KR102074096B1 - Control valve, hydraulic coupling apparatus and pump system using the same - Google Patents

Abstract

The present invention relates to a control valve, and a fluid coupling device and a pump system using the same and, more specifically, to a pump system capable of performing precise automatic adjustment of a variable speed load of a pressure pump, and improving energy consumption efficiency. The pump system of the present invention comprises: a pressure pump; a fluid coupling device; a working fluid; a fluid tank; and a control valve, wherein the control valve includes an upper flange, a lower flange, and a flange-shaped diaphragm.

Description

Control valve, hydraulic coupling apparatus and pump system using the same

The present invention relates to a power transmission device, and more particularly, to a control valve, a fluid coupling device using the same, and a pump system.

The fluid coupling device is a power transmission element that transmits the rotational force of the input shaft to the output shaft via a fluid. The fluid coupling device absorbs shock and torsional vibrations due to the characteristics of the power transmission method through fluid, and generates a slip defined as a value that limits the difference between the synchronous speed of the rotor and the actual speed to the synchronous speed when overloaded. Smooth power transmission is possible. The fluid coupling device may be divided into a fixed speed ratio fluid coupling device and a variable speed fluid coupling device according to the controllability of the rotation speed of the output shaft relative to the rotation speed of the input shaft under normal operating conditions. The fixed speed ratio fluid coupling device usually refers to a general fluid coupling device and may also be referred to as a standard fluid coupling device. In the fixed speed ratio fluid coupling device, when the rotation speed of the input shaft of the fluid coupling device is constant, the output shaft rotates at a constant speed although the amount of slip may vary depending on the amount of load. Specifically, the standard fluid coupling device is a method of transmitting the torque from the pump impeller to the turbine wheel by the flow force of the centrifugal force in accordance with the rotation of the coupling, the rotational speed of the driven shaft is a constant speed during steady state operation Can be in operation.

The variable speed fluid coupling device refers to a coupling capable of controlling the rotational speed of the output shaft independently of the rotational speed of the input shaft by externally adjusting the amount of fluid (eg, oil or water) therein. The variable speed fluid coupling device discharges the fluid inside the impeller / wheel to the outside through a scoop tube or a pump connected to the scoop tube, or supplies the fluid to the inside through a fluid circulation pump to supply the impeller / By regulating the amount of fluid inside the wheel, it is a method of actively controlling the speed change between the drive shaft and the driven shaft by adjusting the power transmission magnitude by the changed fluid amount.

In the driven shaft of the fluid coupling device, there are various types of machines to be connected, and according to the type of each machine, there are various demands on the control of the required power characteristics and precise rotation speed. When rotating the driven device using the variable speed fluid coupling, it is particularly important to precisely control the characteristics of the power and the rotational speed. In particular, when adjusting the variable speed load of the small pressure pump of 50 kw or less, it is difficult to adjust the amount of fluid inside the impeller / wheel of the variable speed fluid coupling device according to the amount of the desired load. Difficult to adjust precisely

In the conventional case, the variable speed load of the small pressurized pump was controlled through an inverter (VVVF) device rather than the variable speed fluid coupling device. However, although the inverter device is an expensive circuit device, it is often required to be installed in a high humidity and closed outdoor environment in which use of an electric device is weak, such as a small pressurized pumping station. In this case, there is usually a problem that it is difficult to deploy a separate management personnel, frequent downtime due to failure, it is difficult to actually operate on site. In addition, the inverter device is a complex automatic load control system that uses electricity and requires energy consumption to drive it.

The technical problem to be solved by the present invention is to provide a fluid coupling device capable of precise variable speed automatic load regulation for the driven side device, reducing energy consumption and simplifying installation and maintenance.

In addition, the technical problem to be solved by the present invention is to provide a pump system capable of precise variable speed automatic load control, reducing energy consumption, easy installation and maintenance, and easy application as a compact pressurization device.

According to one embodiment of the invention, a control valve for regulating the flow of the working fluid in the fluid coupling, the control valve, the control valve includes an upper flange containing a pressure chamber for receiving the discharge pressure of the pressurized fluid therein; A lower flange including an inlet and an outlet of a flow path through which the working fluid flows, and including a working fluid chamber for controlling the flow of the working fluid; And disposed between the upper flange and the lower flange to separate the pressurizing chamber and the working fluid chamber, and to control a flow rate of the working fluid flowing from the inlet to the outlet in accordance with the discharge pressure of the pressurized fluid. A control valve may be provided that includes a diaphragm that is directly deformed by the discharge pressure of the pressurized fluid to change the opening degree of the flow path. The discharge pressure of the pressurized fluid may be higher than the discharge pressure of the working fluid. The working fluid chamber may include a mesa structure or a groove structure for controlling the flow of the working fluid between the inlet and the outlet of the working fluid together with the diaphragm. It may further include an intermediate flange between the diaphragm and the lower flange to limit the deformation of the diaphragm from leaving a certain form. Deformation of the diaphragm may change the vertical cross-sectional area of the opening degree through which the working fluid can flow. When the discharge pressure of the pressurized fluid is not applied, the diaphragm remains unchanged so as to maximize the vertical cross-sectional area, and when the discharge pressure of the pressurized fluid is applied, the diaphragm is the pressurized fluid Concave of the diaphragm when the vertical cross-sectional area is inversely proportional to the discharge pressure of the condensed ecology, and the application of the discharge pressure of the pressurized fluid is stopped. The state can be restored to its original state. Even when the discharge pressure of the pressurized fluid is applied to the diaphragm above the maximum, the vertical cross-sectional area through which the working fluid flows can be controlled so that the minimum flow rate of the working fluid is constantly supplied to the fluid coupling through the outlet. The diaphragm may comprise at least one of a silicone and an elastomer. The thickness of the diaphragm may range from 2 mm to 9 mm. In order to control the flow rate of the working fluid within the maximum allowable deformation range of the diaphragm, the discharge pressure of the pressurized fluid may be reduced through a separate pressure reducing device coupled with the upper flange. The upper flange, the diaphragm and the lower flange may be coupled to each other through at least one fastening hole in the same position.

