JP2006090226A - Control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a control valve of a cooling system capable of preventing the occurrence of cavitation, and capable of improving reliability of the temperature adjusting function of a refrigerant, by effectively using the refrigerant, or adjusting the temperature of the refrigerant. <P>SOLUTION: This cooling system mounted on a vehicle, is composed of a cooling circuit provided with an engine and circulating a coolant, an exhaust heat system flow passage connected to the cooling circuit and provided with a radiator, a thermostat arranged in a confluent position between the exhaust heat system flow passage and the cooling circuit and controlling a flow rate of the coolant to the radiator, a water pump arranged downstream of the thermostat and forcibly feeding the coolant to the cooling circuit, and a control valve 10 for controlling the coolant flowing in the cooling circuit. The control valve 10 has a valve element 15 rotatably journaled in a first cover 11. The valve element 15 has first and second valve plates 17 and 18 formed around a rotary shaft 16. The first and second valve plates 17 and 18 are formed so as to become mutually different in the pressure receiving area for receiving pressure from the coolant. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a control valve for a cooling system mounted on a vehicle.

  In recent years, as a cooling system mounted on a vehicle such as an automobile, a system having a function of not only preventing overheating of an engine but also reducing friction and effectively using heat of a coolant has been proposed. For example, Patent Document 1 proposes a system in which a thermostat is provided on the discharge port side of a flow path provided on the engine side and the liquid temperature of the coolant on the cylinder head side and the cylinder block side is controlled. In this system, the cylinder head side is further cooled to improve knocking control and intake air charging efficiency. On the cylinder block side, the lubricating oil temperature is set to an appropriate temperature to reduce friction and prevent oil deterioration.

On the other hand, in Patent Document 2, the coolant is used as a heat source for the air-conditioning heater by heat exchange between the coolant and air, and the hydraulic fluid of the transmission is set to an appropriate temperature by heat exchange between the coolant and the hydraulic oil. Cooling systems have been proposed that keep the range. The cooling system includes a heat exchanger for heater and a heat exchanger for exchanging heat with hydraulic oil, and a control valve for controlling a flow rate to each heat exchanger in the cooling circuit.
JP-A-10-184358 JP 2002-364362 A

  However, when the number of parts such as thermostats and control valves increases, the water flow resistance of the entire cooling circuit increases. As a result, the suction port side of the pump that pumps the coolant is decompressed, and cavitation is likely to occur. In addition, when the water flow resistance of the entire cooling circuit increases, the differential pressure generated upstream and downstream of the thermostat that closes the flow path on the radiator side increases during the warm-up process, and the thermostat opens due to this differential pressure. there is a possibility. When the differential pressure opening occurs, the coolant flows into the radiator in spite of the warm-up process, and the temperature control function of the coolant is degraded.

  The present invention has been made in view of the above problems, and an object thereof is to effectively use the refrigerant or adjust the temperature of the refrigerant, and to prevent the occurrence of cavitation and improve the reliability of the temperature adjustment function of the refrigerant. The object is to provide a control valve for a cooling system that can.

  In order to solve the above problems, the invention described in claim 1 includes a first cooling circuit connected to a heat source and circulating the refrigerant, and a cooling means connected to the first cooling circuit and radiating heat from the refrigerant. A second cooling circuit, a flow rate control valve provided between the first cooling circuit and the second cooling circuit, for controlling the flow rate of the refrigerant from the first cooling circuit to the second cooling circuit; In the cooling system having a refrigerant pumping means for pumping the refrigerant to both the cooling circuits and a control valve for controlling the flow rate of the refrigerant in the first cooling circuit, the control valve is a passage in the first cooling circuit. The valve body is supported so as to be rotatable inside, and the valve body is formed asymmetrically with respect to the rotation center.

According to a second aspect of the present invention, there is provided a first cooling circuit that is connected to a heat source and in which a refrigerant circulates, a second cooling circuit that is connected to the first cooling circuit and has cooling means for radiating heat of the refrigerant, and the first cooling circuit. A flow rate control valve that is provided between the cooling circuit and the second cooling circuit and controls the flow rate of the refrigerant from the first cooling circuit to the second cooling circuit, and pumps the refrigerant to both cooling circuits. In a cooling system having a refrigerant pressure feeding means and a control valve for controlling the flow rate of the refrigerant in the first cooling circuit, the control valve is rotatably supported in the passage of the first cooling circuit. The gist is that a gap is provided between both ends of the valve body and the passage, and the gap areas of the gaps are different from each other.

  According to a third aspect of the present invention, in the control valve according to the first or second aspect, the passage of the first cooling circuit includes a first flow path and a second flow path into which the refrigerant flows, and the refrigerant is It is composed of a connection part connected to the third flow path that flows out, and controls the flow rate of the refrigerant flowing from the first flow path and the second flow path to the third flow path at the connection part. And

  According to a fourth aspect of the present invention, in the control valve according to any one of the first to third aspects, the control valve is configured such that a pressure difference between the upstream and downstream of the flow control valve is different from the flow control valve. The gist is to operate so that the pressure generated on the suction side of the refrigerant pressure feeding means becomes larger than the pressure generated by cavitation so that the pressure becomes smaller than the pressure opening valve pressure.

A fifth aspect of the present invention is the control valve according to any one of the first to fourth aspects, wherein the valve body is rotated by an electromagnetic drive unit.
According to a sixth aspect of the present invention, in the control valve according to the fifth aspect, the electromagnetic drive unit rotates the valve body in the forward and reverse directions by switching the energization direction, and at each end position, The gist is that the supply current is reduced or cut off.

