US20060150650A1 - Expansion valve for refrigerating cycle - Google Patents

Expansion valve for refrigerating cycle Download PDF

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Publication number
US20060150650A1
US20060150650A1 US11/330,941 US33094106A US2006150650A1 US 20060150650 A1 US20060150650 A1 US 20060150650A1 US 33094106 A US33094106 A US 33094106A US 2006150650 A1 US2006150650 A1 US 2006150650A1
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United States
Prior art keywords
temperature
refrigerant
valve
refrigerating cycle
sensing portion
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Abandoned
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US11/330,941
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English (en)
Inventor
Yoshinori Murase
Yoshitaka Tomatsu
Nobuharu Kakehashi
Hiromi Ohta
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Denso Corp
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Denso Corp
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Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAKEHASHI, NOBUHARU, MURASE, YOSHINORI, OHTA, HIROMI, TOMATSU, YOSHITAKA
Publication of US20060150650A1 publication Critical patent/US20060150650A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/068—Expansion valves combined with a sensor
    • F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas

Definitions

  • the present invention relates to an expansion valve for a refrigerating cycle that controls a refrigerant on a radiator outlet side on the basis of a refrigerant temperature at the radiator (gas cooler) outlet side of a vapor-compression-type refrigerating cycle, and is especially suited to a supercritical refrigerating cycle that uses a refrigerant, such as carbon dioxide (CO 2 ) or the like, in a supercritical range.
  • a refrigerant such as carbon dioxide (CO 2 ) or the like
  • a vapor-compression-type refrigerating cycle that circulates CO 2 as a refrigerant in a closed circuit comprising a compressor 1 , a gas cooler (radiator) 2 , an expansion valve 3 , an evaporator 4 , an accumulator 5 , etc.
  • a pressure control valve as disclosed in JP-A-2000-193347 and JP-A-2003-254460 is known as a mechanical type expansion valve used in such a vapor compression type refrigerating cycle.
  • the pressure control valves disclosed in JP-A-2000-193347 and JP-A-2003-254460 control a refrigerant pressure at an outlet side of a radiator 2 by passing a refrigerant at an outlet of a radiator 2 in a casing 30 , which covers a valve member part, in which gases such as refrigerant or the like are charged in an enclosed space A formed on one side of a diaphragm 32 with the diaphragm therebetween, and a pressure of high pressure refrigerant before pressure reduction acts on the other side to displace the diaphragm 32 to make a valve member 31 move, and detecting a refrigerant in the enclosed space (temperature-sensing portion) A.
  • the pressure control valve of the conventional type involves a problem that the weight is increased to lead to an increase in cost as there is a need for the casing 33 that covers the enclosed space (temperature-sensing portion).
  • a pressure control valve expansion valve of a type in which the casing 30 is eliminated to achieve reduction in cost, an enclosed space is connected to a temperature-sensing cylinder 7 through a capillary tube 6 , the temperature-sensing cylinder 7 is provided in contact with a pipe at an outlet of a radiator 2 , and the temperature-sensing cylinder 7 detects a refrigerant temperature at the outlet of the radiator 2 , but this type of expansion valve involves a problem of an increase in cost as there is a need of a process of assembling the temperature-sensing cylinder 7 .
  • a high pressure control valve is arranged in an engine room in the case where the cycle is applied to a vehicular air conditioning apparatus. As the temperature in the engine room is higher than that of an outside air and a refrigerant cooled by a gas cooler does not flow to the control valve when the cycle is stopped, the control valve is heated to the ambient temperature in the engine room, which is higher than that of an outside air, and sometimes reaches 100° C. to 120° C.
  • the pressure in the temperature-sensing portion rapidly rises when an ambient temperature rises and the charged refrigerant is heated.
  • a maximum temperature in the engine room reaches 30 to 60° C. above a maximum temperature of the refrigerant at the gas cooler outlet. Therefore, the pressure in the temperature-sensing portion at the time of stoppage becomes higher than a maximum pressure of the CO 2 cycle, so that a very high pressure-resistance, above that for other high pressure parts, is demanded of the temperature-sensing portion.
  • the control valve when the control valve is heated to an ambient temperature in the engine room, the pressure in the temperature-sensing portion becomes higher than a normal high-pressure control pressure to bring about a valve-closed state at the startup of the CO 2 cycle. Therefore, cooling of the temperature-sensing portion is conventionally performed by circulating a small quantity of refrigerant through a bleed hole provided near the valve part and causing the refrigerant cooled by a gas cooler to flow to the control valve. Thereafter, the control valve is opened until temperature of the temperature-sensing portion is decreased and internal pressure of the temperature-sensing portion is decreased to a range of high-pressure control pressure, so that the refrigerant is increased in flow rate and a maximum cooling capacity is obtained. Accordingly, in order to reduce the time elapsed until the maximum cooling capacity is attained, that is, cool-down, it becomes important to quickly lower the internal pressure of the temperature-sensing portion to a normal control pressure.
  • a refrigerant in a temperature-sensing portion is put in a supercritical state as the temperature of a refrigerant at a gas cooler outlet, in which high pressure is attained, or an internal heat exchanger outlet is detected.
  • a refrigerant in a temperature-sensing portion is used in a gas-liquid two-phase and a refrigerant pressure is determined at a saturation temperature, that is, a liquid refrigerant temperature, so that pressure in the temperature-sensing portion is not affected by temperatures in other regions.
  • a refrigerant put in a supercritical state is affected by temperatures of those regions, which are communicated to and other than the temperature-sensing portion, to cause a problem that the internal pressure of the temperature-sensing portion is not determined and control pressure is varied.
