EP0147855A2 - Kälteanlage - Google Patents

Kälteanlage Download PDF

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Publication number
EP0147855A2
EP0147855A2 EP84116379A EP84116379A EP0147855A2 EP 0147855 A2 EP0147855 A2 EP 0147855A2 EP 84116379 A EP84116379 A EP 84116379A EP 84116379 A EP84116379 A EP 84116379A EP 0147855 A2 EP0147855 A2 EP 0147855A2
Authority
EP
European Patent Office
Prior art keywords
valve
evaporator
chamber
valve body
refrigerating system
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.)
Granted
Application number
EP84116379A
Other languages
English (en)
French (fr)
Other versions
EP0147855B1 (de
EP0147855A3 (en
Inventor
Youichi Nakamura
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.)
Saginomiya Seisakusho Inc
Original Assignee
Saginomiya Seisakusho Inc
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
Application filed by Saginomiya Seisakusho Inc filed Critical Saginomiya Seisakusho Inc
Publication of EP0147855A2 publication Critical patent/EP0147855A2/de
Publication of EP0147855A3 publication Critical patent/EP0147855A3/en
Application granted granted Critical
Publication of EP0147855B1 publication Critical patent/EP0147855B1/de
Expired 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

Definitions

  • the present invention relates to a refrigerating system with reduced restarting load and more particularly to a refrigerating system with a differential pressure value to block a circuit to prevent condensed medium from flowing into an evaporator when a compressor operation is stopped.
  • Improvement in power efficiency of the refrigerator is achieved by balancing the cooling medium pressure before and after the compressor when the compressor is stopped and by blocking the flow of condensed medium into the evaporator while at the same time keeping the high pressure of the condensed medium in the condensor, in order to reduce the restarting load.
  • Fig. 1 shows a refrigerating apparatus using the pressure valve accomplished according to the previous patent application filed by the inventor of this invention.
  • a rotary compressor A, a condenser B, a capillary tube C, and an evaporator D are connected in series by a pipe E;
  • a differential pressure valve Vl is installed in the pipe between the capillary tube C and the evaporator D;
  • a pressure introducing tube F is connected to the suction side of the rotary compressor A; and
  • a check valve V2 is installed between the evaporator D and the rotary compressor A.
  • the differential pressure valve Vl as shown in Fig. 2, has a primary port 2 and a secondary port 3 formed in its body 1. Between these ports is formed a valve seat 4 with which a ball 5 comes into or out of contact. The ball 5 is provided on the secondary port side.
  • a diaphragm 8 which is held at its periphery by upper and lower covers 6, 7.
  • a pressure chamber is formed in the upper cover 6 and is communicated with the pressure introducing tube F.
  • a valve rod 9 is abutted against the underside of the diaphragm 8 and a spring 10 is installed between the rod 9 and the lower cover 7.
  • the primary port 2 is connected with a pipe El coming from the capillary tube C and the secondary port 3 with a pipe E2 leading to the evaporator D.
  • the differential pressure valve is actuated by a small pressure difference between the pressure on the rotary compressor suction side and the relatively low pressure at the entrance of the evaporator. Therefore, once the operation starts, the pressure at the entrance of the evaporator becomes higher than the pressure on the suction side of the compressor whatever the external atmospheric condition may be. This enables the valve to be opened by a small spring load. That is, the differential pressure valve can be actuated by a slight pressure increase at the suction of the rotary compressor caused by the back flow of high pressure liquid. Thus, it is possible to prevent the back flow of high pressure liquid to the evaporator by rapidly actuating the differential pressure valve when the rotary compressor stops.
  • a capillary tube is provided as a throttle before the differential pressure valve.
  • the cooling medium after passing through the throttle is reduced in pressure and can absorb heat, and therefore there is an energy loss in the pipe section leading to the refrigerating box.
  • the present invention has throttles before and after the differential pressure valve, with all these installed outside the refrigerating box, to perform the pressure reduction in two stages, thereby preventing energy loss while maintaining response speed of the differential pressure valve when the compressor operation stops.
  • FIG. 3 shows an embodiment of the present invention in which the same reference numbers as those in the prior art structure represent the identical components.
  • a rotary compresser A, a condenser B, a capillary tube C, a differential pressure valve Vl, a second capillary tube C', an evaporator D, and a check V2 are provided. More specifically, said condenser B and said evaporator D are connected in series with each other.
  • a first capillary tube C is provided in said series connection between said condenser B and evaporator D.
  • Said rotary compresser A has a delivery side and a suction side. Said delivery side is connected to the condenser B whereas said suction side is connected to the evaporator D. Between said evaporator D and the suction side is provided the check valve V2.
  • Said differential pressure valve Vl is provided between the first capillary tube C and the evaporator D and has a valve section Vs and the control section Cs.
  • Said second capillary tube C' is provided between the differential pressure tube Vl and the evaporator D.
  • Said valve section Vs of the differential pressure valve Vl includes a valve body 1 having a primary port 2 and a secondary port 3.
  • Said primary port 2 communicates with the first capillary tube C whereas said secondary port 3 communicates with the second capillary tube C'.
  • said primary port 2 defines a valve seat 4 within the valve body 1.
  • Said valve body 1 has a bore 1' formed therein communicating with the first primary port 2 and the second primary port 3.
  • a ball is housed within said bore 1' and adapted to rest on said valve seat 4.
  • Said valve body 1 is formed with an annular groove 1" around said bore l' at an axial end thereof.
  • Said control section Cs includes a housing H, a diaphragm 8 provided within said housing H to devide the same into a first chamber Rl and a second chamber R2 and a valve rod 9 extending within said second chamber longitudinally movably.
  • Said valve rod 9 has a ring member 9' attached to the first end thereof to abut against the diaphragm 8.
  • said diaphragm 8 is held at its periphery by upper and lower covers 6 and 7.
  • Said first chamber Rl of the control section Cs communicates with the pressure introducing tube F.
  • Said lower cover 7 has an opening to communicate said second chamber with the secondary port 3.
  • valve body 1 is attached to the lower cover 7 such that said annular groove 1" and said bore 1' communicates the second chamber R2.
  • valve rod 9 is allowed to extend out of the control section Cs into the bore 1' to actuate the ball 5 at a second end thereof for closure of the primary port 2.
  • a coil spring 10 within said annular groove 1" between the body 1 and the ring member 9'.
  • a star-shaped leaf spring 23 having radially extending portions is provided between the coil spring 10 and the ring member 9'. Said radially bent portions are bent to extend within said annular groove 1" and expand radially outward to contact the valve body I within the annular groove 1".
  • the differential pressure valve can be quickly actuated. Also the capillary tube C' as a second stage throttle to achieve a desired pressure reduction can be installed inside the refrigerating box thus eliminating energy loss.
  • the differential pressure valve can rapidly be actuated when the rotary compressor is stopped, thereby reducing the restarting load and eliminating energy loss during operation.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
EP84116379A 1983-12-28 1984-12-27 Kälteanlage Expired EP0147855B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP245324/83 1983-12-28
JP58245324A JPS60140072A (ja) 1983-12-28 1983-12-28 差圧開閉弁付冷凍装置