According to another embodiment of the present invention, a fluid coupling device coupled between a drive source and a driven device, comprising: a primary drive side wheel coupled to the drive source; A secondary driven side wheel disposed opposite the primary drive side wheel to define an operating chamber together with the primary drive side wheel and coupled to the driven device; A working fluid filled or emptied at a controlled level in the working chamber for variable torque transfer from the primary drive side wheel to the secondary driven side wheel; A fluid tank for storing the working fluid; And an inlet connected to the fluid tank and an outlet connected to the inlet of the working chamber, the fluid coupling device including a diaphragm control valve constituting a first circulation path together with the working chamber and the fluid tank. Can be provided. The diaphragm control valve may include an upper flange including a pressurization chamber therein; A lower flange including an inlet and an outlet of a flow path through which the working fluid flows, and including a working fluid chamber for controlling the flow of the working fluid; And a diaphragm disposed between the upper flange and the lower flange to separate the pressurizing chamber from the working fluid chamber and directly deformed by a pressure applied to the pressurizing chamber to change the opening degree of the flow path. The driven device is a pressure pump, and the discharge pressure of the pressurized fluid pressurized by the pressure pump may be applied to the pressure chamber of the upper flange. Even if the discharge pressure of the pressurized fluid is higher than the discharge pressure of the working fluid supplied through the inlet of the control valve, and the discharge pressure of the pressurized fluid is applied to the diaphragm more than the maximum, the minimum flow rate of the working fluid is A constant opening degree may be secured to be constantly supplied to the inlet of the working chamber through the outlet. A second circulation path coupled between the outlet of the working chamber and the fluid tank and constituting a second circulation path for supplying a cooling medium, the discharge from the outlet of the working chamber using a cooling medium supplied through the second circulation path And a heat exchanger for cooling the working fluid, wherein the cooling medium may comprise a portion of the pressurized fluid. The apparatus may further include a pressure reducing device configured to reduce the discharge pressure of the pressurized fluid so as to control the flow rate of the working fluid within the maximum allowable deformation range of the diaphragm. The decompression device comprises: an orifice coupled to a branch passage branched from the pressurized fluid; And a drain hole coupled to an output end of the orifice.

According to another embodiment of the present invention, a pressure pump for pressurizing a pressurized fluid; A first inlet coupled to the primary driving side wheel and the primary driving side wheel coupled to the driving source and coupled to the pressurizing pump for pressurizing the pressurized fluid and the primary driving side wheel; A fluid coupling device defining an operating chamber including a first outlet, the fluid coupling device including a secondary driven side wheel coupled to the pressure pump; A working fluid filled or emptied at a controlled level in the working chamber for variable torque transfer from the primary drive side wheel to the secondary driven side wheel; A fluid tank for storing the working fluid emptied from the working chamber through the first outlet and the working fluid filling the working chamber through the first inlet; And a control valve constituting a first circulation path together with the working chamber and the fluid tank, the control valve comprising: an upper flange including a pressurizing chamber for receiving a discharge pressure of the pressurized fluid; A lower flange including a second inlet connected to the fluid tank and a second outlet connected to the first inlet of the working chamber, the lower flange including a working fluid chamber for flow control of the working fluid; And a flow of the working fluid disposed between the upper flange and the lower flange to separate the pressurizing chamber from the working fluid chamber and provided from the second inlet to the second outlet according to the discharge pressure of the pressurized fluid. In order to control, the diaphragm may be directly deformed by the discharge pressure of the pressurized fluid. Even if the discharge pressure of the pressurized fluid is higher than the discharge pressure of the working fluid supplied through the inlet of the control valve, and the discharge pressure of the pressurized fluid is applied to the diaphragm more than the maximum, the minimum flow rate of the working fluid is A constant opening degree may be secured to be constantly supplied to the inlet of the working chamber through the outlet. And a pressure reducing device for reducing the discharge pressure of the pressurized fluid so as to control the flow rate of the working fluid within the maximum allowable deformation range of the diaphragm, wherein the pressure reducing device is connected to a branch flow passage branched from the pressurized fluid. Combined orifices; And a drain hole coupled to an output end of the orifice. The pressure pump may comprise a small pressure pump having an output of 50 kw or less.

According to an embodiment of the present invention, by using a flange-shaped diaphragm that is directly deformed by the discharge pressure of the pressurized fluid, to control the flow rate of the working fluid according to the discharge pressure of the pressurized fluid, a mechanical valve without complicated electronic control The system enables precise variable speed automatic load regulation of the pressurized pump, improves energy consumption efficiency, facilitates installation and maintenance, and provides a compact pump system.

Further, according to another embodiment of the present invention, by using a flange-shaped diaphragm which is directly deformed by the pressure of the fluid instead of the conventional scoop, the mechanical valve system without complicated and expensive electronic control or actuators A fluid coupling device capable of controlling the speed of the fluid coupling device, improving energy consumption efficiency, simplifying installation and maintenance, and advantageous in miniaturization can be provided.

By using a flange-shaped diaphragm that is directly deformed by the discharge pressure of the pressurized fluid to control the flow rate of the working fluid according to the discharge pressure of the pressurized fluid, precise variable speed automatic load regulation of the pressure pump is possible and energy consumption A pump system can be provided that improves efficiency, is simple to install and maintain, and is advantageous for miniaturization.

1A is a perspective view of a control valve for regulating a working fluid in a fluid coupling device according to an embodiment of the present invention, and FIGS. 1B and 1C are cross-sectional views of the control valve.
2A and 2B show an AA cutaway view in cross section of a control valve according to another embodiment of the invention.
3A and 3B are cross-sectional views of a control valve according to another embodiment of the present invention.
4 is a view showing the configuration of a fluid coupling device including a control valve according to an embodiment of the present invention.
5A and 5B are views for explaining a method of controlling a working fluid in a fluid coupling device according to an exemplary embodiment of the present invention.
6 is a view showing the configuration of a pump system including a fluid coupling device according to an embodiment of the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

The embodiments of the present invention are provided to more fully explain the present invention to those skilled in the art, and the following examples can be modified in many different forms, and the scope of the present invention is as follows. It is not limited to an Example. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art.

In addition, in the following drawings, the thickness or size of each layer is exaggerated for convenience and clarity of description, the same reference numerals in the drawings refer to the same elements. As used herein, the term "and / or" includes any and all combinations of one or more of the listed items.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the singular forms "a", "an" and "the" may include the plural forms as well, unless the context clearly indicates otherwise.

Also, as used herein, "comprise" and / or "comprising" refers to the stated shapes, numbers, steps, actions, members, elements and / or presence of these groups. It is not intended to exclude the presence or addition of one or more other shapes, numbers, operations, members, elements and / or groups.

Although the terms first, second, etc. are used herein to describe various members, parts, regions, layers, and / or parts, these members, parts, regions, layers, and / or parts are defined by these terms. It is obvious that not. These terms are only used to distinguish one member, part, region, layer or portion from another region, layer or portion.

Thus, the first member, part, region, layer or portion, which will be discussed below, may refer to the second member, component, region, layer or portion without departing from the teachings of the present invention.

In an embodiment of the present invention, the fluid coupling device can control the variable speed load of a pressurized pump used as a drain pump or feed water pump through a control valve that regulates the flow rate of the internal working fluid. For example, in the fluid coupling device, a pump may be connected to a drive shaft to configure a pressure pump. The pressure pump is coupled to a drive shaft (or primary wheel, primary blade, pump impeller) connected to an output shaft of a drive source such as a motor and the drive shaft, and a driven shaft (or 2) connected to an input shaft of the pressure pump. And a secondary wheel, a secondary blade, and a turbine wheel, and varying the load of the pressure pump connected to the driven shaft by controlling a speed change between the drive shaft and the driven shaft in accordance with the flow rate of the working fluid in the working chamber. I can regulate it.

