EP2174080B1 - Installation de refroidissement - Google Patents

Installation de refroidissement Download PDF

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Publication number
EP2174080B1
EP2174080B1 EP08758232A EP08758232A EP2174080B1 EP 2174080 B1 EP2174080 B1 EP 2174080B1 EP 08758232 A EP08758232 A EP 08758232A EP 08758232 A EP08758232 A EP 08758232A EP 2174080 B1 EP2174080 B1 EP 2174080B1
Authority
EP
European Patent Office
Prior art keywords
magnet
main valve
valve element
refrigeration system
refrigerant
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.)
Not-in-force
Application number
EP08758232A
Other languages
German (de)
English (en)
Other versions
EP2174080A1 (fr
Inventor
Michael Birkelund
Hans Kurt Petersen
Sune Prytz
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.)
Danfoss AS
Original Assignee
Danfoss AS
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 Danfoss AS filed Critical Danfoss AS
Publication of EP2174080A1 publication Critical patent/EP2174080A1/fr
Application granted granted Critical
Publication of EP2174080B1 publication Critical patent/EP2174080B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • F25B39/02Evaporators
    • F25B39/028Evaporators having distributing means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • F25B41/40Fluid line arrangements
    • F25B41/42Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/48Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow path resistance control on the downstream side of the diverging point, e.g. by an orifice
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00Problems to be solved
    • F25B2500/01Geometry problems, e.g. for reducing size
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/25Control of valves
    • F25B2600/2511Evaporator distribution valves

