JP2010121455A - Thermally-actuated valve gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide, in a cooling system of an internal combustion engine provided with a plurality of heat exchangers, a thermally-actuated valve gear improving warm-up performance of the internal combustion engine while being compact and light and having simple, inexpensive construction, and also appropriately controlling circulation of cooling water to each of the heat exchangers as required. <P>SOLUTION: The thermally-actuated valve gear is driven by a common thermally-actuated element thermally actuated in accordance with a surrounding fluid temperature and includes a plurality of valve bodies which: controls in accordance with the surrounding fluid temperature a degree of communication between a predetermined region and each of a plurality of fluid paths; are provided in correspondence with the plurality of fluid paths; and includes the main valve element controlling a degree of communication between a radiator and the predetermined region. One of the plurality of valve elements other than the main valve element includes a delay mechanism of delaying start of the control of the degree of communication by the main valve element after start of the control of the degree of communication between the predetermined region and the corresponding fluid path. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a thermally responsive valve device. For example, the present invention relates to a thermally responsive valve device applicable to a circulating system of cooling water that is a refrigerant of a combustion device such as an internal combustion engine equipped with a cooling system.

  As this type of cooling system, for example, Patent Document 1 includes a plurality of heat exchangers such as a radiator, an ATF (Automatic Transmission Fluid) cooler, an oil cooler, an intercooler, and an EGR (Exhaust Gas Recirculation) cooler. In a cooling system for an internal combustion engine or the like, a configuration is described in which the circulation path of the cooling water is switched so that the cooling water is circulated in order from the heat exchanger having the highest warm-up priority.

  This is configured to circulate the cooling water in order from the heat exchanger having the highest warm-up priority by switching the circulation path of the cooling water using a plurality of thermostats S1 to S3.

Further, as shown in FIGS. 54 and 55, the piston 56 having the introduction side communication hole 56a is moved in the axial direction by utilizing the expansion / contraction of the thermo wax 57a, and the introduction side according to the movement. A heat circulation path switching device 5 that switches the circulation path that communicates with the communication hole 56a is configured to be configured so that the cooling water is circulated in order from the heat exchanger having the highest warm-up priority. ing.
JP 2007-198206 A

  However, the one described in Patent Document 1 requires a plurality of thermostats, and there is a concern that the configuration becomes complicated, the system becomes larger and the weight increases, and the cost and mounting layout are disadvantageous. is there.

  54 and 55 employs a so-called slide valve that moves the piston 56 having the introduction-side communication hole 56a opened in the axial direction, and the axial line changes according to the movement. Since the communication state of the circulation path arranged side by side is switched, the thermal circulation path switching device 5 becomes longer in the axial direction, the system becomes larger and the weight increases, and in terms of cost and mounting layout, etc. There is a fear that it will be disadvantageous.

  Furthermore, when using a so-called slide valve for a circulation path switching device of such a cooling system, consideration must be given to problems such as sealing performance, performance degradation due to contamination with foreign matter, and sticking, but there is no such consideration. There is a problem that it is difficult to adopt practically.

  In addition, in the cooling system, it is required that the circulation path switching device has a relief function to suppress damage to the heat exchanger or disconnection of the connecting hose due to excessive pressure. Providing such a relief function to the slide valve has a problem that it is difficult to employ practically because the configuration is complicated.

  Further, each system described in Patent Document 1 requires check valves 12 and 13 due to the configuration of the system. Therefore, the system becomes complicated and large in size and increases in weight, and in terms of cost and mounting layout. There is a fear that it will be disadvantageous.

  Furthermore, since each system described in Patent Document 1 focuses on warm-up performance, the heat recovered by the heat exchanger is not dissipated in the engine at high load, high water temperature, etc. There is a concern that the heat load of the engine will increase.

  The present invention has been made in view of such circumstances, and in a cooling system for an internal combustion engine having a plurality of heat exchangers, the warm-up performance of the internal combustion engine is improved while being a small, light, simple and inexpensive configuration. It is another object of the present invention to provide a thermally responsive valve device capable of appropriately controlling the flow of cooling water to each heat exchanger as required. Moreover, it aims at providing the cooling system provided with the said heat responsive valve apparatus.

For this reason, the thermally responsive valve device according to the present invention is:
Corresponding to the plurality of fluid passages that are driven by a common thermal responsive element that is thermally responsive to the surrounding fluid temperature and controls the degree of communication between the predetermined region and each of the plurality of fluid passages according to the surrounding fluid temperature A plurality of valve bodies, one of which is a thermally responsive valve device including a plurality of valve bodies including a main valve body that controls the degree of communication between the radiator and the predetermined region,
After any one of the plurality of valve bodies other than the main valve body starts controlling the degree of communication between the predetermined region and the corresponding fluid passage, the control of the degree of communication of the main valve body is started. A delay mechanism for delaying the process is provided.

  In the thermally responsive valve device according to the present invention, the start of control of the degree of communication between the predetermined region and the corresponding fluid passage is set for each of the plurality of valve bodies according to the required fluid temperature. Can be characterized.

  In the thermally responsive valve device according to the present invention, the delay mechanism delays based on a delay amount until the thermal responsive operation of the common thermal responsive element is transmitted to the main valve body. it can.

  In the thermally responsive valve device according to the present invention, the delay mechanism is based on a movement amount until the main valve body moves and the main valve body is opened according to a thermal responsive operation of the common thermal responsive element. It can be characterized by being delayed.

  In the thermally responsive valve device according to the present invention, a fluid passage that is independent from the plurality of fluid passages and a valve body that opens and closes the fluid passage are provided, and the valve body is driven by the common thermally responsive element. Can be characterized.

  According to the present invention, in the cooling system for an internal combustion engine including a plurality of heat exchangers, the warm-up performance of the internal combustion engine is improved while the configuration is small, lightweight, simple and inexpensive, and An object of the present invention is to provide a thermally responsive valve device capable of appropriately controlling the flow of cooling water as required. Moreover, it aims at providing the cooling system provided with the said heat responsive valve apparatus.

Embodiments of a thermally responsive valve device according to the present invention will be described below in detail with reference to the accompanying drawings. The present invention is not limited to the examples described below.
The fluid to be controlled by the thermally responsive valve device according to the embodiment described below is not limited to a coolant such as cooling water, and is applicable to both incompressible fluid and compressible fluid. It is possible to apply to gas as well as liquid such as tap water and pure water.

  A thermostat (thermally responsive valve device) 100 according to the first embodiment of the present invention is installed in, for example, an automobile or a stationary engine 1 as shown in FIG. 1 (gasoline, light oil, alcohol, etc.). In addition to heat engines such as internal combustion engines and external combustion engines that use various miscellaneous fuels as fuel, the present invention also applies to cooling systems such as a cooling circuit for a combustion device that does not extract power and a cell cooling circuit for a fuel cell. Applicable).

  As shown in FIG. 1, a mechanically driven water pump 2 driven by a crankshaft or the like is connected to an inlet side of a cooling passage (not shown) inside the engine 1. A thermostat 100 is disposed on the outlet side of the cooling passage, and a radiator passage that is connected to the water pump 2 with a radiator 3 that is a heat exchanger for radiating the cooling water of the engine 1 interposed in the thermostat 100. 200 is connected, and a heater core passage 300 connected to the water pump 2 through which the heater core 4 as a heat exchanger for the heater system is interposed is connected.

  The thermostat 100 is connected to a bypass passage 400 that bypasses the radiator 3 and is connected to the water pump 2, and an EGR cooler 5 that is a heat exchanger for cooling EGR gas is interposed between the thermostat 100 and the water pump 2. An EGR cooler passage 500 connected to the oil pump, and an oil cooler passage 600 connected to the water pump 2 through which an oil cooler 6 serving as a heat exchanger for cooling engine oil, transmission oil or the like is connected.

