WO2010067182A1 - Pressure valve - Google Patents

Pressure valve Download PDF

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Publication number
WO2010067182A1
WO2010067182A1 PCT/IB2009/007697 IB2009007697W WO2010067182A1 WO 2010067182 A1 WO2010067182 A1 WO 2010067182A1 IB 2009007697 W IB2009007697 W IB 2009007697W WO 2010067182 A1 WO2010067182 A1 WO 2010067182A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
diaphragm
pressure valve
rupture
Prior art date
Application number
PCT/IB2009/007697
Other languages
French (fr)
Inventor
Masao Toi
Yasutoshi Yamanaka
Original Assignee
Toyota Jidosha Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP2008314913A priority Critical patent/JP2010138982A/en
Priority to JP2008-314913 priority
Application filed by Toyota Jidosha Kabushiki Kaisha filed Critical Toyota Jidosha Kabushiki Kaisha
Publication of WO2010067182A1 publication Critical patent/WO2010067182A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00Actuating devices; Operating means; Releasing devices
    • F16K31/12Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/126Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
    • F16K31/1262Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like one side of the diaphragm being spring loaded
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
    • F01N5/02Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/14Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side with fracturing member
    • F16K17/16Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side with fracturing member with fracturing diaphragm ; Rupture discs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0266Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/06Control arrangements therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001Recuperative heat exchangers
    • F28D21/0003Recuperative heat exchangers the heat being recuperated from exhaust gases
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/12Improving ICE efficiencies

Abstract

A pressure valve (100) includes a reverse plate (3). The single reverse plate (3) has a diaphragm portion (3a) and a rupture portion (3b) that is provided concentrically with the diaphragm portion (3a) and that ruptures at a pressure higher than a pressure at which the diaphragm portion (3a) is actuated. Thus, the single pressure valve (100) has both a pressure switch function and a pressure release function. By applying the pressure valve (100) to an exhaust heat recovery system, it is not necessary to take measures against High Pressure Gas Safety Act, and the size of a condensing unit may be reduced. By so doing, the exhaust heat recovery system may be easily mounted in an underfloor of a vehicle, an engine room, or the like.

Description

PRESSXJRE VALVE
BACKGROUND OF THE INVENTION
1. Field of the Invention
[0001] The invention relates to a pressure valve having a diaphragm that is actuated by fluid pressure, and also to an exhaust heat recovery system provided with the pressure valve.
2. Description of the Related Art
[0002] In recent years, there is known a technique that utilizes the principles of heat pipe to recover exhaust heat of exhaust gas from an exhaust system of an engine of a vehicle to engine coolant, and then uses the recovered heat to facilitate warm-up of the engine.
[0003] A loop heat pipe-type exhaust heat recovery system has been suggested as the exhaust heat recovery system that utilizes the principles of heat pipe (see, for example, Japanese Patent Application Publication No. 2008-051479 (JP- A-200S-051479) and Japanese Patent Application Publication No. 2008-280894 (JP-A-2008-280894)). The loop heat pipe-type exhaust heat recovery system (hereinafter, also referred to as heat pipe-type exhaust heat recovery system), for example, includes a heat pipe. The heat pipe includes an evaporating unit, a condensing unit, a fluid communication unit, and the like. The evaporating unit evaporates a heating medium (for example,' pure water), filled inside the heat pipe, by heat of exhaust gas. The condensing unit cools the heating medium, evaporated at the evaporating unit, by engine coolant. The fluid communication unit provides fluid communication between the evaporating unit and the condensing unit. The heat pipe-type exhaust heat recovery system utilizes the heating medium filled in the heat pipe to exchange heat between exhaust gas and engine coolant io thereby recover exhaust heat to the coolant. [0004] In the above heat pipe-type exhaust heat recovery system, if heat of exhaust gas is constantly recovered, it is difficult to cool engine coolant by a radiator. This brings the coolant to a boil. In order to avoid the above situation, the condensing unit has a pressure valve that switches the state of the exhaust heat recovery system between a heat recover state and a non-heat recovery state (see, for example, JP-A-2008-051479 and JP-A-200S-280894). The pressure valve may be, for example, a diaphragm pressure valve. The diaphragm pressure valve has the following recovery and non-recovery characteristic (switching characteristic). At the time when the heat recovery-side internal pressure increases to a value that is higher than or equal to, for example, a first pressure in a valve open state during normal times, the diaphragm is reversed to enter a valve closed state to thereby shut off a passage that returns the heating medium, condensed at the condensing unit, to the evaporating unit (non-recovery state). At the time when the heat recovery-side pressure decreases to a value that is lower than or equal to a second pressure (the second pressure is lower than the first pressure) in the above valve closed state, the diaphragm is reversed to enter a valve open state to thereby open the passage that returns the heating medium to the evaporating unit (recovery state).
[0005] Incidentally, when the heat pipe-type exhaust heat recovery system is designed so that the internal pressure does not exceed 1 MPa (gauge pressure) even when a malfunction (pressure increase) occurs, it is not necessary to take measures against High Pressure Gas Safety Act. Therefore, the condensing unit has a relief valve that releases pressure at 1 MPa or below.