Definitions

  • the invention relates to a cooling system with a refrigerant circuit, which has a plurality of evaporator sections and a distributor causing a distribution of refrigerant, wherein the distributor has a housing and for each evaporator section a controllable valve.
  • Such a cooling system is for example off DE 195 47 744 A1 known.
  • This cooling system has a single compressor and a single condenser, but two separate evaporators.
  • the supplied by the compressor refrigerant flow is divided after the condenser and before the Expansiosorganen by means of a 3/2-way valve in two sub-streams, the position of the 3/2-way valve is controlled by a control unit.
  • a control unit With such a design, it is difficult to supply more than two evaporator sections.
  • US 5,832,744 shows another cooling system in which the manifold between a refrigerant inlet and a plurality of refrigerant outlets has a valve, which is followed by a rotating turbine disk.
  • the turbine disk should ensure that the refrigerant is evenly distributed to all outlets of the distributor and thus evenly to all evaporators.
  • the refrigerant may not be completely evaporated before it has passed through the evaporator.
  • Another evaporator which is connected to the same evaporator, can get too little refrigerant, so that the evaporator can not provide the desired cooling capacity.
  • the over- or undersupply of the evaporator can lead to difficulties especially if temperature sensors, which are arranged at the evaporators or other locations of the cooling system, control an expansion valve.
  • the expansion valve can be vibrated under unfavorable circumstances, which further deteriorates the capacity and the effectiveness of the cooling system.
  • the invention has for its object to achieve a simple operation of a predetermined operation of the cooling system.
  • cooling system includes cooling systems, freezer systems, air conditioning systems and heat pumps, ie all systems in which a refrigerant is circulated or circulated.
  • refrigeration plant is used for convenience only.
  • the evaporator sections can be arranged in different evaporators. The invention will be explained for the sake of simplicity in the context of multiple evaporators. However, the invention is also applicable when an evaporator has a plurality of individual or groupwise controllable evaporator sections.
  • the distributor has a controllable valve for each evaporator, then it can individually control the supply of the evaporators, i. H. it is then possible to supply each evaporator with the amount of refrigerant it needs. There is no need to worry about the evaporators all having the same flow resistance. It is also of minor importance if the evaporators have to deliver different cooling capacities. An evaporator, which requires a larger cooling capacity, gets correspondingly more refrigerant than an evaporator, which has to provide less cooling capacity.
  • the control of the valves takes place in a simple manner by a magnet arrangement having at least one magnet. A magnet exerts magnetic forces on valves or parts thereof when the magnet is near the valve and active.
  • the magnet moves away from the valve or is passive, such as a solenoid being shut off, it will no longer exert any force on that valve or any part of it. It is thus possible by controlling the position and / or the function of the magnet to ensure that a specific valve is opened, but other valves remain closed.
  • the magnet arrangement preferably has a rotor which carries at least one magnet. Since the magnet is arranged on the rotor, it is displaced by a rotary movement of the rotor from one valve to another. The rotational movement of the rotor can be controlled by a control device. The control device thus ultimately ensures the distribution of the refrigerant to the individual evaporator.
  • the magnet arrangement has at least one magnet designed as an electromagnet. In this case you can turn the magnet on and off.
  • the magnet acts through a closed wall of the housing.
  • This has the advantage that you need for the actuation of the valves no opening through which, for example, a plunger or the like must take. If no corresponding opening is present, the problem of a possible leak does not arise.
  • the only requirement for such a configuration is that the wall does not hinder the action of the magnet.
  • a plastic allows a magnetic field to pass through almost undisturbed. The same applies to many non-magnetic metals.
  • the magnet is guided in a circumferential groove.
  • the circumferential groove thus defines a circular path in which the magnet can move.
  • it is sufficient to set the magnet in the direction of rotation on the rotor.
  • the circumferential groove ensures that the magnet always retains the correct assignment to the valves in the radial direction.
  • the valve is designed as a pilot-operated valve.
  • the forces that a magnet can apply depend, among other things, on the size of the magnet.
  • the size of the magnet in turn is determined by the size of the distributor. As a rule, one does not want to make the distributor too big. Accordingly, the forces which the magnet can exert are limited.
  • the magnet When using a pilot-operated valve, the magnet only has to act on an auxiliary element, which then uses an auxiliary energy, for example the pressure of the refrigerant, to actuate a main valve element.
  • the valve comprises a movable by the magnet Hüfsventilelement and a movable main valve seat by means of refrigerant and cooperates with its main valve seat side facing a pressure chamber
  • the auxiliary valve element comprises a passage from the pressure chamber to a connected to an evaporator section Exit unlocks or locks.
  • the passage is released, so that the pressure in the pressure chamber drops.
  • the decreasing pressure may then be used to lift the main valve member from the main valve seat.
  • the main valve element then remains lifted off the valve seat until the auxiliary valve element blocks the passage again. Then, namely, the pressure in the pressure chamber can again build up so far that the main valve element is moved back to the main valve seat.
  • the auxiliary valve element locks the passage when the magnet is further rotated, so that it can no longer influence the corresponding auxiliary valve element.
  • a throttle path extends parallel to the main valve element from an inlet of the distributor to the pressure chamber.
  • refrigerant can pass from the inlet into the pressure chamber.
  • the then prevailing in the pressure chamber pressure ensures that the main valve element so long applied to the main valve seat, as the auxiliary valve element has not yet released the passage. Only when the auxiliary valve element releases the passage, the pressure in the pressure chamber decreases so far that the main valve element can open. In fact, not enough refrigerant can flow in through the throttle path to produce the pressure required to close the valve when the passage is cleared.
  • the throttle path extends between the main valve element and a guide for the main valve element. This can be used not only the pressure difference across the main valve element to lift the main valve element from the main valve seat.
  • the throttle path may in this case be formed simply by a small clearance between the main valve element and the guide. Of course you can also in the peripheral wall of the main valve element or in the inner wall of the guide Arrange one or more corresponding grooves to form the throttle path.
  • a first pressure drop across the throttle path is greater than a second pressure drop between the pressure chamber and the output.
  • the auxiliary valve element cooperates with a closing spring.
  • the closing spring does not have to apply great forces. You only need to be able to bring the auxiliary valve element to an auxiliary valve seat to the plant. If the manifold is mounted so that the auxiliary valve member comes to rest against the auxiliary valve seat under the force of gravity, then a recoil spring may be dispensable. With the closing spring but you have the advantage that you can choose the mounting position largely free.
