CN101932883A - Refrigerant system with reheat refrigerant circuit - Google Patents
Refrigerant system with reheat refrigerant circuit Download PDFInfo
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- CN101932883A CN101932883A CN2008801259834A CN200880125983A CN101932883A CN 101932883 A CN101932883 A CN 101932883A CN 2008801259834 A CN2008801259834 A CN 2008801259834A CN 200880125983 A CN200880125983 A CN 200880125983A CN 101932883 A CN101932883 A CN 101932883A
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- refrigerant
- refrigerant system
- reheat
- refrigeration agent
- room air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
- F24F11/43—Defrosting; Preventing freezing of indoor units
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- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/06—Removing frost
- F25D21/12—Removing frost by hot-fluid circulating system separate from the refrigerant system
- F25D21/125—Removing frost by hot-fluid circulating system separate from the refrigerant system the hot fluid being ambient air
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
A refrigerant system is provided that includes a cooling refrigerant circuit, a reheat refrigerant circuit, an evaporator fan, and a controller. The evaporator fan forces indoor air in a first direction and a second direction. The indoor air passes across the evaporator before the reheat coil, in the first direction, but passes across the reheat coil before the evaporator, in the second direction. The controller, when in a conventional cooling mode, controls the reheat refrigerant circuit so that the reheat refrigerant circuit is not in fluid communication with the cooling refrigerant circuit and controls the evaporator fan to force the indoor air in the first direction. Conversely, the controller, when in a defrost mode, controls the reheat refrigerant circuit so that the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and controls the evaporator fan to force the indoor air in the second direction.
Description
Technical field
Present disclosure relates to refrigerant system.More specifically, the refrigerant system with the defrost function that is provided by reheat refrigerant circuit is provided present disclosure.
Background technology
Utilize refrigerant system to control the temperature and/or the humidity of the air in the various environment to be regulated.In the typical refrigerant system with the operation of conventional refrigerating mode, cold-producing medium compresses in compressor and is delivered to heat dissipation heat exchanger (perhaps, in many cases, being outdoor heat converter).In heat dissipation heat exchanger, externally between surrounding air and the compressed refrigerant exchanged heat to remove heat from compressed refrigerant.
Cold-producing medium is delivered to expansion gear from heat dissipation heat exchanger, and in expansion gear, cold-producing medium is expanded to lower pressure and lower temperature, and arrives evaporimeter (perhaps, in typical air conditioner facility, being indoor heat converter) then.In evaporimeter, exchanged heat is to remove heat from room air between current cold lower pressure cold-producing medium and room air.In this way, evaporator cools is provided to the air of conditioned environment.
In addition, because the temperature of conditioned air is lowered, therefore usually take away moisture from conditioned air.In this way, refrigerant system is also controlled the humidity level in the conditioned environment.
In some cases, when system during, provide the temperature levels of the conditioned air of wishing that the humidity level is required to be lower than the desired temperature of conditioned air with the operation of conventional refrigerating mode.Therefore, many refrigerant systems comprise hot coil or heat exchanger (being called " coil pipe " hereinafter) again, and hot coil or heat exchanger are positioned in the conditioned air stream in evaporimeter downstream again.In this way, in evaporimeter, be conditioned (for example, cooling and dehumidifying) at air afterwards, hotter again this conditioned air of hot coil.
The moisture that removes from air usually also can be on the outer surface of evaporimeter condensation and freezing often, this can reduce the efficient of refrigerant system, and also can cause the refrigerant system fault.Therefore, defrost system that many refrigerant systems need be special and equipment (such as, electric heater), this can increase the cost and the complexity of refrigerant system.
Therefore, have the lasting needs to the method for refrigerant system and this refrigerant system of control, it makes evaporator defrost overcome above-mentioned one or more problems and other unfavorable effect of prior art simultaneously.
Summary of the invention
The invention provides a kind of refrigerant system, it comprises cooling refrigeration agent loop, reheat refrigerant circuit, evaporator fan and controller.Cooling refrigeration agent loop comprises evaporimeter.Reheat refrigerant circuit comprises hot coil again.Evaporator fan can promote room air at first direction and second direction.Room air passes evaporimeter earlier at first direction and passes hot coil more again, passes evaporimeter again but pass hot coil earlier in second direction again.When being in conventional refrigerating mode, controller control reheat refrigerant circuit makes reheat refrigerant circuit not become fluid to be communicated with cooling refrigeration agent loop and controls evaporator fan to promote room air at first direction.On the contrary, when being in defrosting mode, controller control reheat refrigerant circuit makes reheat refrigerant circuit become fluid to be communicated with cooling refrigeration agent loop and the control evaporator fan promotes room air in second direction.At conventional dehumidification mode, controller control reheat refrigerant circuit makes reheat refrigerant circuit become fluid to be communicated with cooling refrigeration agent loop and controls evaporator fan to promote room air in second direction.