[0006] However, the condensing unit of the heat pipe-type exhaust heat recovery system has the above described pressure valve for switching the state of the exhaust heat recovery system between a heat recover state and a non-heat recovery state. If the relief valve is provided separately from the pressure valve, the condensing unit needs space for installing two components (circular components), that is, the pressure valve and the relief valve. This increases the body size of the condensing unit more than necessary (more than space necessary for obtaining heat exchange efficiency). Therefore, the overall size of the system increases. In addition, there is another
9. possibility that the two components, that is, the pressure valve and the relief valve, are used to problematically increase the cost.
[0007] Note that, other than the heat pipe-type exhaust heat recovery system, for example, in a closed-type system (circuit), such as a floor-type heat pump water heater, or an open-type system (circuit), such as an accumulator and a compressed-air cylinder, two components, that is, a pressure valve and a relief valve, may possibly be used in order to provide a pressure switch function and a pressure release function.
SUMMARY OF THE INVENTION
[0008] The invention provides a pressure valve that has both a pressure switch function and a pressure release function, and an exhaust heat recovery system provided with the pressure valve.
[0009] A first aspect of the invention relates to a pressure valve that includes a diaphragm portion that is actuated by fluid pressure. The pressure valve includes a rupture portion that is provided concentrically with the diaphragm portion and that ruptures at a pressure higher than a pressure at which the diaphragm portion is actuated. More specifically, the diaphragm portion and the rupture portion may be provided concentrically for a single reverse plate.
[0010] The rupture portion that ruptures when subjected to a high pressure is provided concentrically with the diaphragm portion, so the single pressure valve may have both a pressure switch function and a pressure release function. By so doing, it is not necessary to separately provide a relief valve in addition to the pressure valve, so mountability to a system (circuit), such as an exhaust heat recovery system, improves. In addition, it is also excellent in terms of cost.
[0011] The rupture portion may be provided concentrically on an outer peripheral side of the diaphragm portion. In this case, it is possible to provide the pressure valve that places importance on stability of rupture performance. Alternatively, the diaphragm portion may be provided concentrically on an outer peripheral side of the rupture portion. In this case, the working diameter of the diaphragm portion may be increased. Thus, the diameter of the reverse plate may be reduced while maintaining the switching characteristic, so the size of the pressure valve may be reduced.
[0012] In another specific configuration, the rupture portion may be a bent portion having a taper portion that slopes toward a side on which the fluid pressure acts, and the taper portion may be reversed by the fluid pressure to cause the rupture portion to rupture.
[0013] A second aspect of the invention relates to an exhaust heat recovery system that recovers heat of exhaust gas from an internal combustion engine (engine), and transfers the recovered heat to engine coolant. The exhaust heat recovery system includes the above described pressure valve.
[0014] Specifically, the exhaust heat recovery system may have a loop heat pipe that includes: an evaporating unit that evaporates a heating medium, which is the fluid and filled inside the exhaust heat recovery system, by the heat of the exhaust gas from the internal combustion engine; a condensing unit that cools the heating medium, evaporated at the evaporating unit, by the coolant of the internal combustion engine; and a fluid communication unit that provides fluid communication between the evaporating unit and the condensing unit, and the pressure valve may be provided for the condensing unit (specifically, at a condensed water reflux side of the condensing unit).
[0015] With the thus configured exhaust heat recovery system, the pressure valve having both a pressure switch function implemented by reversal of the diaphragm portion and a pressure release function implemented by the rupture portion is provided for the condensing unit. Thus, in comparison with the case where a pressure valve and a relief valve are separately provided for the condensing unit, the size of the condensing unit may be reduced. By so doing, the exhaust heat recovery system may be easily mounted in an underfloor of a vehicle, an engine room, or the like, of which mounting space is limited.
[0016] Note that the pressure valve according to the aspect of the invention may be applied not only to the above described exhaust heat recovery system but also to a closed-type system (circuit), such as a floor-type heat pump water heater, an air conditioner and a refrigerator, or an open-type system (circuit), such as an accumulator, a compressed-air cylinder and a large storage tank for natural gas, or the like.
BRIEF DESCRIPTION OF THE DRAWINGS
[0017] The foregoing and further objects, features and advantages of the invention will become apparent from the following description of example embodiments with reference to the accompanying drawings, wherein like numerals are used to represent like elements and wherein:
FIG. 1 is a longitudinal cross-sectional view that shows a pressure valve according to a first embodiment of the invention;
FIG. 2A is a front view of a reverse plate used for the pressure valve shown in FIG. 1, and FIG. 2B is a longitudinal cross-sectional view of the reverse plate;
FIG. 3A and FIG. 3B are views that illustrate the operation of the pressure valve shown in FIG. '1;
FIG. 4 is a graph that shows open-close operation of the pressure valve shown in FIG. 1;
FIG. 5 is a view that schematically shows a state where the pressure valve shown in FIG. 1 releases pressure;
FIG. 6 is a longitudinal cross-sectional view that shows a pressure valve according to a second embodiment of the invention;
FIG. 7A is a front view of a reverse plate used for the pressure valve shown in FIG. 6, and FIG. 7B is a longitudinal cross-sectional view of the reverse plate;
FIG. 8A and FIG. 8B are views that illustrate the operation of the pressure valve shown in FIG. 6;
FIG 9 is a front view that shows an example of an exhaust heat recovery system according to an embodiment of the invention;
FIG. 10 is a plan view of the exhaust heat recovery system shown in FIG. 9;
FIG. 11 is a side view of the exhaust heat recovery system shown in FIG. 9; and
FIG. 12 is a cross-sectional view taken along the line X-X in FIG. 9. DETAILED DESCRIPTION OF EMBODIMENTS First Embodiment
[0018] FIG. 1 is a cross-sectional view that shows a pressure valve 100 according to a first embodiment of the invention.
