ranges alone by replacing the valve body 25.
    A clearly defined closed position of the control valve results when the valve body, a closure bar is provided which closes the flow channel at least partially in the closed position of the control valve. If the flow channel is not completely closed, the result is a certain amount of leakage in the closed position, which is advantageous in particular for a control valve for a hydrodynamic torque generator, since this ensures a flow through the hydrodynamic torque generator even in the closed position a possible overheating of the rotor of the torque generator can be prevented. 4 / 2Ö3 '
    AV-3623 AT
    If a connecting bridge is arranged substantially diametrically opposite the closure web on the valve body, on the one hand the mechanical strength of the valve body is increased and on the other hand the possible setting range of the control valve is maximized.
    The outflow conditions on the valve body can be improved if a recess is provided in the connection bridge, since this means that the operating medium has to be deflected less and results in lower turbulence.
    In the closed position, a defined amount of leakage can be achieved in a simple manner if the valve body is arranged at least partially radially spaced from the valve housing in order to form a radial gap through which it can flow. The size of the radial gap then defines the achievable leakage quantity.
    In order to direct a leakage amount specifically over the lateral surface of the valve body, at least at one axial end of the lateral surface can be arranged a radially protruding from the circumferential surface circumferential ridge.
    To control a hydrodynamic torque generator, it is particularly advantageous if at the inlet of the torque generator by means of a variable speed pump, a quantity of operating medium supplied to the torque generator is controlled and at the outlet by means of the control valve the effluent from the torque generator amount of operating medium is regulated, so that in the torque generator a water level adjusts to operating medium, which causes the desired load torque. The control of the speed of the variable speed pump allows a more precise and faster control of the supply of operating medium and thus a faster control of the level and thus also the load torque.
    The subject invention will be explained in more detail below with reference to Figures 1 to 10, which show by way of example, schematically and not by way of limitation advantageous embodiments of the invention. It shows
    1 shows a section through an inventive control valve,
    2 shows an isometric view of a valve body of the control valve,
    3 shows a longitudinal section through the control valve in the closed position,
    4 shows a longitudinal section through the control valve in the open position,
    5 shows a typically resulting linear characteristic of a control valve according to the invention,
    6 shows a development of the lateral surface of the valve body with a control channel,
    7 is an isometric view of a valve body of the control valve in an alternative embodiment, 5/20 * '
    AV-3623 AT
    8 shows a development of the lateral surface of this valve body with a control channel, Figure 9 shows a first control concept of a hydrodynamic torque generator with control valve according to the invention and
    10 shows another control concept of a hydrodynamic torque generator with control valve according to the invention.
    The control valve 1 according to the invention, as shown in Fig. 1, consists of a valve housing 2 with an inlet opening 3 and an outlet opening 4, to each of which can be connected in a suitable manner not shown piping for the inflow or outflow of operating medium. An outlet of a hydrodynamic torque generator would be e.g. with a pipe, or directly, connected to the inlet opening 3 of the control valve 1. The inlet opening 3 and the outlet opening 4 are connected by a continuous flow channel 5, through which during operation of the control valve 1 a working medium, usually water, flows from the inlet opening 3 to the outlet opening 4 with a certain flow V (as indicated by the arrow). , In the valve housing 2, a cylindrical valve body 6 is rotatably mounted in the flow channel 5. The axis of rotation 7 of the valve body 6, which coincides with the longitudinal axis of the valve body 6, is arranged substantially normal to the longitudinal axis 8 of the flow channel 5. The valve body 6 is shown in detail in FIG. 2 and reference will also be made below to FIG. 2 in parallel.
    As usual with such control valves 1 in the form of a cylinder valve, the outer, cylindrical lateral surface 10 of the valve body 6 is arranged in the flow channel 5. In the valve body 6, a recess 11 is arranged, which forms in the valve body 6 a continuous through the valve body 6, permeable control channel 12. The control channel 12 is aligned substantially transversely to the axis of rotation 7 of the valve body 6 and intersects the lateral surface 10 of the valve body 6. The operating medium can therefore flow through the control channel 12 in the valve body 6. The control channel 12 thus defines the resulting depending on the position of the valve body 6 free flow cross-section in the control valve 1 and thus the flow V through the control valve. 1
    The valve body 6 is rotatably mounted in the valve housing 2 by means of suitable bearings 16. In addition, suitable sealing elements 17 can be arranged to seal the valve body 2 with respect to the valve housing 2. The valve body 6 is rotatably connected to an actuator 13. The actuator 13 is formed here as an electric motor 15 with angle gear 14, wherein the shaft output of the actuator 13 is connected via a standard Wel-len-hub connection with the valve body 6. About the actuator 13, the valve body 6 can be rotated about the axis of rotation 7 in the flow channel 5. The type and 6 / 2Ö5 '
    AV-3623 AT
    The way in which the valve drive 13 is connected to the valve body 6 and the valve housing 2, but is incidental to the invention. In principle, it would even be possible, instead of the actuator 13, to provide means for manually rotating the valve body 6.
