EP1987301B1 - Installation frigorifique - Google Patents

Installation frigorifique Download PDF

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Publication number
EP1987301B1
EP1987301B1 EP20070702485 EP07702485A EP1987301B1 EP 1987301 B1 EP1987301 B1 EP 1987301B1 EP 20070702485 EP20070702485 EP 20070702485 EP 07702485 A EP07702485 A EP 07702485A EP 1987301 B1 EP1987301 B1 EP 1987301B1
Authority
EP
European Patent Office
Prior art keywords
refrigeration system
valve
refrigerant
valves
evaporator
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.)
Active
Application number
EP20070702485
Other languages
German (de)
English (en)
Other versions
EP1987301A1 (fr
Inventor
Torben Funder-Kristensen
Holger Nicolaisen
Jørgen HOLST
Mogens H. Rasmussen
Jan Holm Nissen
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
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Publication date
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Publication of EP1987301A1 publication Critical patent/EP1987301A1/fr
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Publication of EP1987301B1 publication Critical patent/EP1987301B1/fr
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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2511—Evaporator distribution valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86389—Programmer or timer
    • Y10T137/86405—Repeating cycle
    • Y10T137/86421—Variable

Definitions

  • the invention relates to a cooling system with a refrigerant circuit, which has a plurality of evaporator sections and a distributing a distribution of refrigerant to the evaporator sections distributor.
  • Such a cooling system is off US 5,832,744 known.
  • the distributor has between a refrigerant inlet and a plurality of refrigerant outlets 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 over-supply 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.
  • DE-A-174 075 discloses a refrigeration system according to the preamble of claim 1. The invention has for its object to improve the operation of the cooling system with simple means.
  • cooling system If the following is a "cooling system”, then this term is to be understood. It particularly includes cooling systems, freezer systems, air conditioners and heat pumps.
  • the term “refrigeration plant” has been 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 if an evaporator has a plurality of individually or in groups controllable evaporator sections.
  • the distributor has a controllable valve for each evaporator, then it can control the supply of the evaporator individually, ie it is then possible to supply the amount of refrigerant to each evaporator, he needs. There is no need to worry about the fact that the evaporators all have the same flow resistance. It is also of minor importance if the evaporators have to deliver different cooling capacities. An evaporator in which a larger cooling capacity is required, gets correspondingly more refrigerant than an evaporator, which must provide less cooling capacity.
  • the valves can be controlled by a control device that controls individual valves differently.
  • the control device thus ensures the distribution of the refrigerant to the individual evaporator.
  • the control device can also control the valves so that all valves pass through a certain basic flow rate of refrigerant and then, if necessary, a single valve so control that in each case additionally passes the required amount of refrigerant. This is particularly advantageous if the control device controls the valves offset in time from one another.
  • an evaporator gets only from time to time refrigerant, but in total the required amount of refrigerant.
  • the control device thus controls the duty cycle of the individual valve, ie the ratio of the opening time of the individual valve to a predetermined period length.
  • valves may have been turned on once.
  • the period length is chosen so that keep the pressure fluctuations in the evaporators within reasonable limits or even virtually unnoticeable.
  • the valves can all be adjusted with a basic opening, so that all evaporators are permanently supplied with refrigerant.
  • the controller then clocks the individual valves in addition, so that each evaporator receives an additional amount of refrigerant depending on demand to cover the refrigerant demand.
  • the control device controls only a single valve so that it has a passage opening which is larger than a passage opening the other valves. Normally, when all the valves are closed, the controller will always open only one valve at a time. This facilitates the control and sizing of the refrigerant supplied to a single evaporator. If the individual valves already allow a basic flow rate of refrigerant, then only a single valve is opened at a time, in order to supply the evaporator connected to this valve individually with the required total amount of refrigerant.
  • the control device has a rotor which causes the opening of valves. As a result of the rotation of the rotor, the individual valves are opened. This is a very easy way to control the individual valves one after the other.
  • the rotor is driven by a variable speed motor.
  • the speed can then adjust how long the individual valves are open.
  • the engine is reversible. Due to the reversibility of the motor, it is possible to keep a single valve completely closed for a longer period of time. Before the rotor brings this valve in the open position, the motor is reversed in its direction of rotation, so that this valve remains closed. It is also possible to leave several valves closed when these valves are arranged side by side in the direction of rotation of the rotor.
  • the rotor is connected to a cam and the valves have valve tappets actuatable by the cam are.
  • This is a mechanically particularly simple solution to open or close the valves.
  • the plungers are expediently acted upon in the closing direction of the valves by a closing spring. Then, when the cam comes into contact with the plunger, then the valve is opened against the force of the closing spring. The valve closes again as soon as the cam has been rotated further enough.
  • the cam disc has a single cam. This ensures that only one valve can be opened at the same time or opened more than the other valves. Accordingly, it is also possible to individually adjust the opening time of each valve (or the time of the boosted opening), so that this opening time can be largely unaffected by the opening times of the other valves.
  • valve tappets have in the direction of rotation a distance from each other which is at least as large as the extent of the cam in the direction of rotation. This makes it possible to let the cam come to rest in a position in which no valve tappet is acted upon. In this case, all valves can remain closed.
  • valve tappets are arranged parallel to the rotor axis.
  • parallel is not to be understood here as mathematically exact. It is only important that the valve tappets have a component which is directed parallel to the rotor axis.
  • the cam which is arranged on the cam disk, acts parallel to the rotor axis.
  • the cam disc has a displacement drive which acts in a direction parallel to the rotor axis. If the valve tappets are arranged parallel to the rotor axis, it is possible by the displacement of the cam disc in a simple manner, all valves simultaneously open to allow a certain basic flow rate of refrigerant. The cam then each opens a single valve more than the other valves to ensure individual supply of a single evaporator with refrigerant.