In certain embodiments, refrigerant system comprises cooling refrigeration agent loop, reheat refrigerant circuit, evaporator fan and controller.Cooling refrigeration agent loop comprises evaporimeter.Reheat refrigerant circuit comprises hot coil again.Evaporator fan rotates to promote room air at first direction and to rotate to promote room air in second direction in second direction of rotation in first direction of rotation.Evaporimeter is positioned at hot coil upstream again in first direction.When reheat refrigerant circuit do not become fluid to be communicated with cooling refrigeration agent loop and evaporator fan when first direction of rotation is rotated, controller is operated this refrigerant system with conventional refrigerating mode.When reheat refrigerant circuit become fluid to be communicated with cooling refrigeration agent loop and evaporator fan when second direction of rotation is rotated, controller is also operated this refrigerant system with defrosting mode.When becoming fluid connection and evaporator fan controller when first direction of rotation is rotated with cooling refrigeration agent loop, reheat refrigerant circuit operates this refrigerant system with conventional dehumidification mode.
In other embodiments, refrigerant system comprises cooling refrigeration agent loop, reheat refrigerant circuit, the evaporator fan that rotates in single direction of rotation, one or more air door and controller.Cooling refrigeration agent loop comprises evaporimeter.Reheat refrigerant circuit comprises hot coil again.Air door is in the flow path of room air and have two positions.Primary importance promotes room air at first direction, so room air passes evaporimeter earlier and passes hot coil more again.The second place promotes room air in second direction, so room air passes hot coil earlier again and passes evaporimeter again.When reheat refrigerant circuit does not become fluid to be communicated with or isolates at least in part with cooling refrigeration agent loop and one or more air door when being in primary importance with cooling refrigeration agent loop, controller is operated this refrigerant system with conventional refrigerating mode.Controller is also operated this refrigerant system with defrosting mode when reheat refrigerant circuit becomes fluid connection and one or more air door to be in the second place with cooling refrigeration agent loop.When reheat refrigerant circuit became fluid connection and one or more air door to be in primary importance with cooling refrigeration agent loop, controller was operated this refrigerant system with conventional dehumidification mode.
By specific descriptions, accompanying drawing and appended claims hereinafter, those skilled in the art will understand and understand the above-mentioned and further feature and the advantage of present disclosure.
Description of drawings
Fig. 1 is the schematic depiction according to the exemplary embodiment of the refrigerant system of present disclosure with the operation of normal or conventional refrigerating mode.
Fig. 2 is with the schematic depiction of the refrigerant system of Fig. 1 of heat or conventional dehumidification mode operation again;
Fig. 3 is the schematic depiction with the refrigerant system of Fig. 1 of defrosting mode operation;
Fig. 4 is with the normal mode and the schematic depiction of the alternate embodiment of the refrigerant system of Fig. 1 of heat pattern operation again; And
Fig. 5 is the schematic depiction with the refrigerant system of Fig. 4 of defrosting mode operation.
The specific embodiment
Referring to accompanying drawing and especially referring to Fig. 1, the exemplary embodiment according to the refrigerant system of present disclosure is shown, generally by Reference numeral 10 expressions.
Cooling refrigeration agent loop 12 comprises compressor 18, heat dissipation heat exchanger 20, expansion gear 22 and evaporimeter 24, and all these devices are communicated with to use known cold-producing medium (not shown) that (for example) cooling or heating function are provided each other in fluid in a known way.Refrigerant system 10 also comprises heat dissipation heat exchanger fan 26, evaporator fan 28 and refrigerant system controller 30.
The normal manipulation mode of refrigerant system 10 has been described referring to Fig. 1.
Herein, compressor 18 sucks the low pressure refrigerant 40 of vapor form and this low-pressure steam cold-producing medium is compressed into high pressure and high temperature refrigerant 42.Vapor refrigerant flows to heat dissipation heat exchanger 20 from compressor 18.Controller 30 control by-passing valves 36 make cold-producing medium 42 flow through heat dissipation heat exchanger 20 and do not pass through bypass refrigerant loop 16 to the closed position.Therefore, controller 30 control by-passing valves 36 make that bypass refrigerant loop 16 is not communicated with the 12 one-tenth fluids in cooling refrigeration agent loop during normal manipulation mode.
Heat dissipation heat exchanger 20 serves as condenser in subcritical cycle, perhaps in striding critical cycle, serve as gas cooler, wherein with conduct heat such as a secondary fluid of outside or surrounding air 44 interact during, a secondary fluid is forced by heat dissipation heat exchanger fan 26 and passes heat dissipation heat exchanger 20.In this way, in subcritical applications, vapor refrigerant 42 is condensed into liquid refrigerant 46 and common cold excessively point by desuperheat to it, perhaps just be cooled to thermodynamic state 46 from thermodynamic state 42 simply in striding critical applications.As everyone knows, the alternative fan 26 of liquid pump comes pumping secondary loop liquid, and secondary loop liquid instead of external or surrounding air 44 are carried out to conduct heat in heat dissipation heat exchanger 20 and interacted.