  • the invention has been made in view of the above problems and has as its object to provide an expansion valve for a refrigerating cycle that does not need any casing and any temperature-sensing cylinder, can reduce the body dimensions and the weight of the whole valve and enables a reduction in cost.
  • a further object is to provide an expansion valve for a refrigerating cycle that can decrease the pressure-resistance of a temperature-sensing portion by optimizing control characteristics in the case where an internal heat exchanger is used in combination.
  • a still further object is to provide an expansion valve or a refrigerating cycle comprising an expansion valve which, when used in a supercritical cycle, decreases variation in control pressure and enables miniaturization of an expansion valve member.
  • the invention provides, as means for solving the problem, an expansion valve for a refrigerating cycle according to the respective claims.
  • An expansion valve for a refrigerating cycle is arranged in a refrigerant passage leading from a gas cooler to an evaporator in a vapor compression type refrigerating cycle, and comprises a temperature-sensing portion, inner pressure of which is varied according to the refrigerant temperature at the outlet side of the gas cooler, a valve member that mechanically interlocks with a change in internal pressure of the temperature-sensing portion to adjust an opening degree of the valve port, and a body that accommodates therein the valve member, and the body is provided with a flow passage, through which a refrigerant reduced in pressure by the valve member is led to the evaporator while the refrigerant temperature at the outlet side of the gas cooler is transmitted to the temperature-sensing portion, whereby it is possible to omit a casing that covers the temperature-sensing portion, or a capillary tube and a temperature-sensing cylinder, into which a refrigerant is introduced,
  • An expansion valve for a refrigerating cycle is applied to a vapor compression type refrigerating cycle provided with an internal heat exchanger, and arranged in a refrigerant passage leading from an internal heat exchanger to an evaporator, the expansion valve comprising a temperature-sensing portion, inner pressure of which is varied according to the refrigerant temperature at the outlet side of the gas cooler, a valve member that mechanically interlocks with a change in internal pressure of the temperature-sensing portion to adjust an opening degree of the valve port, and a body that accommodates therein the valve member, and wherein the body is provided with a first flow passage, through which a refrigerant flows to the internal heat exchanger, and a second flow passage, through which a refrigerant reduced in pressure by the valve member is led to the evaporator from the internal heat exchanger, while the refrigerant temperature at the outlet side of the gas cooler is transmitted to the temperature-sensing portion, whereby it is possible in the
  • An expansion valve for a refrigerating cycle is applied to a vapor compression type refrigerating cycle provided with an internal heat exchanger, and is arranged in a refrigerant passage leading from an internal heat exchanger to an evaporator, the expansion valve comprising a temperature-sensing portion, inner pressure of which is varied according to the refrigerant temperature at the outlet side of the internal heat exchanger, a valve member that mechanically interlocks with a change in internal pressure of the temperature-sensing portion to adjust an opening degree of the valve port, and a body that accommodates therein the valve member, and wherein the body is provided with a flow passage, through which a refrigerant reduced in pressure by the valve member flows to the evaporator while the refrigerant temperature at the outlet side of the internal heat exchanger is transmitted to the temperature-sensing portion.
  • the temperature-sensing portion can comprise a diaphragm, and a lid and a lower support member, which interpose therebetween a peripheral edge of the diaphragm from upper and lower directions to define an enclosed space above the diaphragm, and transmission of a refrigerant temperature to the temperature-sensing portion is performed by a clearance, which is formed by the valve member and the lower support member to be communicated to the refrigerant passage, whereby it is possible to transmit a refrigerant temperature to the temperature-sensing portion through the clearance and to omit a casing, or a capillary tube and a temperature-sensing cylinder.
  • the enclosed space of the temperature-sensing portion can be charged with a refrigerant and provided with an adjustment spring, which biases the valve member in a Salve closing direction, and a valve closing force provided by internal pressure in the temperature-sensing portion and the adjustment spring and a valve opening force provided by a refrigerant pressure balance to operate the valve member.
  • the enclosed space of the temperature-sensing portion can be charged with a mixed gas of a refrigerant and gases, which are lower in coefficient of thermal expansion than the refrigerant, and an adjustment spring, which biases the valve member in a valve closing direction, is omitted, whereby it is possible to simplify the construction and reduced the number of parts.
  • An expansion valve for a refrigerating cycle according to the fourth aspect of the present invention is one provided with an internal heat exchanger, and has a feature in that a density, at which a refrigerant is charged in the temperature-sensing portion, is 200 to 600 kg/m 3 in a valve closed state. Thereby, it is possible to optimize control characteristics when an internal heat exchanger is used, and to decrease pressure-resistance of the temperature-sensing body.
  • the density, at which a refrigerant is charged in the temperature-sensing portion can be 200 to 450 kg/m 3 in a valve closed state, whereby it is possible to further optimize control characteristics and to decrease pressure-resistance of the temperature-sensing body.
  • the valve member can be opened when high pressure at the outlet side of the gas cooler or at the outlet side of the internal heat exchanger becomes higher by a predetermined magnitude than inner pressure in the temperature-sensing portion.
  • a load corresponding to the predetermined magnitude can be given by an elastic member, or a non-condensed gas charged in the temperature-sensing portion together with a refrigerant, or the elastic member and the non-condensed gas.
  • the elastic member can be any one of a coil spring, a diaphragm, and a bellows, or an optional combination thereof.
  • the internal heat exchanger can heat a refrigerant sucked into a compressor so that superheat becomes 10° C. or higher.
  • An expansion valve for a refrigerating cycle is one that uses a refrigerant in a supercritical state, and comprises a temperature-sensing portion having a first enclosed space provided above a diaphragm and charged with a refrigerant, and a second enclosed space provided below the diaphragm to be communicated to the first enclosed space.