    FIGS. 3 and 4 each show a longitudinal section AA through the valve housing 2, FIG. 3 showing the closed position (0% open) of the control valve 1 and FIG. 4 the open position (100% open) of the control valve 1 , Through the recess 11 to form the control channel 12 through the valve body 6 is formed on the valve body 6 radially outwardly over part of the circumference of the valve body 6 is an axially extending, cylinder-segment-shaped closure web 20 which is closed in the Position (Figure 3) closes the flow channel 5 of the control valve 1. If no leakage is desired in the closed position of the control valve 1, the closure web 20 must completely close the flow channel 5. Thus, the geometric shape of the closure web 20 on the lateral surface 10, at least the width of the cylinder segment, the valve body 6 is predetermined. In general, forms through the recess 11 on the valve body 6 and a connecting bridge 22, which is arranged substantially diametrically opposite the closure web 20 and, as the closure web 20, the two the lateral surface 10 bounding axial end faces 18 connects. This connection bridge 22 is already alone for reasons of stability and strength advantageous for the valve body. 6
    The substantially diametrical arrangement of the connection bridge 22 has the advantage that a large adjustment range results. The valve body 6 can thus be rotated until the connecting bridge 22 would be pivoted into the flow channel 5. This results in an adjustment range of approximately 180 °.
    However, there is still a significant advantage of the control valve according to the invention 1. By replacing the valve body 6, the control valve 1 can be adjusted in a simple manner to different flow rates V and work areas, which makes the control valve 1 very flexible.
    Especially when using the control valve 1 in a hydrodynamic torque generator, it is advantageous if a certain amount of leakage is set in the closed position. This can for example be achieved so that, as shown in Figure 3, the closure web 20 covers the entire cross-sectional area of the flow channel 5, but at least partially a radial gap 21 is provided in the region of the lateral surface 10 radially between valve body 6 and valve housing 2, through the resources in the closed position of the control valve 1 can flow. Alternatively or additionally, the closure web 20 could also be designed so that it is not in the closed position -6- 7/20
    AV-3623 AT covering the entire cross-sectional area of the flow channel 5, for example, by the provision of cutouts, holes, etc.
    During operation of the hydrodynamic torque generator, the fluid flowing through can also be strongly heated. If, during operation, a faulty, intentional closing of the control valve 1 occurs, the operating medium could be heated very strongly, which can lead to overheating of the rotors of the hydrodynamic torque generator. This could even damage or destroy the hydrodynamic torque generator. By a defined amount of leakage in the closed position that can be effectively prevented. 10 If the leakage amount V ^ is achieved by a radial gap 21, one additionally obtains the advantage of flushing the rotatable valve body 6, whereby the risk of calcification or the accumulation of particles on the valve body 6 is reduced.
    If the valve body 6 is rotated by an angle of rotation α (indicated by the arrow in FIG. 4), the inflow from the operating medium from the flow channel 5 to the control channel 12 15 is continuously opened, whereby the flow V through the control valve 1 increases. Normally, the control valve 1 would be fully open and the flow V would be maximum if the closure web 20 were pivoted out of the flow channel 5 entirely. The adjustment range would be very narrow. In addition, there would be no linear relationship between flow V and angle of rotation α. To escape this, the control channel 12 is configured such that over a large part of the adjustment range, ie from a position α = αι, which is not equal to the closed position at a = 0, to a position α = 02, the Preferably smaller than the open position at a = amaxist, the flow V increases linearly, as shown in Figure 5 in the form of the characteristic flow V over opening in percent. This results in within the setting range a linearized workspace of the control valve 1 between a first angle of rotation αι with flow Vx and a second angle of rotation a2 with flow V2, or as shown in Figure 5 between a first opening of the control valve 1 in percent and a second opening in percent, wherein 100% opening corresponds to the position of the valve body 6 as in Figure 4.