Cold-producing medium 46 comes out to flow to expansion gear 22 from heat dissipation heat exchanger 20.Controller 30 controls first thermal valve 34-1 again make cold-producing medium 46 by expansion gear 22 and not mobile by reheat refrigerant circuit 14 to the closed position.Therefore, controller 30 control first again thermal valve 34-1 make during normal or conventional cooling down operation pattern reheat refrigerant circuit 14 with 12 the one-tenths fluids connections in cooling refrigeration agent loop.
In certain embodiments, second again thermal valve 34-2 can be check-valves, it guarantees that cold-producing medium 46 does not enter reheat refrigerant circuit 14.In other embodiments, second again thermal valve 34-2 can with controller 30 electric connections, controller 30 during normal manipulation mode, control second again thermal valve 34-2 to the closed position to guarantee that cold-producing medium 46 does not enter reheat refrigerant circuit 14.
Can see, again room air 50 mobile the be positioned downstream in first direction 54 of hot coil 32 about causing by evaporator fan 28.But because thermal valve 34-1,34-2 are in the closed position again, the flowing of the conditioned air 52 by hot coil 32 again do not cause any further adjusting of this conditioned air or heat again.
Therefore, during refrigerant system 10 normal manipulation modes, controller 30 starting compressors 18, starting heat dissipation heat exchanger fan 26, close by-passing valve 36, close thermal valve 34-1 and 34-2 again, start expansion valve 22 where necessary, and starting evaporator fan 28 passes evaporimeter 24 and hot coil 32 again to force room air 50 at first direction.Because controller 30 control evaporator fans 28 are to promote room air 50 at first direction 54, this room air is forced to pass earlier evaporimeter 24, passes hot coil 32 then again.
In the embodiment that Fig. 1 described, refrigerant system 10 is configured to promote room air 50 in 56 rotations of first direction of rotation at first direction 54 by control evaporator fan 28.Should be noted that evaporator fan 28 can be variable speed model and makes controller 30 also can control the speed of evaporator fan 28 (if needs).
The hot again operator scheme of refrigerant system 10 is described referring to Fig. 2.
Generally speaking, refrigerant system 10 is being operated in the mode substantially the same with normal mode in the heat pattern again, except controller 30 control first again thermal valve 34-1 make cold-producing medium 46 flow through reheat refrigerant circuit 14 earlier and then only by expansion gear 22 to open position.Therefore, controller 30 control first again thermal valve 34-1 make 12 one-tenth fluids connections of reheat refrigerant circuit 14 and cooling refrigeration agent loop during hot operator scheme again.
In use, compressor 18 sucks the low pressure refrigerant 40 of vapor form and this low-pressure steam cold-producing medium is compressed into high pressure, high temperature refrigerant 42.Vapor refrigerant flows to heat dissipation heat exchanger 20 from compressor 18.
Heat dissipation heat exchanger 20 serves as condenser in subcritical cycle, perhaps in striding critical cycle, serve as gas cooler, wherein during interacting with outside or surrounding air 44 heat transfers, outside or surrounding air 44 are forced by heat dissipation heat exchanger fan 26 and pass heat dissipation heat exchanger 20.In this way, in subcritical applications, vapor refrigerant 42 is condensed into liquid refrigerant 46 and common cold excessively point by desuperheat to it, perhaps just is cooled to thermodynamic state 46 from thermodynamic state 42 simply in striding critical applications.Equally, the liquid pump can replace fan 26 to come pumping secondary loop liquid, and secondary loop liquid instead of external or surrounding air 44 are carried out to conduct heat in heat dissipation heat exchanger 20 and interacted.
Cold-producing medium 46 comes out to flow to the first thermal valve 34-1 again from heat dissipation heat exchanger 20.Controller 30 control first thermal valve 34-1 again makes cold-producing medium 46 flow through hot coil 32 to open position again, by the second thermal valve 34-2 and only flowing in the expansion gear 22 then again.
In certain embodiments, second again thermal valve 34-2 can be check-valves, it allows cold-producing medium 46 to come out to get back to cooling refrigeration agent loop 12 from reheat refrigerant circuit 14.In other embodiments, second again thermal valve 34-2 can with controller 30 electric connections, its during hot operator scheme again control second again thermal valve 34-2 enter cooling refrigeration agent loop 12 once more to allow cold-producing medium 46 to open position.
Because cold-producing medium 46 is not expanded by expansion gear 22 as yet, the thermal capacity that can use cold-producing medium 46 is with the hot again conditioned air 52 of the mode that hereinafter discusses in more detail.