  • the second enclosed space can be provided inside a valve member fixed to the diaphragm.
  • the sum of a half of a volume of the first enclosed space and a volume of the second enclosed space can amount to 60% or more of the sum of a volume of the first enclosed space and the second enclosed space.
  • the expansion valve can further comprise a lid that covers a wall surface of the first enclosed space in contact with an outside air to provide an air layer between the wall surface and the outside air, and can lessen the influence of the temperature of the outside air.
  • At least a part of the wall surface of the first enclosed space in contact with an outside air can be covered by a thermal insulating material, and it is possible to further lessen the influence of temperature of the outside air.
  • FIG. 1 is a view illustrating a vapor compression type refrigerating cycle, in which CO 2 is circulated as a refrigerant;
  • FIG. 2 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a first embodiment of the invention, used in the refrigerating cycle illustrated in FIG. 1 ;
  • FIG. 3 is a view illustrating a vapor compression type refrigerating cycle including an internal heat exchanger
  • FIG. 4 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a second embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 3 ;
  • FIG. 5 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a third embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 3 ;
  • FIG. 6 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a fourth embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 1 or 3 ;
  • FIG. 7 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a fifth embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 3 ;
  • FIG. 8 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a sixth embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 1 or 3 ;
  • FIG. 9 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a seventh embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 1 or 3 ;
  • FIG. 10 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to an eighth embodiment of the invention, applied to the refrigerating cycle illustrated In FIG. 3 ;
  • FIG. 11 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a ninth embodiment of the invention, applied to the refrigerating cycle illustrated in FIG. 3 ;
  • FIG. 12 is a cross sectional view showing a conventional expansion valve for a refrigerating cycle (pressure control valve);
  • FIG. 13 is a view showing an improvement in COP in the case where an internal heat exchanger is used
  • FIG. 14 is a view showing control pressure, at which COP becomes maximum, versus a gas cooler outlet temperature when a refrigerant in an evaporator is 0° C.;
  • FIG. 15 is a view showing control pressure, at which COP becomes maximum, versus a gas cooler outlet temperature when a refrigerant in an evaporator is 20° C.;
  • FIG. 16 is a view showing a collier chart representative of physical properties Of CO 2 refrigerant
  • FIG. 17 is a view schematically showing effects at the time of cool-down
  • FIG. 18 is a view schematically showing a temperature-sensing cylinder corresponding portion of a temperature-sensing body and a portion except the portion;
  • FIG. 19 is a view (first) showing a change in control pressure versus a ratio of a temperature-sensing cylinder corresponding portion;
  • FIG. 20 is a view (second) showing a change in control pressure versus a ratio of a temperature-sensing cylinder corresponding portion
  • FIG. 21 is a view showing an embodiment obtained by providing a lid on a temperature-sensing portion of the ninth embodiment.
  • FIG. 1 is a view illustrating a vapor compression type refrigerating cycle (supercritical refrigerating cycle), in which CO 2 is circulated as a refrigerant
  • FIG. 2 is a cross sectional view showing an expansion valve for a refrigerating cycle, according to a first embodiment of the invention, applied to the vapor compression type refrigerating cycle illustrated in FIG. 1 .
  • the reference numeral 1 denotes a compressor that sucks and compresses a refrigerant (CO 2 ), and 2 a gas cooler (radiator) that cools the refrigerant compressed by the compressor 1 .
  • An expansion valve 3 is arranged on an outlet side of the gas cooler 2 to control a refrigerant pressure at the outlet side of the gas cooler 2 on the basis of a refrigerant temperature at the outlet side of the gas cooler 2 , the expansion valve also functioning as a decompressor that decompresses a refrigerant at high pressure.
  • a temperature-sensing cylinder 7 is mounted on an outlet-side pipe of the gas cooler 2 and connected to the expansion valve 3 through a capillary tube 6 . Accordingly, a valve opening degree of the expansion valve 3 is controlled according to the change in internal pressure, which is based on a refrigerant temperature of gases charged in the temperature-sensing cylinder 7 .
  • the reference numeral 4 denotes an evaporator that evaporates a gas-liquid two-phase refrigerant decreased in pressure by the expansion valve 3 , and 5 an accumulator that separates a gaseous phase refrigerant and a liquid phase refrigerant from each other and temporarily accumulates a surplus refrigerant in the refrigerating cycle.
  • the compressor 1 , the gas cooler 2 , the expansion valve 3 , the evaporator 4 , and the accumulator 5 are connected together by means of piping to form a closed circuit.
  • an expansion valve for a refrigerating cycle 3 A will be described with reference to FIG. 2 .
  • Formed in a body 33 of the expansion valve 3 A is a part of a refrigerant low passage leading from the gas cooler 2 to the evaporator 4 via a valve port 33 a.
  • Formed in the body 33 are an inflow port 33 b connected to a side of the gas cooler 2 , an outflow port 33 c connected to a side of the evaporator 4 , a first opening 33 d, to which a temperature-sensing portion described later is mounted, and a second opening 33 e, in which an adjustment spring 36 is set.
  • a valve member 31 is received in the body 33 to open and close the valve port 33 a whereby an upstream space C 1 connected to an outlet side of the gas cooler 2 and a downstream space C 2 connected to an inlet side of the evaporator 4 , which spaces are disposed in the body 33 , are put into communication and non-communication to each other.
  • the temperature-sensing portion is mounted to the first opening 33 d of the body 33 .
  • the temperature-sensing portion mainly comprises the diaphragm 32 , a lid 35 , and a lower support member 34 , and is formed therein with an enclosed space A. That is, a concave portion 35 a is formed centrally of the lid 35 to define the enclosed space A, and the lid 35 and the lower support member 34 interpose and secure a peripheral edge of the diaphragm 32 therebetween to form the temperature-sensing portion.