[0019] The pressure valve 100 according to the present embodiment includes a body 1, a lid element 2, a reverse plate 3, a valve element 4, a valve guide 5, a valve seat 6, a delivery pipe 7, compression coil springs 8 and 10, a spring shoe 9, a spring seat 11, a support plate 12, a dust cap 13, and the like.
[0020] The body 1 is a member such that a cylindrical portion Ia and a flange Ib are integrally formed with each other. The cylindrical portion Ia has an inflow port Ic for fluid (for example, a heating medium, such as pure water). The support plate 12 has a substantially annular shape, and is fitted around the cylindrical portion Ia of the body 1. The lid element 2 is a member such that a cylindrical portion 2a and a flange 2b are integrally formed with each other. The cylindrical portion 2a has an internal thread 2c formed on an inner surface of the cylindrical portion 2a.
[0021] The peripheral edge portion of the reverse plate 3 is clamped between the flange Ib of the body 1 and the flange 2b of the lid element 2. The reverse plate 3 is held by these body 1 and lid element 2. The reverse plate 3 is, for example, formed of a pressed stainless thin plate. As shown in FIG. 2A and FIG. 2B, in the reverse plate 3, a diaphragm portion 3a and a rupture portion 3b are concentrically formed, and the rupture portion 3b is arranged on the outer peripheral side of the diaphragm portion 3a.
[0022] The valve element 4 and the valve guide 5 are arranged on the pressure receiving side (body 1 side) of the reverse plate 3 along the axis of the body 1.
[0023] The valve element 4 is a stepped cylindrical member formed of a large-diameter portion 4a and a small-diameter portion 4b. A step between the large-diameter portion 4a and the small-diameter portion 4b constitutes a valve surface 4c. An end (end adjacent to the delivery pipe 7) of the large-diameter portion 4a of the valve element 4 is open. In addition, the valve element 4 has a communication hole 4d that allows passage of fluid. The communication hole 4d is a through hole that opens part of the valve element 4. When the valve surface 4c of the valve element 4 is spaced away from the valve seat 6 (state shown in FIG. 1), which will be described later, the communication hole 4d is open. When the valve surface 4c of the valve element 4 is in contact with (seated on) the valve seat 6, the communication hole 4d is shut off by the valve seat 6.
[0024] The valve guide 5 is a cylindrical member. The valve seat 6 is integrally formed at one end (end adjacent to the reverse plate 3) of the valve guide 5. The valve guide 5 is fitted into a boss hole Id of the body 1. In addition, the delivery pipe 7 is coupled to the other end of the valve guide 5. The outer peripheral surface of the other end of the delivery pipe 7 has an external thread 7a that is in mesh with the internal thread 2Of of a valve case 20, which will be described later.
[0025] The large-diameter portion 4a of the valve element 4 is slidably arranged inside the valve guide 5. The valve surface 4c of the valve element 4 is displaceable in a direction in which the valve surface 4c approaches or moves away from the valve seat 6. The compression coil spring 8 is placed between the valve element 4 and an end face (end face adjacent to the reverse plate 3) of the delivery pipe 7. By the elastic force of the compression coil spring 8, the valve element 4 is in contact with the reverse plate 3 while being pressed by the reverse plate 3. Note that the distal end (series- wound portion) of the compression coil spring 8 is accommodated in the small-diameter portion 4b of the valve element 4.
[0026] Then, when the valve surface 4c of the valve element 4 is spaced away from the valve seat 6, the valve opening 6a of the valve seat 6 is open (valve open state), the inside of the body 1 is in fluid communication with the inside of the delivery pipe 7 through the valve opening 6a of the valve seat 6 and the communication hole 4d of the valve element 4. When the valve element 4 is displaced from the valve open state toward the reverse plate 3 and then the valve surface 4c contacts (is seated on) the valve seat 6, the valve opening 6a of the valve seat 6 is shut off, so it enter a valve closed state.
[0027] On the other hand, inside the lid element 2, the spring shoe 9, the compression coil spring 10 and the spring seat 11 are arranged in order from the reverse plate 3 side. The compression coil spring 10 is placed between the spring shoe 9 and the spring seat 11 while being compressed. By the elastic force of the compression coil spring 10, the spring shoe 9 is in contact with the reverse plate 3 while being pressed by the reverse plate 3.