  Here, for example, as shown in FIG. 5, the thermostat 100 according to the present embodiment is configured to include a housing portion 101 that houses the temperature sensing portion 181 side of the thermoelement 180 (thermally responsive element). Further, a support portion 102 that supports the piston rod 181a of the thermo element 180 and a radiator side connection portion 120 to which the radiator passage 200 is connected are provided.

  The housing portion 101 includes an engine side connection portion 110 connected to the outlet side of the water pump 2 (that is, the outlet side of the cooling passage inside the engine 1), and a heater core passage connection portion connected to the heater core passage 300. 130, an EGR cooler passage connection portion 150 connected to the EGR cooler passage 500, and an oil cooler passage connection portion 160 connected to the oil cooler passage 600 are provided.

  A housing portion 104 that houses a lower portion of the rod 183 that is an extension portion of the temperature sensing portion 181 is disposed below the housing portion 101 in FIG. 5, and the bypass passage is provided in the housing portion 104. A bypass passage connecting portion 140 connected to 400 is provided.

  Here, the thermo element 180 includes a temperature sensing unit 181 that encloses a thermal expansion body such as wax that expands and contracts by sensing the temperature of the cooling water in the housing unit 101, and the temperature sensing unit 181 receives the temperature from the temperature sensing unit 181. A piston rod 181a that expands and contracts along the vertical direction in FIG. 5 in accordance with the thermal expansion and contraction of the thermal expansion body inside the sensing unit 181 protrudes.

  One end (upper end in FIG. 5) of the piston rod 181a is supported by the support 102, and the other end is accommodated in the temperature sensing unit 181.

  A spring seat 182 is attached to the temperature sensing portion 181 substantially integrally with the temperature sensing portion 181 on the piston rod 181 a side. The spring seat 182 is connected to the radiator side connecting portion 120 side and the housing portion 101. It is configured to have a valve shape that can function as a valve that communicates or blocks the inside. The spring seat 182 corresponds to the main valve body according to the present invention.

  A spring support portion 103 that is substantially integral with the housing portion 101 (the support portion 102) is provided on the housing portion 101 so as to face the spring seat 182. The spring support portion 103, the spring seat 182, A coil spring 185 that biases the spring seat 182 toward the valve closing side (upward in FIG. 5) is disposed between them. A passage 141 is provided in the central portion of the spring support portion 103, and a rod 183 that is an extension portion of the temperature sensing portion 181 is inserted into the passage 141.

  Thus, in this embodiment, the rod 183 extends to the lower end of the temperature sensing unit 181 on the lower side in FIG. 5, and this rod 183 has the largest diameter rod 183A at the top. The rod 183B having an intermediate diameter at the middle portion thereof and the rod 183C having the smallest diameter at the lowermost portion thereof are configured.

  A spring seat 184C is attached to the lower end of the rod 183C. The spring seat 184C is slidably inserted into the rod 183C, and the downward movement is regulated through a position regulating member 189 such as a snap ring disposed at the lower end of the rod 183C. The position restricting member 189 is biased by a spring 187.

  The spring seat 184C is configured to have a valve shape capable of functioning as a valve that communicates or blocks the bypass passage connecting portion 140 and the interior of the housing portions 101 and 104.

  The coil spring 187 is disposed between the spring seat 184C and a spring seat 184B configured to be able to abut against a step portion between the rod 183B and the rod 183C. Accordingly, the spring seat 184C is urged against the position regulating member 189 on the lower end side of the rod 183, while the spring seat 184B is urged in the valve closing direction.

  In addition, a coil spring 186 is disposed between the spring seat 184B and a spring seat 184A configured to be able to abut on a step portion between the rod 183A and the rod 183B. Thus, the spring seat 184A is biased in the direction of the step between the rod 183A and the rod 183B. In the state of FIG. 5, it is in a state where it is seated and closed at the opening of the oil cooler passage connecting portion 160 provided around the passage 141 before it hits the stepped portion.

  An opening for allowing the corresponding rod 183B to be slidably inserted is provided at the center of the spring seat 184A, and an opening for circulating cooling water is provided around the opening. The outer peripheral side is configured to function as a valve body for closing the oil cooler passage connecting portion 160.

  In addition, an opening for allowing the corresponding rod 183C to be slidably inserted is provided at the center of the spring seat 184B, and an opening for circulating cooling water is provided around the opening. The outer peripheral side is configured to function as a valve body for closing the EGR cooler passage connecting portion 150.

  The spring 188 is disposed between the housing portion 104 and the spring seat 184B. By pushing the spring seat 184B upward in FIG. 5, the spring seat 184B is opened to the opening portion of the EGR cooler passage connecting portion 150. It is energized so as to be seated and closed.

The operation of the thermostat 100 according to this embodiment having the above-described configuration will be described below.
The interior of the housing portion 101 corresponds to a predetermined region according to the present invention, and the radiator passage 200, the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, the oil cooler passage 600, and the like are included in the present invention. The spring seats 182 and 184A to 184C that correspond to an example of the fluid passage and function as valve bodies correspond to a plurality of valve bodies according to the present invention.

(Default (initial: bypass circulation) state: Fig. 1 and Fig. 5)
1 and 5 show a state in which the cooling water temperature is low and the temperature sensing unit 181 is in the initial position. In such an initial state, as shown in FIG. 5, spring seats (valve bodies) 182 and 184A are shown. , 184B is closed, and the spring seat (valve element) 184C is opened.

Therefore, the cooling water fed by the water pump 2 is guided into the housing 101 of the thermostat 100 from the engine side connecting portion 110 connected to the outlet side of the cooling passage inside the engine 1, and as shown in FIG. It flows through the thermostat 100 and is returned to the water pump 2 through the heater core passage 300 and the bypass passage 400 as shown in FIG.
Thereby, the amount of heat taken away from the cooling water to the outside is reduced, and warming up of the engine 1 is promoted.

(First valve open state: FIG. 2 (solid arrow), FIG. 6)
1 and 5, when the coolant temperature rises to a predetermined level by receiving heat from the engine 1, the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 is thermally expanded to extend the piston rod 181a. As shown in FIG. 6, the spring seat 182 is moved downward in FIG. 6 against the urging force of the coil spring 185.

  However, in this first valve open state, even if the spring seat 182 moves downward in FIG. 6, as shown in FIG. 11, the radiator side connecting portion 120 extends to the radiator passage 200 and the housing portion 101. The communication with the inside of the door is configured to be kept in a blocked state. Thereby, it can contribute to warming-up promotion of the engine 1.

That is, as shown in FIGS. 10 to 14, the spring seat 182 moves downward in each figure as the thermal expansion body in the temperature sensing portion 181 of the thermo element 180 thermally expands and the piston rod 181a extends. Until the amount of movement exceeds a predetermined valve opening temperature adjustment allowance A (corresponding to the delay amount according to the present invention) (corresponding to the state shown in FIGS. 13 and 14). In other words, the state where the communication between the radiator passage 200 and the inside of the housing part 101 is blocked is maintained. For example, a lip-shaped rubber (rubber) portion disposed on the spring seat 182 is in contact with the inner wall of the housing portion 101 in the circumferential direction to maintain a sealed state.
Here, even if the thermo-responsive operation of the thermo element 180 is started, the radiator side connecting portion 120 and the radiator passage 200 are extended by a predetermined valve opening temperature adjustment allowance A (corresponding to the delay amount according to the present invention). A configuration that maintains a state where communication between the housing portion 101 and the interior of the housing portion 101 is blocked corresponds to the delay mechanism according to the present invention.

  On the other hand, as shown in FIG. 6, the rod 183 integrated with the temperature sensing unit 181 is also moved downward in FIG. 6, and the spring seat 184B is pushed downward in FIG. 6 by the rod 183B. Open.