  • the magnet arrangement has a controllable magnet, with which a plurality of valves can be controlled simultaneously.
  • a controllable magnet can be designed, for example, as an electromagnet, that is to say as a magnet coil, which can be supplied with electric current in order to activate the magnet. When the power is turned off, the magnet will no longer be effective. If you arrange a magnet so that it can control several or even all valves of the distributor at the same time, then you can open all the valves at the start of the cooling system to quickly lower the temperature in the cooling system. After a suitable filling of the evaporator sections is the controllable Magnet switched off and taken over the further control, for example by means of the rotor.
  • each valve is assigned a separate controllable magnet.
  • a magnet can also be designed as an electromagnet.
  • This embodiment has the advantage that the valves can be controlled independently of each other, that is, in a more or less arbitrary order. Again, you can open all the valves when you start the cooling system simultaneously.
  • Fig. 1 shows a schematic representation of a cooling system 1, in which a compressor 2, a condenser 3, a collector 4, a manifold 5 and an evaporator assembly 6 are connected together with a plurality of evaporators arranged in parallel 7a-7d in a circuit.
  • the evaporator assembly 6 may also include a single evaporator having a plurality of Evaporator lines, which are to be controlled individually or in groups.
  • liquid refrigerant evaporates in the evaporators 7a-7d, is compressed by the compressor 2, liquefied in the condenser 3 and collected in the collector 4.
  • the distributor 5 is intended to distribute the liquid refrigerant to the individual evaporators 7a-7d.
  • a temperature sensor 8a-8d is arranged at the output of each evaporator 7a-7d.
  • the temperature sensor 8a-8d detects the temperature of the refrigerant leaving the evaporator 7a-7d. This temperature information is forwarded to a control unit 9, which controls the distributor 5 as a function of the temperature signals of the temperature sensors 8a-8d.
  • the Fig. 2 to 6 now show the distributor 5 with more details.
  • the manifold 5 has a housing 10 having an inlet 11 and a plurality of outlets 12, each outlet 12 being connected to an evaporator section 7a-7d.
  • the signals from the temperature sensors 8a-8d are supplied to the distributor 5 via electrical lines 13.
  • the housing 10 of the manifold 5 is as it is Fig. 3 can be seen, provided with an insert 14 which in the FIGS. 4 to 6 is shown in more detail.
  • the insert 14 has a motor 15, on the drive shaft 16, a rotor 17 is attached. When the motor rotates the drive shaft 16, the rotor 17 is pivoted about an axis of rotation 18.
  • the rotor 17 is here designed as an arm which is connected to the drive shaft 16.
  • the motor 15 may be formed, for example, as a stepper motor.
  • the rotor At its end remote from the drive shaft 16, the rotor carries a magnet 19, which is guided during a rotation of the rotor 17 in a circumferential groove 20.
  • the circumferential groove 20 is formed in a cover wall 21 which seals a part 12 adjacent to the outputs of the interior 22 of the housing 10.
  • the motor 15 may be pressed, for example, in the housing 10, if no other means are used to hold the motor 15 rotatably in the housing 10.
  • the magnet 19 is expediently designed as a permanent magnet. But you can also form the magnet 19 as an electromagnet, which can be switched on and off, so to speak.
  • an insert housing 23 On the side facing away from the motor 15 of the lid wall 21, an insert housing 23 is arranged, which is covered on its side facing away from the top wall 21 with a bottom plate 24. In the bottom plate 24, an outlet 25 is provided for each outlet 12.
  • the insert housing 23 defines, together with the bottom plate 24, an inlet chamber 26 for refrigerant.
  • the inlet 11 is shown schematically here in order to facilitate understanding.
  • Each outlet 25 forms on its side facing the cover wall 21 a main valve seat 27.
  • a main valve element 28 cooperates.
  • the main valve element 28 delimits a pressure chamber 29 together with a guide 30 which surrounds the main valve element 28 in the circumferential direction.
  • the main valve member 28 is guided with a small clearance in the guide 30, so that there is a throttle line 31 through which refrigerant from the inlet chamber 26 can flow into the pressure chamber 29, even if the main valve element 28 rests against the main valve seat 27 ,
  • an auxiliary channel 32 leads into an auxiliary chamber 33, in which an auxiliary valve element 34 is arranged.
  • the auxiliary valve element 34 is positioned by the force of a closing spring 35, which may be relatively weak, so that it closes the auxiliary channel 32. Refrigerant that has entered the pressure chamber 29, so can not flow out of the pressure chamber 29 in the illustrated, closed position of the auxiliary valve member 35.
  • the refrigerant flowing from the inlet chamber 26 into the pressure space 29 through the throttle passage 31 then generates a pressure difference across the main valve element 28 sufficient to lift the main valve element 28 away from the main valve seat 27.
  • the full pressure of the refrigerant from the inlet chamber 26 in the opening direction acts on the main valve element 28, so that it is held in the open position.
  • the main valve element 28 passes Refrigerant via the corresponding outlet 25 in the output 12 and then in the associated evaporator section 7a-7d.
  • the closing spring 35 presses the auxiliary valve 34 back into the illustrated closed position, so that the auxiliary channel 32 is closed. Since refrigerant still enters the pressure chamber 29 through the throttle section 31, but this can no longer be completed by the auxiliary channel 32 and the auxiliary channel sections 36, 37, a pressure builds up in the pressure chamber 29, causing the main valve element 28 to rest again the main valve seat 27 brings.
  • the main valve element 28, the valve seat 27 and the auxiliary valve element 34 thus form essential parts of a valve 38, wherein for each outlet 25 and thus for each evaporator section 7a-7d provided a separate valve and each valve 38 is individually controlled.
  • the amount of refrigerant, which then enters the respective evaporator section 7a-7d, depends on the length of time in which the magnet 19 remains above the respective auxiliary valve element 34. With one revolution of the drive shaft 16 so that each valve 38 is opened once. If you want to prevent under certain circumstances, that a valve 38 is opened, then the direction of rotation of the drive shaft 16 is reversed before reaching the respective valve 38 or the magnet is very fast driven over the corresponding auxiliary valve member 34 addition. When using an electromagnet can turn off the magnet 19 when a valve 38 is run over, which should not be opened.
  • the throttle section 31 which may also be referred to as a throttle path, has a flow resistance which is greater than the flow resistance of the auxiliary channel 32 and the auxiliary channel sections 36, 37. Accordingly, no pressure can build up in the pressure chamber 29 as long as the auxiliary valve element 34 forms the auxiliary channel 32 releases.
  • control device 9 is arranged separately from the distributor 5. But it is also possible to summarize the control device 9 with the manifold 5 structurally.
  • an additional solenoid may be arranged so that their magnetic field can act on all auxiliary valve elements 34 simultaneously. In this case, all valves 38 are opened simultaneously. This is advantageous when starting the cooling system 1 in order to reduce the temperature quickly.
  • the coil is switched off and the rotor turns the magnet 19 to the various auxiliary elements 34.
  • the effect of such an electromagnet is limited to some or more valves 38.
  • each valve 38 instead of a rotor, which transports the magnet 19 from one valve 38 to the next, for each valve 38 provide its own electromagnet, which then opens the valve 38 individually. All electromagnets are then connected to the control device 9, which controls the control of the valves 38.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (10)