By variably adjusting the load of such a pressurized pump, the fluid coupling device can be used in a pump system that maintains or if necessary increases the water pressure of the drain or feed water.

The fluid coupling device according to an embodiment of the present invention uses an inverter by using a control valve including a diaphragm for controlling the flow rate of the working fluid of the internal working chamber according to the pressure of the pressurized fluid such as the water pressure of the drainage or the feed water. By controlling the variable speed load of the pressure pump in a mechanical method, that is, a non-powered mechanical type, without a separate power supply, it is possible to maintain a constant water pressure of the variable drainage or water supply. However, the present invention is, of course, not limited to, and may be applied to various types of systems using variable speed load regulation through a fluid coupling device.

1A is a perspective view of a control valve CV for adjusting a flow rate of a working fluid of a fluid coupling device according to an embodiment of the present invention, FIG. 1B is a sectional view of the control valve, and FIG. 1C is a sectional view of the control valve. Figure AA shows the cutting plane.

1A and 1B, the control valve CV which regulates the flow of the working fluid in the fluid coupling device includes an upper flange UF, a lower flange LF and an upper flange UF and a lower flange LF. It may include a diaphragm (DP) coupled to.

The upper flange UF may comprise a pressurizing chamber for receiving the discharge pressure of the pressurized fluid provided perpendicular to the flow of the working fluid. In one embodiment, the pressurized fluid is provided from a drainage or feedwater supplied through a pressurized pump connected to a driven shaft of the fluid coupling device, and the discharge pressure of the pressurized fluid is from a discharge flow path coupled to the pressurized pump. It may refer to the hydraulic pressure of the fluid supplied branched. In addition, the working fluid inside the working chamber used to control the speed change between the drive shaft and the driven shaft can be either water or oil. Preferably, the working fluid may be water in consideration of environmental pollution.

The pressurization chamber may be defined as the inner hollow CT of the upper flange UF. The hollow CT may have a horizontal cross section of a circle or polygon perpendicular to the central axis AA of FIG. 1B. Preferably, the hollow CT of the upper flange UF may be a cylindrical hollow having a circular horizontal cross section having a predetermined diameter.

The lower flange LF provides a flow path through which the working fluid of the fluid coupling device flows, and includes an inlet IL and an outlet OL, and a flow of the working fluid between the inlet IL and the outlet OL. It may include a working fluid chamber for control. The blue arrows in FIGS. 1A and 1B refer to working fluids. The inlet IL of the working fluid is an inlet into which the working fluid is introduced from the fluid tank to be described later, and the outlet OL of the working fluid may be an outlet for discharging the working fluid into the working chamber in the fluid coupling device to be described later. have. The working fluid chamber may refer to a flow path space for controlling the flow rate of the working fluid introduced through the inlet IL and provided through the outlet OL. To this end, in one embodiment, the working fluid chamber is a mesa structure (MS) for adjusting the opening degree of the flow path space with a diaphragm to control the flow of the working fluid between the inlet (IL) and the outlet of the working fluid. It may include. In addition, the discharge pressure of the aforementioned pressurized fluid may be higher than the discharge pressure of the working fluid.

In one embodiment, the diaphragm DP may be an elastomer. For example, the elastomer may include an elastic polymer such as silicone polymer, rubber, and elastomer. Preferably, the diaphragm DP may include a silicon polymer.

In addition, the thickness of the diaphragm DP may range from 2 mm to 9 mm. When the thickness of the diaphragm DP is 2 mm or less, it may be easily damaged or broken by the discharge pressure of the pressurized fluid. When the thickness of the diaphragm DP is 9 mm or more, the working fluid between the inlet IL and the outlet may be It can be difficult to control the flow precisely.

In one embodiment, the diaphragm DP can be easily fixed by crimping these edge portions by combining the upper flange UF and the lower flange LF overlapping each other. The diaphragm DP may physically separate the pressurizing chamber of the upper flange UF and the working fluid chamber of the lower flange LF. In one embodiment, the control valve may further include an intermediate flange (MF) between the diaphragm (DP) and the lower flange (LF) to limit the deformation of the diaphragm (DP) from leaving the concave shape. In addition, the intermediate flange MF can prevent or minimize wear of the diaphragm DP due to disassembly and dismantling of the control valve for maintenance.

When the pressurized fluid filling the inner hollow CT of the upper flange UF presses the diaphragm DP in the vertical arrow direction, the diaphragm DP may be directly deformed by the pressurized fluid. If the pressurized fluid is provided from the pressurized fluid compressed by the pressurized pump coupled to the fluid coupling device, the discharge pressure of the pressurized fluid becomes the pressure of the pressurized fluid as it is, and is immediately transmitted to the diaphragm DP, The diaphragm DP can be convexly deformed toward the mesa structure MS as shown in FIG. 1B.

In one embodiment, when the upper flange UF transfers the discharge pressure of the pressurized fluid through the pressurization chamber in a direction perpendicular to the first surface DP_S1 of the diaphragm DP, the discharge pressure of the pressurized fluid is increased. At least a portion of the first surface DP_S1 of the applied diaphragm DP may be deformed in a concave shape in the discharge pressure direction of the pressurized fluid. The degree of deformation into the concave shape may be proportional to the magnitude of the discharge pressure of the pressurized fluid. The deformation of the diaphragm DP adjusts the distance between the second surface DP_S2 of the diaphragm DP and the mesa structure MS, so that the level of the diaphragm DP changes depending on the vertical cross-sectional area of the flow path through which the working fluid can flow. opening can be adjusted.

Referring to FIG. 1C together with FIG. 1C, when the discharge pressure PI of the pressurized fluid is applied to the center region of the diaphragm DP through the inner hollow CT of the upper flange UF, the diaphragm ( The central area of DP) may be deformed in a concave shape with respect to the vertical direction of the discharge pressure PI of the pressurized fluid. The greater the discharge pressure PI of the applied pressurized fluid, the greater the degree of deformation of the concave shape.

When the reduced pressure discharge pressure PI1 of the pressurized fluid is zero or smaller than the set reference value, the diaphragm DP may hardly be deformed. At this time, the vertical cross-sectional area (H1) through which the working fluid flows is maximized to implement the maximum opening degree. When the reduced pressure discharge pressure PI2 of the pressurized fluid is greater than PI1, the diaphragm DP may be deformed in a concave shape with respect to the vertical direction of the reduced pressure discharge pressure PI2 of the pressurized fluid. At this time, the vertical cross-sectional area (H2), that is, the opening degree through which the working fluid flows may be smaller than H1. In addition, when the reduced pressure discharge pressure PI3 of the pressurized fluid is larger than PI2, the diaphragm DP may have a larger deformation in a concave form with respect to the vertical direction of the reduced pressure discharge pressure PI3 of the pressurized fluid. . At this time, the vertical cross-sectional area (H3), that is, the opening degree through which the working fluid flows may be smaller than H2.

