EP0846927B1 - Thermal type expansion valve - Google Patents

Thermal type expansion valve Download PDF

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Publication number
EP0846927B1
EP0846927B1 EP96119717A EP96119717A EP0846927B1 EP 0846927 B1 EP0846927 B1 EP 0846927B1 EP 96119717 A EP96119717 A EP 96119717A EP 96119717 A EP96119717 A EP 96119717A EP 0846927 B1 EP0846927 B1 EP 0846927B1
Authority
EP
European Patent Office
Prior art keywords
passage
expansion valve
refrigerant
valve
diaphragm
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP96119717A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0846927A1 (en
Inventor
Satoru Okada
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pacific Industrial Co Ltd
Original Assignee
Pacific Industrial Co Ltd
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 JP08122435A priority Critical patent/JP3130246B2/ja
Application filed by Pacific Industrial Co Ltd filed Critical Pacific Industrial Co Ltd
Priority to DE1996607846 priority patent/DE69607846T2/de
Priority to EP96119717A priority patent/EP0846927B1/en
Publication of EP0846927A1 publication Critical patent/EP0846927A1/en
Application granted granted Critical
Publication of EP0846927B1 publication Critical patent/EP0846927B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/05—Cost reduction
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
    • F25B2500/221—Preventing leaks from developing