  According to a seventh aspect of the present invention, in the control valve according to the fifth or sixth aspect, the electromagnetic drive unit is configured such that a pressure difference between the upstream and downstream of the flow control valve is a differential pressure opening of the flow control valve. The gist is that the supply current is controlled at a pressure smaller than the pressure, and the supply current is controlled according to the operating conditions of the vehicle.

(Function)
According to the first aspect of the present invention, the valve body that is rotatably supported in the passage of the first cooling circuit is formed asymmetrically with respect to the center of rotation. When the pressure applied to the valve body by the flow of the refrigerant becomes a predetermined value or more, it is rotated at an unbalanced force so as to reduce the passage resistance of the passage. Therefore, for example, by adjusting the cavitation generation pressure on the suction side of the flow control valve and the suction side of the refrigerant pressure feeding means, and the rotation conditions of the control valve, the differential pressure opening valve and the cavitation before By rotating the valve body to a position where the water resistance can be reduced, the water resistance of the entire cooling system can be reduced.

  According to the second aspect of the present invention, the gap is provided between the valve body rotatably supported in the passage of the first cooling circuit and the passage, and the gap areas of the gaps are different from each other. Therefore, when the pressure applied to the valve body by the flow of the refrigerant becomes a predetermined value or more, the valve body is rotated by a force imbalance and is disposed at a position where the passage resistance of the passage is reduced. Therefore, for example, by adjusting the cavitation generation pressure on the suction side of the flow control valve and the suction side of the refrigerant pressure feeding means, and the rotation conditions of the control valve, the differential pressure opening valve and the cavitation before By rotating the valve body to a position where the water resistance can be reduced, the water resistance of the entire cooling system can be reduced. Further, the structure of the control valve can be simplified.

  According to the third aspect of the present invention, the passage through which the valve body of the control valve is supported is provided at the connection portion where the first and second flow paths and the third flow path provided in the cooling circuit are connected. Therefore, the water flow resistance of the cooling circuit can be controlled while controlling the flow rate distributed to the first and second flow paths.

According to the fourth aspect of the present invention, the control valve operates such that the pressure difference between the upstream and downstream of the flow control valve is smaller than the differential pressure opening pressure of the flow control valve. Alternatively, the control valve operates so that the pressure generated on the suction side of the refrigerant pressure feeding means is larger than the pressure generated by cavitation. For this reason, it is possible to prevent the occurrence of cavitation on the suction side of the differential pressure opening valve of the flow rate control valve and the refrigerant pressure sending means in the cooling system.

According to the fifth aspect of the present invention, since the valve body is rotated by the electromagnetic drive unit, it is possible to improve the reliability of the operation control of the on-off valve of the control valve.
According to the sixth aspect of the invention, the electromagnetic drive unit rotates the valve body in the forward and reverse direction by switching the energization direction, and the supply current is reduced or cut off at the terminal position, so that the power consumption can be reduced. . Further, since the valve body can be rotated by the pressure from the refrigerant or the like when the current is reduced or cut off, the valve body can be easily rotated.

  According to the seventh aspect of the present invention, the supply current of the electromagnetic drive unit is controlled at a pressure where the pressure difference between the upstream and downstream of the control valve is smaller than the differential pressure opening pressure of the flow control valve. In addition, since the supply current of the electromagnetic drive unit is controlled according to the operating conditions of the vehicle, the temperature of the refrigerant in the cooling system can be optimized.

  ADVANTAGE OF THE INVENTION According to this invention, while performing the effective use of a refrigerant | coolant or refrigerant temperature control, the control valve of the cooling system which can aim at the reliability improvement of cavitation generation | occurrence | production prevention and a refrigerant | coolant temperature adjustment function can be provided.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic diagram illustrating a configuration of a heat source and an engine cooling system as an internal combustion engine. As shown in FIG. 1, a cooling system 1 mounted on a vehicle such as an automobile includes a cooling circuit 4 that circulates a coolant as a refrigerant between an engine 2 and a radiator 3 as a cooling means. The cooling circuit 4 includes an exhaust heat system flow path 4 c as a second cooling circuit connected to the cooling circuit 4 that supplies the cooling liquid to the radiator 3 and sends out the cooling liquid that has passed through the radiator 3. The radiator 3 is a water-cooled device generally used in an internal combustion engine, and releases the heat of the coolant. In the middle of the cooling circuit 4, a water pump 5 as a refrigerant pressure feeding means is provided to circulate the coolant in the cooling circuit 4.

  The cooling circuit 4 includes a head-side channel 4 a disposed on the cylinder head 2 a side of the engine 2 and a block-side channel 4 b disposed on the cylinder block 2 b side of the engine 2. The head side flow path 4a and the block side flow path 4b branch between the discharge port of the water pump 5 and the introduction port of the cylinder head 2a and the cylinder block 2b, and the discharge ports of the cylinder head 2a and the cylinder block 2b. Merge at the downstream. Further, between the discharge port of the cylinder block 2b and the junction of the head side channel 4a and the block side channel 4b, which is the block side channel 4b, the head side channel 4a and the block side channel 4b. There is provided a control valve 10 capable of controlling the flow rate of the coolant distributed to the.

  Further, the cooling circuit 4 includes a bypass flow path 6 branched so as to bypass the radiator 3. A thermostat 7 as a flow control valve is disposed between the discharge side of the bypass flow path 6 and the exhaust heat system flow path 4c. When the coolant is lower than a predetermined temperature, the thermostat 7 closes the flow path on the radiator 3 side by the first valve 7a or reduces the flow rate of the coolant, and the bypass flow path 6 and the cooling circuit 4 on the engine 2 side Communicate. Further, the thermostat 7 closes the bypass passage 6 by the second valve 7b or reduces the flow rate of the cooling liquid when the cooling liquid is at a predetermined temperature or higher, and increases the flow rate of the cooling liquid distributed to the radiator 3. To dissipate the coolant.