[0028] The outer peripheral surface of the spring seat 11 has an external thread 11a that is in mesh with the internal thread 2c of the Hd element 2. By adjusting the screw-in amount of the spring seat 11, the elastic force of the compression coil spring 10 may be adjusted, thus making it possible to adjust a first pressure Pl and a second pressure P2, which will be described later. In addition, a vent hole lib is formed at the center of the spring seat 11. The vent hole lib is used to open the inside of the Hd element 2 to the atmosphere. Note that a dustproof dust cap 13 is attached to the cylindrical portion 2a of the Hd element 2.
[0029] The above described pressure valve 100 is fitted to the valve case 20. As shown in FIG. 1, the valve case 20 is a stepped cylindrical member having a large-diameter portion 20a and a small-diameter portion 20b. A flange 20c is integrally formed with the periphery of an end of the large-diameter portion 20a. The large-diameter portion 20a of the valve case 20 has an inlet port 2Od for fluid. The open end of the small-diameter portion 20b constitutes an outlet port 2Oe.
[0030] Then, to fit the pressure valve 100 to the valve case 20, the delivery pipe 7 of the pressure valve 100 is initially inserted into the large-diameter portion 20a of the valve case 20. Subsequently, the external thread 7a of the delivery pipe 7 is screwed to the internal thread 2Of of the small-diameter portion 20b of the valve case 20 to bring the support plate 12 of the pressure valve 100 into contact with the flange 20c of the valve case 20 with a pressing force to a certain extent. In this state, the support plate 12 is welded to the flange 20c of the valve case 20. In the above fitted state, as shown in FIG. 1, the inside of the body 1 is in fluid communication with the inside of the valve case 20 through the inflow port Ic formed in the body 1. By so doing, fluid (for example, condensed water) flowing into the inside of the valve case 20 passes through the inflow port Ic and flows into the inside of the body 1 (space • defined by the body 1 and the reverse plate 3). Then, the pressure of that fluid acts on the reverse plate 3.
[0031] Note that, in the pressure valve 100 shown in FIG. 1, a stopper may be provided on the body 1 side surface of the surface of the diaphragm portion 3a in order to regulate the displacement of the diaphragm portion 3a.
[0032] Next, the operation of the above described pressure valve 100 will be described with reference to FIG. 3A, FIG. 3B and FIG. 4.
[0033] The pressure valve 100 is in a valve open state during normal times. When the pressure valve 100 is in a valve open state, as shown in FIG. 1 and FIG. 3A, the valve surface 4c of the valve element 4 is spaced apart from the valve seat 6, and the valve opening 6a of the valve seat 6 is open. In this open state, the inside of the body 1 (inside of the valve case 20) is in fluid communication with the inside of the delivery pipe 7 through the valve opening 6a of the valve seat 6 and the communication hole 4d of the valve element 4. By so doing, fluid flowing through the inlet port 2Od of the valve case 20 into the inside of the case sequentially passes through the inflow port Ic of the body 1, the inside of the body 1, the valve opening 6a of the valve seat 6 and the communication hole 4d of the valve element 4, flows into the inside of the delivery pipe 7, and then flows out through the outlet port 2Oe of the valve case 20.
[0034] When the internal pressure inside the body 1 (internal pressure in the space defined by the body 1 and the reverse plate 3) increases from the above valve open state as shown in FIG. 4, the pressure valve 100 enters a valve closed state at the time when the internal pressure becomes Pl or above. Specifically, at the time when the internal pressure in the body 1 reaches Pl, as shown in FIG. 3B, the diaphragm portion 3a of the reverse plate 3 of the pressure valve 100 is reversed. Owing to the reversal of the diaphragm portion 3a, the valve element 4 is displaced toward the lid element 2. At the time when the valve surface 4c of the valve element 4 contacts (is seated on) the valve seat 6, the valve opening 6a of the valve seat 6 is shut off, and the pressure valve 100 enters a valve closed state.
[0035] Here, the diaphragm portion 3a is a reverse plate that is reversed in a snap action manner and that has the following hysteresis characteristic. When a pressure higher than or equal to the above first pressure Pl acts on the diaphragm portion 3a, the diaphragm portion 3a is reversed in a direction indicated in FIG. 3B. When the pressure acts on the diaphragm portion 3a decreases to a pressure lower than the first pressure, the diaphragm portion 3a is reversed (returned) to the original position (position shown in FIG. 3A). Thus, as shown in FIG. 4, even when the pressure (internal pressure) inside the body 1 decreases from the pressure higher than or equal to the first pressure Pl to a pressure lower than the first pressure Pl, the diaphragm portion 3a is not immediately reversed. At the time when the pressure decreases to the second pressure P2, the diaphragm portion 3a is reversed. Then, by the elastic force of the compression coil spring 10, the valve element 4 is displaced in a direction to move away from the valve seat 6, so it returns to a valve open state (state shown in FIG. 3A). Note that, as described above, these first pressure Pl and second pressure P2 may be adjusted by adjusting the screw-in amount of the spring seat 11 to the lid element 2.