Definitions

  • the present invention relates to a thermal type expansion valve for a refrigerating circuit of an air-conditioning apparatus, and more particularly, to a thermal type expansion valve that adjusts the flow rate of refrigerant conveyed to an evaporator in accordance with the temperature of the refrigerant discharged from the evaporator toward a compressor.
  • US-A-4,819,443 discloses a two-piece expansion valve consisting of a housing body made of resin including a metallic cartridge.
  • the valve is assembled by merely inserting the metallic cartridge into the body and the cartridge apparently operates as the factual expansion valve means without the body which only serves as a housing therefor.
  • the cartridge itself consists of an own (metallic) body in which the several design elements of the expansion valve are located. Therefore, the metallic cartridge of this state of the art forms, in fact, the means which operate as the expansion valve without requiring the housing body for this function.
  • the cartridge which forms the factual valve body housing the several expansion valve means is made of metal, the thermal conductivity of such body is high.
  • EP-A-0,736,737 describes a further type of a known expansion valve with a pressure-operating housing comprising a plug member that can be reliably established only by projection welding and which is free from corrosion of the housing.
  • FIG. 4 A cross-sectional view of a prior art thermal type expansion valve very similar to that of EP-A-0 718 569, which is installed in a refrigerating circuit of an automobile air-conditioning apparatus, is illustrated in Fig. 4.
  • the air-conditioning apparatus includes a compressor 1, a condenser 2, a receiver 3, the expansion valve 4, and an evaporator 5.
  • the compressor 1 which is operably connected to an engine by an electromagnetic clutch (not shown) and driven by the rotational force of the engine, compresses gasified refrigerant sent from the evaporator 5.
  • the condenser 2 then condenses the high temperature, high pressure refrigerant gas through heat exchange with air from outside the automobile and liquefies the refrigerant.
  • the receiver 3 receives and temporarily reserves the liquefied refrigerant cooled by the condenser 2 and incorporates a drier (not shown) to remove moisture and particulate matter from the refrigerant.
  • the expansion valve 4 expands the liquefied refrigerant sent from the receiver 3. This lowers the temperature and pressure of the refrigerant and atomizes the refrigerant.
  • the atomized refrigerant from the expansion valve is vaporized by the evaporator 5 through heat exchange with air sent into a passenger compartment of the automobile.
  • the prior art expansion valve 4 includes a metal main body 6 having a rectangular parallelopiped shape.
  • the main body 6 is provided with a first passage 7, which is connected with the outlet of the condenser 2 via the receiver 3, a second passage 8, which is connected to the inlet of the evaporator 5, and a third passage 9, which connects the outlet of the evaporator 5 with the inlet of the compressor 1.
  • a restricting mechanism 13 is arranged inside the first passage 7.
  • the restricting mechanism 13 includes an orifice 25, a valve member 27, and a coil spring 29.
  • the orifice 25 is formed in the main body 6 to connect the first passage 7 with the second passage 8.
  • the inlet of the orifice 25 is located in the first passage 7.
  • a valve seat 26 is defined on the area surrounding the inlet.
  • the valve member 27 is urged toward the valve seat 26 by the coil spring 29. The valve member 27 closes the orifice 25 when it abuts against the valve seat 26 and opens the orifice 25 when it is separated from the seat 26.
  • a controlling mechanism 14 is attached to the upper section of the main body 6 and is provided with an upper lid 16, a lower lid 18, and a film-like diaphragm 17 made of stainless steel and retained between the upper and lower lids 16, 18.
  • a cylindrical coupling tube 18a is formed integrally with the lower lid 18 and is provided with a threaded outer surface 18b.
  • a pressure chamber 11 is defined in the upper section of the main body 6 and connected with the third passage 9. The pressure chamber 11 opens at the upper surface of the main body 6 and has a threaded inner surface.
  • the controlling mechanism 14 is attached to the upper section of the main body 6 by screwing the coupling tube 18a into the pressure chamber 11. An adhesive agent is applied to the coupled section to prevent the loosening of the coupling tube 18a.
  • a heat detecting chamber 10, in which saturated gas is sealed, is defined between the upper lid 16 and the diaphragm 17.
  • a pipe 33 is brazed to the upper lid 16 to permit saturated gas to be charged into the detecting chamber 10. After charging the saturated gas, the distal end of the pipe is flattened to seal the detecting chamber 10. The pipe 33 is then permanently closed by soldering or the like to maintain the detecting chamber 10 in a sealed state.
  • a support hole 32 is formed in the generally center section of the main body 6 and is connected to the third passage 9.
  • the detecting rod 21 extends downward through the third passage 9 from inside the pressure chamber 11.
  • the lower end of the detecting rod 21 is slidably supported by the support hole 32.
  • An elongated actuating rod 24 is supported by the main body 6 and is movable in the longitudinal direction. The upper end of the actuating rod 24 abuts against the lower end surface of the detecting rod 21 and the lower end of the actuating rod 24 abuts against the valve member 27 through the orifice 25.
  • the liquefied refrigerant drawn into the first passage 7 from the condenser 2 via the receiver 3 expands as it passes through the orifice 25 and is thus converted into a low temperature, low pressure refrigerant mist.
  • the refrigerant mist enters the second passage 8 and is then sent to the evaporator 5 to be gasified by the evaporator 5.
  • the refrigerant gas is then sent to the compressor 1 via the third passage 9 of the expansion valve 4.