  Further, the cooling circuit 4 includes a heat exchange flow path 8. The heat exchange channel 8 branches from between the discharge port of the engine 2 and the introduction port of the bypass channel 6, and joins the cooling circuit 4 between the delivery port of the thermostat 7 and the introduction port of the water pump 5. ing. The heat exchange flow path 8 includes a first heat exchange flow path 8a as a first flow path and a second heat exchange flow path 8b as a second flow path, and these first and second heat exchange flow paths 8a, In the middle of 8b, an oil-water heat exchanger 9a and a heater heat exchanger 9b are provided. The head side channel 4a, the block side channel 4b, the bypass channel 6, the first and second heat exchange channels 8a and 8b (heat exchange channel 8), and the third channel 8c are within the scope of the claims. The first cooling circuit described is configured.

  The oil-water heat exchanger 9a performs heat exchange between the coolant flowing through the first heat exchange channel 8a and the hydraulic oil for the automatic transmission. When the temperature of the automatic transmission fluid is low, the viscosity increases and the resistance of the drive system increases, so that the fuel consumption deteriorates. On the contrary, when the temperature is high, the deterioration progresses quickly. Therefore, in the oil-water heat exchanger 9a, when the hydraulic oil is hotter than the coolant, the heat of the hydraulic oil is radiated by heat exchange, and when the hydraulic oil is lower than the coolant, the heat of the coolant is discharged. The hydraulic oil absorbs heat to reduce the viscosity so that the temperature of the hydraulic oil is always adjusted to an appropriate temperature range.

  The heater heat exchanger 9b is a heat exchanger having a known configuration and is a device that uses heat released from the cooling liquid for warm air by exchanging heat between the cooling liquid and air in the passenger compartment. is there. Moreover, these 1st and 2nd heat exchange flow paths 8a and 8b merge downstream of each heat exchanger 9a and 9b, and connect to the 3rd flow path 8c.

  Next, the control valve 10 will be described with reference to FIGS. 2 and 3 are cross-sectional views in a direction orthogonal to the axial direction of the control valve 10. FIG. 4 is a cross-sectional view of the main part of the control valve 10 in the axial direction. In the present embodiment, the control valve 10 is a rotary solenoid valve, and includes a covered cylindrical first cover 11 made of synthetic resin or the like as shown in FIGS. The 1st cover 11 is provided with the upper wall part 11a and the surrounding wall part 11c, and the accommodation space 12 which comprises a channel | path is formed in the inner side.

  As shown in FIG. 2, a first port 13 and a second port 14 formed in a cylindrical shape project from the peripheral wall portion 11c. The first port 13 is formed with a first communication passage 13a that forms a passage communicating with the block-side flow path 4b. The second port 14 is formed with a second communication path 14a that constitutes a path communicating with the joining portion of the head side flow path 4a and the block side flow path 4b.

  Moreover, as shown in FIG.2 and FIG.4, the valve body 15 is pivotally supported by the accommodation space 12 so that rotation is possible. The valve body 15 includes a rotating shaft 16, and the tip portion thereof is rotatably supported by a bearing 11d that is recessed in the upper wall portion 11a shown in FIG. Thereby, the rotating shaft 16 is pivotally supported at a position deviated from the central axis of the flow path of the first cover 11, as shown in FIG. The valve body 15 includes a plate-like first valve plate 17 and a second valve plate 18 that extend from the rotary shaft 16. The first and second valve plates 17 and 18 are formed in a direction and in a straight line so as to be separated from each other with the rotating shaft 16 interposed therebetween. Further, as shown in FIG. 2, the first and second valve plates 17 and 18 are arranged such that, when the valve body 15 is positioned so that the opening area in the accommodating space 12 is minimized, the respective front ends thereof are the first cover. 11 is separated from the inner side surface by a predetermined length. Further, the width of the second valve plate 18 (the length in the direction orthogonal to the central axis of the first cover 11) is formed to be longer than the width of the first valve plate 17. Accordingly, the first and second valve plates 17 and 18 are formed asymmetrically with respect to the rotating shaft 16 (rotation center), and the pressure receiving area of the second valve plate 18 is larger than the pressure receiving area of the first valve plate 17. ing.

As shown in FIG. 4, a flat sealing portion 21 is disposed in the opening of the first cover 11. With this sealing portion 21, the accommodation space 12 of the first cover 11 is sealed. A shaft hole 21a through which the rotary shaft 16 is pivotably inserted is formed through substantially the center of the sealing portion 21. Furthermore, a latching protrusion 21 b is formed on the side surface of the sealing portion 21 opposite to the accommodation space 12. One end of the coil spring 22 is fixed to the latching protrusion 21b.

  A bottomed cylindrical second cover 23 is attached to the outside of the sealing portion 21. A bearing 23a is formed on the second cover 23 and supports the rotary shaft 16 so as to be rotatable. A fitting recess 16a is provided in the middle of the rotating shaft 16, and an engaging member 25 is fitted and fixed to the fitting recess 16a. The engagement member 25 includes a base end portion 25a fitted and fixed to the fitting recess 16a, and an engagement piece 25b erected from one location of the base end portion 25a. The other winding end of the coil spring 22 is fixed to the engagement piece 25b. When the external force is not applied to the coil spring 22 hooked on the sealing portion 21 and the engagement member 25, the valve body 15 is indicated by a two-dot chain line in FIG. The first end position is urged.