Can see that hot coil 32 is about by mobile the be positioned downstream of evaporator fan 28 caused room airs 50 in first direction 54 again.Because cold-producing medium 46 is just flowing through hot coil 32 again, conditioned air 52 flows through hot coil 32 again and makes that again hot coil 32 serves as heat dissipation heat exchanger, wherein take place from the cold-producing medium to the air the biography reheat heat this air, and wherein conditioned air 52 is forced by evaporator fan 28 and passes hot coil 32 again.In this way, conditioned air 52 can reheat to temperature desired by hot coil 32 again and keep desirable humidity to provide by the air 58 of heat again by evaporimeter 24 simultaneously.
Therefore, during the hot again operator scheme of refrigerant system 10, controller 30 starting compressors 18, starting heat dissipation heat exchanger fan 26, control by-passing valve 36, open the first thermal valve 34-1 again, start expansion valve 22 and starting evaporator fan 28 where necessary and pass evaporimeter 24 and hot coil 32 again at first direction 54 to force room air 50.Therefore, thereby controller 30 control evaporator fans 28 force room air 50 to pass evaporimeter 24 earlier to promote air at first direction 54, pass hot coil 32 then to provide by the air 58 of heat more again.
In the embodiment shown in Figure 2, refrigerant system 10 is configured to rotate in first direction of rotation 56 and force room air 50 at first direction 54 by control evaporator fan 28.
Will be appreciated that many reheat loop schematic diagrames are known in the air-conditioning technical.Therefore, Fig. 2 schematic diagram is exemplary, and any refrigerant system that has merged any other reheat loop configuration can be benefited from present disclosure equally.
The defrost operation pattern of refrigerant system 10 is described referring to Fig. 3.
Substantially, refrigerant system 10 in defrosting mode to operate with the substantially the same mode of heat pattern again, preferably control by-passing valve 36 except controller 30 and make at least a portion of high pressure, high temperature refrigerant 42 flow through bypass refrigerant loop 16 but not heat dissipation heat exchanger 20, and the flow direction that makes room air 50 pass evaporimeter 24 is reversed second direction 60 (Fig. 3) from first direction 54 (Fig. 1 and Fig. 2) to open position.In addition, bypass refrigerant loop 16 can be designed to basically, and all vapor refrigerant 42 flow through bypass refrigerant loop 16, perhaps alternatively, cut-off electromagnetic valve (not shown) can be positioned over heat dissipation heat exchanger 20 upstreams and flows by any of heat dissipation heat exchanger 20 to prevent vapor refrigerant 42.
In the defrost operation pattern, compressor 18 sucks the low pressure refrigerant 40 of vapor form and this low-pressure steam cold-producing medium is compressed into high pressure, high temperature refrigerant 42.Vapor refrigerant 42 flows to heat dissipation heat exchanger 20 and bypass refrigerant loop 16 from compressor 18.
But in certain embodiments, controller 30 can be controlled by-passing valve 36 makes the part of vapor refrigerant 42 flow through heat dissipation heat exchanger 20 and remainder flows through bypass circulation 16 to partially opening the position.In addition, in certain embodiments, controller 30 can control heat dissipation heat exchanger fan 26 to off-state to prevent any available heat exchange between the cold-producing medium and surrounding air in the heat dissipation heat exchanger 20.And, should be noted that in some cases such as refrigerant charge migration excessive under some environmental conditions, controller 30 can be controlled by-passing valve 36 to the closed position.
High pressure, high temperature refrigerant 42A comes out to flow to the first thermal valve 34-1 again from bypass refrigerant loop 16 and/or heat dissipation heat exchanger 20.Controller 30 control first thermal valve 34-1 again makes high pressure, high temperature refrigerant 42A flow through hot coil 32 to open position again, by the second thermal valve 34-2 and only flowing in the expansion gear 22 then again.
In certain embodiments, second again thermal valve 34-2 can be check-valves, it allows cold-producing medium 42B to come out to get back to cooling refrigeration agent loop 12 from reheat refrigerant circuit 14.In other embodiments, second again thermal valve 34-2 can with controller 30 electric connections, during the defrost operation pattern, controller 30 control second thermal valve 34-2 is again returned to allow cold-producing medium 42B to enter the cooling refrigeration agent once more to open position. road 12.
Present disclosure has determined that the heat (being aided with the heat that evaporator fan 28 provides) of cold-producing medium 42A can be used for being reversed second direction 60 (Fig. 3) by the flow direction that makes the room air 50 that passes evaporimeter 24 simply from first direction 54 (Fig. 1 and Fig. 2) in the mode that hereinafter discusses in more detail and makes evaporimeter 24 defrostings.