  • the refrigerant gas that passes through the third passage 9 flows into the pressure chamber 11.
  • the temperature of the refrigerant gas in the third passage 9 and the pressure chamber 11 is transmitted to the saturated gas in the detecting chamber 10 through the detecting rod 21, the flange 22, and the diaphragm 17. Therefore, the saturated gas in the detecting chamber 10 expands or contracts in accordance with the temperature of the refrigerant gas passing through the third passage.
  • the pressure inside the detecting chamber 10 is fluctuated by the expansion or contraction of the saturated gas.
  • the diaphragm 17 is displaced upwards or downwards by the pressure fluctuation in the detecting chamber 10. The movement of the diaphragm 17 is transmitted to the valve member 27 through the detecting rod 21 and the actuating rod 24.
  • the flow rate of the refrigerant mist drawn into the evaporator 5 is adjusted by controlling the area of the orifice 25 opened by the valve member 27 in accordance with the temperature of the refrigerant gas discharged from the evaporator 5 toward the compressor 1.
  • Another objective of the present invention is to provide an expansion valve having a controlling mechanism for the controlling of the valve member that is easily and securely attached to a main body.
  • a further objective of the present invention is to provide an expansion valve having a smoothly moving heat detecting rod.
  • Another objective of the present invention is to provide a compact expansion valve that is capable of easily and securely sealing saturated gas in a heat detecting chamber.
  • the expansion valve according to the present invention includes a valve body, an adjusting mechanism for adjusting a flow rate of a refrigerant supplied to an evaporator and a control mechanism for controlling the adjusting mechanism in accordance with a temperature of the refrigerant supplied to a compressor from the evaporator.
  • the body has a first passage for introducing the refrigerant to the body, a second passage for supplying the refrigerant from the first passage to the evaporator and a third passage for transferring the refrigerant to the compressor from the evaporator.
  • the adjusting mechanism has a restriction for connecting the first passage with the second passage and a valve member for adjusting a degree of the restriction.
  • the control mechanism has a heat sensitive chamber filled with the gas in a sealing manner and a diaphragm movable in accordance with pressure in the sensitive chamber.
  • a transmitting member transmits the temperature of the refrigerant flowing in the third passage to the gas in the sensitive chamber and the movement of the diaphragm to the valve member.
  • the body is made of a synthetic resin and has a pressure chamber defined in its upper section and a first hole and a second hole for slidably supporting the transmitting member at its middle and lower sections, wherein the first and second holes are separate from the restriction, aligned to each other and disposed on opposite sides of the third passage.
  • the first hole has grooves for passage of the refrigerant from the third passage to the pressure chamber and a metal member is secured to the body with an orifice axially extending therethrough to connect the first passage and the second passage.
  • the metal member has the restriction and a metallic valve seat for contacting the valve member.
  • the degree of superheating of the gasified refrigerant at the outlet of the evaporator is continually controlled at a constant value. Also the thermal conductivity of the main body of the expansion valve according to the invention is very much reduced compared with that in the prior art expansion valve. Therefore, the ambient high temperature outside the expansion valve does not effect the gasified refrigerant in the pressure chamber. The flow rate of the refrigerant drawn into the evaporator can acurately be adjusted.
  • the use of the expansion valve according to the invention results in the cooling efficiency of the air-conditioning apparatus being improved.
  • the main body which is made of a synthetic resin, has a weight of only one half of that of the prior art expansion valve, which prevents damages inflicted on the pipes connected to the inventive expansion valve that may be caused by vibration.
  • the synthetic main body of the expansion valve according to the invention allows a reduction in machining costs.
  • Fig. 1 is a cross-sectional side view showing an expansion valve 40 installed in a refrigerating circuit for an automobile air-conditioning apparatus.
  • the expansion valve 40 includes a main body 41 made of a synthetic resin, a restricting mechanism 46, and a control mechanism 54.
  • polyphenylene sulfide be used as the synthetic resin from which the main body 40 is made.
  • Polyphenylene sulfide resin has high strength and superior heat resistance.
  • polyphenylene sulfide does not deteriorate despite the existence of refrigerant and lubricating oil contained in the refrigerant. Another characteristic of this resin is that it deforms only slightly with temperature changes.
  • the main body 41 is provided with a first passage 42, which is connected to the outlet of the condenser 2 by way of the receiver 3, a second passage 43, which is connected to the inlet of the evaporator 5, and a third passage 44, which connects the outlet of the evaporator 5 with the inlet of the compressor 1.
  • the restricting mechanism 46 is located in a valve chamber 45, which is defined inside the first passage 42.
  • the restricting mechanism 46 includes a metal member 47, in which an orifice 47a is formed, a valve member 48, and a coil spring 49.
  • the metal member 47 is made from a material such as aluminum and fixed to the main body 41 between the first passage 42 and the second passage 43.
  • the orifice 47a extends axially through the metal member 47 to connect the first passage 42 with the second passage 43.
  • the inlet of the orifice 47a is located in the valve chamber 45.
  • a valve seat 50 is defined on the area surrounding the inlet.