  The spring seat 184A is opened in contact with the rod 183A. However, due to the existence of the valve opening temperature adjustment allowance X shown in FIGS. 5 and 15, the spring seat 184A has a predetermined value from the valve opening temperature of the spring seat 184B. Therefore, even if the rod 183 (rod 183A) moves downward in FIG. 6, the spring seat 184A does not open, and the oil cooler side connecting portion 160 extends. In other words, the communication between the oil cooler passage 600 and the interior of the housing portion 101 is configured to be maintained in a blocked state.

  Incidentally, the valve opening amount of the spring seat 184C (distance from the upper end face (valve seat) in FIG. 6 of the bypass passage connecting portion 140) is reduced by the amount of movement of the rod 183 downward in FIG.

  As a result, as shown in FIG. 6, the cooling water fed by the water pump 2 flows into the EGR cooler passage connecting portion 150 and then into the EGR cooler passage 500, and is indicated by a solid line arrow in FIG. As shown, the water is returned to the water pump 2 through the heater core passage 300, the bypass passage 400, and the EGR cooler passage 500.

  Therefore, cooling of the EGR gas is performed by the EGR cooler 5 interposed in the EGR passage 500, or when the EGR gas temperature is low, the temperature is raised to improve combustion at a low temperature, and further to a certain degree By supplying the cooling water, it becomes possible to prevent moisture condensation in the EGR gas.

(Second valve open state: FIG. 2 (solid arrow + broken arrow), FIG. 7)
2 (solid arrow) and FIG. 6, when the cooling water temperature further rises due to the heat of the engine 1, the thermal expansion body in the temperature sensing portion 181 of the thermo element 180 further thermally expands, causing the piston rod 181 a to move. In order to extend, the spring seat 182 is moved downward in FIG. 7 against the urging force of the coil spring 185 as shown in FIG.

  However, even in the second valve open state, even if the spring seat 182 moves downward in FIG. 7 as described above, as shown in FIG. 12, the radiator side connecting portion 120 extends to the radiator passage. The communication between the housing 200 and the interior of the housing portion 101 is maintained in a blocked state.

  On the other hand, as shown in FIG. 7, the rod 183 integrated with the temperature sensing unit 181 is also moved downward in FIG. 7. The seat 184A is pushed downward by the rod 183A in FIG. 7 and opened.

  The spring seat 184B is maintained in an open state, and the valve opening amount (distance from the lower end surface (valve seat) in FIG. 7 of the EGR cooler passage connecting portion 150) of the rod 183 moves downward in FIG. It is increased by the amount.

  Further, the valve opening amount of the spring seat 184C (the distance from the upper end surface (valve seat) in FIG. 7 of the bypass passage connecting portion 140) is reduced by the amount of movement of the rod 183 downward in FIG.

  As a result, as shown in FIG. 7, the cooling water fed by the water pump 2 flows into the oil cooler passage connecting portion 160 and also into the oil cooler passage 600, and the solid arrow in FIG. As indicated by the broken line arrows, the water is returned to the water pump 2 through the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600.

  For this reason, the oil cooler 6 interposed in the oil cooler passage 600 is used, for example, when the temperature of engine oil, transmission oil, or the like is low, the temperature is raised quickly to realize low friction, or the engine oil And transmission oil can be cooled.

(Third valve open state: FIGS. 3 and 8)
2 (solid arrow + broken line arrow) and the state of FIG. 7, when the coolant temperature further rises due to the heat of the engine 1, the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 further expands, and the piston In order to extend the rod 181a, as shown in FIG. 8, the spring seat 182 is moved downward in FIG. 8 against the urging force of the coil spring 185 to open the valve, as shown in FIG. Thus, the radiator side connecting portion 120 and the radiator passage 200 and the inside of the housing portion 101 are in communication with each other.

  The spring seats 184A and 184B are maintained in an open state, and the valve opening amount is increased by the amount that the rod 183 has moved downward in FIG.

  Further, the valve opening amount of the spring seat 184C (distance from the upper end surface (valve seat) in FIG. 8 of the bypass passage connecting portion 140) is reduced by the amount of movement of the rod 183 downward in FIG.

  As a result, as shown in FIG. 8, the cooling water fed by the water pump 2 flows into the radiator side connecting portion 120 and also into the radiator passage 200, and as shown in FIG. The water is returned to the water pump 2 through the radiator passage 200, the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600.

  For this reason, the cooling water of the engine 1 can be cooled by the radiator 3 interposed in the radiator passage 200.

(Temperature control state: FIGS. 3 and 8)
When the spring seat 182 is opened in the third valve open state, the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 is thermally expanded or contracted in accordance with the temperature change of the cooling water, and the piston rod. By extending or contracting 181a, the degree of communication between the radiator-side connecting portion 120 and the radiator passage 200 and the inside of the housing portion 101 (that is, the valve opening amount of the spring seat 182) is adjusted. Accordingly, the amount of heat released from the cooling water by the radiator 3 is controlled, so that the temperature of the cooling water can be controlled to a predetermined temperature.

  Further, since the valve opening amounts of the spring seats 184A and 184B are controlled in accordance with the movement of the rod 183 interlocking with the expansion or contraction of the piston rod 181a, the amount of cooling water flowing into the EGR cooler passage 500 and the oil cooler passage 600 is controlled. Therefore, the temperature state of EGR gas by the EGR cooler 5 and the temperature state of engine oil, transmission oil, etc. by the oil cooler 6 can be suitably maintained as required.

(Bypass valve closed state: FIGS. 4 and 9)
When the temperature of the cooling water further rises from the above temperature control state, the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 further expands and the piston rod 181a is extended, as shown in FIG. While the valve seats of the spring seats 182 (see FIG. 14), 184A, 184B are maintained, the spring seat 184C attached to the rod 183C moves downward in FIG. As a result, a closed state is established in which communication between the bypass passage 400 and the inside of the housing portion 101 is blocked.

  That is, it functions to gradually reduce the cooling water flowing into the bypass passage 400 as the spring seat 184C approaches the valve closing, and to increase the cooling water flowing into the radiator passage 200. As shown in FIG. 4, the cooling water fed by the water pump 2 is blocked from flowing into the bypass passage side connecting portion 140 and the bypass passage 400, so that the radiator passage 200, the heater core passage 300, The water is returned to the water pump 2 through the EGR cooler passage 500 and the oil cooler passage 600.

  For this reason, since the flow rate of the cooling water passing through the radiator 3 interposed in the radiator passage 200 can be increased, it is possible to effectively suppress the cooling water of the engine 1 from becoming higher than a predetermined temperature. Is possible.

  The second embodiment is an example in which the thermostat 100 is disposed on the suction side of the water pump 2 (the inlet side of the cooling passage inside the engine 1) as shown in FIGS. Is shown.

Since the operation of the thermostat 100 is the same as that of the first embodiment, detailed description thereof is omitted here. However, in the second embodiment, in contrast to the first embodiment, the spring 188 is disposed between the housing portion 104 and the spring seat 184B, and the spring seat 184B is pushed upward in FIG. The rod 183B that contacts the spring seat 184B and then the rod 183 (that is, the temperature sensing unit 181) is pushed upward in FIG. 5 to urge the temperature sensing unit 181 to return to the initial position (original position). It will function as a spring.
The spring 188 urges the spring seat 184B to be seated on the opening of the EGR cooler passage connecting portion 150 and closed together with such a return function.

  In addition, as shown in FIGS. 16 to 19, the flow of the cooling water in the thermostat 100 can be considered the same as FIGS. 5 to 9 described in the first embodiment when the direction is taken into consideration. Detailed description here is omitted.

  That is, even when the thermostat 100 is disposed on the suction side of the water pump 2 (the inlet side of the cooling passage inside the engine 1) as in the present embodiment, the same operational effects as in the first embodiment can be obtained. It can be done.

  In the second embodiment, the same thermostat 100 as in the first embodiment can be used. However, in both the first and second embodiments, a thermostat 1200 as shown in FIGS. 20 to 24 can be used.