As such, the opening degree determined by the vertical cross-sectional areas H1, H2, H3 of the working fluid flowing through the working fluid chamber of the lower flange LF decreases with the reduced pressure discharge pressure PI1, PI2, PI3 of the pressurized fluid. Alternatively, in one embodiment, the flow rate of the working fluid may also be controlled to be output to the outlet OL in inverse proportion to the reduced pressure discharge pressure PI1, PI2, PI3 of the pressurized fluid.

Mesa structure (MS) is a fluid coupling device to be described later to control the change in speed between the drive shaft and the driven shaft, depending on the flow rate of the working fluid by interrupting or delaying the flow of the working fluid with the deformation of the diaphragm (DP) This allows the working fluid to be supplied at the desired timing.

Without mesa structure (MS), the vertical cross-sectional area through which the working fluid flows becomes smaller, and the opening degree increases as the flow velocity of the working fluid increases, so that the flow rate of the working fluid reaches the fluid coupling device exactly at the desired time. Difficult to control to be fed Thus, the amount of working fluid can be supplied to the fluid coupling device at a timing other than the desired first time point or at a timing requiring a speed change between the drive shaft and the driven shaft. Therefore, it may be difficult to induce a speed change between the drive shaft and the driven shaft in the fluid coupling device according to the water pressure of the feed water or the drainage by the pressure pump that changes in real time.

In an embodiment, the upper portion MS_U of the mesa structure MS may have a concave shape MS_B, a convex shape MS_O, or a flat shape MS_P. Preferably, the upper portion MS_U of the mesa structure MS has a concave shape MS_B in consideration of the diaphragm DP deformed into a concave shape with respect to the vertical direction of the discharge pressure PI of the pressurized fluid.

In one embodiment, when the discharge pressure of the pressurized fluid is applied to the diaphragm (DP) to the maximum, or through the pressure pump connected to the driven shaft of the fluid coupling device to maintain the maximum water pressure of the drainage or water supply Even in this case, the fluid coupling device according to the embodiment of the present invention is provided so that the minimum flow rate of the working fluid is constantly supplied to the fluid coupling through the outlet OL so that the fluid coupling device is not always stopped or turned off. The vertical cross section through which the working fluid flows can be controlled. Specifically, according to an embodiment of the present invention, although the opening degree is adjusted by the deformation of the diaphragm DP, even if the discharge pressure is applied to the maximum, the second surface DP_S2 of the diaphragm DP is the upper portion of the mesa structure MS. It is impossible to completely zero the opening of the working fluid chamber by the degree of contact with the surface, so that the opening of the working fluid chamber is not zero such that the minimum flow rate of the working fluid is constantly supplied to the working chamber in the fluid coupling device. There are great benefits that are not offered. In an embodiment, a constant opening can be ensured such that the minimum flow rate of the working fluid is constantly supplied through the outlet OL to the inlet of the working chamber.

In one embodiment, in order to control the flow rate of the working fluid within the allowable deformation range of the diaphragm DP, the discharge pressure of the pressurized fluid is decompressed through a separate pressure reducing device coupled with the upper flange UF. The discharge pressure of the pressure-reduced pressurized fluid may be provided to the diaphragm DP. This is because the discharge pressure of the pressurized fluid is relatively greater than the discharge pressure of the working fluid so that the discharge pressure of the pressurized fluid is always applied regardless of the magnitude of the discharge pressure of the pressurized fluid. Since the diaphragm DP can be deformed at the maximum, the opening degree control ability of the diaphragm DP may be lost.

Therefore, in order to deform the diaphragm DP linearly or in proportion to the discharge pressure of the variable pressurized fluid to be applied, the diaphragm DP for controlling the flow rate of the working fluid is determined by the discharge pressure of the variable pressurized fluid. It is necessary to reduce the pressure so as to satisfy the allowable deformation range of.

In one embodiment, the control valve of FIG. 1A may include a connecting portion CB to receive the pressurized fluid and the discharge pressure of the pressurized fluid from the outside, the first end of the connecting portion CB being external The second end opposite the first end of the connection CB can be connected with the upper flange UF. In addition, like the upper flange UF, the connecting portion CB has a hollow, and the hollow of the connecting portion CB and the hollow of the upper flange UF are connected to each other, and thus the upper flange UF through the hollow of the connecting portion CB. ), The discharge pressure of the pressurized fluid can be transmitted to the hollow.

In one embodiment, the upper flange (UF), the diaphragm (DP) and the lower flange (LF) has at least one fastening hole (NT) in the same position, the fastening hole (NT) is coupled to the bolt (BT), The upper flange UF, the diaphragm DP, and the lower flange LF may be fixed or coupled. Therefore, when only the bolt BT is separated from the fastening hole NT during maintenance of the control valve, the control valve can be easily and easily disassembled and dismantled, thereby making it easy to maintain.

FIG. 2A is a control valve CV according to another embodiment of the invention, and FIG. 2B is a cross-sectional view showing the opening degree change in the working fluid chamber according to the pressure PI.

Referring to FIG. 2A, the lower flange LF of the control valve CV may include a groove structure GR between the inlet IL and the outlet OL of the working fluid. Referring to FIG. 1C, when the discharge pressure PI of the pressurized fluid is applied in a direction perpendicular to the center region of the diaphragm DP through the inner hollow of the upper flange UF, the center region of the diaphragm DP may be avoided. It may be deformed in a concave shape with respect to the vertical direction of the discharge pressure PI of the pressurized fluid. As the discharge pressure PI of the pressurized fluid to be applied increases, the degree of deformation of the concave shape increases while the opening degree decreases.

In the absence of the groove-shaped structure GR, when the vertical cross-sectional area in which the working fluid flows decreases, the discharge pressure of the working fluid decreases, so that it is difficult to control the amount of the working fluid to be supplied to the fluid coupling device at a desired time. . For example, an amount of working fluid may be supplied to the fluid coupling device at a timing other than the desired first time point or at a timing that requires a speed change between the drive shaft and the driven shaft. Therefore, it may be difficult to change the speed between the drive shaft and the driven shaft in the fluid coupling device according to the water pressure of the feed water or the drainage by the pressure pump that changes in real time.

In one embodiment, even if the discharge pressure PI of the variable pressurized fluid is applied to the diaphragm DP to a maximum or more, the minimum flow rate of the working fluid is described later through the outlet OL of the fluid coupling device 100. A constant opening degree may be secured between the upper surface MS_U of the mesa structure MS and the second surface DP_S2 of the diaphragm DP so as to be constantly supplied to the working chamber. Specifically, even when the discharge pressure PI of the variable pressurized fluid is applied to the diaphragm at a maximum or more, the upper surface MS_U of the mesa structure MS and the second surface DP_S2 of the diaphragm DP do not touch.

In another embodiment, when the discharge pressure PI of the variable pressurized fluid is applied to the diaphragm DP to a maximum or more, the upper surface MS_U of the mesa structure MS and the second surface DP_S2 of the diaphragm DP. Even if this is closed, the bypass through hole BPH may be used to allow the minimum flow rate of the working fluid to flow through the outlet OL as shown in FIG. 3A.

