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 refrigeration system is known from US 5 832 744.
• 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 known distributors theoretically ensure a uniform distribution of the refrigerant to the individual evaporator.
• the individual evaporators basically have the same thermal load and also the same flow resistance. If this is not the case, the case may occur that an evaporator receives too much refrigerant, so that the refrigerant is not fully recovered. is constantly evaporated before it has passed through the evaporator.
• Another evaporator which is connected to the same manifold, can get too little refrigerant, so that the evaporator can not provide the desired cooling capacity.
• the over-supply or the 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 conditions, which further deteriorates the capacity and the effectiveness of the cooling system.
• the invention has for its object to improve the operation of the cooling system with simple means.
• cooling system any cooling system that 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 connection with several 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 evaporators individually, ie it is then possible to supply the amount of refrigerant to each evaporator. feed that 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 which 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 means controls only a single valve so that it has a passage opening which is larger than a fürlouöff- tion of 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 5 already allow a basic flow rate of refrigerant, only one single valve is ever opened further in order to supply the evaporator connected to this valve individually with the required total amount of refrigerant.
• control device has a rotor, which the
• Opening of valves causes. 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 into 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 plate 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 communicating with an inlet of the distributor and a radially extending outlet channel, the mouth of which, in rotation with outlet openings communicating with the evaporators, can be brought in overlap. So you use the rotor at the same time as an element of the valve. If the mouth of the outlet channel is in register with an outlet opening, then a flow path from the inlet of the distributor to an outlet associated with a particular evaporator 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 vaporizer. This overlap time can be changed by adjusting the speed at which the rotor turns.
• the outlet openings in the rotational direction 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 is a schematic representation of a cooling system with multiple evaporators
• FIG. 2 is a plan view of a first embodiment of a distributor
• FIG. 3 shows a section III-III of FIG. 2
• Fig. 4 is a sectional view IV-IV of FIG. 5 by a second embodiment of a distributor and
• FIG. 5 is a sectional view V-V of FIG .. 4
• 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 with a plurality of evaporators arranged in parallel 7a-7d are connected together in a circuit.
• the evaporator arrangement 6 can also have a single evaporator, which has a plurality of evaporator sections, 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.
• each evaporator 7a-7d At the outlet of each evaporator 7a-7d is a temperature sensor 8a
• 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.
• FIG. 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-1 Of is separated from the input 11 by a valve 12. Since the valves are all the same are constructed, the following description is 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 can be seen by the left valve (in Fig. 3).
• 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.
• Valve stem 16 leaves, 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 output 10 b associated valve 12.
• 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 a size 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.
• the individual valves 12 are now each opened so long during one revolution of the cam disc 21 that a sufficient amount of refrigerant can flow through the respective exits 10a-10f, so that the evaporators 7a -7d get enough refrigerant, but not too much refrigerant. If an evaporator requires less refrigerant, then when the cam 22 engages the corresponding plunger 16 of the valve 12, the cam plate 21 will be rotated faster, leaving the valve 12 open only for a shorter time. On the other hand, if an evaporator required a larger amount of refrigerant, the cam disc 21 would rotate more slowly when the cam 22 is in the region of the valve associated with the corresponding outlet.
• 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 displaced downwardly (based on the illustration of FIG. 3), then all the valves 12 are slightly opened, so that refrigerant can flow permanently through all the outlets 10a-1 Of. 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.
• FIGS. 4 and 5 show a modified embodiment of a distributor
• the distributor 5 of FIGS. 4 and 5 also has a rotor 25.
• the rotor 25 has an inlet channel 27 constantly in register with the inlet 11 in the valve housing 20, i. regardless of the rotational position of the rotor 25th
• the rotor 25 also has an output channel 28 which is directed substantially radially.
• the outlet channel 28 has an orifice 29, which, upon rotation of the rotor 25, is provided with outlet openings 30a-30f in overflow. come cover.
• the outlet ports 30a-30f are connected to the ports 10a-10f through which communication with evaporators of the evaporator assembly 6 can be made.
• 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 position of the rotor 25 shown in Fig. 4, therefore, the output port 28 is closed, so that no refrigerant can be distributed.
• the operation of the distributor 5 is similar to the embodiment of the distributor 5 shown in FIGS. 2 and 3.
• the rotor 25 is controlled under the control of the control unit 9, under circumstances changing rotational speeds, so that there is always a connection between the input 11 and one of the output ports 30 for a certain time. 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 accordingly receives a predetermined amount of refrigerant.
• the connection is opened for a relatively long time. If, however, 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 opening 30a-30f can also be excluded from the connection with the input 11, so that a signal to this output opening 30a is provided.
• 3Of connected evaporator receives no refrigerant at all for a certain time. During this time, this evaporator can defrost.

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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)

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• 2006
  • 2006-02-13 DE DE200610006731 patent/DE102006006731A1/de not_active Withdrawn
• 2007
  • 2007-02-09 JP JP2008553619A patent/JP4896993B2/ja not_active Expired - Fee Related
  • 2007-02-09 RU RU2008136475A patent/RU2395759C2/ru not_active IP Right Cessation
  • 2007-02-09 AT AT07702485T patent/ATE473404T1/de active
  • 2007-02-09 EP EP20070702485 patent/EP1987301B1/fr active Active
  • 2007-02-09 DE DE200750004320 patent/DE502007004320D1/de active Active
  • 2007-02-09 WO PCT/DK2007/000067 patent/WO2007093175A1/fr active Application Filing
  • 2007-02-09 CN CN200780005185.3A patent/CN101384869B/zh active Active
  • 2007-02-09 US US12/278,158 patent/US8191384B2/en active Active
• 2012
  • 2012-04-20 US US13/451,872 patent/US8656732B2/en active Active

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