Because cold-producing medium 42A drag flow fortune promotes room airs 50 by hot coil 32 again and in second direction 60, this room air 50 is heated into air 62 in the hot cell by the cold-producing medium that flows through again hot coil 32, forces subsequently that air 62 passes evaporimeter 24 in this hot cell.
Herein, hot coil 32 serves as heat dissipation heat exchanger again, and wherein heat is transferred to room air 50 from cold-producing medium 42A, and room air 50 is forced by evaporator fan 28 and passes hot coil 32 again.In this way, room air 50 can be heated to temperature desired and make the air 62 fusible any frosts that formed in the hot cell on the outer surface of evaporimeter 24.
In addition, hot coil 32 serves as heat dissipation heat exchanger again, wherein make that desuperheat is condensed into the point of liquid refrigerant 42B to it under the situation of vapor refrigerant 42A at condenser during interacting conducting heat with room air 50, liquid refrigerant 42B is then usually by cold excessively, and is cooled to thermodynamic state 42B under the situation of gas cooler simply.Expansion gear 22 expand into low-pressure low-temperature two-phase mixture cold-producing medium 48 with cold-producing medium 42B and makes it to flow in the evaporimeter 24.Evaporimeter 24 serves as and is subjected to heat-heat exchanger, wherein takes place between the air 62 to conduct heat in cold-producing medium 48 and hot cell to interact, and air is forced by evaporator fan 28 and passes evaporimeter 24 in the hot cell.In this way, low-pressure steam cold-producing medium 40 is got back in cold-producing medium 48 evaporations, and air 62 is cooled so that air 64 to be provided in the hot cell.Vapor refrigerant 40 flows back to compressor 18 from evaporimeter 24 then.
Therefore, during the defrost operation pattern of refrigerant system 10, controller 30 starting compressors 18, inactive where necessary heat dissipation heat exchanger fan 26, open (if needs) by-passing valve 36, open the first thermal valve 34-1 again, control (if needs) expansion valve 22, and make evaporator fan 28 force room air 50 to pass evaporimeter 24 and hot coil 32 again in second direction 60.
In the embodiment shown in fig. 3, refrigerant system 10 can by control evaporator fan 28 in second direction of rotation 66 (it is opposite with first direction of rotation 56) thus rotation at second direction 60 promotion room airs 50.
Will be appreciated that refrigerant system 10 describes in illustrational mode hereinbefore, it is provided at the room air 50 of first direction 54 and second direction 60 by the direction of rotation that changes evaporator fan 28 between first direction of rotation 56 and second direction of rotation 66.Certainly, present disclosure contemplates the room air 50 that refrigerant system 10 is configured to be provided at by any way first direction 54 and second direction 60.Should be appreciated that when controller 30 and operate this refrigerant system 10 with defrosting mode and when second direction 60 moves room air 50, but outside air 64 guide chamber that evaporimeter 24 comes out, indoor or any other assigned position.
Will be appreciated that axial fan and transverse fan are suitable for switching air-flow direction most, the former is (by switching the direction of rotation of fan simply) and the latter (by implement special design feature (being generally lever) in fan drum).The decision design configuration of centrifugal fan is described hereinafter.In addition, the design alternative of refrigerant system 10 and various configuration are feasible and within the scope of the invention and can benefit from present disclosure equally.
For example, in the alternate embodiment of the configuration of the refrigerant system 10 of the room air 50 that is provided at first direction 54 and second direction 60 shown in Fig. 4 and Fig. 5., the part of refrigerant system 10 only is shown for clarity herein, but has described the air duct configuration in more detail.
In this embodiment, controller 30 control evaporator fans 28 are in the single direction rotation, such as first direction of rotation 56.In addition, the position of the one or more air doors 70 of controller 30 controls is to change the flow direction of room air 50 by the indoor member of refrigerant system 10.
Therefore, air door 70 is positioned to when refrigerant system 10 is in normal manipulation mode or hot operator scheme more shown in Figure 4, can promote room air 50 at first direction 54 and pass evaporimeter 24 earlier to form conditioned air 52, force this conditioned air 52 to pass again hot coil 32 then to cause room air 50 to be forced to.At normal manipulation mode, conditioned air 52 be can't help hot coil 32 heat more again, and hot coil breaks away from again, and the feasible air that is cooled and is dehumidified usually 52 is provided to conditioned environment in the mode of above being discussed.In hot operator scheme again, conditioned air 52 by hot coil 32 more again heat make again the air 58 of heat be provided to conditioned environment in the mode of above being discussed.
On the contrary, air door 70 is positioned to when refrigerant system 10 is in defrost operation pattern shown in Figure 5, can promote room airs 50 in second direction 60 and pass again hot coil 32 earlier to form air 62 in the hot cell, force then that air passes evaporimeter 24 so that evaporator defrost in this hot cell to cause room air 50 to be forced to.