  That is, the spring seat 182 is not integrally attached to the temperature sensing unit 181 of the thermo-element 180, but, for example, between the spring seat 182 and the temperature sensing unit 180, as shown in FIGS. In addition, an elastic body (such as an O-ring) that is slidable while maintaining a sealed state is disposed, and the spring seat 182 is slidably attached to the temperature sensing unit 181 of the thermo element 180. In addition, the same code | symbol is attached | subjected to the element similar to what was shown in FIGS. 5-9, and description is abbreviate | omitted.

Then, when the coolant temperature rises due to the heat of the engine 1, the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 thermally expands to expand the piston rod 181a. 21 to 24. In FIG. 21 (first valve opening state) and FIG. 22 (second valve opening state), the spring seat 182 has the valve opening temperature adjustment allowance Y shown in FIG. (Equivalent to the delay amount according to the present invention), even if the piston rod 181a extends according to the cooling water temperature, the spring seat 182 does not move downward, and the radiator-side connecting portion 120 extends to the radiator. The communication between the passage 200 and the inside of the housing part 101 is configured to be kept in a blocked state. Thereby, it contributes to warm-up promotion of the engine 1.
Here, such a configuration corresponds to the delay mechanism according to the present invention.

  Further, in FIG. 23 (third valve opening state) and FIG. 24 (bypass valve closing state), the piston rod 181a extends to a predetermined value or more according to the cooling water temperature, and the valve opening temperature adjustment allowance Y disappears. The seat 182 is opened, and the radiator-side connecting portion 120 and the radiator passage 200 are communicated with the interior of the housing portion 101 by a valve opening amount corresponding to the cooling water temperature.

  Therefore, the thermostat 1200 having such a configuration can achieve the same operational effects as the thermostat 100 described with reference to FIGS.

  In the third embodiment of the present invention, as shown in FIG. 25, a branch passage 210 that is branched after passing through the radiator passage 200 is provided with respect to FIG. 1 described in the first embodiment. The passage is branched into a passage 510 connected to the upstream side of the cooling water flow of the EGR cooler 5 and a passage 610 connected to the upstream side of the cooling water flow of the oil cooler 6.

Further, the arrangement of the spring seat 184C in the present embodiment is different from that in the first embodiment as shown in FIG. That is, the spring seat 184C is disposed on the upstream side of the passage 141 (upper part of the rod 183 in FIG. 29), and is configured to function as a valve body that opens and closes the passage 141.
In the third embodiment, the same elements as those described in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  The operation of the thermostat 1300 according to this embodiment having the above-described configuration will be described below.

(Default (initial) state: FIGS. 25 and 29)
25 and 29 show a state in which the cooling water temperature is low and the temperature sensing unit 181 is in the initial position. In this initial state, as shown in FIG. 29, the spring seats 182, 184A, 184B are shown. Is closed, and the spring seat 184C is opened.

Accordingly, as in the first embodiment, the cooling water flows through the thermostat 100 as shown in FIG. 29 and returns to the water pump 2 through the heater core passage 300 and the bypass passage 400 as shown in FIG. Will be.
Thereby, the amount of heat taken away from the cooling water to the outside is reduced, and warming up of the engine 1 is promoted.

(First valve open state: FIG. 26 (solid arrow), FIG. 30)
25 and 29, when the cooling water temperature rises to a predetermined level due to the heat of the engine 1, the spring seats 182 and 184A are closed as shown in FIG. 184B and 184C are opened.

  Therefore, as in the first embodiment, the cooling water flows through the thermostat 100 as shown in FIG. 30, and the cooling water fed by the water pump 2 extends from the EGR cooler passage connecting portion 150 to the EGR cooler passage. As shown by the solid arrows in FIG. 26, the air is returned to the water pump 2 through the heater core passage 300, the bypass passage 400, and the EGR cooler passage 500.

  Thereby, the EGR gas is cooled by the EGR cooler 5 interposed in the EGR passage 500, or when the EGR gas temperature is low, the temperature is raised to improve the combustion at a low temperature, and further, the temperature is raised to some extent. By supplying the cooling water, it becomes possible to prevent condensation of moisture in the EGR gas.

(Second valve open state: FIG. 26 (solid arrow + broken arrow), FIG. 31)
When the coolant temperature rises to a predetermined level by receiving heat from the engine 1 from the state of FIG. 26 (solid arrow) and FIG. 30, the spring seat 182 is closed as shown in FIG. The spring seats 184A, 184B, 184C are opened.

  Accordingly, as in the first embodiment, the cooling water fed by the water pump 2 flows into the oil cooler passage connecting portion 160 and then into the oil cooler passage 600, and is indicated by solid arrows and broken line arrows in FIG. As shown, the water is returned to the water pump 2 through the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600.

  For this reason, as in the first embodiment, when the oil cooler 6 interposed in the oil cooler passage 600 is used to cool engine oil, transmission oil, or the like, or when the temperature of the engine oil, transmission oil, or the like is low, It is possible to reduce the friction by raising the temperature early.

(Third valve open state: FIGS. 27 and 32)
When the cooling water temperature further rises due to the heat of the engine 1 from the state of FIG. 26 (solid arrow + broken arrow) and FIG. 31, the spring seat 182 is shown in FIG. The valve is moved in the middle and downward to open, and the radiator-side connecting portion 120 and the radiator passage 200 and the interior of the housing portion 101 are in communication with each other.

  Further, the spring seats 184A and 184B are maintained in an open state, and the valve opening amount is increased by the amount that the rod 183 has moved downward in FIG.

  On the other hand, the valve opening amount of the spring seat 184C (the distance from the upper end surface (valve seat) in FIG. 31 of the passage 141) is reduced by the amount that the rod 183 has moved downward in FIG.

  Thus, as shown in FIG. 32, the cooling water fed by the water pump 2 flows into the radiator side connecting portion 120 and also into the radiator passage 200. As shown in FIG. The water is returned to the water pump 2 through the radiator passage 200, the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600.

  Further, in the present embodiment, as shown in FIG. 32, the cooling water that has passed through the radiator 3 flows into the branch passage 210 and is connected to the EGR cooler 5 and the passage connected to the oil cooler 6. A cooling water path that is returned to the water pump 2 after passing through the EGR cooler 5 and the oil cooler 6, respectively, is also formed.

For this reason, the cooling water of the engine 1 can be cooled by the radiator 3 interposed in the radiator passage 200.
Furthermore, according to the present embodiment, the cooling water cooled by passing through the radiator 3 can be circulated to the EGR cooler 5 and the oil cooler 6, so that the EGR gas and the oil to be cooled can be more effectively used. It can be cooled.

(Temperature control state: FIGS. 27 and 32)
Similar to the first embodiment, when the spring seat 182 is opened in the third valve open state, the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 is heated according to the temperature change of the cooling water. When the piston rod 181a is expanded or contracted by expansion or contraction, the degree of communication between the radiator side connection portion 120 and the radiator passage 200 and the inside of the housing portion 101 (that is, the opening of the spring seat 182). The amount of heat released from the cooling water by the radiator 3 is controlled, so that the temperature of the cooling water can be controlled to a predetermined temperature.

  Further, as in the first embodiment, the valve opening amounts of the spring seats 184A and 184B are controlled in accordance with the movement of the rod 183 that is interlocked with the expansion or contraction of the piston rod 181a, so that the EGR cooler passage 500, the oil cooler Since the amount of cooling water flowing into the passage 600 is controlled, the temperature state of the EGR gas by the EGR cooler 5 and the temperature state of the oil to be cooled by the oil cooler 6 can be suitably maintained as required. Become.

(Bypass valve closed state: FIGS. 28 and 33)
When the temperature of the cooling water further rises from the above temperature control state and the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 further expands and the piston rod 181a is extended, as shown in FIG. While the valve seats of the spring seats 182, 184A, and 184B are maintained, the spring seat 184C moves downward in FIG. 33 and the valve 141 is closed.