[0036] Next, the rupture portion 3b of the reverse plate 3 will be described. As shown in FIG. 2A and FIG. 2B, the rupture portion 3b is a bent portion having a taper portion 31b that slopes toward the inside of the body 1. The rupture portion 3b is configured so that, when a pressure (release pressure Ps) that is higher than a pressure at which the diaphragm portion 3a is actuated (higher than or equal to the first pressure Pl) and that is lower than, for example, 1 MPa (gauge pressure) acts on the body 1 inner side surface of the reverse plate 3, as shown in FIG. 5, the taper portion 31b of the rupture portion 3b buckles to be reversed and then, at the time of the reversal, the apex A of the bent portion ruptures to open.
[0037] The rupture portion 3b and the diaphragm portion 3a are provided for the single reverse plate 3, and the rupture portion 3b is provided concentrically with the diaphragm portion 3a. Thus, the single pressure valve 100 may have both a pressure switch function and a pressure release function. By so doing, it is not necessary to separately provide a relief valve in addition to the pressure valve, so mountability to a system (circuit), such as an exhaust heat recovery system, improves. In addition, it is also excellent in terms of cost.
[0038] Note that the pressure valve 100 according to the first embodiment places importance on stability of rupture performance of the rupture portion 3b, the diaphragm portion 3a that frequently repeats reversal is provided at the inner side of the reverse plate 3, and the rupture portion 3b is provided on the outer peripheral side of the diaphragm portion 3a. Second Embodiment
[0039] Next, a pressure valve 200 according to a second embodiment of the invention will be described with reference to FIG. 6 to FIG. 8B.
[0040] The pressure valve 200 according to the second embodiment differs from the pressure valve 100 according to the first embodiment only in the configuration of a reverse plate 203. The other configuration, that is, the configuration of the body 1, lid element 2, valve element 4, valve guide 5, valve seat 6, delivery pipe 7, compression coil springs 8 and 10, spring shoe 9, spring seat 11, support plate 12, dust cap 13, and the like, is basically similar to that of the first embodiment.
[0041] As shown in FIG. 7 A and FIG. 7B, the reverse plate 203 used in the pressure valve 200 according to the present embodiment has a rupture portion 203b at an inner side thereof, and a diaphragm portion 203a is concentrically formed on the outer peripheral side of the rupture portion 203b. Note that the rupture portion 203b is a bent portion having a taper portion 231b that slopes toward the inside of the body 1 as in the case of the reverse plate 3 shown in FIG. 2 A and FIG. 2B.
[0042] Then, the pressure valve 200 according to the present embodiment is also in a valve open state during normal times. When the pressure valve 200 is in a valve open state, as shown in FIG. 6 and FIG. 8A, the valve surface 4c of the valve element 4 is spaced away from the valve seat 6, and the valve opening 6a of the valve seat 6 is open. In this open state, the inside of the body 1 (inside of the valve case 20) is in fluid communication with the inside of the delivery pipe 7 through the valve opening 6a of the valve seat 6 and the communication hole 4d of the valve element 4. By so doing, fluid flowing through the inlet port 2Od of the valve case 20 into the inside of the case sequentially passes through the inflow port Ic of the body 1, the inside of the body 1, the valve opening 6a of the valve seat 6 and the communication hole 4d of the valve element 4, flows into the inside of the delivery pipe 7, and then flows out through the outlet port 2Oe of the valve case 20.
[0043] When the internal pressure in the body 1 increases from the above valve open state as shown in FIG. 4, the pressure valve 200 enters a valve closed state at the time when the internal pressure becomes the first pressure Pl or above. Specifically, at the time when the internal pressure in the body 1 reaches the first pressure Pl, as shown in FIG. 8B, the diaphragm portion 203a of the reverse plate 203 of the pressure valve 200 is reversed. Owing to the reversal of the diaphragm portion 203a, the valve element 4 is displaced toward the lid element 2. At the time when the valve surface 4c of the valve element 4 contacts (is seated on) the valve seat 6, the valve opening 6a of the valve seat 6 is shut off, and the pressure valve 200 enters a valve closed state.
[0044] Even when the internal pressure in the body 1 decreases from the valve closed state (state where the internal pressure is higher than or equal to the first pressure Pl) to a pressure lower than the first pressure Pl, the pressure valve 200 is not closed. At the time when the internal pressure in the body 1 decreases to the second pressure P2, the diaphragm portion 203a is reversed (returned). Then, by the elastic force of the compression coil spring 10, the valve element 4 is displaced in a direction to move away from the valve seat 6, so it returns to a valve open state shown in FIG. 8A.
[0045] In addition, in the pressure valve 200 according to the present embodiment as well, the reverse plate 203 has the rupture portion 203b. Thus, when a pressure (release pressure Ps) that is higher than a pressure at which the diaphragm portion 203a is actuated (higher than or equal to the first pressure Pl) and that is lower than, for example, 1 MPa acts on the body inner side surface of the reverse plate 203, the rupture portion 203b ruptures as in the similar mechanism to that of FIG. 5. Therefore, the single pressure valve 200 may have both the above described pressure switch function implemented by reversal of the diaphragm portion 203a and the pressure release function implemented by the rupture portion 203b. By so doing, it is not necessary to separately provide a relief valve in addition to the pressure valve, so mountability to a system (circuit), such as an exhaust heat recovery system, improves. In addition, it is also excellent in terms of cost.