    In the closed position of the control valve 1 a Lecka-30 mixture is provided in the illustrated characteristic. Without a leakage amount, in this area in FIG. the dashed curve of the characteristic result. Below the desired working range, ie at α < αι, the characteristic can not be linear, but can also be wholly or partially linear. 8 / 2Ö7 '
    AV-3623 AT
    The second angle of rotation a2 of the working area need not, but may coincide with 100% opening, but is preferably below the complete opening of the control valve 1. The range from the second angle of rotation a2 to the full opening with maximum flow V ^ is preferably also with a linear characteristic 5), again by appropriate design of the control channel 12. However, this range α> α2 does not necessarily have to be designed with a linear characteristic, as shown in FIG. This range α> α2 represents an overload range which, in certain operating situations of the hydrodynamic torque generator, e.g. during load shedding or during a classic overload. In the operation of the torque generator, it may also be necessary to vary the level within the torque generator by varying the amount of operating fluid flowing out of the torque generators. This variation is usually not carried out on the supplied operating medium amount, but on the outflowing amount of operating medium, since this can be changed much more dynamically by means of the control valve 1, especially when the inflowing amount of operating medium is controlled by a conventional valve or by means of a pump at the inflowing operating medium amount is subject to mechanical inertia. The range between a2 and amax (ie 100% opening) thus represents a control reserve, for example, for the rapid lowering of the level in the torque generator, and no longer necessarily meet the linear requirements.
    The characteristic in Fig. 5 applies to a certain pressure difference, here e.g. 0.05bar, between inlet port 3 and outlet port 4 of the control valve 1. Normally, one will have a set of characteristics for different pressure differences for a control of the control valve 1. Likewise, a possible influence of the temperature of the operating medium on the characteristic could be taken into account, e.g. again by corresponding characteristics.
    The shape of the control channel 12 can be determined, for example, by calculating an optimum profile of the contour 23 of the control channel 12, which gives the required linearity when rotating the valve body 6, which can then be iteratively optimized, e.g. by means of measuring experiments. An empirical determination of the shape of the recess 11 and the control channel 12 would be conceivable. In principle, a person skilled in the field of hydrodynamics is able to determine the shape of the recess 11. Due to the required linear characteristic of the flow, one will come to a somewhat narrower in cross-section contour 23 of the control channel 12, as indicated in the figures.
    The design of the valve body 6 as shown in Figure 2, for example, first carried out on the basis of the specification of a linear curve of the characteristic in a desired Arbeitsbe- 9 / 2Ö8 '
    AV-3623 AT rich (ai to a2) of about 2/3 of the control range (a = 0 to amax). Thus, on the basis of existing theoretical hydrodynamic relationships, a setpoint recess was calculated as a function of the angle of rotation α, with the boundary conditions of a desired leakage amount V ^ in the closed position at a = 0 ° and the complete opening of the available geometric cross section of the flow channel 5 in FIG open position at amax. The theoretical nominal function of the opening profile of the recess 11 resulting from the shape of the flow channel 5 in order to achieve the desired characteristic curve was verified by a flow test and the deviation from the theoretically determined profile was determined. For the inserted rectangular cross-section of the flow channel 5, e.g. a power function A (a) = ^ 0 ^ + A (0). Here, A designates the resulting flow cross-section of the control channel 12 at a twist angle α and k a scaling parameter which scales the function to the maximum possible opening area. For the application of this relationship to a cylindrical valve body 6 and a flow channel 5 with a rectangular flow cross-section S, a deviation from this theoretical opening course of the control channel 12 is to be expected. This deviation was determined by the experimental setup based on experiments and found the optimal shape of the contour 23 of the control channel 12 in several adaptation stages.
    In Figure 6, the lateral surface 10 of the valve body 6 is shown unwound, for the sake of simplicity, only the contour 23 of the control channel 12 via the angle of rotation α and the flow cross-section S of the flow channel 5 are shown in different open positions of the control valve 1. Strichliert is shown in Figure 6, the 35% opening and dash-dotted the 100% opening of the control valve 1. It can be seen that 12 different flow cross-sections A result in different open positions according to the contour 23 of the control channel. The contour 23 essentially follows a power function here. The jump at about 95 ° designates the angle of rotation a2, from which deviates from the linear characteristic (see Fig.5) This opening curve causes the linear characteristic within the working range (ai to a2), as explained above.