Should be appreciated that refrigerant system 10 describes in illustrational mode in Fig. 4 and Fig. 5, make air-flow direction reverse by using four air doors 70.Certainly, present disclosure contemplates refrigerant system 10 and comprises that the air, ducted systems that is associated of air door 70 has various configurations and additional designs feature.All these are configured in the scope of present disclosure and can benefit from present disclosure equally.
Should also be clear that at Fig. 1 can have various selections and promote feature to refrigerant system 10 shown in Figure 3, all these imaginations are in the scope of present disclosure and can similarly benefit from present disclosure.
For example, 12 one-tenth selectivity fluids in position and cooling refrigeration agent loop of being illustrated between heat dissipation heat exchanger 20 and the expansion gear 22 of reheat refrigerant circuit 14 are communicated with.But present disclosure contemplates any configuration that refrigerant system 10 has reheat loop 14, prerequisite be during normal manipulation mode and hot again operator scheme again hot coil 32 50 be positioned at the downstream about flowing of the room air that causes by evaporator fan 28.
Should also be clear that term " first ", " second ", " the 3rd ", " on ", D score and similar word can be used to modify various elements in this article.These qualifiers do not hint space, order or the layering order of the element of being modified, unless so statement clearly.
Though described present disclosure with reference to one or more exemplary embodiments, it will be understood by a person skilled in the art that and under the situation of the scope that does not depart from present disclosure, can make various variations and equivalent can replace element of the present invention.In addition, under the situation that does not depart from scope of the present invention, can make many modifications so that particular condition or material adapt to the instruction content of present disclosure.Therefore, be intended that present disclosure and be not limited to open specific embodiment, but present disclosure will comprise all embodiment in the scope that falls into appended claims as the preferred forms that is contemplated.
Claims (20)
1. refrigerant system, it comprises:
Cooling refrigeration agent loop, it comprises heat dissipation heat exchanger and the evaporimeter that is communicated with each other in serial fluid;
Reheat refrigerant circuit, it comprises the heat-heat exchanger again that becomes the selectivity fluid to be communicated with described cooling refrigeration agent loop;
Evaporator fan, it is configured to promote room air at first direction and second direction, pass described evaporimeter earlier at the described room air of described first direction and pass described heat-heat exchanger more again, pass described heat-heat exchanger more earlier at the described room air of described second direction and pass described evaporimeter again; And,
Controller, it is configured to the described refrigerant system of one of refrigerating mode and defrosting mode operation,
Wherein, when described refrigerant system is in described refrigerating mode, described controller is controlled described reheat refrigerant circuit and is made described reheat refrigerant circuit isolate with described cooling refrigeration agent loop at least in part and control described evaporator fan promoting described room air at described first direction, and
Described controller is controlled described reheat refrigerant circuit and is made described reheat refrigerant circuit become fluid to be communicated with described cooling refrigeration agent loop and control described evaporator fan to promote described room air in described second direction when described refrigerant system is in described defrosting mode.
2. refrigerant system as claimed in claim 1, wherein, described controller also is configured to make described reheat refrigerant circuit become the fluid connected sum to control described evaporator fan with described cooling refrigeration agent loop to operate described refrigerant system to promote described room air at described first direction with heat pattern again by controlling described reheat refrigerant circuit.
3. refrigerant system as claimed in claim 1, it also comprises the heat dissipation heat exchanger fan, described heat dissipation heat exchanger fan is configured to optionally force outdoor air to pass described heat dissipation heat exchanger, when described refrigerant system was in described defrosting mode, described controller is configured to control described heat dissipation heat exchanger fan did not force described outdoor air to pass described heat dissipation heat exchanger.
4. refrigerant system as claimed in claim 1, it comprises that also the bypass refrigerant loop that becomes the connection of selectivity fluid with described cooling refrigeration agent loop is so that at least a portion of cold-producing medium gets around described heat dissipation heat exchanger.
5. refrigerant system as claimed in claim 4, wherein, when described refrigerant system was in described defrosting mode, described controller is controlled described bypass refrigerant loop made described bypass refrigerant loop and described cooling refrigeration agent loop isolate at least in part.
6. refrigerant system as claimed in claim 4, wherein, when described refrigerant system was in described defrosting mode, described controller is controlled described bypass refrigerant loop made described bypass refrigerant loop become fluid to be communicated with described cooling refrigeration agent loop.
7. refrigerant system as claimed in claim 1, wherein, the direction of rotation of described controller control fan electromotor, this fan electromotor drives described evaporator fan to promote described room air at described first direction and described second direction respectively.
8. refrigerant system as claimed in claim 1, wherein, the control of described controller with respect to the position of the one or more air doors of described evaporator fan to promote described room air at described first direction and second direction respectively.
9. refrigerant system as claimed in claim 1, wherein, described evaporator fan is a variable speed fan.