[0046] Here, in the reverse plate 203 used in the pressure valve 200 according to the present embodiment, the diaphragm portion 203a is provided to the outside of the rupture portion 203b. Thus, the working diameter of the diaphragm portion 203a may be increased. By so doing, the diameter of the reverse plate 203 may be reduced as compared with the reverse plate 3 shown in FIG. 2A and FIG. 2B while maintaining the switching characteristic. Therefore, the size of the pressure valve 200 may be reduced. Exhaust Heat Recovery System
[0047] An exhaust heat recovery system according to an embodiment of the invention will be described with reference to FIG. 9 to FIG. 12.
[0048] The exhaust heat recovery system 300 according to the present embodiment includes a loop heat pipe 301. The loop heat pipe 301 is formed by sequentially connecting an evaporating unit 302, a fluid communication passage 304, a condensing unit 303, the valve case 20, the above described pressure valve 100, a reflux pipe 305, and the like. The evaporating unit 302 is assembled to an exhaust passage 400 of an engine. The condensing unit 303 is arranged outside the exhaust passage 400.
[0049] The heat pipe 301 is provided with a filling portion (not shown). The inside of the heat pipe 301 is decompressed (vacuumed) through the filling portion. The heat pipe 301 is filled with a heating medium through the filling portion, and then the filling portion is sealed. In this embodiment, pure water is used as the heating medium.
[0050] As shown in FIG. 12, the evaporating unit 302 is formed of tubes 321, fins 322, an upper header 323, a lower header 324, and the like. The tubes 321 each are a long slender tubular member that extends vertically. A plurality of the tubes 321 are arranged in columns at a predetermined pitch in a direction to intersect with flow of exhaust gas (horizontal direction in FIG. 12), and a plurality of the tubes 321 are also arranged in columns at a predetermined pitch in a direction of flow of exhaust gas (horizontal direction in FIG. 9). [0051] The fins 322. are arranged as heat exchange members between the adjacent tubes 321. These fins 322 are bonded to the outer wall surfaces (surfaces) of the corresponding tubes 321. The fins 322 expand the area of heat exchange with exhaust gas. In this embodiment, corrugated fins that are formed in a corrugated shape from a thin sheet material by rolling are used. These tubes 321 and fins 322 constitute a heat exchange portion of the evaporating unit 302.
[0052] The upper ends of the tubes 321 are open into the upper header 323 arranged at the upper portion of the evaporating unit 302. In addition, the lower ends of the tubes 321 are open into the lower header 324 arranged at the lower portion of the evaporating unit 302.
[0053] Then, an upstream connecting duct 300a and a downstream connecting duct 300b are connected to the evaporating unit 302. These upstream connecting duct 300a and downstream connecting duct 300b are used to make it possible to assemble the evaporating unit 302 to the exhaust passage 400 of the engine.
[0054] As shown in FIG. 9 and FIG. 12, the inside of the condensing unit 303 is partitioned into two chambers by a partition wall 331. The inner chamber with respect to the partition wall 331 constitutes a condensing chamber 332. The inside of the condensing chamber 332 is in fluid communication with the inside of the upper header 323 of the evaporating unit 302 through the fluid communication passage 304. In addition, the outer chamber with respect to the partition wall 331 constitutes a coolant passage 333. A coolant introducing pipe 303a and a coolant delivery pipe 303b are connected to the coolant passage 333.
[0055] In the condensing unit 303, heat is exchanged between engine coolant introduced from the coolant introducing pipe 303a to the coolant passage 333 and vapor guided from the evaporating unit 302 to the condensing chamber 332 through the fluid communication passage 304. The vapor deprived of heat through heat exchange with the engine coolant is condensed from a gaseous phase to a liquid phase. In addition, the engine coolant that has exchanged heat with vapor at the condensing unit 303 flows out from the coolant passage 333 to the outside of the condensing unit 303 through the coolant delivery pipe 303b.
[0056] The valve case 20 (see FIG. 1) is arranged at the lower portion of the condensing unit 303. The pressure valve 100 shown in FIG. 1 to FIG. 3B is attached to the valve case 20 in the above described manner. Note that parts of the cylindrical portion 20a and flange 20c of the valve case 20 are welded to the wall of the condensing unit 303.
[0057] The inlet port 20d of the valve case 20 is connected to the condensing chamber 332 of the condensing unit 303. The outlet port 2Oe of the valve case 20 is connected to the lower header 324 of the evaporating unit 302 through the reflux pipe 305. By so doing, a passage is formed from the condensing chamber 332 of the condensing unit 303 via the inlet port 2Od of the valve case 20 and the inside of the valve case 20 to the inside of the body 1 of the pressure valve 100. In addition, another passage is formed from the inside of the delivery pipe 7 of the pressure valve 100 (inside of the valve guide 5) via the outlet port 2Oe of the valve case 20 and the reflux pipe 305 to the lower header 324 of the evaporating unit 302.