  • the rotor has an axially extending inlet channel, which communicates with an input of the distributor, and a radially extending outlet channel, the mouth of which, in rotation with outlet openings, which are in communication with the evaporators in Cover can be brought. So you use the rotor at the same time as an element of the valve.
  • the mouth of the exit port is in register with an exit port, a flow path from the entrance of the transfer port to an exit associated with a particular vaporizer is released. As long as the overlap exists, refrigerant may flow from the manifold inlet to the respective evaporator.
  • the refrigerant supply to the evaporator just described is interrupted and the next output in the direction of rotation is supplied with refrigerant.
  • a greater or lesser amount of refrigerant may flow into the evaporator. This overlap time can be changed by adjusting the speed at which the rotor turns.
  • the outlet openings in the direction of rotation at a distance from each other, which is at least as large as the extension of the mouth of the outlet channel in the rotational direction.
  • a sensor is arranged, which is connected to the control device.
  • This sensor may be, for example, a temperature sensor.
  • Each evaporator can then be supplied with refrigerant depending on the temperature at its outlet.
  • the evaporator sections are arranged with a capacitor in series and a sensor is arranged in front of the condenser or the compressor.
  • a sensor is arranged in front of the condenser or the compressor.
  • a single sensor is sufficient if one knows otherwise the operating behavior of the cooling system. With the knowledge of the operating behavior can then decide which evaporator or evaporator section how much coolant to be supplied.
  • 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 sections 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.
  • FIGS. 2 and 3 show a first embodiment of a distributor 5.
  • the distributor 5 according to Fig. 2 here has six outputs 10a-10f (for six evaporators) and an input 11. Each output 10a-10f is separated from the input 11 by a valve 12. Because the valves all built the same are the following description based on valves 12, which are associated with the outputs 10b, 10e.
  • Each valve 12 has a valve seat 13 which is arranged in a housing block 14. Furthermore, each valve 12 has a valve element 15 which is connected to a valve tappet 16, which protrudes from the housing block 14 on the side opposite the valve seat 13. Both the housing block 14 and the valve element 15 are supported by springs 17, 18 on a cover 19, through which the input 11 is guided and which closes a valve housing 20.
  • the spring 18 is designed as a closing spring which acts on the valve element 15 against the valve seat 13.
  • a cam plate 21 is rotatably mounted in the valve housing 20, a cam plate 21 is rotatably mounted.
  • the cam disc 21 has a single cam 22, which acts on a rotation of the cam disc 21 about a rotation axis 23 each have a valve stem 16 as shown by the left valve (in Fig. 3 ) is recognizable.
  • the cam 22 acts on the valve stem 16
  • the valve element 15 lifts off the valve seat 13 and a passage from the inlet 11 to the outlet 10e is released.
  • the valve element 15 is brought under the action of the spring 18 again to rest against the valve seat 13 and the corresponding valve 12 closes, as can be seen from the valve 10 associated with the output 10b.
  • the cam plate 21 is rotated by a motor 24, which is shown here only schematically.
  • the motor 24 is driven by the control unit 9.
  • the motor 24 is operable at a controlled speed.
  • the maximum speed is for example in the order of 100 U / min.
  • the speed of the motor 24 can be changed.
  • the engine 24 can also be stopped for a short time. Also, the direction of rotation of the motor is changeable.
  • each evaporator is supplied at least once in a period of about one second refrigerant, it can be achieved that the pressure in the corresponding evaporator varies only slightly, so that a negative impact on the cooling system 1 is not to be feared.
  • the cam plate 21 is mounted on a rotor 25 of the motor 24.
  • the rotor 25 can now be displaced by an axial drive 26 in a direction parallel to the axis of rotation 23. For example, if it is moved downwards (based on the representation of the Fig. 3 ), then all the valves 12 are slightly opened, so that permanent refrigerant can flow through all the outputs 10a-10f. This ensures a certain basic supply of all evaporators.
  • the exact setting The amount of refrigerant which is then supplied to the individual evaporator, as before, by the cam 22 of the cam disc 21st
  • the individual valves 12 have in the circumferential or rotational direction of the cam disc 21 a distance which is at least as large as the extent of the cam 22 in the circumferential direction. Accordingly, it is possible to stop the cam plate 21 in a position in which no valve has been opened. Such a position is taken, for example, when the refrigerant supply to any evaporator is not required.
  • the 4 and 5 show a modified embodiment of a manifold 5, in which the same and functionally identical elements are provided with the same reference numerals.
  • the distributor 5 of 4 and 5 also has a rotor 25.
  • the rotor 25 has an input channel 27 which is constantly in register with the input 11 in the valve housing 20, that is independent of the rotational position of the rotor 25th
  • the rotor 25 also has an output channel 28 which is directed substantially radially.
  • the exit channel 28 has an orifice 29 which coincides with exit openings 30a-30f upon rotation of the rotor 25 come.
  • the outlet openings 30a-30f are connected to the exits 10a-10f through which communication with evaporators of the evaporator assembly 6 can be established.
  • the distance between the outlet openings 30a-30f is at least as large as the extent of the mouth 29 of the outlet channel 28 in the circumferential direction. In the in Fig. 4 shown position of the rotor 25, therefore, the output port 28 is closed, so that no refrigerant can be distributed.
  • the operation of the distributor 5 is similar to that in the FIGS. 2 and 3 illustrated embodiment of the distributor. 5
  • the rotor 25 is controlled by the control unit 9, with possibly changing rotational speeds, so that always for a certain time a connection between the input 11 and one of the output ports 30 is present. During this time, refrigerant can flow from the inlet 11 into the corresponding outlet opening 30a-30f and from there to the connected evaporator, which is accordingly charged with a predetermined amount of refrigerant.
  • the connection is opened for a relatively long time. In contrast, if the rotor 25 rotates faster in this situation, then a correspondingly shorter opening time is available. With a longer opening time, more refrigerant can flow into the corresponding evaporator than with a shorter opening time.
  • a predetermined output port 30a-30f can be excluded from the connection with the input 11, so that an output port 30a-30f connected evaporator receives no refrigerant at all for a certain time. During this time, this evaporator can defrost.
  • this sensor is then no longer able to evaluate the desired information for each evaporator or each evaporator section individually.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (12)