  • the diaphragm 32 is in the form of a thin film made of a stainless steel material to be deformed and displaced according to a pressure difference inside and outside the enclosed space A.
  • the lower support member 34 comprises a cylindrical portion 34 a and a flange portion 34 b, and a threaded portion formed on an outer periphery of the cylindrical portion 34 a is threaded into the first opening 33 d of the body 33 to mount the temperature-sensing portion to the body 33 .
  • a charge pipe 35 b is mounted to the lid 35 and a refrigerant is charged into the enclosed space A through the charge pipe 35 b. After the refrigerant is charged, the charge pipe 35 b is sealed.
  • One end 31 b of the valve member 31 extending upwardly, of a valve portion 31 a through the cylindrical portion 34 a of the lower support member 34 is fixed to the diaphragm 32 , and a clearance B having an annular-shaped cross section is formed between an inner surface of the cylindrical portion 34 a and an outer peripheral surface of the valve member 31 .
  • the clearance B is communicated to an upstream space C 1 connected to the outlet side of the gas cooler 2 . Accordingly, a refrigerant on the outlet side of the gas cooler 2 flows into the clearance B, so that a refrigerant temperature is transmitted to a refrigerant in the enclosed space A and at the same time pressure of the refrigerant on the outlet side of the gas cooler 2 acts on the diaphragm 32 .
  • an adjustment nut 37 is threaded onto the other end 31 c of the valve member 31 extending downwardly of the valve portion 31 a through the valve port 33 a.
  • the adjustment spring 36 that biases the valve member 31 in a valve closing direction is interposed between a neighborhood of an underside of the valve port 33 a and the adjustment nut 37 , and an initial set load (an elastic force in a state, in which the valve port 33 a is closed) of the adjustment spring 36 can be optionally adjusted by rotating the adjustment nut 37 .
  • the adjustment spring 36 , the adjustment nut 37 , etc. are provided in the downstream space C 2 connected to the inlet side of the evaporator 4 .
  • a cap 38 is fitted into the second opening 33 e of the body 33 whereby a lower part of the downstream space C 2 is closed.
  • a valve closing force of the valve member 31 is provided by inner pressure in the enclosed space A and the adjustment spring 36
  • a valve opening force of the valve member 31 is provided by a refrigerant pressure at the outlet side of the gas cooler 2
  • balance of the both forces affords opening and closing the expansion valve 3 A.
  • the inner pressure in the enclosed space A is varied depending upon temperature of that refrigerant on the outlet side of the gas cooler 2 , which flows into the clearance B, whereby the valve port 33 a is varied in opening degree to control the refrigerant pressure at the outlet side of the gas cooler 2 .
  • FIG. 3 is a view illustrating a vapor compression type refrigerating cycle, in which an internal heat exchanger is incorporated.
  • the vapor compression type refrigerating cycle including an internal heat exchanger is a conventionally known refrigerating cycle to improve a cooling capacity.
  • an internal heat exchanger 8 is arranged in the cycle as shown in FIG. 3 so as to make heat exchange between a refrigerant going to the expansion valve 3 from the gas cooler 2 and a refrigerant returning to the compressor 1 from the accumulator 5 .
  • the evaporator valve 3 is arranged in a refrigerant passage leading from the internal heat exchanger 8 to the evaporator 4 .
  • the remaining construction is the same as the vapor compression type refrigerating cycle illustrated in FIG. 1 and so an explanation therefor is omitted.
  • the refrigerating cycle according to the invention is also applicable to a vapor compression type refrigerating cycle including such an internal heat exchanger.
  • FIG. 4 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 B, according to a second embodiment, applied to a vapor compression type refrigerating cycle including an internal heat exchanger.
  • a first flow passage D making a part of a refrigerant flow passage leading from a gas cooler 2 to an internal heat exchanger 8 and a second flow passage E making a part of a refrigerant flow passage leading from the internal heat exchanger 8 to an evaporator 4 via a valve port 33 a, respectively, are formed independently in a body 33 of the expansion valve 3 B according to the second embodiment.
  • a clearance B through which a refrigerant temperature at an outlet side of the gas cooler 2 is transmitted to a refrigerant in an enclosed space A of a temperature-sensing portion, is provided on a side of the first flow passage D, and a valve portion 31 a of a valve member 31 , which opens and closes the valve port 33 a, is provided on a side of the second flow passage E.
  • one end 31 b of the valve member 31 extending upwardly of a valve portion 31 a across the first flow passage D and through a cylindrical portion 34 a of a lower support member 34 is fixed to a diaphragm 32 , and a clearance B having an annular-shaped cross section is provided between an inner surface of the cylindrical portion 34 a and an outer peripheral surface of the valve member 31 .
  • the clearance E is communicated to the first flow passage D connected to the outlet side of the gas cooler 2 .
  • a refrigerant on the outlet side of the gas cooler 2 flows into the clearance B, so that the refrigerant temperature is transmitted to a refrigerant in the enclosed space A and at the same time pressure of the refrigerant on the outlet side of the gas cooler 2 acts on the diaphragm 32 .
  • a valve port 33 a providing for communication between the internal heat exchanger 8 and the evaporator 4 is provided in the second flow passage E. Accordingly, the valve portion 31 a of the valve member 31 , which opens and closes the valve port 33 a, an adjustment spring 36 provided on the other end 31 c of the valve member 31 extending downward through the valve port 33 a, an adjustment nut 37 , etc. are provided in the second flow passage E.
  • the remaining detailed construction is the same as that of the first embodiment and so an explanation therefor is omitted.