[0058] In the above described exhaust heat recovery system 300, in process of an increase in internal pressure in the heat pipe 301 (pressure inside the body 1 of the pressure valve 100), when the internal pressure is lower than the above described first pressure Pl, the pressure valve 100 is in a valve open state (see FIG. 4). In this state, pure water (heating medium) in the heat pipe 301 receives heat from exhaust gas at the evaporating unit 302 to boil and vaporize to become vapor to go up inside the tubes 321. This upward vapor flows out from the tubes 321 and then flows into the condensing chamber 332 of the condensing unit 303 via the upper header 323 and the fluid communication passage 304. The vapor flowing into the condensing chamber 332 is cooled by engine coolant, flowing through the coolant passage 333, to become condensed water. The condensed water passes through the valve case 20, the pressure valve 100 in a valve open state and the reflux pipe 305, and returns to the lower header 324 of the evaporating unit 302.
[0059] In this way, heat of exhaust gas is transferred to the heating medium (pure water) and is transported from the evaporating unit 302 to the condensing unit 303. Then, the heat is released as condensed latent heat when vapor condenses at the condensing unit 303. Thus, engine coolant that flows through the condensing unit 303 is actively heated. That is, this facilitates the warm-up of the engine, so it is possible to achieve reduction in friction loss of the engine and improvement in low-temperature startability of the engine. Therefore, it is possible to improve fuel consumption rate (fuel economy).
[0060] Then, as shown in FIG. 4, as the internal pressure in the heat pipe 301 (pressure inside the body 1 of the pressure valve 100) exceeds the first pressure Pl, the pressure valve 100 is closed to shut off reflux of condensed water from the condensing unit 303 to the evaporating unit 302. Thus, recovery of exhaust heat is stopped. By so doing, it is possible to prevent engine coolant from being excessively heated, so overheating may be prevented. Note that, as the pressure valve 100 is closed to stop recovery of exhaust heat, the internal pressure in the heat pipe 301 decreases, and, at the time when the internal pressure decreases to the second pressure P2 (see FIG. 4), the pressure valve 100 returns to a valve open state, and then recovery of exhaust heat is resumed.
[0061] Here, as described above, the pressure valve 100 used in the exhaust heat recovery system 300 according to the present embodiment has a hysteresis characteristic such that the diaphragm portion 3a is reversed in a direction indicated in FIG. 3B when a pressure higher than or equal to the first pressure Pl acts on the diaphragm portion 3a, and the diaphragm portion 3a returns (is reversed) to the original position (position shown in FIG. 3A) when the pressure decreases to the second pressure P2 lower than the first pressure Pl. Thus, it is possible to prevent hunting of the pressure valve 100 between a valve open state and a valve closed state against minute variations in the internal pressure in the heat pipe 301 (pressure inside the body 1 of the pressure valve 100). By so doing, stable heat recovery or stop of heat recovery is possible. In this embodiment, the first pressure Pl at which the pressure valve 100 enters a valve closed state is set in consideration of, for example, a pressure corresponding to a warm-up lβ temperature of the engine.
[0062] In addition, in the pressure valve 100 used in the exhaust heat recovery system 300 according to the present embodiment, the reverse plate 3 not only has the above described diaphragm portion 3a that regulates the recovery of heat between heat recovery and non-heat recovery but also has the rupture portion 3b (see FIG. 2A, FIG. 2B and FIG. 5). Thus, when the internal pressure in the heat pipe 301 reaches the release pressure Ps (pressure higher than or equal to the first pressure Pl and lower than 1 MPa), the rupture portion 3b ruptures to open the inside of the body 1 of the pressure valve 100, that is, the inside of the heat pipe 301, to the atmosphere. Thus, it is not necessary to take measures against High Pressure Gas Safety Act.
[0063] Here, the release pressure Ps of the pressure valve 100 has an upper limit of 1 MPa (Ps < 1 MPa) in order to comply with High Pressure Gas Safety Act, and is set at a pressure that makes it possible to prevent fatigue crack of the rupture portion 3b of the reverse plate 3 due to repeated load. Note that the lower limit of the release pressure Ps is, for example, set at twice or above of the upper limit value of the internal pressure in the heat pipe 301 (pressure inside the body 1 of the pressure valve 100) during normal times in consideration of preventing the above fatigue crack.
[0064] With the exhaust heat recovery system 300 according to the present embodiment, the pressure valve 100 having a pressure switch function implemented by reversal of the diaphragm portion 3a and a pressure release function implemented by the rupture portion 3b is provided at a condensed water reflux side of the condensing unit 303. Thus, in comparison with the case where a pressure valve and a relief valve are separately provided for the condensing unit 303, the size of the condensing unit 303 may be reduced. By so doing, the exhaust heat recovery system 300 may be easily mounted in an underfloor of a vehicle, an engine room, or the like, of which mounting space is limited.
[0065] Note that the exhaust heat recovery system 300 according to the present embodiment uses the pressure valve 100 shown in FIG. 1; instead, the exhaust heat recovery system 300 may use the pressure valve 200. [0066] In addition, in the above embodiments, the pressure valve 100 (or the pressure valve 200) having both pressure switch function and pressure release function is applied to a loop heat pipe-type exhaust heat recovery system. However, the aspect of the invention is not limited to this configuration, the pressure valve 100 (or the pressure valve 200) may be applied to another system (circuit).