  1. Installation de refroidissement avec un circuit de réfrigérant qui présente plusieurs voies d'évaporation et un distributeur provoquant une distribution de réfrigérant, sachant que le distributeur présente un boîtier et pour chaque voie d'évaporation, une soupape pouvant être commandée, et un ensemble magnétique commandant les soupapes (38), caractérisée en ce que la soupape (38) est réalisée comme une soupape précommandée et en ce que la soupape (38) présente un élément de soupape auxiliaire (34) pouvant être déplacé par l'aimant (19) et un élément de soupape principale (28) pouvant être déplacé par du réfrigérant, qui coagit avec un siège de soupape principale (27) et délimite une chambre de refoulement (29) avec son côté éloigné du siège de soupape principale (27), sachant que l'élément de soupape auxiliaire (34) libère ou bloque un passage (32, 36, 37) de la chambre de refoulement (29) à une sortie (25) reliée à une voie d'évaporation (7a-7d).
  2. Installation de refroidissement selon la revendication 1, caractérisée en ce qu'une voie d'étranglement (31) s'étend d'une entrée (11) du distributeur (5) à la chambre de refoulement (29) parallèlement à l'élément de soupape principale (28).
  3. Installation de refroidissement selon la revendication 2, caractérisée en ce que la voie d'étranglement (31) s'étend entre l'élément de soupape principale (28) et un guidage (30) pour l'élément de soupape principale (28).
  4. Installation de refroidissement selon la revendication 2 ou 3, caractérisée en ce qu'une première chute de pression sur la voie d'étranglement (31) est supérieure à une seconde chute de pression entre la chambre de refoulement (29) et la sortie (25).
  5. Installation de refroidissement selon la revendication 1, caractérisée en ce que l'ensemble magnétique présente un rotor (17) portant au moins un aimant (19).
  6. Installation de refroidissement selon la revendication 5, caractérisée en ce que l'ensemble magnétique présente au moins un aimant (19) réalisé comme un électroaimant.
  7. Installation de refroidissement selon la revendication 5 ou 6, caractérisée en ce que l'aimant (19) agit au travers d'une paroi fermée (21) du boîtier.
  8. Installation de refroidissement selon l'une quelconque des revendications 5 à 7, caractérisée en ce que l'aimant (19) est guidé dans une rainure périphérique (20).
  9. Installation de refroidissement selon l'une quelconque des revendications 1 à 8, caractérisée en ce que l'ensemble magnétique présente un aimant pouvant être commandé, avec lequel plusieurs soupapes peuvent être commandées en même temps.
  10. Installation de refroidissement selon la revendication 1, caractérisée en ce qu'un propre aimant pouvant être commandé est associé à chaque soupape.
EP08758232A 2007-06-19 2008-06-17 Installation de refroidissement Not-in-force EP2174080B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007028565A DE102007028565A1 (de) 2007-06-19 2007-06-19 Kühlanlage
PCT/DK2008/000223 WO2008154923A1 (fr) 2007-06-19 2008-06-17 Installation de refroidissement