  • FIG. 5 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 C, according to a third embodiment, applied to a vapor compression type refrigerating cycle including an internal heat exchanger.
  • a part of a refrigerant flow passage leading from an internal heat exchanger 8 to an evaporator 4 via a valve port 33 a is formed in a body 33 of the expansion valve 3 C. That is, the remaining construction is the same as that of the expansion valve 3 A of the first embodiment except that an inflow port 33 b of the body 33 is connected to the internal heat exchanger 8 in place of a gas cooler 2 .
  • a refrigerant on an outlet side of the internal heat exchanger 8 flows into a clearance B, so that a refrigerant temperature at the outlet side of the internal heat exchanger 8 is transmitted to a refrigerant charged in an enclosed space A of a temperature-sensing portion.
  • a refrigerant pressure at the outlet side of the internal heat exchanger 8 acts on a diaphragm 32 .
  • FIG. 6 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 D, according to a fourth embodiment, applied to the vapor compression type refrigerating cycle illustrated in FIG. 1 or FIG. 3 .
  • the fourth embodiment in place of the adjustment spring 36 , for example, nitrogen gases (N 2 ), helium gases (He), etc., which are lower in the coefficient of thermal expansion than a refrigerant, together with the refrigerant are charged in an enclosed space A in the expansion valve according to the first embodiment in FIG. 2 or in the expansion valve according to the third embodiment in FIG. 5 .
  • a refrigerant and gases which are lower in coefficient of thermal expansion than the refrigerant, are charged in the enclosed space A of the temperature-sensing portion, a second opening 33 e of a body 33 is closed, and a portion extending downwardly of a valve portion 31 a of a valve member 31 , an adjustment spring 36 , an adjustment nut 37 , etc. are removed.
  • the remaining construction is the same as that of the first embodiment or the third embodiment and so an explanation therefor is omitted.
  • a refrigerant is carbon dioxide (CO 2 ) and the gas being mixed are nitrogen gas (N 2 )
  • CO 2 carbon dioxide
  • N 2 nitrogen gas
  • FIG. 7 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 E, according to a fifth embodiment, applied to a vapor compression type refrigerating cycle including the internal heat exchanger shown in FIG. 3 .
  • the fifth embodiment as in the fourth embodiment, in place of the adjustment spring 36 , for example, nitrogen gas (N 2 ) helium gas (He), etc., which are lower in the coefficient of thermal expansion than a refrigerant, together with the refrigerant are charged in an enclosed space A in the expansion valve 3 B according to the second embodiment.
  • N 2 nitrogen gas
  • He helium gas
  • a mixed gas of a refrigerant and gases which are lower in coefficient of thermal expansion than the refrigerant, are charged in an enclosed space A of a temperature-sensing portion, a second opening 33 e of a body 33 is closed, and a portion extending downwardly of a valve portion 31 a of a valve member 31 , an adjustment spring 36 , an adjustment nut 37 , etc. are removed from a second flow passage E.
  • the remaining construction is the same as that of the second embodiment and so an explanation therefor is omitted.
  • a refrigerant is carbon dioxide (CO 2 ) and the gases being mixed are nitrogen gas (N 2 )
  • CO 2 carbon dioxide
  • N 2 nitrogen gases
  • FIG. 8 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 F, according to a sixth embodiment of the invention, applied to the refrigerating cycle shown in FIG. 1 or FIG. 3 .
  • a cavity 31 d communicated to an enclosed space A of a temperature-sensing portion is formed in the valve member 31 of the expansion valve 3 according to the first embodiment in FIG. 2 or according to the third embodiment in FIG. 5 .
  • the enclosed space of the temperature-sensing portion can comprise the sum of (the enclosed space A+the cavity 31 d +the charge pipe 35 b ), and the enclosed space charged with a refrigerant can be enlarged, so that it is possible to improve the temperature-sensing portion in accuracy.
  • the remaining construction is the same as that of the first embodiment or the third embodiment and so an explanation therefor is omitted.
  • FIG. 9 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 G, according to a seventh embodiment of the invention, applied to the refrigerating cycle shown in FIG. 1 or FIG. 3 .
  • a cavity 31 d communicated to an enclosed space A of a temperature-sensing portion is formed in the valve member 31 of the expansion valve 3 according to the fourth embodiment in FIG. 6 .
  • the enclosed space of the temperature-sensing portion can be further increased by a volume of the cavity 31 d, so that it is possible to improve the temperature-sensing portion in accuracy.
  • the remaining construction is the same as that of the fourth embodiment and so an explanation therefor is omitted.
  • FIG. 10 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 H, according to an eighth embodiment of the invention, applied to the refrigerating cycle shown in FIG. 3 .
  • a cavity 31 d communicated to an enclosed space A of a temperature-sensing portion is formed in the valve member 31 of the expansion valve 3 according to the fifth embodiment in FIG. 7 .
  • the enclosed space of the temperature-sensing portion can be further increased by a volume of the cavity 31 d, so that it is possible to improve the temperature-sensing portion, in accuracy.
  • the remaining construction is the same as that of the fifth embodiment and so an explanation therefor is omitted.
  • FIG. 11 is a cross sectional view showing an expansion valve for a refrigerating cycle 3 I, according to a ninth embodiment of the invention, applied to the refrigerating cycle shown an FIG. 3 .
  • a cavity 31 d communicated to an enclosed space A of a temperature-sensing portion is formed in the valve member 31 of the expansion valve 3 according to the second embodiment in FIG. 4 .
  • the enclosed space of the temperature-sensing portion can be further increased by a volume of the cavity 31 d, so that it is possible to improve the temperature-sensing portion, in accuracy.