3A is a control valve CV in accordance with another embodiment of the present invention. Referring to FIG. 3A, the control valve CV may further include a bypass through hole BPH passing through the mesa structure MS. When the discharge pressure PI of the variable pressurized fluid is applied to the diaphragm DP above the maximum, the upper part MS_U of the mesa structure MS and the second surface DP_S2 of the diaphragm DP are closed to secure an opening. Although not possible, the minimum flow rate FF of the working fluid may flow through the bypass through hole BPH to the outlet OL.

As described above, when the decompressed discharge pressure PI of the pressurized fluid is zero or smaller than the set reference value, the diaphragm DP may hardly be deformed. At this time, the working fluid CF1 flows back from the inlet IL of the control valve CV, the working fluid CF2 flows back from the outlet OL of the control valve CV, or a combination thereof. By CF1 and CF2, the diaphragm DP may be convexly deformed, which may damage or break the diaphragm DP.

In order to prevent the diaphragm DP from being damaged or broken by the backflow working fluids CF1 and CF2, the backflow preventing member CFP may be used as shown in FIG. 3B.

3B is a control valve CV in accordance with another embodiment of the present invention. Referring to FIG. 3B, the backflow preventing member CFP is disposed on the inner wall UF_S of the upper flange UF, and the diaphragm DP convexly deformed by the countercurrent working fluids CF1 and CF2 is above the reference value. It can serve to suppress the deformation.

In one embodiment, the non-return member CFP is arranged in discontinuous n (A) to the inner wall (UF_S) of the upper flange (UF) or continuous strip form (B) to the inner wall (UF_S) of the upper flange (UF). )

4 is a configuration diagram of a fluid coupling device 100 including a control valve CV according to an embodiment of the present invention, and FIGS. 4A and 4B illustrate a fluid coupling device 100 according to an embodiment of the present invention. It is a figure for demonstrating the method of controlling the working fluid in a inside.

Referring to FIG. 4, the fluid coupling device 100 includes a primary drive side wheel DH1, a secondary driven side wheel DH2, a working fluid WF, a fluid tank FT, and a control valve CV. It may include. Optionally, the fluid coupling device may further comprise a heat exchanger (HE) and / or a pressure reduction device (DCD).

The primary drive side wheel DH1 is coupled to a drive source such as a motor or engine, and the secondary driven side wheel DH2 is disposed opposite the primary drive side wheel DH1 to define the working chamber WC, and pressurize It may be coupled to a driven device such as a pump or wheel. The drive source transmits power to the primary drive side wheel DH1 through the drive shaft X1, and the driven device receives power through the driven shaft X2.

The working fluid WF may be filled or emptied at a controlled level in the working chamber WC for variable torque transfer from the primary drive side wheel DH1 to the secondary driven side wheel DH2. The working fluid WF may fill the working chamber WC through the first inlet IL and may be emptied from the working chamber WC through the first outlet OL. The fluid tank FT may store the working fluid WF to ensure circulation of the working fluid WF in the fluid coupling device 100.

The control valve CV includes a second inlet IL2 connected to the fluid tank FT and a second outlet OL2 connected to the first inlet IL of the working chamber WC, and the working chamber WC. ) And the fluid tank FT may constitute the first circulation path CP1. Regarding the control valve CV, reference may be made to the detailed descriptions of FIGS. 1A to 1C unless there is a contradiction.

The working fluid used as a medium for controlling the speed change between the drive shaft X1 and the driven shaft X2 receives the heat generated by the SLIP of the primary drive shaft hill DH1 and the secondary driven shaft hill DH2. Since the temperature of the fluid can be raised, it is necessary to cool the hot working fluid for smooth power transmission.

In one embodiment of the invention, the heat exchanger HE may be coupled between the first outlet OL of the working chamber WC and the fluid tank WF. In one embodiment, a second circulation path CP2 for supplying the cooling medium is constructed, and with the cooling medium supplied through the second circulation path CP2, the first outlet OL of the working chamber WC. The working fluid WF discharged from it can be cooled. The cooling medium may comprise a portion of the pressurized fluid which is exposed to the outside to cool or includes drainage or water supply. The used cooling medium can be used for drainage or water supply via the second circulation path CP2.

In one embodiment of the invention, the primary drive side wheel DH1 and the secondary driven side wheel DH2 may be protected via a fluid coupling housing HCC. The working chamber WC including the primary drive side wheel DH1 and the secondary driven side wheel DH2 may further comprise some area inside the fluid coupling housing HCC. For example, the actuation chamber WC is a first actuation chamber defined from the engagement of the primary drive side wheel DH1 and the secondary driven side wheel DH2 and a second actuation inside the fluid coupling housing HCC. A chamber may be included, and the first working chamber and the second working chamber may be organically connected to each other.

In one embodiment of the invention, the physical position of the fluid tank FT is arranged to be higher than the physical position of the control valve CV such that the working fluid from the fluid tank FT is removed by the gravity of the control valve CV. It can be supplied to the two inlets IL2. The working fluid in the fluid tank FT is transferred to the control valve CV side with the aid of gravity, which advantageously eliminates the need for a separate pump for the circulation of the working fluid.

In one embodiment, the working fluid WF introduced into the lower space of the fluid coupling device 100 is driven by the rotation of the primary drive side wheel DH1 and the secondary driven side wheel DH2, or It can be guided by the tube ST and fed back to the fluid tank WF. The tube ST is fixed so that the working fluid WF can be discharged from the working chamber at any time through the outlet OL, and if the working fluid is sufficient in the working chamber, the working fluid can be discharged at a constant flow rate. The flow rate of the working fluid in the working chamber WC can be adjusted by the amount of working fluid drawn from the control valve CV coupled to the inlet IL.

In one embodiment, the decompression device DCD is applied to the diaphragm DP in consideration of the operating range of the diaphragm DP considering the maximum allowable deformation range of the diaphragm DP for an accurate opening control operation of the diaphragm DP. The drive pressure can be reduced. For example, when the discharge pressure of the pressurized fluid is used as a pressure source as it is, the discharge pressure of the pressurized fluid is applied to the diaphragm DP as it is, so that the maximum allowable deformation range is determined according to the design conditions of the diaphragm DP. In this case, accurate opening of the diaphragm may not be controlled. According to the embodiment of the present invention, the diaphragm (DV) is coupled between the control valve CV and the pressure source without coupling the pressure source applied to the diaphragm DP directly to the diaphragm DP. Accurate opening control of DP) is possible, and the control valve CV having a diaphragm DP designed to be driven within a predetermined pressure range enables operation within various pressure ranges by adjusting the pressure of the pressure reducing device DCD. Technical advantages can be provided.

In one embodiment, when using the discharge pressure PI of the pressurized fluid as the pressure source, the decompression device DCD decompresses the first sub-pressurized fluid branched from the pressurized fluid into a second sub-pressurized fluid. It may include an orifice and a drain (drain) for discharging a portion of the second sub-pressurized fluid to another place. By discharging a portion of the second sub-pressurized fluid elsewhere, the discharge pressure of the second sub-pressurized fluid can be reduced, and the discharged second sub-pressurized fluid can be reduced to the pressurized fluid.