  Further, the second cover 23 is insert-molded so that the exciting coil 26 a constituting the stator portion faces the base end portion of the rotating shaft 16 protruding from the sealing portion 21. Further, a cylindrical magnet 27 constituting the rotor portion is fixed to the base end portion of the rotating shaft 16 so as to face the exciting coil 26a. In the present embodiment, the excitation coil 26a and the magnet 27 constitute a rotary solenoid 26 as an electromagnetic drive unit. When the excitation coil 26a (rotary solenoid 26) is energized, the magnet 27 (rotating shaft 16) rotates against the elastic force of the coil spring 22, and the valve body 15 is in the second terminal position shown in FIG. Placed in.

  In the second terminal position shown in FIG. 2, the communication portion C <b> 1 is provided by a gap formed between the tips of the first and second valve plates 17 and 18 and the inner surface of the first cover 11. By this communication portion C1, the first and second communication passages 13a and 14a are communicated to compensate for the flow of the minimum amount of coolant through the block-side flow path 4b.

  On the other hand, when the rotary solenoid 26 is in a non-energized state, the valve element 15 is arranged at the first terminal position indicated by a two-dot chain line in FIG. As shown in FIG. 3, the first terminal position is such that the tips of the first and second valve plates 17 and 18 do not face the peripheral wall portion 11c, and the first valve plate 17 and the second valve plate 18 are It arrange | positions so that it may become substantially parallel to the axial direction of 1st and 2nd communicating path 13a, 14a. When the first valve plate 17 and the second valve plate 18 of the valve body 15 are parallel to the axial direction of the first and second communication passages 13a and 14a as shown by a two-dot chain line in FIG. The flow rate per unit time of the two communication passages 13a and 14a is maximized. Therefore, when the valve body 15 is disposed at the first terminal position, the flow rate of the block-side flow path 4b increases.

  Further, when the valve body 15 is disposed at the second terminal position shown in FIG. 2, the pressure of the coolant received from the first communication path 13a side and the pressure of the coolant received from the second communication path 14a side The first and second valve plates 17 and 18 are configured to rotate in the clockwise direction in FIG. 2 when the pressure difference becomes equal to or greater than the pressure difference PG. That is, the first and second valve plates 17 and 18 rotate against the driving force of the rotary solenoid 26.

  More specifically, when the control valve 10 is arranged at the second terminal position, the flow rate of the block-side flow path 4b is minimum, but the first pressure of the control valve 10 is transmitted by the discharge pressure of the water pump 5 being transmitted. The communication passage 13a side has a relatively high pressure. For this reason, as shown in FIG. 2, in the valve body 15 arranged at the second terminal position, the pressure received at the inlet side 15a is greater than the pressure received at the outlet side 15b. At this time, since the pressure receiving area of the second valve plate 18 is larger than the pressure receiving area of the first valve plate 17, the balance of force about the rotating shaft 16 is broken, and the valve body 15 is rotated in the clockwise direction in FIG. To turn.

  Next, the control device C that controls the control valve 10 will be described with reference to FIG. The control device C is a device having a function of controlling at least the on-off valve of the control valve 10 and may be a device that performs other operation control of the cooling system 1 together. The control device C receives the temperature information of the coolant passing through the block-side flow path 4b from the liquid temperature sensor WS provided in the block-side flow path 4b and downstream of the discharge port of the cylinder block 2b. .

  Moreover, the control apparatus C makes the control valve 10 (rotary solenoid 26) into an energized state or a non-energized state according to the input temperature information. When the coolant passing through the block side flow path 4b becomes lower than the predetermined temperature P1, the control device C energizes the rotary solenoid 26. Further, when the coolant passing through the block-side flow path 4b reaches a predetermined temperature P1 or higher (vehicle operating conditions), the control device C stops energization of the rotary solenoid 26 (non-energized state). The predetermined temperature P1 is, for example, a lower limit value of a temperature range suitable for cooling the cylinder block 2b. Since the cylinder block 2b is required to be held at a temperature higher than that of the cylinder head 2a, the predetermined temperature P1 is higher than the valve opening temperature TH of the thermostat 7 that shuts off the radiator 3 for the purpose of warming up. (That is, the predetermined temperature P1> the valve opening temperature TH).

  Next, the operation of the cooling system 1 will be described. When the liquid temperature of the coolant passing through the thermostat 7 is equal to or higher than the valve opening temperature TH, the first valve 7a is opened and the coolant passes through the radiator 3. At this time, the water temperature of the coolant passing through the block-side flow path 4b is also usually equal to or higher than the predetermined temperature P1, so that the control valve 10 is also opened.

  When the liquid temperature on the discharge port side of the radiator 3 is lower than the valve opening temperature TH, the first valve 7a of the thermostat 7 is disposed at the valve closing position, and the second valve 7b is opened. For this reason, the coolant flows through the bypass flow path 6 and circulates so as to bypass the radiator 3.

  At this time, when the controller C detects that the liquid temperature on the discharge port side of the cylinder block 2b is equal to or lower than the predetermined temperature P1, the rotary solenoid 26 of the control valve 10 is energized. When the rotary solenoid 26 is energized and the valve body 15 is disposed at the second end position, the flow rate of the block side flow path 4b becomes the minimum flow rate, and the liquid temperature of the coolant flowing through the block side flow path 4b rises.