  That is, as the spring seat 184C approaches the valve closing, the radiator 141 is gradually reduced while gradually reducing the cooling water flowing into the passage 141 and the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600. It functions to increase the cooling water flowing into the passage 200. After the valve is closed, as shown in FIG. 33, the cooling water fed by the water pump 2 is the bypass passage 400, the EGR cooler passage 500, Inflow to the oil cooler passage 600 is cut off and returned to the water pump 2 through the radiator passage 200 and the heater core passage 300.

  For this reason, since the flow rate of the cooling water passing through the radiator 3 interposed in the radiator passage 200 can be increased, it is possible to effectively suppress the cooling water of the engine 1 from becoming higher than a predetermined temperature. It becomes possible.

  Further, in the closed state of the bypass valve, the relatively high-temperature cooling water that does not pass through the radiator 3 is stopped from flowing directly into the EGR cooler 5 or the oil cooler 6 and is cooled through the radiator 3. Since the cooling water can flow into the EGR cooler 5 and the oil cooler 6, the EGR gas and the oil to be cooled can be more effectively cooled.

  It should be noted that the relationship between the above states and the "flow rate of cooling water from the radiator 3" and the "flow rate of cooling water from the thermostat 1300" passing through the EGR cooler 5 with respect to the cooling water temperature in a predetermined region in the present embodiment. This is shown in FIG.

  FIG. 36 shows the relationship between each of the above states and the “flow rate of cooling water from the radiator 3” and “flow rate of cooling water from the thermostat 1300” passing through the oil cooler 6 with respect to the cooling water temperature. .

  The fourth embodiment is an example in which the thermostat 1300 is disposed on the suction side of the water pump 2 (the inlet side of the cooling passage inside the engine 1) as shown in FIGS. Is shown.

  Since the operation of the thermostat 300 is the same as that of the third embodiment, detailed description thereof is omitted here.

  In addition, as shown in FIGS. 37 to 40, the flow of the cooling water in the thermostat 300 can be considered to be the same as that of the third embodiment when the direction is taken into consideration, and thus detailed description thereof is omitted here. To do.

  By the way, in the case where the thermostat 300 is disposed on the suction side of the water pump 2 (inlet side of the cooling passage inside the engine 1) as in this example, Example 3 (example of engine outlet side mounting) is In contrast to “supplying cooling water cooled by passing through the radiator 3 to the heat exchanger”, “cooling water heated by the heat exchanger is cooled by the radiator 3”. There is an advantage that the heat returned to the engine 1 through the radiator 3 can be radiated by the radiator 3.

  In addition, the relationship between the above states with respect to the cooling water temperature in the present embodiment, “the flow rate of cooling water to the radiator 3” and “the flow rate of cooling water to the thermostat 1300” passing through the EGR cooler 5 is It is shown simultaneously in FIG.

  Further, the relationship between the above-described states with respect to the cooling water temperature, and the “flow rate of cooling water to the radiator 3” and the “flow rate of cooling water to the thermostat 1300” passing through the oil cooler 6 are shown in the third embodiment. It is shown simultaneously in FIG.

  In the fifth embodiment of the present invention, as shown in FIG. 41 with respect to FIG. 37 of the fourth embodiment, a thermostat 1400 is provided, and the heat storage tank 7 and the electric water pump 8 are interposed in the thermostat 1400. The stored heat storage tank passage 700 is connected. The other end side of the heat storage tank passage 700 joins the bypass passage 400 and is connected to the outlet side of the cooling passage inside the engine 1.

  In the present embodiment, the cooling water that has become hot during operation of the engine 1 is transferred to and stored in a so-called thermos-like heat storage tank 7 during operation (or immediately after stopping), while the electric pump before the next engine start. 8 is driven to supply the engine 1 with the relatively high-temperature cooling water stored in the heat storage tank 7 to warm it (preheat), improving the startability and the combustion characteristics after the start, and warming up the engine 1 1 shows an example in which a thermostat according to the present invention is applied to a heat storage system in which the time to completion can be shortened and the emission of unburned substances can be reduced.

In particular,
In the present embodiment, during preheating, the electric water pump 8 is driven before starting the engine to supply the engine 1 with relatively high-temperature cooling water stored in the heat storage tank 7 to warm up the engine. However, in the preheat mode, when the electric water pump 8 is driven before cranking by the starter when the engine 1 is cold started, the cooling water pressure on the discharge side of the electric water pump 8 is increased. Then, the cooling water tends to flow into the housing portion 101 of the thermostat 1400 from the engine side connection portion 110 of the thermostat 1400 shown in FIG.

  At this time, the heat storage tank passage 700 between the heat storage tank passage connection 750 and the electric water pump 8 is on the suction side of the electric water pump 8, and the cooling water pressure in this portion is reduced. Then, the pressing force generated by the cooling water pressure in the housing part 101 exceeds the sum of the pressing force generated by the cooling water pressure on the heat storage tank passage 700 side and the urging force of the coil spring 153, and the check valve 751 is In FIG. 42, the valve is moved to the right and the valve is opened (the notch 752 is opened), and the passage of the cooling water from the housing part 101 side to the heat storage tank passage 700 side is allowed.

Therefore, the relatively high-temperature cooling water in the heat storage tank 7 discharged by the electric water pump 8 pushes the cooling water cooled while the engine 1 is stopped to the heat storage tank 7 side, and the engine 1 inside the engine 1 is not shown. The cooling passage (including the water jacket and the like) is filled with the relatively high-temperature cooling water stored in the heat storage tank 7, so that the engine 1 is warmed up before the engine is started (preheating). .
Thereby, the startability at the time of the cold start of the engine 1 and the combustion characteristics after the start are improved, and in particular, it becomes possible to effectively reduce the discharge amount of unburned substances.
After the engine is started, the thermostat 1400 operates as follows.

(Default (initial) state: Fig. 42)
FIG. 42 shows a state where the cooling water temperature is low and the temperature sensing unit 181 is in the initial position. In this initial state, as shown in FIG. 42, the spring seats 182, 184A, 184B are closed. Thus, the spring seat 184C is opened. Note that the check valve 751 is closed.

Accordingly, the cooling water is returned to the water pump 2 through the heater core passage 300 and the bypass passage 400 as in the third and fourth embodiments.
Thereby, the amount of heat taken away from the cooling water to the outside is reduced, and warming up of the engine 1 is promoted.

(First valve open state: FIG. 43)
When the coolant temperature rises to a predetermined level in response to the heat of the engine 1 from the state of FIG. 42, the spring seats 182 and 184A are closed as shown in FIG. The seats 184B and 184C are opened. Note that the check valve 751 is closed.

Therefore, the cooling water fed by the water pump 2 is returned to the water pump 2 through the heater core passage 300, the bypass passage 400, and the EGR cooler passage 500, as in the third and fourth embodiments. Become.
Thereby, the EGR gas is cooled by the EGR cooler 5 interposed in the EGR passage 500, or when the EGR gas temperature is low, the temperature is raised to improve the combustion at a low temperature, and further, the temperature is raised to some extent. By supplying the cooling water, it becomes possible to prevent condensation of moisture in the EGR gas.

(Second valve open state: FIG. 44)
43, when the coolant temperature rises to a predetermined level due to the heat of the engine 1, the spring seat 182 is closed and the spring seats 184A, 184B are closed as shown in FIG. 44, as in the third and fourth embodiments. , 184C is open. Note that the check valve 751 is closed.

  Accordingly, as in the third and fourth embodiments, the cooling water fed by the water pump 2 is supplied to the water pump via the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600. Will be returned to 2.