    In Figure 7, an alternative embodiment of the valve body 6 is shown. Here are at the axial ends of the lateral surface 10, radially projecting from the lateral surface 10 protruding circumferential webs 24 which substantially close the radial gap 21 between the valve body and valve housing (Fig.3, 4) in the region of the circumferential webs 24 to the amount of leakage targeted over the To conduct lateral surface 10 of the valve body 6. Under certain circumstances, however, only such a circumferential ridge 24 may be sufficient. In addition, a recess 25 is provided in the connecting bridge 22, are formed by the two connecting webs 26. Through the recess 25 results in an improved outflow 10/20 '
    AV-3623 AT behavior of the operating medium from the valve body, as the operating medium is less deflected and there is less turbulence.
    8, the lateral surface 10 of the valve body 6 is shown unwound again according to FIG. The contour 23 of the control channel 12 follows here an elliptic function (Ellipsenglei-5 chung) to the open position at 100% (amax). This results in a linear characteristic close to the 100% open position of the valve body. 6
    FIG. 9 also shows an exemplary use of a hydrodynamic torque generator 31 in a test stand, in which case a control valve 1 according to the invention is used at the outflow of the hydrodynamic torque generator 31. The hydrodynamic torque generator 31 is connected to a connecting shaft 32 with a specimen 30, e.g. an internal combustion engine or powertrain, and generates a load torque MB. The loading torque MB is set by controlling the flow of an operating medium through the hydrodynamic torque generator 31, which sets a level in the torque generator. For this purpose, an inlet valve 33 is arranged at the inlet of the torque generator 31 and the control valve 1 according to the invention is arranged at the outlet. Of course, the inlet valve 33 can also be designed as a control valve 1 according to the invention. The inlet valve 33 controls the inflow Vzu and the control valve 1 the outflow Vab of operating medium to obtain a desired level of the operating medium in the torque generator 31, which ultimately causes the desired 20 load torque MB.
    For this purpose, a control unit 34 may be provided, which is to be set a desired load moment MB, soii, e.g. from a higher-level control device such as a test bench control device. The control unit 34 can detect further measured quantities of the torque generator 31, in particular the pressure p at the inlet of the torque generator 31 and a temperature T of the operating medium, and uses this control algorithm to determine a control variable α to be set for the control valve 1 (or control valve). the actuator 13 of the control valve 1), and possibly also a manipulated variable S for the inlet valve 33 for the amount of water supplied.
    An alternative control of the torque generator 31 is described with FIG. At the outlet of the torque generator 31, in turn, the control valve 1 according to the invention for adjusting the outflowing amount Vab is arranged on the operating medium. It can be arranged at the output but also another suitable control valve, in particular a non-linear control valve for this scheme. At the inlet of the torque generator 31 but now no inlet valve is provided. The torque converter 11 / 2¾0-
    AV-3623 AT grower 31 supplied amount Vzu to operating medium is controlled here by means of a speed-controlled pump 36, which ensures a defined pressure profile at the input of the torque generator 31. For this purpose, the pressure at the input of the torque generator 31 can be measured by means of a pressure sensor 35. The pressure is important because the characteristic of the control valve 1 is pressure-dependent, as described above. The control of the speed nP a speed-controlled pump 36 allows a more precise and also faster control of the feed Vzu of operating medium compared with commonly performed
    Pressure regulators or control valves at the inlet. By feeding the pump 36 from an intermediate tank 38, one also achieves independence from short-term fluctuations in the pressure in a service network for the operating medium, e.g. the mains network of the water supply. The level in the intermediate tank 38 can simply be e.g. be controlled by a float valve 37, but can also be kept in the required range by other known methods.
    The hydrodynamic torque generator 31 can also have a dependence in the rotational number n of the torque generator 31, which can be taken into account in the implemented control algorithm, as indicated in FIG. -11 12/20
    权利要求:
    Claims (8)
    [1]
    A control valve with a valve housing (2) having an inlet opening (3) and an outlet opening (4), which are connected by a flow channel (5), wherein in the flow 5 channel (5) rotatably mounted cylindrical Valve body (6) is arranged and the axis of rotation (7) of the valve body (6) is arranged normal to the longitudinal axis (8) of the flow channel (5) and wherein in the valve body (6) has a recess (11) is provided, one through the valve body (6) forms a continuous control channel (12) which intersects the lateral surface (10) of the valve body (6), characterized in that the control channel 10 (12) is shaped to rotate upon rotation of the valve body (6) between a first, of the closed position different valve position (ai) and a second valve position (a2) with a larger flow (V) than in the first valve position (ai) a substantially linear relationship between valve position (a) and through to achieve flow (V).