  1. Installation de réfrigération (1) comportant un circuit frigorifique, qui présente plusieurs sections d'évaporation (7a-7d) et un distributeur (5) entraînant une répartition de l'agent frigorifique sur les sections d'évaporation (7a-7d), le distributeur (5) présentant pour chaque section d'évaporation (7a-7d) une soupape (12 ; 28, 30a-30f) pouvant être commandée et les soupapes (12 ; 28, 30a-30f) pouvant être commandées par un dispositif de commande (9, 24), lequel commande différemment les diverses soupapes (12 ; 28, 30a-30f), caractérisée en ce que le dispositif de commande (9, 24) présente un rotor (25), lequel provoque l'ouverture des soupapes (12 ; 28, 30a-30f), le dispositif de commande (9, 24) commandant uniquement une seule soupape (12 ; 28, 30a-30f) de telle manière que ladite soupape présente une ouverture de passage plus grande que l'ouverture de passage des autres soupapes.
  2. Installation de réfrigération selon la revendication 1, caractérisée en ce que le rotor (25) est entraîné par un moteur (24) à vitesse variable.
  3. Installation de réfrigération selon la revendication 2, caractérisée en ce que le moteur (24) est réversible.
  4. Installation de réfrigération selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le rotor (25) est relié à un disque à came (21), et les soupapes (12) présentent des poussoirs de soupape (16), lesquels peuvent être actionnés grâce au disque à came (21).
  5. Installation de réfrigération selon la revendication 4, caractérisée en ce que le disque à came (21) présente une seule came (22).
  6. Installation de réfrigération selon la revendication 5, caractérisée en ce que les poussoirs de soupape (16) présentent les uns par rapport aux autres dans le sens de la rotation une distance, qui est au moins aussi grande que l'extension de la came (22) dans le sens de la rotation.
  7. Installation de réfrigération selon l'une quelconque des revendications 4 à 6, caractérisée en ce que les poussoirs de soupape (16) sont disposés de manière parallèle par rapport à l'axe du rotor (23).
  8. Installation de réfrigération selon la revendication 7, caractérisée en ce que le disque à came (21) présente une commande de déplacement (26), laquelle agit dans une direction, de manière parallèle par rapport à l'axe du rotor (23).
  9. Installation de réfrigération selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le rotor (25) présente un canal d'entrée (27) s'étendant de manière axiale, lequel canal d'entrée est en liaison avec une entrée (11) du distributeur (5), et un canal de sortie (28) s'étendant de manière radiale, dont l'embouchure (29) peut être amenée lors de la rotation en chevauchement avec des ouvertures de sortie (30a-30f), lesquelles sont en liaison avec les évaporateurs.
  10. Installation de réfrigération selon la revendication 9, caractérisée en ce que les ouvertures de sortie (30a-30f) présentent les unes par rapport aux autres dans le sens de la rotation une distance, qui est au moins aussi grande que l'extension de l'embouchure (29) du canal de sortie (28) dans le sens de la rotation.
  11. Installation de réfrigération selon l'une quelconque des revendications 1 à 10, caractérisée en ce qu'un capteur (8a-8d) est disposé au niveau de la sortie de chaque section d'évaporation (7a-7d), lequel capteur est relié au dispositif de commande (9, 24).
  12. Installation de réfrigération selon l'une quelconque des revendications 1 à 10, caractérisée en ce que les sections d'évaporation (7a-7d) sont disposées en rangée avec un condensateur (3), et un capteur est disposé avant le condensateur (3) ou le compresseur (2).
EP20070702485 2006-02-13 2007-02-09 Installation frigorifique Active EP1987301B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610006731 DE102006006731A1 (de) 2006-02-13 2006-02-13 Kühlanlage
PCT/DK2007/000067 WO2007093175A1 (fr) 2006-02-13 2007-02-09 Installation frigorifique