  Therefore, as in the third and fourth embodiments, the oil cooler 6 interposed in the oil cooler passage 600 allows the temperature of the engine oil, transmission oil, and the like to be raised quickly to reduce friction when the temperature of the engine oil or transmission oil is low. Or cooling of engine oil, transmission oil, or the like can be realized.

(Third valve open state: FIG. 45)
When the cooling water temperature is further increased by receiving the heat of the engine 1 from the state of FIG. 44, the spring seat 182 is opened as shown in FIG. 45, as in the third and fourth embodiments. The valve seats 184A and 184B are maintained in an open state, and the valve opening amount is increased by the amount that the rod 183 moves downward in FIG.

  Further, the valve opening amount of the spring seat 184C (distance from the upper end surface (valve seat) in FIG. 45 of the passage 141) is reduced by the amount of movement of the rod 183 downward in FIG.

  As a result, as in the third and fourth embodiments, the cooling water fed by the water pump 2 is supplied from the radiator passage 200, the heater core passage 300, the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage. It is returned to the water pump 2 via 600.

  In the present embodiment, a cooling water path that is returned to the water pump 2 through the passage 510 and the passage 610 is also formed.

  Further, in the present embodiment, as shown in FIG. 45, the check valve 751 follows the shape of the guide member 710 that is substantially integrally attached to the temperature sensing portion 181 (for example, the spring seat 182) of the thermo element 180. However, it is moved to the right in FIG. 45 against the coil spring 753 and opened.

  Thus, when the check valve 751 is opened, the cooling water flows into the housing portion 101 through the notch 752 of the check valve 651, the heat storage tank passage connection portion 750, and the heat storage tank passage 700. become. Therefore, in the heat storage tank 7 interposed in the heat storage tank passage 700, the low-temperature cooling water previously stored can be replaced and stored by the relatively high-temperature cooling water newly flowing in. . The timing of opening the check valve 751 can be arbitrarily set regardless of the third valve opening state (opening of the spring seat 182).

(Temperature control state: Fig. 45)
As in the third and fourth embodiments, when the spring seat 182 is opened in the third valve open state, the heat in the temperature sensing unit 181 of the thermo element 180 is changed according to the temperature change of the cooling water. When the expansion body is thermally expanded or contracted and the piston rod 181a is expanded or contracted, the degree of communication between the radiator-side connecting portion 120 and the radiator passage 200 and the inside of the housing portion 101 (that is, the spring) Therefore, the amount of heat released from the cooling water by the radiator 3 is controlled, so that the temperature of the cooling water can be controlled to a predetermined temperature.

  Further, as in the third and fourth embodiments, the valve opening amounts of the spring seats 184A and 184B are controlled in accordance with the movement of the rod 183 that is interlocked with the expansion or contraction of the piston rod 181a. Since the amount of cooling water flowing into the oil cooler passage 600 is controlled, the temperature state of the EGR gas by the EGR cooler 5 and the temperature state of the oil to be cooled by the oil cooler 6 are suitably maintained as required. It becomes possible.

  In addition, since the check valve 751 is also opened, introduction into the high-temperature cooling water into the heat storage tank 7 is continued, and the high-temperature cooling water is sent to the heat storage tank 7 so that it is as hot as possible for the next start-up. It is possible to store the cooling water in the heat storage tank 7.

(Bypass valve closed state: Fig. 46)
When the temperature of the cooling water further rises from the above temperature control state and the thermal expansion body in the temperature sensing portion 181 of the thermo element 180 further expands and the piston rod 181a is extended, as shown in FIG. While the spring seats 182, 184 A, 184 B and the check valve 751 are kept open, the spring seat 184 C moves downward in FIG. 46 so that the passage 141 is shut off.

  Thereby, like Example 3 and Example 4, the cooling water fed by the water pump 2 is blocked from flowing into the bypass passage 400, the EGR cooler passage 500, and the oil cooler passage 600, and The water is returned to the water pump 2 through the radiator passage 200 and the heater core passage 300.

  For this reason, since the flow rate of the cooling water passing through the radiator 3 interposed in the radiator passage 200 can be increased, it is possible to effectively suppress the cooling water of the engine 1 from becoming higher than a predetermined temperature. It becomes possible.

  In addition, the relatively high-temperature cooling water that does not pass through the radiator 3 is stopped from flowing directly into the EGR cooler 5 and the oil cooler 6, and the cooling water that has been cooled through the radiator 3 is passed through the EGR cooler 5 and Since the oil can be circulated to the oil cooler 6, the EGR gas and the oil to be cooled can be cooled more effectively.

  Further, in this embodiment, since the check valve 751 is opened, the introduction to the high-temperature cooling water into the heat storage tank 7 is continued, and the high-temperature cooling water is sent to the heat storage tank 7 to start next time. It is possible to store cooling water as hot as possible in the heat storage tank 7 in preparation for the occasion.

  By the way, when the thermostat 1300 is arranged on the suction side of the water pump 2 (the inlet side of the cooling passage inside the engine 1) as in this embodiment, the thermostat is connected to the outlet of the engine 1 as in the third embodiment. The cooling water heated by the heat exchanger is cooled by the radiator 3 as opposed to “supplying the cooling water cooled by passing through the radiator 3 to the heat exchanger” when arranged on the side. Therefore, there is an advantage that the heat returned to the engine 1 through the heat exchanger can be radiated by the radiator 3.

A sixth embodiment will be described with reference to FIGS. 47 and 48 to 51.
As shown by a broken line in FIG. 47, the thermostat 1500 according to the present embodiment is provided with an engine cooler 6 that cools engine oil circulated by an oil pump 9 that supplies engine oil to the engine 1. A passage 900 is connected.
In addition, about the element similar to another Example, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

  As shown in FIG. 48, in the thermostat 1500 according to the present embodiment, the spring seats 184A and 184B provided in the other embodiments are omitted, and a spring seat 184D is newly provided.

  The spring seat 184D is substantially integrally attached to the lower end of the rod 183, and a cylindrical portion 184D1 that is slidably inserted into the inner wall of the passage 141 with a predetermined sealing property, and FIG. 48 of the cylindrical portion 184D1. And a disc-shaped spring seat portion 184D2 that is connected to the middle and lower end portions and is slidably inserted into the large-diameter passage 143 with a predetermined sealing property. For example, a lip-shaped rubber (rubber) portion disposed on the outer periphery of the spring seat 184D1 contacts the inner wall of the passage 141 in the circumferential direction and slides while maintaining a sealed state. . Further, for example, a lip-shaped rubber (rubber) portion disposed on the outer periphery of the spring seat 184D2 comes into contact with the inner wall of the passage 143 in the circumferential direction and slides while maintaining a sealed state. ing.

  In addition, an opening through which cooling water flows is provided on the upper end surface in FIG. 48 of the cylindrical portion 184D1 of the spring seat 184D.

  The spring seat 184D having such a configuration is a valve for opening and closing the engine oil passage 900 through which engine oil or the like disposed in the housing portion 101 of the thermostat 1500 flows while suppressing mixing with the cooling water in the housing portion 101. 48, as shown in FIG. 48, the spring seat portion 184D2 and the valve seat portion 901 come into contact with each other, so that the right and left engine oil passages 900 in FIG. 184D2 and the valve seat portion 901 are separated from each other, whereby the right and left engine oil passages 900 in FIG. 48 are communicated with each other.

And the thermostat 1500 which has this structure operate | moves as follows.
(Default (initial) state: Fig. 48)
FIG. 48 shows a state in which the cooling water temperature is low and the temperature sensing unit 181 is in the initial position. In this initial state, as shown in FIG. 48, the spring seats 182 and 184D are closed, The spring seat 184C is in the opened state.

  Therefore, the cooling water is returned to the water pump 2 through the heater core passage 300 and the bypass passage 400. Further, the engine oil passage 900 is closed, and the flow of engine oil to the oil cooler 6 is stopped.