  Thus, when not only the flow path on the radiator 3 side but also the block side flow path 4b is almost closed, the water flow resistance of the entire cooling circuit 4 increases. For this reason, the flow rate passing through the cooling circuit 4 is reduced, and a high-pressure portion or a low-pressure portion is locally generated. Specifically, when the discharge port of the water pump 5 is upstream, the pressure on the suction port side (suction side) of the water pump 5 that is the most downstream is reduced. Further, the outlet side of the thermostat 7 connected to the suction port of the water pump 5 is also in a low pressure state. On the other hand, the head-side channel 4a has a relatively high pressure. For this reason, the exhaust heat system flow path 4c communicated with the head side flow path 4a is transmitted with a relatively high pressure. Therefore, in the thermostat 7, the inlet port provided on the radiator 3 side becomes high pressure, and the outlet side becomes low pressure, so that the differential pressure generated upstream and downstream of the thermostat 7 increases. At this time, if the differential pressure between the inlet side and the outlet side of the thermostat 7 exceeds a predetermined pressure, the first valve 7a opens due to the differential pressure. Further, when the pressure on the suction port side of the water pump 5 becomes a predetermined pressure or less, cavitation tends to occur.

On the other hand, in the control valve 10, the pressure on the discharge port side of the water pump 5 is transmitted, and the first communication passage 13a side is in a high pressure state. When the differential pressure on both sides of the valve body 15 becomes equal to or greater than the pressure difference PG, the valve body 15 at the second terminal position moves to the first terminal position against the driving force of the rotary solenoid 26. Here, the pressure difference PG, which is the rotational pressure condition, is set to a pressure difference that can prevent the occurrence of differential pressure opening and cavitation. In other words, the differential pressure applied to the control valve 10 before and after the occurrence of differential pressure opening and cavitation is obtained in advance through experiments or the like, and the pressure difference before the occurrence of differential pressure opening and cavitation is It is set as the pressure difference PG at which the body 15 opens.

  If the valve body 15 is arrange | positioned in a 1st termination | terminus position, the water flow resistance of the whole cooling circuit 4 will become small. Then, the pressure deviation of the entire cooling circuit 4 is eliminated, and the pressure on the suction port side of the water pump 5 rises within an appropriate range. For this reason, the excessive differential pressure in the upstream and downstream of the thermostat 7 and the pressure drop near the suction port of the water pump 5 are eliminated, and the occurrence of the differential pressure opening valve and cavitation is prevented.

According to the first embodiment, the following effects can be obtained.
(1) In 1st Embodiment, the control valve 10 which controls the flow volume of the block side flow path 4b was equipped with the valve body 15 pivotally supported by the 1st cover 11 grade | etc.,. The valve body 15 includes first and second valve plates 17 and 18 having different pressure receiving areas. Then, when the valve body 15 at the second terminal position becomes more than the pressure difference PG on the first communication path 13a side and the second communication path 14a side, the valve body 15 is in an unbalanced state and automatically rotates toward the valve opening position. It was made to move.

  Further, the pressure receiving area ratio (pressure difference PG) of the first and second valve plates 17 and 18 is set so that the valve body 15 moves to the first terminal position before the differential pressure opening of the thermostat 7 is generated. Further, the pressure receiving area ratio (pressure difference PG) of the first and second valve plates 17 and 18 was set so that the pressure generated on the suction side of the water pump 5 was larger than the pressure generated by cavitation. For this reason, the control valve 10 can be opened before the differential pressure opening and cavitation are generated, and the water flow resistance of the entire cooling circuit 4 can be reduced. For this reason, it is possible to prevent the temperature adjustment function from being lowered by the differential pressure opening valve, noise generated by cavitation, and damage to the cooling pipe and the water pump 5.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. In addition, since 2nd Embodiment is a structure which only changed the control valve 10 of 1st Embodiment, about the same part, the code | symbol is made the same and the detailed description is abbreviate | omitted.

  As shown in FIG. 5, the control valve 30 of the present embodiment is provided at a connection portion between the first heat exchange channel 8a, the second heat exchange channel 8b, and the third channel 8c, and each heat exchanger. It is used as a valve device for controlling the distribution flow rate of the coolant for 9a and 9b.

  As shown in FIG. 6, the control valve 30 includes a first cover 31, and an accommodation space 31 a that forms a passage is formed in the first cover 31. The first cover 31 is formed with first and second ports 32 and 33 and a pump side port 34. The first port 32 is formed with a first communication path 32a that constitutes a path communicating with the first heat exchange flow path 8a. The second port 33 is formed with a second communication passage 33a that constitutes a passage communicating with the second heat exchange flow path 8b. The pump-side port 34 is formed with a pump-side communication passage 34a that constitutes a passage communicating with the water pump 5 side.

  A valve body 35 is pivotally supported on the first cover 31 and the sealing portion 21 so as to be rotatable within a predetermined angle range. The valve body 35 has the same configuration as that of the valve body 15 of the first embodiment, and the first and second valve plates 37 and 38 serving as rotating parts are connected to the inner surface of the first cover 31 and the communication part. It is configured to rotate in a state separated by C2.

Further, the drive mechanism of the control valve 30 has a configuration in which the coil spring 22 and the engagement member 25 of the control valve 10 of the first embodiment are omitted, and a rotary solenoid 26 (excitation coil 26a) as an electromagnetic drive unit is directly connected. When energized in the direction, it is arranged at the first terminal position indicated by a two-dot chain line in FIG. When the valve body 35 is disposed at the first terminal position, the opening area of the first communication path 32a is maximized, and the water flow resistance of the first heat exchange channel 8a is minimized. The discharge port of the second communication path 33a is closed by the valve body 35, but the second communication path 33a and the pump side communication path 34a are communicated with each other through the communication portion C2. Therefore, although the water flow resistance of the second heat exchange channel 8b is increased, a small amount of coolant flows. For this reason, the flow rate of the coolant to the oil-water heat exchanger 9a is maximized, and the flow rate to the heater heat exchanger 9b is minimized.