Publications (2)

Publication Number Publication Date
EP1987301A1 EP1987301A1 (fr) 2008-11-05
EP1987301B1 true EP1987301B1 (fr) 2010-07-07

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070702485 Active EP1987301B1 (fr) 2006-02-13 2007-02-09 Installation frigorifique

Country Status (8)

Country Link
US (2) US8191384B2 (fr)
EP (1) EP1987301B1 (fr)
JP (1) JP4896993B2 (fr)
CN (1) CN101384869B (fr)
AT (1) ATE473404T1 (fr)
DE (2) DE102006006731A1 (fr)
RU (1) RU2395759C2 (fr)
WO (1) WO2007093175A1 (fr)

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CN2397325Y (zh) * 1999-09-21 2000-09-20 洪陵成 流体切换阀
JP2003004340A (ja) * 2001-06-20 2003-01-08 Fujitsu General Ltd 冷媒分配器
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KR100447204B1 (ko) * 2002-08-22 2004-09-04 엘지전자 주식회사 냉난방 동시형 멀티공기조화기 및 그 제어방법
DE102004028865B4 (de) * 2003-06-20 2007-06-06 Danfoss A/S Kälteanlage
US6804976B1 (en) * 2003-12-12 2004-10-19 John F. Dain High reliability multi-tube thermal exchange structure
US6898945B1 (en) * 2003-12-18 2005-05-31 Heatcraft Refrigeration Products, Llc Modular adjustable nozzle and distributor assembly for a refrigeration system
KR100546616B1 (ko) 2004-01-19 2006-01-26 엘지전자 주식회사 멀티공기조화기의 제어방법
JP4268931B2 (ja) * 2004-12-30 2009-05-27 中山エンジニヤリング株式会社 冷蔵・冷凍設備及びその制御方法
DE102006006731A1 (de) * 2006-02-13 2007-08-16 Danfoss A/S Kühlanlage

Also Published As

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CN101384869A (zh) 2009-03-11
JP2009526192A (ja) 2009-07-16
RU2395759C2 (ru) 2010-07-27
EP1987301A1 (fr) 2008-11-05
DE102006006731A1 (de) 2007-08-16
US20120198876A1 (en) 2012-08-09
CN101384869B (zh) 2014-10-01
US8191384B2 (en) 2012-06-05
US8656732B2 (en) 2014-02-25
ATE473404T1 (de) 2010-07-15
JP4896993B2 (ja) 2012-03-14
WO2007093175A1 (fr) 2007-08-23
US20090217687A1 (en) 2009-09-03
DE502007004320D1 (de) 2010-08-19
RU2008136475A (ru) 2010-03-20

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