  For this reason, the amount of heat removed from the coolant and engine oil to the outside via the radiator 3 and the oil cooler 6 is reduced, and warming up of the engine 1 is promoted.

(First valve open state: FIG. 49)
When the coolant temperature rises to a predetermined level in response to the heat of the engine 1 from the state of FIG. 48, the spring seat 182 is closed and the spring seats 184D and 184C are opened as shown in FIG. ing.

  Therefore, the cooling water fed by the water pump 2 is returned to the water pump 2 through the heater core passage 300 and the bypass passage 400, and the engine oil flows through the engine oil passage 900.

  As a result, the engine oil can be cooled by the oil cooler 6 interposed in the engine oil passage 900.

(Second valve open state and temperature control state: FIG. 50)
From FIG. 49, when the coolant temperature rises to a predetermined level by receiving heat from the engine 1, the spring seat 182 is opened and the spring seat 184D is further opened as shown in FIG. The spring seat 184C is also opened, and the valve opening amount is reduced compared to the first valve opening state.

  Therefore, the cooling water fed by the water pump 2 is returned to the water pump 2 through the radiator passage 200, the heater core passage 300, and the bypass passage 400, and the engine oil flows through the engine oil passage 900. Become.

  As a result, the radiator 3 interposed in the radiator passage 200 can cool the cooling water of the engine 1 and the oil cooler 6 interposed in the engine oil passage 900 can reduce the engine oil. Cooling can be performed.

(Bypass valve closed state: Fig. 51)
When the temperature of the cooling water further rises from the state of FIG. 50 and the thermal expansion body in the temperature sensing unit 181 of the thermo element 180 further expands and the piston rod 181a is extended, as shown in FIG. While maintaining the open state of the spring seats 182 and 184D, the spring seat 184C moves downward in FIG. 51, and the valve 141 is closed.

  As a result, the coolant supplied by the water pump 2 is blocked from flowing into the bypass passage 400 and returned to the water pump 2 through the radiator passage 200 and the heater core passage 300.

  Therefore, the flow rate of cooling water passing through the radiator 3 interposed in the radiator passage 200 is increased while the engine oil is efficiently cooled by the oil cooler 6 interposed in the engine oil passage 900. Therefore, it is possible to suppress the cooling water of the engine 1 from becoming a temperature higher than a predetermined temperature.

  Example 7 shows an example in which a thermostat 1500 is disposed on the suction side of the water pump 2 (inlet side of the cooling passage inside the engine 1) as shown in FIG. Yes.

  Since the operation of the thermostat 1500 is the same as that of the sixth embodiment, detailed description thereof is omitted here.

  In addition, the flow of the cooling water in the thermostat 1500 can be considered to be the same as that of the sixth embodiment when the direction is taken into consideration, and thus detailed description thereof is omitted here.

  That is, even when the thermostat 1500 is disposed on the suction side of the water pump 2 (the inlet side of the cooling passage inside the engine 1) as in the present embodiment, the same operational effects as in the sixth embodiment can be obtained. It can be done.

  As described above, according to the thermostat according to each of the above embodiments, in the cooling system for an internal combustion engine including a plurality of heat exchangers, the warm-up performance of the internal combustion engine is small, light, simple, and inexpensive. In addition, it is possible to appropriately control the flow of the cooling water to each heat exchanger as required.

  By the way, in each of the above-described embodiments, a thin plate-shaped spring seat is configured to have a function as a valve body, and in the case of providing sealing performance around the valve body, sealing performance is provided by a rubber-like lip portion or the like. Therefore, the outer periphery of the slide valve (piston) that is long in the moving direction is used, as in the configuration in which the flow path is switched using the conventional slide valve that is long in the moving direction as described in Patent Document 1. Compared to those that need to have a sealing property by reducing the clearance between the cylinder that houses the slide valve and the sealing valve, it has a simple and inexpensive configuration and facilitates quality control, but also performance due to sealing problems and contamination There is an advantage that problems such as lowering and sticking can be made difficult to occur.

  Further, in each of the above-described embodiments, the thin plate-like spring seat has a function as a valve body and is configured to be urged to close by an elastic spring, so that the differential pressure across the valve body becomes a predetermined value or more. Sometimes, it is possible to provide a pressure relief function by setting the urging force so that the valve body is opened, thereby causing damage to the heat exchanger due to excessive pressure, disconnection of the connecting hose, Is capable of suppressing the occurrence of so-called cavitation and the like, and has a relief function with a simple and inexpensive configuration as compared with the one using a so-called slide valve as described in Patent Document 1, thereby providing a highly reliable apparatus. It is possible to achieve sexualization.

  In each of the above-described embodiments, the EGR cooler passage 500 and the oil cooler passage 600 can be replaced with each other, and another passage (for example, a torque converter or torque converter oil is cooled as required). For example, a passage of cooling water supplied to the heat exchanger for cooling, a passage of cooling water supplied to the intercooler for cooling the supply air, and the like.

  In each embodiment, the case where the heater core 4 and the heater core passage 400 are connected has been described. However, the heater system can be controlled by an independent control system, and thus the heater core 4 and the heater core passage 400 are not connected. The present invention is applicable also to cases.

  Further, in each of the above-described embodiments, the temperature sensing unit 181 that encloses a thermal expansion body such as wax of the thermo element 180 that is a thermally responsive element senses the temperature of the cooling water in the housing unit 101 (predetermined region). However, the present invention is not limited to this, and a thermal expansion body such as wax of the thermo element 180 is enclosed so that the desired temperature of the cooling water to be controlled can be sensed. The temperature sensing unit 181 may be configured to be disposed at a site different from the inside of the housing unit 101 (predetermined region).

  In addition, this invention is not limited to the structure demonstrated by each Example mentioned above, The shape of each part which comprises the thermostat (thermally responsive valve) apparatus 100, 600-900, a structure, etc. can be changed suitably and can be changed. Needless to say.

  In addition, the actuator of the thermally responsive valve is not limited to a thermo element enclosing a thermal expansion body such as wax that senses and expands and contracts by detecting the temperature described in each of the above-described embodiments, but may be a temperature such as a bimetal or a shape memory alloy. A member using a member that deforms accordingly can also be used.

  Moreover, each thermostat which concerns on each Example mentioned above may be arrange | positioned in the engine cooling water circuit at the entrance side of the engine 1, or may be arrange | positioned at the exit side.

  Furthermore, the thermostat (thermally responsive valve) device according to the present invention is not limited to the case where it is applied to a cooling system for an internal combustion engine, but is used for cooling a fuel cell vehicle such as a vehicle, equipment, or the like that requires refrigerant distribution. It can also be applied to devices, other cooling devices that require warm-up, and liquid lines.