  • the remaining construction is the same as that of the second embodiment and so an explanation therefor is omitted.
  • the expansion valve for a refrigerating cycle is not limited thereto but is also applicable to a vapor compression type refrigerating cycle, in which the refrigerant is fluorocarbon or the like, not to mention a vapor compression type refrigerating cycle, in which a refrigerant, such as ethylene, ethane, nitrogen oxide, etc., used in a supercritical zone, is used.
  • the expansion valve according to the embodiment is intended for firstly, improving COP of a refrigerating cycle including an internal heat exchanger, secondly, enabling decreasing the pressure-resistance of a temperature-sensing portion to achieve reduction in cost, and thirdly, accelerating the cool-down. Therefore, the embodiment prescribes the density at which a refrigerant is charged in a temperature-sensing portion.
  • FIG. 13 shows effects of an improvement in COP in the case where an internal heat exchanger is used to provide for superheat in a sucked refrigerant.
  • TS in the figure indicates a refrigerant evaporating temperature in an evaporator. Accordingly, the higher a refrigerant temperature in an evaporator, the higher an improvement in COP.
  • a compressor In a vehicular air conditioner, a compressor is decreased in rotating speed at the time of idling and a cooling capacity becomes minimum.
  • COP of a vehicular air conditioner is enhanced when an internal heat exchanger is used. In this manner, the use of an internal heat exchanger in a vehicular air conditioner produces a great advantage.
  • FIGS. 14 and 15 show high pressure control pressures, at which COP becomes a maximum, relative to a gas cooler outlet refrigerant temperature in the case where a refrigerant temperature in an evaporator is 0° C. and in the case where a refrigerant temperature in an evaporator is 20° C., and show characteristics that in the case where an internal heat exchanger is used to heat a compressor sucked refrigerant, the lower control pressure in case of possessing superheat, the higher a refrigerant evaporating temperature in an evaporator and the higher a gas cooler outlet refrigerant temperature.
  • COP assumes a maximum value when a refrigerant temperature at a gas cooler outlet is 60° C. and control pressure is 15 MPa.
  • a charging density a charged refrigerant density
  • COP Since COP is improved when an internal heat exchanger having a large heat exchanging capacity is used, it is conceivable to increase a quantity of superheat further. As a discharge temperature also rises when a sucked refrigerant temperature of a compressor becomes high, however, a quantity of superheat is preferred to be in the range of 15 to 25° C. In case of adopting a quantity of superheat in the range of 15 to 25° C., COP becomes maximum in the case where control pressure is made 14.2 MPa, for example, when a gas cooler outlet refrigerant temperature is 60° C. In order to make a control pressure attain 14.2 MPa, it is necessary to adopt a charging density in the order of about 570 kg/m 3 .
  • density, at which a refrigerant is charged in a temperature-sensing portion of an expansion valve is desirably low in terms of pressure-resistance of the expansion valve described later
  • inner pressure in the temperature-sensing portion is set low by about 2 MPa by further using in combination a spring for biasing the valve in a valve closing direction whereby control pressure, at which COP becomes maximum, can be ensured even in a charging density in the order of about 450 kg/m 3 when a gas cooler outlet refrigerant temperature is 60° C.
  • a maximum allowable pressure of high-pressure parts is set to about 18 MPa
  • an upper limit of pressure in a temperature-sensing portion is made in the same order as the pressure to eliminate the need of excessively heightening only the temperature-sensing portion in strength to enable making the same equal to other high-pressure parts in strength, thus enabling providing a control valise at low cost.
  • a temperature-sensing portion charging density be set to at most about 550 kg/m 3 when a maximum ambient temperature is 80° C., at most about 450 kg/m 3 when a maximum ambient temperature is 100° C., and at most about 360 kg/m 3 when a maximum ambient temperature is 120° C.
  • the charging density be set to at most 450 kg/m 3 since 100° C. at the highest must be taken account of even when a position of low temperature is selected as a mount position in an engine room.
  • a charging density for an intended control pressure can be reduced by a quantity corresponding to a spring load by giving a load in a direction of closure with the use of a spring or the line, it is effective to use the spring or the like in combination.
  • control pressure for a gas cooler outlet refrigerant temperature is decreased but the control pressure, at which COP becomes maximum, is also decreased in case of using an internal heat exchanger, so that the use of the internal heat exchanger makes it possible to decrease that density, at which a refrigerant is charged in a temperature-sensing portion of an expansion valve, without decreasing COP.
  • the temperature-sensing portion charging density is desirably 200 kg/m 3 or higher.
  • cooling of a temperature-sensing portion is performed by circulating a small quantity of refrigerant through a bleed hole provided near a valve part and causing the refrigerant cooled by a gas cooler to flow to a control valve, and the control valve is opened when the temperature-sensing portion is decreased in temperature and internal pressure of the temperature-sensing portion is decreased to a range of high-pressure control pressure. Accordingly, in order to accelerate cool-down, it becomes important to quickly lower the internal pressure of the temperature-sensing portion to a normal range of control pressure.
  • FIG. 17 schematically shows effects at the time of cool-down.
  • a refrigerating cycle When a refrigerating cycle is stopped, an expansion valve in an engine room is heated to high temperature, for example, about 80° C.
  • the valve When the refrigerating cycle is started in this state, the valve is closed because the internal pressure of a temperature-sensing portion exceeds an upper limit pressure (in this case, 13 MPa) in operation of the cycle. Therefore, a small quantity of refrigerant cooled by a gas cooler flows through a bleed hole provided near a valve part to cool the temperature-sensing portion.
  • a compressor is varied in capacity so as not to exceed the upper limit pressure in operation, thus controlling high pressure.