Publications (2)

Publication Number Publication Date
EP2174080A1 EP2174080A1 (fr) 2010-04-14
EP2174080B1 true EP2174080B1 (fr) 2012-02-22

Family

ID=39731600

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08758232A Not-in-force EP2174080B1 (fr) 2007-06-19 2008-06-17 Installation de refroidissement

Country Status (9)

Country Link
US (1) US8689582B2 (fr)
EP (1) EP2174080B1 (fr)
JP (1) JP5048129B2 (fr)
CN (1) CN101784848B (fr)
AT (1) ATE546698T1 (fr)
DE (1) DE102007028565A1 (fr)
MX (1) MX2009013756A (fr)
RU (1) RU2426958C1 (fr)
WO (1) WO2008154923A1 (fr)

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JP4623797B2 (ja) * 2000-05-17 2011-02-02 株式会社鷺宮製作所 自動販売機用電動式切換弁
CN1144989C (zh) * 2000-11-03 2004-04-07 Lg电子株式会社 热泵制冷循环的冷却剂分配器
JP4256692B2 (ja) * 2003-02-14 2009-04-22 株式会社鷺宮製作所 電動式切換弁
CN100455953C (zh) * 2004-05-27 2009-01-28 乐金电子(天津)电器有限公司 冷媒分配器及其控制方法
DE102006006731A1 (de) * 2006-02-13 2007-08-16 Danfoss A/S Kühlanlage
DE102007028562B4 (de) * 2007-06-19 2009-03-19 Danfoss A/S Kühlanlage

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JP2010530520A (ja) 2010-09-09
MX2009013756A (es) 2010-01-26
CN101784848A (zh) 2010-07-21
DE102007028565A1 (de) 2008-12-24
US8689582B2 (en) 2014-04-08
WO2008154923A1 (fr) 2008-12-24
US20100281913A1 (en) 2010-11-11
JP5048129B2 (ja) 2012-10-17
RU2426958C1 (ru) 2011-08-20
CN101784848B (zh) 2011-11-16
ATE546698T1 (de) 2012-03-15
EP2174080A1 (fr) 2010-04-14

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