  The embodiment described above is merely an example for explaining the present invention, and various modifications can be made without departing from the gist of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram which shows roughly an example of the cooling system system (bypass circulation state) (thermostat engine exit side arrangement | positioning) which concerns on Example 1 of this invention. It is a figure which shows the flow of the cooling water of the cooling system in the 1st valve opening state and 2nd valve opening state of the thermostat of Example 1. FIG. It is a figure which shows the flow of the cooling water of the cooling system in the 3rd valve opening state of the thermostat of Example 1. FIG. It is a figure which shows the flow of the cooling water of the cooling system in the bypass valve closed state of the thermostat of Example 1. FIG. It is sectional drawing explaining the operation state in the default (bypass circulation) state of the thermostat of Example 1. FIG. It is sectional drawing explaining the operation state in the 1st valve opening state of the thermostat of Example 1. FIG. It is sectional drawing explaining the operation state in the 2nd valve opening state of the thermostat of Example 1. FIG. It is sectional drawing explaining the operation state in the 3rd valve opening state of the thermostat of Example 1. FIG. It is sectional drawing explaining the operation state in the bypass valve closed state of the thermostat of Example 1. FIG. FIG. 3 is a partial enlarged cross-sectional view showing a state of the main valve (spring seat 182) in the default state of the thermostat of Example 1. FIG. 3 is a partial enlarged cross-sectional view illustrating a state of the main valve (spring seat 182) in the first valve open state of the thermostat of the first embodiment. FIG. 6 is a partially enlarged cross-sectional view showing a state of the main valve (spring seat 182) in the second valve open state of the thermostat of the first embodiment. FIG. 6 is a partially enlarged cross-sectional view showing a state of the main valve (spring seat 182) in the third valve open state of the thermostat of the first embodiment. FIG. 3 is a partial enlarged cross-sectional view showing a state of the main valve (spring seat 182) in a closed state of the bypass valve of the thermostat of the first embodiment. 1 is a perspective view showing a partial cross section of a thermostat of Example 1. FIG. It is a whole block diagram which shows roughly an example of the cooling system system (bypass circulation state) (thermostat engine entrance side arrangement | positioning) which concerns on Example 2 of this invention. It is a figure which shows the flow of the cooling water of the cooling system in the thermostat of Example 2 in the 1st valve opening state and the 2nd valve opening state. It is a figure which shows the flow of the cooling water of the cooling system in the 3rd valve opening state of the thermostat of Example 2. FIG. It is a figure which shows the flow of the cooling water of the cooling system in the bypass valve closed state of the thermostat of Example 2. FIG. It is sectional drawing explaining the operation state in the default (bypass circulation) state of the other structural example of the thermostat which can be utilized by this invention. It is sectional drawing explaining the operation state in the 1st valve opening state of a thermostat same as the above. It is sectional drawing explaining the operation state in the 2nd valve open state of a thermostat same as the above. It is sectional drawing explaining the operation state in the 3rd valve opening state of a thermostat same as the above. It is sectional drawing explaining the operation state in the bypass valve closed state of a thermostat same as the above. It is a whole block diagram which shows roughly an example of the cooling system system (bypass circulation state) (thermostat engine exit side arrangement | positioning) which concerns on Example 3 of this invention. It is a figure which shows the flow of the cooling water of the cooling system in the 1st valve opening state of a thermostat of Example 3, and a 2nd valve opening state. It is a figure which shows the flow of the cooling water of the cooling system in the 3rd valve opening state of the thermostat of Example 3. FIG. It is a figure which shows the flow of the cooling water of the cooling system in the bypass valve closed state of the thermostat of Example 3. It is sectional drawing explaining the operation state in the default (bypass circulation) state of the thermostat of Example 3. FIG. It is sectional drawing explaining the operation state in the 1st valve opening state of the thermostat of Example 3. FIG. It is sectional drawing explaining the operation state in the 2nd valve opening state of the thermostat of Example 3. FIG. It is sectional drawing explaining the operation state in the 3rd valve opening state of the thermostat of Example 3. FIG. It is sectional drawing explaining the operation state in the bypass valve closed state of the thermostat of Example 3. FIG. 6 is a perspective view showing a partial cross section of a thermostat of Example 3. FIG. In Example 3, it is a figure which shows the relationship with said each state with respect to the cooling water temperature, "The flow volume of the cooling water from the radiator 3" which passes the EGR cooler 5, and the "flow volume of the cooling water from the thermostat 1300". . FIG. 10 is a diagram illustrating the relationship between the above-described states and the “flow rate of cooling water from the radiator 3” and the “flow rate of cooling water from the thermostat 1300” passing through the oil cooler 6 with respect to the cooling water temperature in Example 3. . It is a whole block diagram which shows roughly an example of the cooling system system (bypass circulation state) (thermostat engine entrance side arrangement | positioning) which concerns on Example 4 of this invention. It is a figure which shows the flow of the cooling water of the cooling system in the 1st valve opening state of a thermostat of Example 4, and a 2nd valve opening state. It is a figure which shows the flow of the cooling water of the cooling system in the 3rd valve opening state of the thermostat of Example 4. FIG. It is a figure which shows the flow of the cooling water of the cooling system in the bypass valve closed state of the thermostat of Example 4. It is a whole block diagram which shows roughly an example of the cooling system system (thermostat engine entrance side arrangement | positioning) which concerns on Example 5 of this invention. It is sectional drawing explaining the operation state in the default (bypass circulation) state of the thermostat of Example 5. It is sectional drawing explaining the operation state in the 1st valve opening state of the thermostat of Example 5. FIG. It is sectional drawing explaining the operation state in the 2nd valve opening state of the thermostat of Example 5. FIG. It is sectional drawing explaining the operation state in the 3rd valve open state of the thermostat of Example 5. FIG. It is sectional drawing explaining the operation state in the bypass valve closed state of the thermostat of Example 5. FIG. It is a whole block diagram which shows roughly an example of the cooling system system (thermostat engine exit side arrangement | positioning) which concerns on Example 6 of this invention. It is sectional drawing explaining the operation state in the default (bypass circulation) state of the thermostat of Example 6. It is sectional drawing explaining the operation state in the 1st valve opening state of the thermostat of Example 6. FIG. It is sectional drawing explaining the operation state in the 2nd valve opening state of the thermostat of Example 6. FIG. It is sectional drawing explaining the operation state in the bypass valve closed state of the thermostat of Example 6. FIG. 10 is a perspective view showing a partial cross section of a thermostat of Example 6. FIG. It is a whole block diagram which shows roughly the cooling system system at the time of arrange | positioning the thermostat of Example 6 to the engine exit side. It is a figure which shows an example of cooling systems, such as the conventional internal combustion engine. It is a figure which shows an example of the conventional heat circulation channel | path switching device (slide valve).

Explanation of symbols

1 Engine (equivalent to combustion device)
2 Water pump 3 Radiator 4 Heater core 5 EGR cooler 6 Oil cooler 100 Thermostat (thermally-responsive valve device)
180 Thermo element 181 Temperature sensing unit 182 Spring seat (valve)
184A Spring seat (valve)
184B Spring seat (valve)
184C Spring seat (valve)
200 Radiator passage 300 Heater core passage 400 Bypass passage 500 EGR cooler passage 600 Oil cooler passage 1200 Thermostat (thermally responsive valve device)
1300 Thermostat (thermally responsive valve device)
1400 Thermostat (thermally responsive valve device)
1500 Thermostat (thermally responsive valve device)
A Valve opening temperature adjustment allowance X Valve opening temperature adjustment allowance Y Valve opening temperature adjustment allowance

Claims (5)

Corresponding to the plurality of fluid passages that are driven by a common thermal responsive element that is thermally responsive to the surrounding fluid temperature and controls the degree of communication between the predetermined region and each of the plurality of fluid passages according to the surrounding fluid temperature A plurality of valve bodies, one of which is a thermally responsive valve device including a plurality of valve bodies including a main valve body that controls the degree of communication between the radiator and the predetermined region,
After any one of the plurality of valve bodies other than the main valve body starts controlling the degree of communication between the predetermined region and the corresponding fluid passage, the control of the degree of communication of the main valve body is started. A thermally responsive valve device provided with a delay mechanism for delaying the operation.   The start of control of the degree of communication between the predetermined region and the corresponding fluid passage is set for each of the plurality of valve bodies in accordance with the required fluid temperature. Thermally responsive valve device.   The thermal response according to claim 1 or 2, wherein the delay mechanism delays the main valve body based on a delay amount until the thermal response operation of the common thermal response element is transmitted to the main valve body. Valve device.   2. The delay mechanism according to claim 1, wherein the delay mechanism delays the main valve body based on a movement amount until the main valve body moves and the main valve body is opened in accordance with a thermal responsive operation of the common thermal responsive element. The thermally responsive valve device according to any one of claims 3 to 4.   A fluid passage independent of the plurality of fluid passages and a valve body for opening and closing the fluid passage are provided, and the valve body is driven by the common thermal actuator. Item 5. The thermally responsive valve device according to any one of items 4.

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