    [2]
    2. Control valve according to claim 1, characterized in that on the valve body (6) has a 15 Verschluß (20) is formed, which closes the flow channel (5) at least in part in the closed position of the control valve (6).
    [3]
    3. Control valve according to claim 2, characterized in that on the valve body (6) substantially diametrically opposite the closure web (20) a connecting bridge (22) is arranged.
    [4]
    4. Control valve according to claim 3, characterized in that in the Verbindungsbrü bridge (22) has a recess (25) is provided.
    [5]
    5. Control valve according to one of claims 1 to 4, characterized in that the valve body (6) for forming a permeable radial gap (21) in the region of the lateral surface (10) at least partially radially spaced from the valve housing (2) is arranged 25.
    [6]
    6. Control valve according to claim 5, characterized in that at least one axial end of the lateral surface (10) from the lateral surface (10) radially protruding circumferential ridge (24) is arranged.
    [7]
    A hydrodynamic torque generator comprising a control valve (1) according to any one of claims 1 to 6, wherein the control valve (1) is arranged at the outlet of the torque generator (31) -12- 13/20 AV-3623 AT in order to detect the torque produced by the torque generator (31). 31) outflowing amount (Vab) to adjust operating medium.
    [8]
    8. A method for controlling a hydrodynamic torque generator (31) with a load torque (MB) of the torque generator (31) with a control valve 5 (1) is adjusted according to one of claims 1 to 6, wherein the control valve (1) at the outlet the torque generator (31) is arranged, characterized in that at the inlet of the torque generator (31) by means of a variable speed pump (36) to the torque generator (31) supplied amount (V ^) is regulated to operating medium and by means of the control valve (1) the from the torque generator (31) Abflie-10 ßende amount (Vab) is controlled to operating medium, so that in the torque generator (31) adjusts a level of operating medium, which causes the desired load torque (Mb). -13- 14/20
    类似技术:
    公开号 | 公开日 | 专利标题
    DE2423620A1|1974-12-05|VISCOSITY COUPLING
    DE69911306T2|2004-07-15|Method and device for regulating a line network
    DE102013224792A1|2014-06-12|Exhaust gas recirculation valve
    EP0911715A1|1999-04-28|Flow control valve with integrated pressure controller
    DE102010022536A1|2011-12-08|Method and device for controlling a valve
    DE10356971A1|2005-01-27|Circuit for controlling the supply quantity of a hydraulic pump
    DE10130471B4|2014-03-27|Method for controlling an exhaust gas recirculation system
    EP0967475A1|1999-12-29|Method for the determination of the viscosity of a liquid
    EP3164626B1|2019-12-11|Linear control valve
    WO2013143800A2|2013-10-03|Gas control valve
    DE102010061179A1|2012-06-14|Arrangement useful for producing drinking water of selected hardness, comprises ion exchanger, inlet for connecting to drinking water supply, outlet for providing the drinking water of selected hardness, and mixing valve
    EP3215744B1|2020-05-13|Method for producing a set of characteristic curves of a fluid pump, use of a limited valve, use of a staging valve, and control device for a fluid conveying system
    EP2837829B1|2019-12-18|Control of the characteristics of centrifugal pumps
    DE3625600A1|1987-02-12|SERVOLINE SYSTEM
    WO2000047875A1|2000-08-17|Camshaft control device and control valve with leakage compensation
    DE102014200823A1|2014-07-24|Device for generating adjustable differential pressure of compressible medium at flow of fluid guide, has valve assembly as device for generating variable flow resistance of medium with hose line as part of fluid guide
    WO2010136255A1|2010-12-02|Digital hydraulic controller
    AT14194U1|2015-05-15|Circulating lubrication system for a fiber web machine