  • the valve When the temperature-sensing portion is decreased in temperature and the internal pressure thereof becomes equal to or lower than the upper limit pressure in operation, the valve is opened and the compressor becomes maximum in capacity, so that the refrigerant is increased in flow rate and a maximum cooling capacity is demonstrated.
  • the above is taken into consideration and an optimum value of a temperature-sensing portion charging density in a refrigerating cycle, in which an internal heat exchanger is used, is prescribed in the following manner.
  • that density, at which a refrigerant is charged into the enclosed space A of the temperature-sensing portion of the expansion valve 3 I is set in the range of about 200 kg/m 3 to about 600 kg/m 3 .
  • an upper limit value of the range of charging density may be made in the order of about 570 kg/m 3
  • the charging density can be made in the order of about 450 kg/m 3 .
  • that density, at which a refrigerant is charged into the temperature-sensing portion of the expansion valve is set in the range of about 200 kg/m 3 to about 450 kg/m 3 .
  • the expansion valve 3 H used in a refrigerating cycle in which the internal heat exchanger according to the seventh embodiment and illustrated with reference to FIG. 10 is used, the expansion valve being provided with no adjustment spring, it is preferable to adopt a charged refrigerant density being the same as that described above. That is, that density, at which a refrigerant is charged into the enclosed space A of the temperature-sensing portion of the expansion valve 3 H and the cavity 31 d, is set in the range of about 200 kg/m 3 to about 600 kg/m 3 .
  • an upper limit value in the range of charging density may be made in the order of about 570 kg/m 3 and, further, in the case where an elastic member for biasing in a valve closing direction is used in combination, the charging density can be in the order of about 450 kg/m 3 . More desirably, that density, at which a refrigerant is charged into the temperature-sensing portion of the expansion valve, is set in the range of about 200 kg/m 3 to about 450 kg/m 3 .
  • a refrigerating cycle in which the internal heat exchanger according to the second, third, and fifth embodiments ( FIGS. 4, 5 , and 7 ) is provided, and a refrigerating cycle, in which the internal heat exchanger according to the fourth, sixth, and seventh embodiments ( FIGS. 6, 8 , 9 ) is provided, that density, at which a refrigerant is charged into the temperature-sensing portion of the expansion valve, is set in the range of about 200 kg/m 3 to about 600 kg/m 3 .
  • an upper limit value in the range of charging density may be in the order of about 570 kg/m 3 and, further, in the case where an elastic member for biasing in a valve closing direction is used in combination, the charging density can be made in the order of about 450 kg/m 3 . More desirably, that density, at which a refrigerant is charged into the temperature-sensing portion of the expansion valve, is set in the range of about 200 kg/m 3 to about 450 kg/m 3 .
  • the cavity 31 a being an enclosed space is formed below the diaphragm so as to be communicated to the enclosed space A of the temperature-sensing portion formed above the diaphragm 32 . Consequently, the enclosed space of the temperature-sensing portion is enlarged to the enclosed space A+the cavity 31 d from a conventional enclosed space A.
  • the charge pipe 35 b is separated from the enclosed space in the foregoing explanation, it is included in the enclosed space A in this case. Accordingly, it can be said that the temperature-sensing portion according to the sixth to ninth embodiments comprises the enclosed space A and the cavity 31 d.
  • the cavity 31 d increases a volume of the enclosed space, in which a refrigerant is charged, and improves the temperature-sensing portion in accuracy.
  • the enclosed space A is a flat space formed above the diaphragm, temperature of a refrigerant is transmitted to the enclosed space through the diaphragm, and an outer wall of the enclosed space A contacts with an outside air to be susceptible to influences of an outside air temperature. Accordingly, it can be said in the construction of the temperature-sensing portion that, the portion to which temperature of a refrigerant is transmitted and which is heated, that is, the cavity 31 d below the diaphragm and a lower half of the enclosed space A in contact with the diaphragm correspond to a temperature-sensing cylinder, and an upper half of the enclosed space A susceptible to influences of an outside air temperature, corresponds to another portion different from the temperature-sensing cylinder. Accordingly, by attaching an insulating material to the outer wall portion, temperature variation of the upper half of the enclosed space A is lessened to enable ensuring a minimum temperature-sensing volume.
  • a ratio of the portion (here, the lower half of the enclosed space A and the cavity 31 d ) corresponding to the temperature-sensing cylinder to the whole temperature-sensing portion is prescribed to lessen variation in control pressure.
  • FIG. 18 schematically shows a temperature-sensing cylinder corresponding portion P and another portion Q.
  • FIG. 19 shows temperature effects of the portion Q versus a ratio of the portion P to a whole volume, that is, a volume ratio of a direct temperature-sensing portion P/(P+Q) for the temperature-sensing cylinder corresponding portion P and another portion Q in the case where the charged refrigerant density assumes a standard value of 450 kg/m 3 and temperature of the portion P is 60° C.
  • Temperature of the portion Q is 65° C., 70° C., and 80° C.
  • a target control pressure is one in the case where temperature of the portion Q is 60° C. to be the same as that of the portion P.
  • the portion P is at 60° C.
  • the portion Q is at 60° C.
  • a volumetric ratio of the portion P is 50% (the ratio of 0.5)
  • the refrigerant density at the portion P is 538 kg/m 3
  • the refrigerant density at the portion Q is 362 kg/m 3
  • internal pressures of the both balance at 13.51 MPa and an average density is 450 kg/m 3 .
  • a point S indicates pressures balance at the respective temperatures and the volumetric ratio.
  • control pressure for the expansion valve is varied by an ambient temperature in the engine room being affected by temperature of other portions than the temperature-sensing cylinder corresponding portion. Accordingly, it is necessary to lessen influences of temperature of other portions than the temperature-sensing cylinder corresponding portion.