  • An adjusting screw 51 which also serves as a cap, is screwed into the bottom of the main body 41.
  • the coil spring 49 is placed on the upper surface of the screw 51 in the valve chamber 45.
  • the valve member 48 is mounted on the upper end of the coil spring 49 and urged toward the valve seat 50 by the spring 49.
  • the orifice 47a is closed when the valve member 48 abuts against the valve seat 50 and opened when the member 48 is separated from the seat 50.
  • the opened area of the orifice 47a is determined by the position of the valve member 48 with respect to the valve seat 50.
  • a seal ring 53 is attached to the peripheral surface of the screw 51 to prevent leakage of refrigerant from the valve chamber 45.
  • the controlling mechanism 54 is attached to the upper section of the main body 41.
  • the controlling mechanism 54 includes an upper lid 55, a lower lid 56, and a film-like diaphragm 57 made of stainless steel and retained between the upper and lower lids 55, 56.
  • the peripheral sections of the upper and lower lids 55, 56 are welded to each other with the diaphragm 57 held in between. This secures the upper lid 55, the lower lid 56, and the diaphragm 57 integrally to one another.
  • the main body 41 is provided with a flange 41a formed at its top peripheral section.
  • a pressure chamber 58 is defined in the upper section of the main body 41 with an opening along the top surface of the body 41.
  • the lower lid 56 of the controlling mechanism 54 is placed on the top surface of the main body 41 with a packing 59 provided in between.
  • the peripheral surfaces of the controlling mechanism 54 and the flange 41a are encompassed by a cylindrical metal fastener 60.
  • the upper and lower parts of the fastener 60 are crimped in this state to clamp the peripheral section of the controlling mechanism 54 and the flange 41a. In this manner, the controlling mechanism 54 is attached to the upper section of the main body 41.
  • the upper lid 55 may be totally encompassed by a dome-shaped fastener 60 that is formed through pressing.
  • a heat detecting chamber 61 is defined between the upper lid 55 and the diaphragm 57.
  • Gas, such as HFC-134a, which is saturated, is charged into the detecting chamber 61 through an opening 55a formed in the center of the upper lid 55.
  • a steel pellet 62 is then spot welded and fixed to the hole 55a.
  • the detecting chamber 61 is sustained in a sealed state with the steel pellet 62 closing the opening 55a.
  • the detecting chamber 61 is sealed with the saturated gas filled therein when the steel pellet 62 is spot welded and fixed to the opening 55a.
  • a first support hole 63 extends axially through the main body 41 between the pressure chamber 58 and the third passage 44.
  • a second support hole 64 extends axially through the generally center section of the main body 41 and is connected to the third passage 44. The axes of the first and second support holes 63, 64 are aligned with the axis of the orifice 47a.
  • a heat detecting rod 65 includes a shaft 66 and a flange 67 fixed to the upper end of the shaft 66. The detecting rod 65 extends downward through the third passage 44 from the pressure chamber 58.
  • the shaft 66 is slidably inserted into and supported by the first and second support holes 63, 64 at its middle and lower sections. The upper surface of the flange 67 is adhered to the diaphragm 57.
  • a plurality of grooves 63a are formed in the inner surface of the first support hole 63 to connect the pressure chamber 58 with the third passage 44.
  • a support hole 68 extends axially through the main body 41 between the bottom of the second support hole 64 and the second passage 43.
  • the support hole 68 is aligned with the axis of the orifice 47a.
  • An actuating rod 69 is supported by the support hole 68 and movable in the axial direction.
  • the upper end of the actuating rod 69 abuts against the lower end surface of the detecting rod 65, and the lower end of the actuating rod 69 is abutted against the valve member 48 through the orifice 47a.
  • a seal ring 70 is fitted on the lower outer surface of the shaft 66 of the detecting rod 65 to seal the space between the second and third passages 43, 44.
  • the operation of this device will now be described.
  • the high temperature, high pressure gasified refrigerant, compressed by the compressor 1 is condensed and liquefied by the condenser 2.
  • the liquefied refrigerant is then drawn into the first passage 42 of the expansion valve 40 via the receiver 3.
  • the liquefied refrigerant is expanded as it passes through the orifice 47a and converted into a low temperature, low pressure atomized refrigerant.
  • the atomized refrigerant drawn into the second passage 43 is sent to the evaporator 5.
  • the evaporator 5 gasifies the atomized refrigerant.
  • the gasified refrigerant is drawn into the compressor 1 via the expansion valve's 40 third passage 44.
  • gasified refrigerant flows into the pressure chamber 58 through the grooves 63a of the first support hole 63.
  • the detecting rod 65 is constantly urged upward by the coil spring 49 through the valve member 48 and the actuating rod 69.
  • the upward force acting on the detecting rod 65 is determined by the urging force of the coil spring 49 and the pressure within the pressure chamber 58, while the downward force is determined by the pressure within the detecting chamber 61.
  • the heat of the gasified refrigerant in the third passage 44 and the pressure chamber 58 is transmitted to the saturated gas inside the detecting chamber 61 by way of the detecting rod 65 and the diaphragm 57.
  • This causes the saturated gas to expand or contract in the detecting chamber 61 in accordance with the temperature of the gasified refrigerant flowing through the third passage 44.
  • the expansion and contraction of the saturated gas changes the pressure in the detecting chamber 61 and displaces the diaphragm 57 upwards or downwards.
  • the displacement of the diaphragm 57 is transmitted to the valve member 48 through the detecting rod 65 and the actuating rod 69.