    EP0822332A1|1998-02-04|Hydraulic power station
    DE2408876C3|1976-12-16|Hydrodynamic brake
    DE102019205113A1|2020-10-15|Volume flow controller and method for regulating a volume flow
    DE102008056617B4|2012-05-31|Turbine with compact inlet housing thanks to internal control valves
    DE102007034562A1|2009-01-29|Hydrodynamic retarder with tangential inflow and outflow principle
    DE2747980A1|1978-05-03|FLOW CONTROL VALVE WITH CYLINDRICAL VALVE BODY
    EP2988038B1|2019-12-11|Electromagnetically actuated valve for metering a gas and method for producing such a valve
    同族专利:
    公开号 | 公开日
    EP3164626B1|2019-12-11|
    US20170184205A1|2017-06-29|
    AT514248B1|2016-05-15|
    EP3164626A1|2017-05-10|
    AT514248A3|2015-05-15|
    WO2016001401A1|2016-01-07|
    US10816096B2|2020-10-27|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3349799A|1965-04-20|1967-10-31|Mueller Co|Rotary plug valve|
    GB1202751A|1968-02-28|1970-08-19|Heenan & Froude Ltd|Hydrokinetic dynamometer control systems|
    GB1375828A|1970-11-27|1974-11-27|
    US4020684A|1975-07-26|1977-05-03|Carl Schenck Ag|Control valve especially for hydraulic absorption dynamometers|
    US4793357A|1986-11-24|1988-12-27|Picker International, Inc.|CT blood flow mapping with xenon gas enhancement|
    FI81895C|1988-12-30|1990-12-10|Neles Oy|REGLERVENTIL.|
    US5108075A|1991-04-26|1992-04-28|Esm Ii Inc.|Orifice valve assembly|
    DE4117445C2|1991-05-28|1994-10-06|Gastechnic Prod Vertriebges|Valve for controlling or regulating the flow of a fluid|
    JPH0556961U|1991-12-27|1993-07-30|関西日本電気株式会社|Liquid processing device|
    JP3405466B2|1992-09-17|2003-05-12|富士通株式会社|Fluid switching valve and semiconductor device manufacturing apparatus|
    DE4319015A1|1993-06-08|1994-12-15|Vdo Schindling|Device for controlling a mass flow|
    US5551467A|1995-08-11|1996-09-03|H-Tech, Inc.|Ball valve with controlled flow variation|
    US6561324B2|1996-03-08|2003-05-13|Voith Turbo Gmbh & Co. Kg|Drive unit including a motor and a retarder|
    US5834654A|1996-03-11|1998-11-10|Mcfarland; Robert A.|Torque and temperature control for a water brake dynamometer|
    JP2003184757A|2001-12-19|2003-07-03|Heiwa Denshi Kogyo Kk|Opening/closing valve and massage machine using the same|
    EP1781976B1|2004-08-02|2016-10-05|Belimo Holding AG|Pressure independent control valve|
    ITBS20060221A1|2006-12-18|2008-06-19|Enolgas Bonomi S P A|INTERCEPTING VALVE|
    DE102010041704A1|2010-09-30|2012-04-05|Siemens Aktiengesellschaft|Regulating valve for controlling flow volume inside pipeline, is arranged in pipeline rotatable around rotational axis and corresponding to its rotational position decontrols flow cross-section inside pipeline|
    AT509677B1|2011-06-24|2012-09-15|Avl List Gmbh|HYDRODYNAMIC TORQUE GENERATOR FOR TEST STANDS AND CONTROL METHOD THEREFOR|
    CN102322536B|2011-09-05|2012-11-07|上海鸿润科技有限公司|Valve core assembly and valve using same|
    EP2695816B1|2012-08-10|2020-10-07|Tetra Laval Holdings & Finance S.A.|Valve for controlling an air flow|
    DE102012110872A1|2012-11-13|2014-05-15|Ihi Charging Systems International Gmbh|Control device for an exhaust gas guide section of a turbine and exhaust gas guide section for a turbine|RU2695561C2|2017-12-25|2019-07-25|Акционерное общество "Корпорация "Московский институт теплотехники" |Hot gas flow rate control valve|
    WO2021151470A1|2020-01-28|2021-08-05|Ut99 Ag|Throttle|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50467/2014A|AT514248B1|2014-07-04|2014-07-04|Linear control valve|ATA50467/2014A| AT514248B1|2014-07-04|2014-07-04|Linear control valve|
    US15/320,587| US10816096B2|2014-07-04|2015-07-03|Linear control valve|
    EP15734145.4A| EP3164626B1|2014-07-04|2015-07-03|Linear control valve|
    PCT/EP2015/065183| WO2016001401A1|2014-07-04|2015-07-03|Linear control valve|
    [返回顶部]