In one embodiment, the discharge pressure of the pressurized fluid may be higher than the discharge pressure of the working fluid supplied through the inlet of the control valve, even if the discharge pressure of the pressurized fluid is applied to the diaphragm more than the maximum, A constant opening degree can be ensured so that the minimum flow rate of the working fluid is constantly supplied to the inlet of the working chamber through the outlet.

5A and 5B, although one control valve CV is exemplarily described in FIG. 3A, in another embodiment, a plurality of control valves CV1 and CV2 are disposed in the first circulation path CP1. The flow rate of the working fluid can also be adjusted in conjunction. The blue horizontal arrows in FIGS. 5A and 5B refer to the working fluid. The blue vertical arrow indicates the reduced pressure discharge pressures PI1 and PI2 of the pressurized fluid. The reduced pressure discharge pressure PI1 size of the pressurized fluid and the reduced pressure discharge pressure PI2 size of the pressurized fluid respectively input to the control valves CV1 and CV2 may be the same or different.

The working fluid can be controlled through the first control valve CV1 and the second control valve CV2, and the first control valve CV1 is disposed between the fluid tank FT and the inlet IL of the working chamber. The flow rate of the working fluid WF flowing into the working chamber WC is regulated, and the second control valve CV2 is disposed between the discharge chamber OL of the working chamber and the fluid tank FT, and thus from the working chamber WC. The flow rate of the discharged working fluid WF can be adjusted. Alternatively, both of the first control valve CV1 and the second control valve CV2 are disposed between the fluid tank FT and the inlet IL of the working chamber, so that the working fluid WF flows into the working chamber WC. The flow rate can be adjusted.

In another embodiment, the working fluid discharged from the working chamber WC is disposed between the first control valve CV1 and the second control valve CV2 both between the outlet OL of the working chamber and the fluid tank FT. The flow rate of (WF) can be adjusted.

As shown in FIG. 5A, the first control valve CV1 and the second control valve CV2 have the same size and the same control level capacity, or as shown in FIG. 5B, as shown in FIG. 5B. The second control valve CV2 may have different sizes and different control level capacities.

4, the first circulation path CP1, the second circulation path CP2, the control valve CV and the pressure reducing device DCD are illustrated as separate components from the fluid coupling housing HCC, although other components are illustrated. In an embodiment, all or part of the first circulation path CP1, the second circulation path CP2, the control valve CV and the pressure reducing device DCD may be arranged inside the fluid coupling housing HCC. This arrangement can be convenient in terms of maintenance through modularity.

6 is a diagram illustrating a configuration of a pump system 200 including a fluid coupling device 100 according to an embodiment of the present invention.

Referring to FIG. 6, the primary drive side wheel DH1, the secondary driven side wheel DH2, the working fluid WF, the fluid tank FT and the control valve CV for pressurizing the pressurized fluid A pump system is disclosed that includes a fluid coupling device 100 and a pressure pump PP coupled thereto. Optionally, the fluid coupling device may further comprise a heat exchanger (HE) and a pressure reduction device (DCD).

The pressure pump PP may pressurize the pressurized fluid to compensate for the reduced water supply or drainage pressure or increase the pressure of the water supply or drainage if necessary when the pressure of the water supply or the drainage is reduced in the water supply or the drainage station. This pressurization of the pressure pump PP is changed by controlling the speed change between the primary drive side wheel DH1 and the secondary driven side wheel DH2 according to the flow rate of the working fluid of the fluid coupling device 100. You can. The pressurized pump PP is preferably applied to a small pressurized pump requiring an output of 50 kw or less, which is capable of non-power control using the control valve CV and thus does not require expensive inverter power control.

The primary driving side wheel DH1 may be coupled to a driving source MT such as a motor or an engine. The secondary drive side wheel DH2 may be disposed opposite the primary drive side wheel DH1 to define the working chamber WC together with the primary drive side wheel DH1 and may be coupled to the pressure pump PP. . The working fluid WF may be filled or emptied at a controlled level in the working chamber WC for variable torque transfer from the primary drive side wheel DH1 to the secondary driven side wheel DH2. The working fluid WF may fill the working chamber WC through the first inlet IL or empty from the working chamber WC through the first outlet OL. The fluid tank FT may store the working fluid WF.

The control valve CV includes a second inlet IL2 connected to the fluid tank FT and a second outlet OL2 connected to the first inlet IL of the working chamber WC, and the working chamber WC. ) And the fluid tank FT may constitute the first circulation path CP1. Concerning the control valve CV, reference may be made to the description of the control valve disclosed with reference to FIGS. 1A-1C, unless there is a contradiction. Also, regarding the fluid coupling device, reference may be made to the description of the fluid coupling device disclosed with reference to FIG. 3.

In one embodiment of the present invention, the fluid W pressurized through the pressure pump (PP) is supplied to a place such as an apartment, a shopping mall building by a predetermined hydraulic pressure through the drainage pipe, a portion of the pressurized fluid (W) The first pressurized fluid) may be transferred to the heat exchanger HE through the first branch conduit DL1 and used as a cooling medium. The heat exchanger HE may feed back the first pressurized fluid used as the cooling medium to the input end of the pressure pump PP.

In an embodiment, referring again to FIGS. 1A and 1B in conjunction with FIG. 6, a portion of the pressurized fluid branches from the pressurized fluid W to allow the top flange (FIGS. 1A and 1) to control the opening of the control valve CV. (See UF in FIG. 1B). The branched pressurized fluid may press the diaphragm DF while filling the inner hollow CT of the upper flange UF. As the discharge pressure of the pressurized fluid W is increased, the strain of the diaphragm DP is increased and thereby the opening degree is reduced, and as a result, the working fluid drawn into the working chamber WC of the fluid coupling device 100 ( The amount of WF is reduced so that the power transmitted from the drive source MT to the pump PP is automatically reduced and the increase in discharge pressure by the drive source MT can be suppressed. On the contrary, when the discharge pressure of the pressurized fluid W is reduced, the strain of the diaphragm DP is reduced, thereby increasing the opening degree, and as a result, into the working chamber WC of the fluid coupling device 100. The amount of the working fluid WF drawn in is increased so that the power transmitted from the drive source MT to the pump PP is increased, and as a result, the discharge pressure of the pressurized fluid W can be increased.

Thus, according to an embodiment of the present invention, the working fluid through the outlet OL by controlling the amount of working fluid WF drawn into the inlet IL of the fluid coupling device 100 by the control valve CV Complicated and expensive actuators, such as scoops for flow control of (WC), are not required, and mechanically actuated control valves (CVs) by utilizing the discharge pressure of the pressurized fluid (W) are used for non-powered mechanical control. It is possible to provide an instantaneous and reliable pressurization device, whereby a low power device can be realized and an economical pressure pump system can be provided without the need for expensive control circuits.