10. refrigerant system, it comprises:
Cooling refrigeration agent loop, it comprises evaporimeter;
The reheat refrigerant circuit that becomes the selectivity fluid to be communicated with described cooling refrigeration agent loop, it comprises heat-heat exchanger again;
Evaporator fan, it is configured in first direction of rotation rotation promoting room air at first direction and to be configured in the rotation of second direction of rotation to promote room air in second direction, and described evaporimeter is positioned the upstream of described heat-heat exchanger again at described first direction; And,
Controller, it is configured to operate described refrigerant system with refrigerating mode and defrosting mode, at reheat refrigerant circuit described in the refrigerating mode and described cooling refrigeration agent loop isolates at least in part and described evaporator fan rotates in described first direction of rotation, become fluid to be communicated with described cooling refrigeration agent loop and described evaporator fan rotates in described second direction of rotation at reheat refrigerant circuit described in the defrosting mode.
11. refrigerant system as claimed in claim 10, wherein, described controller also is configured to operate described refrigerant system with heat pattern again, becomes fluid to be communicated with described cooling refrigeration agent loop and described evaporator fan rotates in described first direction of rotation at reheat refrigerant circuit described in the heat pattern again.
12. a refrigerant system, it comprises:
Cooling refrigeration agent loop, it comprises evaporimeter;
The reheat refrigerant circuit that becomes the selectivity fluid to be communicated with described cooling refrigeration agent loop, it comprises heat-heat exchanger again;
Evaporator fan, it is configured in single direction of rotation rotation;
One or more air doors, it is in the flow path of described room air, described one or more air door has the primary importance and the second place, described primary importance is configured to promote described room air at first direction, pass described evaporimeter earlier at the described room air of this first direction and pass described heat-heat exchanger more again, and the described second place is configured to promote described room air in second direction, passes described heat-heat exchanger more earlier at the described room air of this second direction and passes described evaporimeter again; And,
Controller, it is configured to operate described refrigerant system with at least one pattern in refrigerating mode and the defrosting mode, at reheat refrigerant circuit described in the described refrigerating mode and described cooling refrigeration agent loop isolates at least in part and described one or more air door is in described primary importance, become fluid to be communicated with described cooling refrigeration agent loop and described one or more air door is in the described second place at reheat refrigerant circuit described in the described defrosting mode.
13. refrigerant system as claimed in claim 12, wherein, described controller also is configured to operate described refrigerant system with heat pattern again, becomes fluid to be communicated with described cooling refrigeration agent loop and described one or more air door is in described primary importance at reheat refrigerant circuit described in the heat pattern again.
14. a method of controlling refrigerant system, it comprises:
When described refrigerant system is in refrigerating mode, the control reheat refrigerant circuit makes described reheat refrigerant circuit and cooling refrigeration agent loop isolate at least in part and controls evaporator fan and pass evaporimeter to force room air at first direction, passes heat-heat exchanger more then; And,
When described refrigerant system during at defrosting mode, control described reheat refrigerant circuit and make described reheat refrigerant circuit become fluid to be communicated with described cooling refrigeration agent loop and control described evaporator fan and pass described heat-heat exchanger again in second direction, pass described evaporimeter then to force described room air.
15. method as claimed in claim 14, it also comprises when described refrigerant system is in heat pattern again, controls described reheat refrigerant circuit and makes described reheat refrigerant circuit become fluid to be communicated with described cooling refrigeration agent loop and control described evaporator fan to promote described room air at described first direction.
16. method as claimed in claim 14 wherein, is controlled described evaporator fan and is comprised that to promote described room air at described first direction the described evaporator fan of control rotates in first direction of rotation, and
Control described evaporator fan and comprise that to promote described room air in described second direction the described evaporator fan of control is to rotate in second direction of rotation.
17. method as claimed in claim 14 wherein, is controlled described evaporator fan and is comprised that to promote described room air at described first direction the described evaporator fan of control moves to primary importance in the rotation of first direction of rotation and with one or more air doors, and
Control described evaporator fan and comprise that to promote described room air in described second direction the described evaporator fan of control moves to the second place in described first direction of rotation rotation and with described one or more air doors.
18. method as claimed in claim 14, it comprises also that when described refrigerant system is in described defrosting mode control heat dissipation heat exchanger fan does not force outdoor air to pass heat dissipation heat exchanger.
19. method as claimed in claim 14, it also comprises when described refrigerant system is in described defrosting mode, and bypass refrigerant loop and described cooling refrigeration agent loop are isolated at least in part.