  • the temperature of the gasified refrigerant sent to the compressor 1 from the evaporator 5 controls the area of the orifice 47a, opened by the valve member 48, and adjusts the flow rate of the atomized refrigerant drawn into the evaporator 5. In this manner, the degree of superheating of the gasified refrigerant at the outlet of the evaporator 5 is continually controlled at a constant value.
  • the main body 41 of the expansion valve 40 is made of polyphenylene sulfide resin.
  • the thermal conductivity of the main body 41 is one one-hundred-fiftieth (1/150) of that in the prior art expansion valve. Therefore, the ambient high temperature outside the expansion valve 40 does not effect the gasified refrigerant in the pressure chamber 58 and the temperature of the refrigerant in the pressure chamber 58 is generally maintained at the same value as the temperature of the refrigerant flowing through the third flow passage 44.
  • the temperature of the saturated gas in the detecting chamber 61 is substantially the same as the temperature of the refrigerant flowing through the third passage 44 when the heat of the refrigerant in the pressure chamber 58 is transmitted to the saturated gas in the detecting chamber 61.
  • heat is accurately transmitted between the saturated gas in the detecting chamber 61 and the refrigerant flowing through the third passage 44. Consequently, the area of the orifice 47a opened by the valve member 48 is accurately controlled and the flow rate of the refrigerant drawn into the evaporator 5 is thus accurately adjusted.
  • Fig. 3 (a) shows a graph for the preferred embodiment illustrating the fluctuations of pressure P1, which is the pressure at the outlet of the condenser 2, pressure P2, which is the pressure at the inlet of the evaporator 5, pressure P3, which is the pressure at the outlet of the evaporator 5, and temperature T2, which is the temperature of the air sent into the passenger's compartment from the evaporator 5, under conditions where the expansion valve's 40 ambient temperature T1 is maintained at approximately 75 degrees Celsius.
  • Fig. 3 (b) shows a graph for the prior art expansion valve illustrating the fluctuations of the pressure P1, the pressure P2, the pressure P3, and the temperature T2 under conditions where the prior art expansion valve's 4 ambient temperature T1 is maintained at approximately 75 degrees Celsius.
  • the main body 41 made of a synthetic resin having low thermal conductivity suppresses conduction of heat between the high temperature liquefied refrigerant in the first passage 42 and the low temperature atomized refrigerant in the second passage 43. As a result, the loss of heat energy is suppressed and the cooling efficiency of the air-conditioning apparatus is improved.
  • the main body 41 made of a synthetic resin, is only one half the weight of the prior art expansion valve 4, the main body of which is made of metal such as aluminum. This prevents damages inflicted on the pipes connected to the passages 42, 43, 44 that may be caused by vibration. Furthermore, the synthetic main body 41 allows a reduction in machining costs.
  • the orifice 47a is formed in the metal member 47, which is fixed to the main body 41 and has a strength greater than the synthetic resin.
  • This structure prevents damage to the valve seat 50 that may by caused by repetitive abutment of the valve member 48 against the seat 50.
  • the valve seat 50 may be formed by pressing a steel spherical body, that has the same dimension as the valve member 48, against the area surrounding the inlet of the orifice 47a. Therefore, the space between the valve member 48 and the valve seat 50 is completely sealed when the member 48 contacts the seat 50 and the passage of the refrigerant is thus securely blocked.
  • the controlling mechanism 54 is attached to the main body 41 by crimping the metal fastener 60. Hence, thread machining and application of an adhesive agent, used to prevent loosening of the coupled parts, are not necessary according to the present invention whereas they were required in the prior art. This allows the controlling mechanism 54 to be easily and securely attached to the main body 41.
  • the detecting rod 65 is supported by the first and second support holes 63, 64. That is, the detecting rod 65 is directly supported by the main body 41 at its middle and lower section.
  • the formation of the first and second support holes 63, 64 aligned along the same axis is rather simple. This leads to smooth movement of the detecting rod 65, which in turn allows smooth movement of the valve member 48.
  • the detecting rod 65 includes the shaft 66 and the flange 67 fixed to the top end of the shaft 66.
  • the shaft 66 may be formed by machining a cylindrical piece of metal and the flange 67 may be formed by pressing a piece of metal.
  • the shaft 66 and the flange 67 may be formed from different materials. This enables fine adjustment of thermal conduction in the detecting rod 65. In such cases, it is preferable that the shaft 66 be made of stainless while the flange 67 be made of aluminum or brass.
  • the steel pellet 62 is spot welded and fixed to the opening 55a in the upper lid 55 after charging the detecting chamber 61 with saturated gas through the opening 55a.
  • saturated gas is securely sealed in the detecting chamber 61. Accordingly, there are no parts projecting upward from the upper lid 55 and the size of the entire expansion valve 40 is compact. This allows positioning of the expansion valve 40 within a small space. Since, the direction of the steel pellet 62 with respect to the opening 55a is not limited when fixing the pellet 62 to the opening 55a, automation of the fixing process is rather simple. This facilitates the sealing operation of the saturated gas.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
EP96119717A 1995-07-13 1996-12-09 Thermal type expansion valve Expired - Lifetime EP0846927B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP08122435A JP3130246B2 (ja) 1995-07-13 1996-04-18 温度式膨張弁
DE1996607846 DE69607846T2 (de) 1996-12-09 1996-12-09 Thermisches Entspannungsventil
EP96119717A EP0846927B1 (en) 1995-07-13 1996-12-09 Thermal type expansion valve