  Further, the rotary solenoid 26 is in a state where the supply current is cut off when the valve body 35 is disposed at the first terminal position. The valve body 35 is restricted from rotating counterclockwise in FIG. 6 by the frictional force between the rotating shaft 36, the first cover 31, and the sealing portion 21 and the pressure from the coolant.

  When the rotary solenoid 26 is energized in the reverse direction, the valve element 35 rotates to the second end position shown by the solid line in FIG. When the valve body 35 is disposed at the second terminal position, the opening area of the second communication passage 33a is maximized, and the flow rate of the second heat exchange channel 8b is maximized. The first communication path 32a communicates with the pump-side communication path 34a via the communication part C2, and a necessary minimum flow rate is ensured in the first heat exchange flow path 8a. Further, the rotary solenoid 26 is in a non-energized state when the valve body 35 is disposed at the second terminal position.

  As described above, when the flow path on the side of the radiator 3 is closed and the water flow resistance of the entire cooling circuit 4 is increased, the valve body 35 has the differential pressure generated on both sides thereof, the first and second When the resultant force with the pressure difference applied to the valve plates 37 and 38 becomes the pressure difference PG, it is arranged near the intermediate position shown in FIG. That is, since the first and second valve plates 37 and 38 are formed so as to have different widths, the coolant that is going to pass through the communication portion C2 applies the tips of the first and second valve plates 37 and 38 to each other. When the pressure is applied, the rotational moment generated in the second valve plate 38 becomes larger. Further, since the pressure receiving areas of the first and second valve plates 37 and 38 are different from each other, when the differential pressure on both sides of the valve body 35 increases, the equilibrium state is lost, and the second valve plate 38 has a high pressure. It turns from the side toward the low pressure side. For example, as shown by the solid line in FIG. 6, when the valve body 35 is disposed at the second terminal position, the first communication path 32 a side with a small flow rate becomes high pressure, and the differential pressure on both sides of the valve body 35 becomes excessive. Become. Since the second valve plate 38 has a larger pressure receiving area than the first valve plate 37, the pressure received by the second valve plate 38 is larger, and the clockwise direction from the first communication path 32a side to the second communication path 33a side. To turn. As shown in FIG. 8, the valve body 35 is disposed at an intermediate position where the tip of the second valve plate 38 does not face the inner surface of the first cover 31 and the pressure is balanced.

  The pressure difference PG which is the rotational pressure condition of the valve body 35 is a pressure difference that prevents the differential pressure opening valve of the thermostat 7 and the cavitation of the water pump 5 from occurring. That is, the control valve 30 communicates with the suction port of the water pump 5 via the pump side communication passage 34a, and the introduction port side communicates with the flow path on the radiator 3 side. It can be calculated by experiments or the like based on the valve opening pressure condition and the cavitation pressure condition.

  When the valve body 35 is disposed at the intermediate position, the water flow resistances of the first heat exchange flow path 8a and the second heat exchange flow path 8b are both minimized, and the water flow resistance of the entire cooling circuit 4 is reduced. Then, the flow rate of the heat exchange channel 8 increases, and the low pressure state on the suction port side of the water pump 5 is eliminated. For this reason, the differential pressure generated upstream and downstream of the thermostat 7 is reduced, and cavitation occurring on the suction port side of the water pump 5 is prevented.

According to the second embodiment, the following effects can be obtained.
(2) In the second embodiment, the control valve 30 that controls the flow rate to each of the heat exchangers 9a and 9b includes the valve body 35 that is rotatably supported by the first cover 31 and the like. The valve body 35 is provided with first and second valve plates 37 and 38 having different pressure receiving areas. And when the difference of the pressure which the valve body 35 in the 1st and 2nd terminal position receives from the 1st communicating path 32a side and the 2nd communicating path 33a side becomes more than the pressure difference PG, it will be in an unbalanced state. Therefore, it turned to the middle position by itself.

  Further, the pressure receiving area ratio (pressure difference PG) of the first and second valve plates 37 and 38 is set so that the valve body 35 moves to the intermediate position before the differential pressure opening of the thermostat 7 is generated. Further, the pressure receiving area ratio (pressure difference PG) of the first and second valve plates 37 and 38 was set so that the pressure generated on the suction side of the water pump 5 was larger than the pressure generated by cavitation. For this reason, the control valve 30 can be opened before the differential pressure opening and cavitation are generated, and the water flow resistance of the entire cooling circuit 4 can be reduced. For this reason, it is possible to prevent the temperature adjustment function from being lowered due to the differential pressure opening valve, noise due to cavitation, and damage to the cooling pipe and the water pump 5.

In addition, you may change each said embodiment as follows.
-In 1st Embodiment, the valve body 15 provided in the control valve 10 may slide on the inner surface of the 1st cover 11, and you may make it the structure which does not provide the communication part C1.

  The cooling system 1 may be configured as shown in FIG. The cooling system 40 shown in FIG. 8 includes first and second heat exchange channels 40a and 40b, and the first heat exchange channel 40a has an inlet side on the outlet side of the water pump 5 and an inlet port of the engine 2. Is branched from a communication path 41 that communicates with each other. The second heat exchange channel 40 b is branched directly from the cooling circuit 4 that sends out the coolant from the engine 2 toward the radiator 3 on the inlet side. The first and second heat exchange channels 40a and 40b join together downstream of the heat exchangers 9a and 9b to form a third channel 40c. The control valve 10 is provided in the middle of the first heat exchange channel 40a and upstream of the oil-water heat exchanger 9a. And the control valve 10 reduces or closes the flow volume of the 1st heat exchange flow path 40a. Furthermore, the control valve 10 is configured to open by itself at a pressure before the differential pressure opening and cavitation occur.

