EP0147855B1 - Système frigorifique - Google Patents

Système frigorifique Download PDF

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Publication number
EP0147855B1
EP0147855B1 EP84116379A EP84116379A EP0147855B1 EP 0147855 B1 EP0147855 B1 EP 0147855B1 EP 84116379 A EP84116379 A EP 84116379A EP 84116379 A EP84116379 A EP 84116379A EP 0147855 B1 EP0147855 B1 EP 0147855B1
Authority
EP
European Patent Office
Prior art keywords
valve
evaporator
valve body
chamber
differential pressure
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
Application number
EP84116379A
Other languages
German (de)
English (en)
Other versions
EP0147855A3 (en
EP0147855A2 (fr
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/fr
Publication of EP0147855A3 publication Critical patent/EP0147855A3/en
Application granted granted Critical
Publication of EP0147855B1 publication Critical patent/EP0147855B1/fr
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 according to the precharacterizing portion of claim 1.
  • 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.
  • the function of said differential pressure valve depends essentially from the reliability and the resilience of said foldable skin which, however, cannot be guaranteed.
  • the differential pressure valve V1 as shown in Fig. 1, 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 E1 coming from the capillary tube C and the secondary port 3 with a pipe E2 leading to an evaporator D described below.
  • 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. 2 shows an embodiment of the present invention.
  • a rotary compressor A, a condenser B, a capillary tube C, a differential pressure valve V1, 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 compressor 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 V1 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 V1 and the evaporator D.
  • Said valve section Vs of the differential pressure valve V1 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 l' 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 1' at an axial end thereof.
  • Said control section Cs includes a housing H, a diaphragm 8 provided within said housing H to divide the same into a first chamber R1 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 R1 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.
  • Said valve body 1 is attached to the lower cover 7 such that said annular groove 1" and said bore 1' communicates with 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 1 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)

Claims (6)