In one embodiment, in order for the discharge pressure PI of the pressurized fluid W to deform the diaphragm DP of the control valve CV according to the control valve, the discharge pressure PI of the variable pressurized fluid is changed. An apparatus for reducing the discharge pressure PI of the pressurized fluid to PI2 may be required to correspond to a wide range of the pressure of the pressurized fluid within an allowable deformation range of the diaphragm DP for controlling the flow rate of the working fluid. have. In one embodiment, the pressure reducing device DCD for reducing the discharge pressure of the pressurized fluid W may be coupled between the output side of the pump PP and the input side of the control valve CV.

In one embodiment, the decompression device DCD diverts a portion of the first pressurized fluid of the first branch conduit DL1 to supply a second pressurized fluid for use as a control factor of the control valve CV. (OF) and a drain D for discharging a part of the second sub-pressurized fluid to another place. The second pressurized fluid is a fluid depressurized from the first pressurized fluid, and the discharge pressure PI of the pressurized fluid W and the discharge pressure PI of the first pressurized fluid may be the same. have.

A part of the second sub-pressurized fluid is discharged through the drain port D, so that the discharge pressure PI2 of the second sub-pressurized fluid is greater than the discharge pressure PI of the pressurized fluid depending on the amount of the discharged fluid. The pressure may be reduced to the discharge pressure PI2 of the small second sub-pressurized fluid.

The reduced pressure discharge pressure PI2 of the second pressurized fluid may be higher than the discharge pressure of the working fluid WF supplied through the second inlet OL2 of the control valve CV. This is for controlling the flow rate of the working fluid WF in inverse proportion to the discharge pressure PI of the pressurized fluid, and if the reduced pressure discharge pressure PI2 of the second pressurized fluid is the second of the control valve CV, When the discharge pressure of the working fluid WF supplied through the inlet OL2 is less than or equal to the discharge pressure PI, the flow rate of the working fluid WF is difficult to be controlled in inverse proportion to the discharge pressure PI of the pressurized fluid.

Further, even when the discharge pressure PI of the pressurized fluid is applied to the diaphragm DP to a maximum or more, a minimum flow rate of the working fluid WF is constant through the outlet to the inlet of the working chamber WC. A certain opening degree can be secured so as to be supplied. It is always associated with the pressure pump PP by supplying the minimum flow rate of the working fluid WF to the working chamber WC in the fluid coupling device 100 even if the hydraulic pressure does not need to drive the pressure pump PP. This is to prevent the fluid coupling device from stopping.

As described above, the flange-type diaphragm DP directly deformed by the discharge pressure PI of the pressurized fluid is controlled to control the flow rate of the working fluid WF according to the discharge pressure PI of the pressurized fluid. By using this, precise variable speed automatic load regulation of a small pressure pump is possible. The physical position of the fluid tank FT is arranged to be higher than the physical position of the control valve CV so that the working fluid WF from the fluid tank FT is gravity-induced by the second inlet OL2 of the control valve CV. By implementing to be supplied to the, it is possible to drive the control valve (CV) with no power. In addition, by using the control valve (CV) in the form of a flange, the installation and maintenance can be simple.

The present invention described above is not limited to the above-described embodiment and the accompanying drawings, and various substitutions, modifications, and changes are possible within the scope without departing from the technical spirit of the present invention. It will be apparent to those who have the knowledge of.

UF: upper flange LF: lower flange
DP: flanged diaphragm MF: intermediate flange
MS: Mesa structure GR: Groove structure
NT: Fastener BT: Bolt
IL: Inlet OL: Outlet
CB: connection DH1: primary drive side wheel
DH2: Secondary driven wheel WF: Working fluid
FT: fluid tank CV: control valve
PP: pressure pump HE: heat exchanger
DCD: Pressure Reducing Device WC: Working Chamber
CP1: first circulation path CP2: second circulation path
ST: Scoop tube PI: Pressurized fluid discharge pressure
D: Drain OF: Orifice
DL1: first branch pipeline

Claims (16)