20. method as claimed in claim 14, it also comprises when described refrigerant system is in described defrosting mode, the bypass refrigerant loop is placed with described cooling refrigeration agent loop become fluid to be communicated with.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2008/001225 WO2009096915A1 (en) | 2008-01-30 | 2008-01-30 | Refrigerant system with reheat refrigerant circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101932883A true CN101932883A (en) | 2010-12-29 |
Family
ID=40913062
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008801259834A Pending CN101932883A (en) | 2008-01-30 | 2008-01-30 | Refrigerant system with reheat refrigerant circuit |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20100307172A1 (en) |
| EP (1) | EP2250445A1 (en) |
| CN (1) | CN101932883A (en) |
| WO (1) | WO2009096915A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102997517A (en) * | 2011-09-09 | 2013-03-27 | 珠海格力电器股份有限公司 | Thermostatic dehumidification system of air conditioner |
| CN110234940A (en) * | 2017-01-30 | 2019-09-13 | 比泽尔制冷设备有限公司 | Expansion cell for being encased in refrigerant circuit |
| CN111609631A (en) * | 2019-02-26 | 2020-09-01 | 青岛海尔电冰箱有限公司 | Refrigerator with fan in middle of evaporator |
| CN112902498A (en) * | 2021-01-14 | 2021-06-04 | 山东三土能源股份有限公司 | Air source heat pump refrigerant circulating system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP5669658B2 (en) * | 2011-04-11 | 2015-02-12 | 住友重機械工業株式会社 | Cryopump system, compressor, and cryopump regeneration method |
| ITBS20110084A1 (en) * | 2011-06-10 | 2012-12-11 | Bmb Di Begarelli Bruno & C Sas | DEFROSTING SYSTEM OF A REINFORCED HEAT PUMP MACHINE THROUGH REUSE OF HEAT PRODUCED BY THE SAME MACHINE |
| CN115388481A (en) * | 2017-01-12 | 2022-11-25 | 尼蓝宝股份有限公司 | Control system for controlling temperature and relative humidity |
| CN107166643A (en) * | 2017-05-17 | 2017-09-15 | 青岛海尔空调器有限总公司 | A kind of control method and device of air-conditioning |
| US11530857B2 (en) | 2020-11-10 | 2022-12-20 | Rheem Manufacturing Company | Air conditioning reheat systems and methods thereto |
| KR20230010865A (en) * | 2021-07-12 | 2023-01-20 | 엘지전자 주식회사 | operating method for a refrigerator |
| CN115371258A (en) * | 2022-08-15 | 2022-11-22 | 马鞍山市博浪热能科技有限公司 | Air source heat pump water heater with economizer arranged in water side heat exchanger |
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| US2939295A (en) * | 1958-12-29 | 1960-06-07 | American Air Filter Co | Air conditioning apparatus |
| JPS57131966A (en) * | 1981-02-09 | 1982-08-16 | Hitachi Ltd | Absorption type air conditioner |
| US4346566A (en) * | 1981-06-04 | 1982-08-31 | General Electric Company | Refrigeration system gravity defrost |
| JPS6470636A (en) * | 1987-09-10 | 1989-03-16 | Toshiba Corp | Air-conditioning machine |
| US5105629A (en) * | 1991-02-28 | 1992-04-21 | Parris Jesse W | Heat pump system |
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| TWI308631B (en) * | 2002-11-07 | 2009-04-11 | Sanyo Electric Co | Multistage compression type rotary compressor and cooling device |
| KR100463548B1 (en) * | 2003-01-13 | 2004-12-29 | 엘지전자 주식회사 | Air conditioner |
| WO2005114072A2 (en) * | 2004-05-22 | 2005-12-01 | Gerald Landry | Desiccant-assisted air conditioning system and process |
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2008
- 2008-01-30 US US12/864,122 patent/US20100307172A1/en not_active Abandoned
- 2008-01-30 EP EP08724970A patent/EP2250445A1/en not_active Withdrawn
- 2008-01-30 CN CN2008801259834A patent/CN101932883A/en active Pending
- 2008-01-30 WO PCT/US2008/001225 patent/WO2009096915A1/en active Application Filing
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102997517A (en) * | 2011-09-09 | 2013-03-27 | 珠海格力电器股份有限公司 | Thermostatic dehumidification system of air conditioner |
| CN110234940A (en) * | 2017-01-30 | 2019-09-13 | 比泽尔制冷设备有限公司 | Expansion cell for being encased in refrigerant circuit |
| CN111609631A (en) * | 2019-02-26 | 2020-09-01 | 青岛海尔电冰箱有限公司 | Refrigerator with fan in middle of evaporator |
| CN112902498A (en) * | 2021-01-14 | 2021-06-04 | 山东三土能源股份有限公司 | Air source heat pump refrigerant circulating system |
| CN112902498B (en) * | 2021-01-14 | 2022-12-20 | 山东三土能源股份有限公司 | Air source heat pump refrigerant circulation system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009096915A1 (en) | 2009-08-06 |
| US20100307172A1 (en) | 2010-12-09 |
| EP2250445A1 (en) | 2010-11-17 |
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