  The control valve 10 may be disposed at any position in the cooling circuit 4 as long as it can control the amount of coolant supplied to the cylinder block 2b. Further, the control valve 10 may be disposed for the purpose other than controlling the amount of coolant supplied to the cylinder block 2b, and bypasses the engine 2 and the flow path in the water jacket disposed in the engine 2. It may be provided in the middle of the bypass channel.

  -In 1st Embodiment, you may make it a structure like the control valve 50 shown in FIG. The control valve 50 includes an accommodation space 12 in the first cover 11 having the same configuration as that of the first embodiment, and pivotally supports the valve body 54 so as to be rotatable by a predetermined angle. The communication portions C3 and C4 as gaps provided between the first cover 11 and the first valve plate 55 and the second valve plate 56 are formed so that the second valve plate 56 is shorter than the first valve plate 55. As a result, the gap areas are different. Alternatively, the opening area may be different by providing a part of the first cover 11 with an unillustrated enlarged portion and forming the first and second valve plates 55 and 56 to have the same length. For this reason, the flow rate that passes through the communication portion C4 having a large gap area is larger than the flow rate that passes through the communication portion C3 having a small gap area. Accordingly, the second valve plate 56 receives a greater pressure from the coolant than the first valve plate 55. When the difference in rotational force applied to the first and second valve plates 55 and 56 is less than a predetermined value, the valve body 54 has a driving force of the rotary solenoid 26 and a frictional force between the valve body 54 and the first cover 11 and the like. Does not rotate due to etc. When the difference in rotational force becomes equal to or greater than a predetermined value, the pressure received by the second valve plate 56 exceeds the driving force of the rotary solenoid 26 and the like, and is arranged at the end position indicated by a two-dot chain line in FIG.

The control valve may be configured as a control valve 60 shown in FIG. The control valve 60 includes a first cover 61, and the first cover 61 includes a housing space 61 a (passage) and a first communication passage 62 a (passage) communicating with the block-side flow path 4 b. And the head side flow path 4
The 2nd port 63 provided with the 2nd communicating path 63a (passage) connected to the confluence | merging part of a and the block side flow path 4b is protrudingly formed. The first cover 61 is formed with a bearing 65 that pivotally supports the valve body 64. The valve body 64 includes a rotating shaft 66 and a valve plate 67 extending from the rotating shaft 66. The valve plate 67 rotates around the rotation shaft 66 between a first end position indicated by a solid line in FIG. 10 and a second end position indicated by a two-dot chain line. The valve body 64 disposed at the first terminal position is located between the first communication path 62a side communicating with the first heat exchange flow path 8a and the second communication path 63a side communicating with the second heat exchange flow path 8b. When the pressure difference PG becomes the pressure difference PG, it is rotated to the second terminal position.

  In the second embodiment, the control valve 30 may be configured like the control valve 70 shown in FIG. The control valve 70 includes an accommodation space 71a (passage) in the first cover 71, and pivotally supports the valve body 75 so as to be rotatable by a predetermined angle. The first cover 71 includes a first port 72 having a first communication path 72a (passage) communicated with the first heat exchange flow path 8a, and a second communication path 73a (communication with the second heat exchange flow path 8b). A second port 73 provided with a passage) and a pump side port 74 provided with a pump side communication passage 74a (passage) communicated with the water pump 5 side. The first cover 71 and the valve body 75 are formed so that the gap areas of the communication portions C5 and C6 as gaps provided between the first cover 71 and the first valve plate 76 and the second valve plate 77 are different. Has been.

  For this reason, the flow rate that has passed through the communication portion C6 is greater than the flow rate that passes through the communication portion C5, and the pressure that the second valve plate 77 receives from the coolant is greater than that of the first valve plate 76. When the difference in rotational force applied to the first valve plate 76 and the second valve plate 77 is less than a predetermined value, it is rotated by the driving force of the rotary solenoid 26 or the frictional force between the valve body 75 and the first cover 71 and the like. do not do. When the difference in rotational force applied to the first valve plate 76 and the second valve plate 77 is greater than or equal to a predetermined value, the second valve plate 77 rotates from the high pressure side toward the low pressure side, and is shown by a solid line in FIG. It is arranged at an intermediate position between the second end position and the first end position indicated by a two-dot chain line in FIG.

  The control valve may be configured as a control valve 80 shown in FIG. The control valve 80 includes a first cover 81, and the first cover 81 includes a housing space 81a (passage) and a first communication passage 82a (passage) communicated with the first heat exchange flow path 8a. A second port 83 having a second communication passage 83a (passage) communicating with the port 82 and the second heat exchange flow path 8b is provided. Further, the first cover 81 is provided with a pump-side port 84 having a pump-side communication passage 84a (passage) communicated with the water pump 5 side. The first cover 81 is formed with a bearing 86 that pivotally supports the valve body 85. The valve body 85 includes a rotating shaft 87 and a valve plate 88 extending from the rotating shaft 87. The valve plate 88 rotates around the rotation shaft 87 between a second terminal position indicated by a solid line in FIG. 12 and a first terminal position indicated by a two-dot chain line. The valve body 85 has a pressure difference PG between the first communication path 82a communicating with the first heat exchange channel 8a and the second communication path 83a communicating with the second heat exchange channel 8b. Then, it turns to the low pressure side.