A control valve that regulates the flow of working fluid in a fluid coupling,
The control valve,
An upper flange including a pressurizing chamber configured to receive a discharge pressure of the pressurized fluid therein;
A lower flange including an inlet and an outlet of a flow path through which the working fluid flows, and including a working fluid chamber for controlling the flow of the working fluid; And
The blood chamber disposed between the upper flange and the lower flange to separate the pressurizing chamber and the working fluid chamber, and to control a flow rate of the working fluid flowing from the inlet to the outlet according to the discharge pressure of the pressurized fluid. A diaphragm which is directly deformed by the discharge pressure of the pressurized fluid to change the opening degree of the flow path;
A mesa structure or a groove structure provided on the lower flange side so as to face the diaphragm, and for controlling the flow of the working fluid between the inlet and the outlet with the diaphragm; And
An intermediate flange between the diaphragm and the lower flange,
The intermediate flange exposes the mesa structure or the groove structure and has a through hole perpendicular to the discharge pressure of the pressurized fluid,
An area excluding the through hole of the intermediate flange is in close contact with the diaphragm such that deformation of the diaphragm is not transmitted through the through hole beyond a certain shape.
And the diaphragm deforms the intermediate region of the diaphragm to be concave in a vertically limited direction only through the through hole to change the opening degree of the flow path between the deformed diaphragm and the mesa structure or the groove structure. The method of claim 1,
A control valve having a discharge pressure of the pressurized fluid higher than a discharge pressure of the working fluid. delete delete The method of claim 1,
Deforming the diaphragm alters the vertical cross-sectional area of the opening degree through which the working fluid can flow. The method of claim 5, wherein
When the discharge pressure of the pressurized fluid is not applied, the diaphragm is maintained without deformation so that the vertical cross-sectional area is maximum,
When the discharge pressure of the pressurized fluid is applied, the diaphragm is deformed into a concave ecology in compliance with the direction of the discharge pressure of the applied pressurized fluid so that the vertical cross-sectional area is changed in inverse proportion to the discharge pressure of the pressurized fluid. ,
And when the application of the discharge pressure of the pressurized fluid is stopped, the concave state of the diaphragm is restored to its original state. The method of claim 1,
And a vertical cross-sectional area in which the working fluid flows so that the minimum flow rate of the working fluid is constantly supplied to the fluid coupling through the outlet, even if the discharge pressure of the pressurized fluid is applied to the diaphragm above a maximum. The method of claim 1,
And the diaphragm comprises at least one of silicone and elastomer. The method of claim 1,
The diaphragm has a thickness in the range of 2 mm to 9 mm. The method of claim 1,
In order to control the flow rate of the working fluid within the maximum allowable deformation range of the diaphragm, the discharge pressure of the pressurized fluid is reduced through a separate pressure reducing device coupled with the upper flange. The method of claim 1,
And the upper flange, the diaphragm and the lower flange are coupled to each other through at least one fastening hole in the same position. A fluid coupling device coupled between a drive source and a driven device,
A primary drive side wheel coupled to the drive source;
A secondary driven side wheel disposed opposite the primary drive side wheel to define an operating chamber together with the primary drive side wheel and coupled to the driven device;
A working fluid filled or emptied at a controlled level in the working chamber for variable torque transfer from the primary drive side wheel to the secondary driven side wheel;
A fluid tank for storing the working fluid; And
A fluid couple comprising the diaphragm type control valve of claim 1 comprising an inlet connected to the fluid tank and an outlet connected to the inlet of the working chamber, the diaphragm type control valve of claim 1 constituting a first circulation path with the working chamber and the fluid tank. Ring device. The method of claim 12,
The diaphragm control valve may include an upper flange including a pressurization chamber therein;
A lower flange including an inlet and an outlet of a flow path through which the working fluid flows, and including a working fluid chamber for controlling the flow of the working fluid; And
And a diaphragm disposed between the upper flange and the lower flange to separate the pressurizing chamber and the working fluid chamber, and directly deformed by a pressure applied to the pressurizing chamber to change an opening degree of the flow path. . A fluid coupling device coupled between a drive source and a driven device,
A primary drive side wheel coupled to the drive source;
A secondary driven side wheel disposed opposite the primary drive side wheel to define an operating chamber together with the primary drive side wheel and coupled to the driven device;
A working fluid filled or emptied at a controlled level in the working chamber for variable torque transfer from the primary drive side wheel to the secondary driven side wheel;
A fluid tank for storing the working fluid; And
A diaphragm control valve including an inlet connected to the fluid tank and an outlet connected to the inlet of the working chamber, the diaphragm control valve constituting a first circulation path together with the working chamber and the fluid tank;
The diaphragm control valve may include an upper flange including a pressurization chamber therein;
A lower flange including an inlet and an outlet of a flow path through which the working fluid flows, and including a working fluid chamber for controlling the flow of the working fluid; And
A diaphragm disposed between the upper flange and the lower flange to separate the pressurizing chamber from the working fluid chamber, and directly deformed by a pressure applied to the pressurizing chamber to change the opening degree of the flow path,
The driven device is a pressure pump,
The discharge pressure of the pressurized fluid pressurized by the pressure pump is applied to the pressure chamber of the upper flange,
The discharge pressure of the pressurized fluid is higher than the discharge pressure of the working fluid supplied through the inlet of the control valve,
Even if the discharge pressure of the pressurized fluid is applied to the diaphragm at a maximum or more, a constant opening degree is ensured so that the minimum flow rate of the working fluid is constantly supplied to the inlet of the working chamber through the outlet,
A second circulation path coupled between the outlet of the working chamber and the fluid tank, which constitutes a second circulation path for supplying a cooling medium, and with the cooling medium supplied through the second circulation path, discharges from the outlet of the working chamber Further comprising a heat exchanger for cooling the working fluid being
The cooling medium comprises a portion of the pressurized fluid,
And a pressure reducing device for reducing the discharge pressure of the pressurized fluid so as to control the flow rate of the working fluid within the maximum allowable deformation range of the diaphragm,
The decompression device,
An orifice coupled to a branch flow path branched from the pressurized fluid; And
And a drain hole coupled to the output end of the orifice. A pressurizing pump for pressurizing the pressurized fluid;
A first inlet coupled to the primary driving side wheel and the primary driving side wheel coupled to the driving source and coupled to the pressurizing pump for pressurizing the pressurized fluid and the primary driving side wheel; A fluid coupling device defining an operating chamber including a first outlet, the fluid coupling device including a secondary driven side wheel coupled to the pressure pump;
A working fluid filled or emptied at a controlled level in the working chamber for variable torque transfer from the primary drive side wheel to the secondary driven side wheel;
A fluid tank for storing the working fluid emptied from the working chamber through the first outlet and the working fluid filling the working chamber through the first inlet; And
A control valve constituting a first circulation path with the working chamber and the fluid tank,
The control valve,
An upper flange including a pressurizing chamber for receiving a discharge pressure of the pressurized fluid;
A lower flange including a second inlet connected to the fluid tank and a second outlet connected to the first inlet of the working chamber, the lower flange including a working fluid chamber for flow control of the working fluid; And
Disposed between the upper flange and the lower flange to separate the pressurizing chamber and the working fluid chamber, and the flow of the working fluid provided from the second inlet to the second outlet according to the discharge pressure of the pressurized fluid A diaphragm directly deformed by the discharge pressure of the pressurized fluid to control;
A mesa structure or a groove structure provided on the lower flange side opposite the diaphragm and for controlling the flow of the working fluid between the inlet and the outlet together with the diaphragm; And
An intermediate flange between the diaphragm and the lower flange,
The intermediate flange exposes the mesa structure or the groove structure and has a through hole perpendicular to the discharge pressure of the pressurized fluid,
An area excluding the through hole of the intermediate flange is in close contact with the diaphragm such that deformation of the diaphragm is not transmitted through the through hole beyond a certain shape.
And the diaphragm deforms the intermediate region of the diaphragm to be concave in a vertically limited direction only through the through hole to change the opening degree of a flow path between the deformed diaphragm and the mesa structure or the groove structure. A pressurizing pump for pressurizing the pressurized fluid;
A first inlet coupled to the primary driving side wheel and the primary driving side wheel coupled to the driving source and coupled to the pressurizing pump for pressurizing the pressurized fluid and the primary driving side wheel; A fluid coupling device defining an operating chamber including a first outlet, the fluid coupling device including a secondary driven side wheel coupled to the pressure pump;
A working fluid filled or emptied at a controlled level in the working chamber for variable torque transfer from the primary drive side wheel to the secondary driven side wheel;
A fluid tank for storing the working fluid emptied from the working chamber through the first outlet and the working fluid filling the working chamber through the first inlet; And
A control valve constituting a first circulation path with the working chamber and the fluid tank,
The control valve,
An upper flange including a pressurizing chamber for receiving a discharge pressure of the pressurized fluid;
A lower flange including a second inlet connected to the fluid tank and a second outlet connected to the first inlet of the working chamber, the lower flange including a working fluid chamber for flow control of the working fluid; And
Disposed between the upper flange and the lower flange to separate the pressurizing chamber and the working fluid chamber, and the flow of the working fluid provided from the second inlet to the second outlet according to the discharge pressure of the pressurized fluid And a diaphragm which is directly deformed by the discharge pressure of the pressurized fluid to be controlled,
The discharge pressure of the pressurized fluid is higher than the discharge pressure of the working fluid supplied through the inlet of the control valve,
Even if the discharge pressure of the pressurized fluid is applied to the diaphragm with a maximum or more, a constant opening degree is ensured so that the minimum flow rate of the working fluid is constantly supplied to the inlet of the working chamber through the outlet,
A pressure reducing device for reducing the discharge pressure of the pressurized fluid so as to control the flow rate of the working fluid within the maximum allowable deformation range of the diaphragm,
The decompression device,
An orifice coupled to a branch flow path branched from the pressurized fluid; And
A drain port coupled to the output end of the orifice,
The pressure pump comprises a small pressure pump having an output of 50 kw or less.

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