1. Système frigorifique ou de réfrigération comprenant:
(a) un condenseur (B) et un evaporateur (D) reliés l'un à l'autre en serie,
(b) des premiers moyens (C) d'obturation disposés dans ladite liaison en série entre ledit condenseur (B) et ledit évaporateur (D),
(c) un compresseur (A) rotatif à piston ayant un côté de distribution et un côté d'aspiration, ledit côté de distribution etant relié audit condenseur
(B), ledit côté d'aspiration étant relié audit évaporateur (D),
(d) une valve (V2 anti-retour disposée entre ledit évaporateur (D), et ledit côté d'aspiration dudit compresseur (A) rotatif à piston,
(e) une valve (V1) de compression différentielle disposée entre lesdits premiers moyens (C) d'obturation et ledit évaporateur (D),
(f) un tube (F) de mise en pression mettant en communication le côté d'aspiration dudit compresseur (A) rotatif à piston avec ladite valve (V1) de compression différentielle, et
(g) des seconds moyens (C') d'obturation disposés entre ledit évaporateur (D) et ladite valve (V1) de compression différentielle, caractérisé en ce que
(h) ladite valve (V1) différentielle comporte une partie valve (Vs) et une partie de contrôle (CS); en ce que
(i) ladite partie valve (Vs) de ladite valve (V,) de compression différentielle comprend un corps de valve (1) ayant un orifice (2) primaire perce dedans, communiquant avec lesdits premiers moyens (C) d'obturation et définissant un siège (4) de soupape à l'intérieur dudit corps de valve (1) ainsi qu'un second orifice (3) et une bille (5) logée à l'intérieur dudit corps de valve (1) et adaptée à reposer sur ledit siège (4) de soupape; en ce que
(j) ladite partie de contrôle (Cs) comprend une enveloppe (H/6, 7), une membrane (8) disposée à l'intérieur de ladite enveloppe (H/6, 7) pour la diviser en une première chambre (R,) et une seconde chambre (R2) et une tige (9) de soupape s'étendant à l'intérieur de ladite seconde chambre (R2) pour s'y déplacer longitudinalement et reposant contre ladite membrane (8) à une première de ses extrémités; en ce que
(k) ladite première chambre (R,) de ladite partie de contrôle (Cs) communique avec ledit tube (F) de mise en pression; en ce que
(I) ladite seconde chambre (R2) de ladite partie de contrôle (Cs) possède une ouverture (1') pour mettre en communication ladite seconde chambre (R2) avec l'orifice (3) secondaire et pour permettre à ladite tige (9) de soupape de se prolonger hors de ladite partie de contrôle (Cs) jusque dans ladite partie valve (Vs) afin d'actionner par une seconde de ses extrémités ladite bille (5) et de fermer ainsi ledit orifice (2) primaire; en ce que
(m) ladite tige (9) de soupape possède une couronne (9') assujettie a ladite première extrémité et reposant contre ladite membrane (8) au niveau de sa première extrémité; en ce que
(n) des moyens élastiques (10) sont adaptés à maintenir en contact ladite tige (9) de soupape et ladite membrane (8); et en ce que
(o) un ressort (23) à lamelles est disposé maintenu entre lesdits moyens élastiques (10) et ladite couronne (9') à l'intérieur de ladite seconde chambre (R2) dudit corps de valve (1 ledit ressort (23) à lamelles ayant des extensions radiales recourbees afin de se prolonger à l'intérieur dudit corps de valve (1) et de s'écarter vers l'extérieur pour être en contact avec ledit corps de valve (1).
2. Système frigorifique ou de réfrigération selon la revendication 1, caractérisé en ce que ledit corps de valve (1) est perce d'un conduit (1') en communication avec ledit orifice (2) primaire et ledit orifice (3) secondaire.
3. Système frigorifique ou de réfrigération selon la revendication 1 ou la revendication 2, caractérisé en ce que ledit corps de valve (1) possède une gorge annulaire (1") autour dudit conduit (1') au niveau de son extrémité axiale.
4. Système frigorifique ou de réfrigération selon l'une quelconque des revendications 1 à 3, caractérisé en ce que lesdits moyens élastiques (10) comprennent un ressort (10) à boudin disposé à l'intérieur de ladite gorge annulaire (1") entre ledit corps de valve (1) et ladite couronne (9').
5. Système frigorifique ou de réfrigération selon la revendication 3 ou la revendication 4, caractérisé en ce que ledit ressort (23) à lamelles est en forme d'étoile et en ce que lesdites extensions radiales sont recourbées de façon à se prolonger à l'intérieur de ladite gorge annulaire (1") et à s'écarter vers l'extérieur pour être en contact avec ledit corps de valve (1) à l'intérieur de ladite gorge annulaire (1").
EP84116379A 1983-12-28 1984-12-27 Système frigorifique Expired EP0147855B1 (fr)

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 EP0147855A2 (fr) 1985-07-10
EP0147855A3 EP0147855A3 (en) 1986-06-11
EP0147855B1 true EP0147855B1 (fr) 1989-10-11

Family

ID=17131963

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116379A Expired EP0147855B1 (fr) 1983-12-28 1984-12-27 Système frigorifique

Country Status (3)

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

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6329165A (ja) * 1986-07-23 1988-02-06 サンデン株式会社 冷凍サイクルの冷媒制御装置
DK125395A (da) * 1995-11-10 1997-05-11 Danfoss As Køleanlæg og menbranventil til brug i anlægget
GB2325723B (en) * 1997-05-27 1999-06-02 Matthew James Harold Rawlings Improvements in control valves

Citations (2)

* 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
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPS5740423B2 (fr) * 1973-01-24 1982-08-27
US4081971A (en) * 1976-09-17 1978-04-04 The Trane Company Air cooled centrifugal refrigeration machine with provision to prevent evaporator freezing
US4136528A (en) * 1977-01-13 1979-01-30 Mcquay-Perfex Inc. Refrigeration system subcooling control
JPS58162458U (ja) * 1982-04-22 1983-10-28 株式会社東芝 冷凍サイクル
JPS59215552A (ja) * 1983-05-23 1984-12-05 三菱電機株式会社 冷凍装置

Patent Citations (2)

* 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
US3785554A (en) * 1970-09-25 1974-01-15 Evans Mfg Co Jackes Temperature responsive throttling valve

Also Published As

Publication number Publication date
EP0147855A3 (en) 1986-06-11
EP0147855A2 (fr) 1985-07-10
DE3480113D1 (en) 1989-11-16
JPS60140072A (ja) 1985-07-24

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