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP20175495 1995-07-13
JP08122435A JP3130246B2 (ja) 1995-07-13 1996-04-18 温度式膨張弁
EP96119717A EP0846927B1 (en) 1995-07-13 1996-12-09 Thermal type expansion valve

Publications (2)

Publication Number Publication Date
EP0846927A1 EP0846927A1 (en) 1998-06-10
EP0846927B1 true EP0846927B1 (en) 2000-04-19

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ID=27237471

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96119717A Expired - Lifetime EP0846927B1 (en) 1995-07-13 1996-12-09 Thermal type expansion valve

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EP (1) EP0846927B1 (ja)
JP (1) JP3130246B2 (ja)

Families Citing this family (17)

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Publication number Priority date Publication date Assignee Title
JPH11223425A (ja) 1998-02-10 1999-08-17 Fujikoki Corp 膨張弁
JP4034883B2 (ja) * 1998-07-08 2008-01-16 サンデン株式会社 温度自動膨張弁
JP4153133B2 (ja) * 1999-05-11 2008-09-17 株式会社不二工機 膨張弁
JP2001116401A (ja) 1999-10-15 2001-04-27 Tgk Co Ltd 膨張弁
JP2001183032A (ja) * 1999-12-24 2001-07-06 Denso Corp 温度式膨張弁
JP3751505B2 (ja) 2000-06-07 2006-03-01 株式会社テージーケー 可変容量圧縮機用制御弁の真空室形成方法
JP2002350010A (ja) 2001-05-29 2002-12-04 Fuji Koki Corp 膨張弁
JP4041334B2 (ja) 2002-04-08 2008-01-30 株式会社不二工機 膨張弁及び冷凍サイクル
WO2004036125A2 (en) * 2002-10-18 2004-04-29 Parker-Hannifin Corporation Refrigeration expansion valve with thermal mass power element
JP2006258283A (ja) * 2005-02-18 2006-09-28 Denso Corp 流体制御弁、および電磁弁
DE102006020457A1 (de) * 2006-04-28 2007-11-15 Otto Egelhof Gmbh & Co. Kg Thermokopf für Expansionsventile
JP2012013217A (ja) * 2010-06-29 2012-01-19 Tgk Co Ltd 膨張弁
JP6828532B2 (ja) * 2017-03-17 2021-02-10 株式会社デンソー 温度式膨張弁
KR101967738B1 (ko) * 2017-06-01 2019-04-10 이경환 보강구조를 갖는 전동침대
JP7173837B2 (ja) * 2018-11-06 2022-11-16 株式会社鷺宮製作所 温度式膨張弁
KR101994946B1 (ko) * 2019-01-31 2019-07-01 이경환 보강구조를 갖는 전동침대
JP7373857B2 (ja) * 2021-03-29 2023-11-06 株式会社不二工機 パワーエレメント及びそれを用いた膨張弁

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Publication number Priority date Publication date Assignee Title
EP0736737A2 (en) * 1995-04-07 1996-10-09 Fujikoki Mfg. Co., Ltd. Expansion valve and refrigerating system

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Also Published As

Publication number Publication date
EP0846927A1 (en) 1998-06-10
JPH0989154A (ja) 1997-03-31
JP3130246B2 (ja) 2001-01-31

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