[0067] The above pressure valve 100 (or the pressure valve 200) may be applied to a closed-type system (circuit) that needs to prevent an abnormal increase in pressure of a heat exchanger, such as a floor-type heat pump water heater, an air conditioner and a refrigerator. In addition, the above pressure valve 100 (or the pressure valve 200) may be applied for crisis management of an open-type system (circuit), such as an accumulator, a compressed-air cylinder and a large storage tank for natural gas, or the like.

Claims

CLAIMS:
1. A pressure valve comprising: a diaphragm portion that is actuated by fluid pressure; and a rupture portion that is provided concentrically with the diaphragm portion and that ruptures at a pressure higher than a pressure at which the diaphragm portion is actuated.
2. The pressure valve according to claim 1, wherein the rupture portion is provided on an outer peripheral side of the diaphragm portion.
3. The pressure valve according to claim 1, wherein the rupture portion is provided on an inner peripheral side of the diaphragm portion.
4. The pressure valve according to any one of claims 1 to 3, wherein the diaphragm portion and the rupture portion are provided for a single reverse plate.
5. The pressure valve according to any one of claims 1 to 4, wherein the rupture portion is a bent portion having a taper portion that slopes toward a side on which the fluid pressure acts, and the taper portion is reversed by the fluid pressure to cause the rupture portion to rupture.
6. An exhaust heat recovery system that recovers heat of exhaust gas from an internal combustion engine, and transfers the recovered heat to coolant of the internal combustion engine, comprising: the pressure valve according to any one of claims 1 to 4.
7. The exhaust heat recovery system according to claim 6, wherein the exhaust heat recovery system has a loop heat pipe that includes: an evaporating unit that evaporates a heating medium and filled inside the exhaust heat recovery system, by the heat of the exhaust gas from the internal combustion engine; a condensing unit that cools the heating medium, evaporated at the evaporating unit, by the coolant of the internal combustion engine; and a fluid communication unit that provides fluid communication between the evaporating unit and the condensing unit, and the pressure valve is provided for the condensing unit.
8. The exhaust heat recovery system according to claim 7, further comprising: a reflux passage that returns the heating medium, cooled at the condensing unit, to the evaporating unit through the pressure valve.
PCT/IB2009/007697 2008-12-10 2009-12-09 Pressure valve WO2010067182A1 (en)

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JP2008-314913 2008-12-10

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102401162A (en) * 2010-09-19 2012-04-04 上海华理安全装备有限公司 Temperature and pressure dual acting explosion-proof device
CN103759562A (en) * 2014-01-18 2014-04-30 门立山 One-way heat transfer valve
CN104806108A (en) * 2013-12-27 2015-07-29 拉蒂尔菲雅克公司 Emergency actuating device special for aircraft door
WO2017127645A1 (en) * 2016-01-20 2017-07-27 Fisher Controls International Llc Control regulator diaphragm assembly with integrated pressure relief

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3155271A (en) * 1963-07-05 1964-11-03 Calmec Mfg Corp Rupture disc mounting
GB1189186A (en) * 1967-10-24 1970-04-22 Karl Erb Pressure Relief Valve
EP1801531A1 (en) * 2005-12-20 2007-06-27 Denso Corporation Waste heat collecting apparatus
JP2008280894A (en) 2007-05-09 2008-11-20 Denso Corp Exhaust heat recovery system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3155271A (en) * 1963-07-05 1964-11-03 Calmec Mfg Corp Rupture disc mounting
GB1189186A (en) * 1967-10-24 1970-04-22 Karl Erb Pressure Relief Valve
EP1801531A1 (en) * 2005-12-20 2007-06-27 Denso Corporation Waste heat collecting apparatus
JP2008051479A (en) 2005-12-20 2008-03-06 Denso Corp Exhaust heat recovery device
JP2008280894A (en) 2007-05-09 2008-11-20 Denso Corp Exhaust heat recovery system

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102401162A (en) * 2010-09-19 2012-04-04 上海华理安全装备有限公司 Temperature and pressure dual acting explosion-proof device
CN104806108A (en) * 2013-12-27 2015-07-29 拉蒂尔菲雅克公司 Emergency actuating device special for aircraft door
US9695625B2 (en) 2013-12-27 2017-07-04 Ratier Figeac Device for emergency actuation especially intended for an aircraft opening
CN104806108B (en) * 2013-12-27 2018-11-13 拉蒂尔菲雅克公司 Particularly for the urgent actuation means of aircraft door
CN103759562A (en) * 2014-01-18 2014-04-30 门立山 One-way heat transfer valve
CN103759562B (en) * 2014-01-18 2015-06-10 门立山 One-way heat transfer valve
WO2017127645A1 (en) * 2016-01-20 2017-07-27 Fisher Controls International Llc Control regulator diaphragm assembly with integrated pressure relief
US10215297B2 (en) 2016-01-20 2019-02-26 Fisher Controls International Llc Control regulator diaphragm assembly with integrated pressure relief

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