-In 1st Embodiment, the coil spring 22 may be abbreviate | omitted from the control valve 10, and the valve body 15 may be arrange | positioned only by control of the rotary solenoid 26 in a 1st and 2nd terminal position.
In the first embodiment, the control valve 10 is energized or de-energized based on the temperature information input from the liquid temperature sensor WS. However, the rotational speed of the engine 2 is greater than or equal to a predetermined value (vehicle operating conditions). In some cases, the power may be turned off.

  -In 2nd Embodiment, when the valve body 35 was arrange | positioned in the 1st and 2nd terminal position, electricity supply was stopped, However, You may make it reduce supply current. Further, the valve body 35 may be biased to either the first or second terminal position by a biasing spring. Further, the engine 2 may be de-energized when the rotational speed of the engine 2 is equal to or greater than a predetermined value (vehicle operating condition).

  -In each said embodiment, the oil-water heat exchanger 9a may adjust the temperature of other oils, such as engine oil. Moreover, the heat exchanger 9b for heaters may be used for apparatuses other than an air conditioner.

  In the above embodiments, the cooling system 1 may be a device that cools other heat sources or driving devices. For example, the cooling system 1 may be a system that is mounted on a vehicle using a battery (fuel cell) and cools a heat source such as the battery.

The schematic diagram of the cooling system of 1st Embodiment of this invention. Sectional drawing of the control valve of the cooling system. Sectional drawing of the control valve. Sectional drawing of the principal part of the control valve. The schematic diagram of the cooling system of 2nd Embodiment of this invention. Sectional drawing of the control valve of the cooling system. Sectional drawing of the control valve. The schematic diagram of the cooling system of another example of this invention. Sectional drawing of the control valve of another example of this invention. Sectional drawing of the control valve of another example of this invention. Sectional drawing of the control valve of another example of this invention. Sectional drawing of the control valve of another example of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1,40 ... Cooling system, 2 ... Engine as heat source, 3 ... Radiator as cooling means, 4 ... Cooling circuit, 4a ... Head side flow path constituting first cooling circuit, 4b ... Constructing first cooling circuit Block side flow path, 4c: Waste heat system flow path as second cooling circuit, 5 ... Water pump as refrigerant pressure feeding means, 6: Bypass flow path constituting first cooling circuit, 7 ... Thermostat as flow control valve , 8... Heat exchange flow path constituting the first cooling circuit, 8a, 40a... First heat exchange flow path constituting the first cooling circuit and the first flow path, 8b, 40b. Second heat exchange flow path constituting the path, 8c, 40c ... Third flow path constituting the first cooling circuit 10, 30, 50, 60, 70, 80 ... Control valve, 12, 31a, 61a, 71a, 81a ... Accommodating space constituting the passage, 13a, 2a, 62a, 72a, 82a ... first communication passage constituting the passage, 14a, 33a, 63a, 73a, 83a ... second communication passage constituting the passage, 15, 35, 54, 64, 75, 85 ... valve body 16, 36, 66, 87... Rotating shaft, 26... Rotary solenoid as an electromagnetic drive unit, 34 a, 74 a, 84 a.

Claims (7)

A first cooling circuit connected to the heat source and circulating the refrigerant;
A second cooling circuit connected to the first cooling circuit and having cooling means for radiating the refrigerant;
A flow rate control valve provided between the first cooling circuit and the second cooling circuit for controlling the flow rate of the refrigerant from the first cooling circuit to the second cooling circuit;
Refrigerant pumping means for pumping the refrigerant to both cooling circuits;
A cooling system having a control valve for controlling a flow rate of the refrigerant in the first cooling circuit,
The control valve includes a valve body that is rotatably supported in a passage in the first cooling circuit, and the valve body is formed asymmetrically with respect to a rotation center. Control valve. A first cooling circuit connected to the heat source and circulating the refrigerant;
A second cooling circuit connected to the first cooling circuit and having cooling means for radiating the refrigerant;
A flow rate control valve provided between the first cooling circuit and the second cooling circuit for controlling the flow rate of the refrigerant from the first cooling circuit to the second cooling circuit;
Refrigerant pumping means for pumping the refrigerant to both cooling circuits;
A cooling system having a control valve for controlling a flow rate of the refrigerant in the first cooling circuit,
The control valve has a valve body that is rotatably supported in a passage of the first cooling circuit, and a gap is provided between each end of the valve body and the passage, A control valve characterized in that the gap areas of each other are different from each other.   The passage of the first cooling circuit is configured by a connection portion to which a first flow path and a second flow path into which the refrigerant flows and a third flow path from which the refrigerant flows out are connected. The control valve according to claim 1, wherein the flow rate of the refrigerant flowing from the first flow path and the second flow path to the third flow path is controlled.   The control valve is configured so that the pressure difference between the upstream and downstream of the flow control valve is smaller than the differential valve opening pressure of the flow control valve, or the pressure generated on the suction side of the refrigerant pumping means is cavitation. The control valve according to any one of claims 1 to 3, wherein the control valve operates so as to be larger than a generated pressure.   The control valve according to claim 1, wherein the valve body is rotated by an electromagnetic drive unit.   The said electromagnetic drive part rotates the said valve body to a forward / reverse direction by switching of an electricity supply direction, and supply current is reduced or interrupted | blocked in each terminal position. Control valve.   The electromagnetic drive unit controls the supply current when the pressure difference between the upstream and downstream of the flow control valve is smaller than the differential valve opening pressure of the flow control valve, and supplies the current according to the operating condition of the vehicle. The control valve according to claim 5 or 6, wherein the current is controlled.

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