  • the volumetric ratio of the temperature-sensing cylinder corresponding portion is ensured, which amounts to a predetermined magnitude or more.
  • an insulating material may be attached to the other portion than the temperature-sensing cylinder corresponding portion to prevent heating due to an ambient temperature.
  • the variation in pressure it is necessary to make the variation equal to or less than about 0.5 MPa in order to make the same in the order of dispersion in a pressure sensor or the like, and assuming that a maximum temperature of a gas cooler outlet refrigerant is 60° C. and temperature in the engine room is 80 to 100° C., the outer wall portion above the diaphragm rises 5 to 6° C. in temperature even in the case where an insulating material is attached thereto. Accordingly, in order to rake the variation equal to or less than about 0.5 MPa, it suffices to ensure a volume of at least 50% at the minimum for the volumetric ratio of the temperature-sensing cylinder corresponding portion as seen from FIG. 19 .
  • the control pressure is low so that there is a margin for an upper limit pressure in the cycle. Since a temperature difference between the refrigerant temperature and an ambient temperature becomes large, the influence of the ambient temperature becomes large.
  • FIG. 20 shows effects of temperature of the portion Q (other than the temperature-sensing cylinder corresponding portion) due to an ambient temperature in the case where a refrigerant temperature is 40° C. 50° C., 60° C., 80° C., and 100° C. are shown for temperature of the portion Q.
  • a target control pressure is attained when temperature of the portion except the temperature-sensing portion is 40° C. While for example, when a refrigerant temperature is 40° C., temperature of the outer wall rises about 10° C. to attain 50° C.
  • the volumetric ratio of the temperature-sensing cylinder equal to or more than 60% in order to make variation in high pressure equal to 0.5 MPa.
  • volumetric ratio when the volumetric ratio is made equal to or more than 70%, variation in control pressure can be made equal to about 0.5 MPa even when an insulating material is omitted for the portion except the temperature-sensing cylinder corresponding portion.
  • the volumetric ratio of the temperature-sensing cylinder corresponding portion to the enclosed space is made equal to or more than 60%.
  • volumetric ratio in the embodiment is represented by the following formula ( Vu ⁇ 0.5+ Vb )/( Vu ⁇ Vb )>0.6 where Vu indicates a volume of the enclosed space above the diaphragm and Vb indicates a volume of the enclosed space below the diaphragm.
  • the expansion valve 3 G used in a refrigerating cycle with no internal heat exchanger, illustrated with reference to FIG. 9 is formed such that the volumetric sum of 1 ⁇ 2 of the enclosed space A (including the charge pipe 35 b ) and the cavity 31 d amounts to at least 60% of the volumetric sum of the enclosed space A (including the charge pipe 35 b ) and the cavity 31 .
  • the embodiment is directed to an expansion valve used in a refrigerating cycle with no internal heat exchanger, it may be applied to a refrigerating cycle with an internal heat exchanger.
  • the expansion valve, according to the sixth, eighth, and ninth embodiments illustrated with reference to FIGS. 8, 10 , 11 can also be formed such that the volumetric sum of 1 ⁇ 2 of the enclosed space A (including the charge pipe 35 b ) and the cavity 31 amounts to at least 60% of the volumetric sum of the enclosed space A (including the charge pipe 35 b ) and the cavity 31 d.
  • variation in control pressure can be suppressed in the expansion valve 31 , according to the ninth embodiment, shown in FIG. 11 by providing a lid 39 , which covers the cuter wall of the temperature-sensing portion and the charge pipe 35 b, and forming an air layer between the outer wall of the temperature-sensing portion and an outside air to thermally insulate a portion except the temperature-sensing cylinder corresponding portion of the temperature-sensing portion.
  • a refrigerant temperature is transmitted to an interior of the enclosed space A through the clearance B, it is possible to omit a casing or a capillary tube and a temperature-sensing cylinder, which are used in the related art, and to achieve miniaturization and lightening of an expansion valve and reduction in cost.
  • gases which are charged in an enclosed space, of mixed gas of a refrigerant and gases which are lower in the coefficient of thermal expansion than the refrigerant, it is possible to omit an adjustment spring or the like and to further simplify an expansion valve.
  • the density, at which a refrigerant is charged into a temperature-sensing body it is possible to optimize control characteristics when an internal heat exchanger is used, and to decrease pressure-resistance of the temperature-sensing body. Further, as a ratio of a temperature-sensing body to a whole temperature-sensing cylinder corresponding portion is prescribed, it is possible to lessen the partial influences of temperature of the temperature-sensing body.

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  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
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US20070227165A1 (en) * 2006-03-31 2007-10-04 Denso Corporation Supercritical cycle and expansion valve used for refrigeration cycle
US20080011363A1 (en) * 2006-07-13 2008-01-17 Denso Corporation Pressure Control Valve
US20080251742A1 (en) * 2005-02-24 2008-10-16 Sadatake Ise Pressure Control Valve
USRE42908E1 (en) * 2003-03-05 2011-11-15 Denso Corporation Vapor-compression-type refrigerating machine
US20120297804A1 (en) * 2010-02-12 2012-11-29 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US10330214B2 (en) * 2016-09-02 2019-06-25 Fujikoki Corporation Control valve

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JP2007139208A (ja) 2005-11-14 2007-06-07 Denso Corp 冷凍サイクル用膨張弁
JP5754627B2 (ja) * 2011-04-25 2015-07-29 株式会社大気社 流体冷却方法、及び、流体冷却装置
CN102809253B (zh) * 2011-05-31 2015-06-24 郑州大学 两相流膨胀机
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