Publications (3)

Publication Number Publication Date
EP0147855A2 true EP0147855A2 (de) 1985-07-10
EP0147855A3 EP0147855A3 (en) 1986-06-11
EP0147855B1 EP0147855B1 (de) 1989-10-11

Family

ID=17131963

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116379A Expired EP0147855B1 (de) 1983-12-28 1984-12-27 Kälteanlage

Country Status (3)

Country Link
EP (1) EP0147855B1 (de)
JP (1) JPS60140072A (de)
DE (1) DE3480113D1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0255035A2 (de) * 1986-07-23 1988-02-03 Sanden Corporation Kältekreislauf
WO1997017579A1 (en) * 1995-11-10 1997-05-15 Danfoss A/S Refrigeration plant and diaphragm valve for use in the plant
GB2325723A (en) * 1997-05-27 1998-12-02 Matthew James Harold Rawlings Check and metering valves for spray apparatus

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB165455A (en) * 1917-09-11 1921-07-07 Harry Egerton Wimperis Viewing or sighting devices for use on aircraft
CH188957A (de) * 1936-01-21 1937-01-31 Sulzer Ag Kompressionskältemaschine.
US2326093A (en) * 1940-05-29 1943-08-03 Detroit Lubricator Co Refrigerating system
DE873394C (de) * 1944-06-22 1953-04-13 Siemens Ag Kaeltemaschine
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve
US3855836A (en) * 1973-01-24 1974-12-24 Hitachi Ltd Device for controlling coolant pressure in evaporator
US4081971A (en) * 1976-09-17 1978-04-04 The Trane Company Air cooled centrifugal refrigeration machine with provision to prevent evaporator freezing
FR2377590A1 (fr) * 1977-01-13 1978-08-11 Mac Quay Perfex Inc Systeme de commande pour une installation de refrigeration
DE3314140A1 (de) * 1982-04-22 1983-11-03 Tokyo Shibaura Denki K.K., Kawasaki, Kanagawa Kuehlkreislauf
JPS59215552A (ja) * 1983-05-23 1984-12-05 三菱電機株式会社 冷凍装置

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB165455A (en) * 1917-09-11 1921-07-07 Harry Egerton Wimperis Viewing or sighting devices for use on aircraft
CH188957A (de) * 1936-01-21 1937-01-31 Sulzer Ag Kompressionskältemaschine.
US2326093A (en) * 1940-05-29 1943-08-03 Detroit Lubricator Co Refrigerating system
DE873394C (de) * 1944-06-22 1953-04-13 Siemens Ag Kaeltemaschine
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve
US3855836A (en) * 1973-01-24 1974-12-24 Hitachi Ltd Device for controlling coolant pressure in evaporator
US4081971A (en) * 1976-09-17 1978-04-04 The Trane Company Air cooled centrifugal refrigeration machine with provision to prevent evaporator freezing
FR2377590A1 (fr) * 1977-01-13 1978-08-11 Mac Quay Perfex Inc Systeme de commande pour une installation de refrigeration
DE3314140A1 (de) * 1982-04-22 1983-11-03 Tokyo Shibaura Denki K.K., Kawasaki, Kanagawa Kuehlkreislauf
JPS59215552A (ja) * 1983-05-23 1984-12-05 三菱電機株式会社 冷凍装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0255035A2 (de) * 1986-07-23 1988-02-03 Sanden Corporation Kältekreislauf
EP0255035A3 (en) * 1986-07-23 1989-11-15 Sanden Corporation Refrigeration circuit
WO1997017579A1 (en) * 1995-11-10 1997-05-15 Danfoss A/S Refrigeration plant and diaphragm valve for use in the plant
GB2325723A (en) * 1997-05-27 1998-12-02 Matthew James Harold Rawlings Check and metering valves for spray apparatus
GB2325723B (en) * 1997-05-27 1999-06-02 Matthew James Harold Rawlings Improvements in control valves

Also Published As

Publication number Publication date
EP0147855B1 (de) 1989-10-11
EP0147855A3 (en) 1986-06-11
JPS60140072A (ja) 1985-07-24
DE3480113D1 (en) 1989-11-16

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