CN103946441A - A laundry dryer with a heat pump system - Google Patents
A laundry dryer with a heat pump system Download PDFInfo
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- CN103946441A CN103946441A CN201280057032.4A CN201280057032A CN103946441A CN 103946441 A CN103946441 A CN 103946441A CN 201280057032 A CN201280057032 A CN 201280057032A CN 103946441 A CN103946441 A CN 103946441A
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- heat exchanger
- refrigerant
- outlet
- air stream
- entrance
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- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F58/00—Domestic laundry dryers
- D06F58/20—General details of domestic laundry dryers
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F58/00—Domestic laundry dryers
- D06F58/20—General details of domestic laundry dryers
- D06F58/206—Heat pump arrangements
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- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Detail Structures Of Washing Machines And Dryers (AREA)
Abstract
The present invention relates to a laundry dryer with a heat pump system comprising a refrigerant circuit (10) for a refrigerant and an air stream circuit (12) for an air stream. The refrigerant circuit (10) includes a compressor (14), a first heat exchanger (16), an expansion device (18), a second heat exchanger (20) and an additional heat exchanger (22) connected in series and forming a loop. The air stream circuit (12) includes at least one air stream fan (24), a laundry drum (26), the second heat exchanger (20), the additional heat exchanger (22) and the first heat exchanger (16) connected in series and forming a loop. The refrigerant circuit (10) and the air stream circuit (12) are thermally coupled by the first heat exchanger (16), the second heat exchanger (20) and the additional heat exchanger (22). The first heat exchanger (16) is provided for heating up the air stream and cooling down the refrigerant. The second heat exchanger (20) is provided for cooling down the air stream and heating up the refrigerant. The additional heat exchanger (22) is provided for pre-heating the air stream and cooling down the refrigerant. The additional heat exchanger (22) on the one hand and the first heat exchanger (16) or the second heat exchanger (20) on the other hand are formed as one heat exchanger assembly (36) including one air stream channel (34) and one or two refrigerant channels (42; 44, 46).
Description
The present invention relates to a kind of with having according to the clothesdrier of the heat pump as described in the preamble of claim 1.
At present, in clothesdrier, heat pump techniques due to reduced energy consume because of but the efficient way of drying clothes.In conventional heat pump clothesdrier, air stream flows in the air stream loop of sealing.Circulation of air passing through fan moves and passes laundry drum, thereby removes moisture from wet clothes.Then, air stream is cooled and dehumidifies and be heated in condenser or gas cooler in evaporimeter or gas heater.Finally, air stream is reintroduced back in laundry drum again.
Cold-producing medium is by compressor compresses.Then, cold-producing medium is condensed or is cooled in gas cooler in condenser.Then, cold-producing medium in expansion gear by layering.Finally, cold-producing medium is vaporized or is heated in gas heater in evaporimeter.If cold-producing medium operates under critical pressure, cold-producing medium is cooled respectively and is heated in gas heater in gas cooler so.The temperature of air stream and cold-producing medium associated accurately each other.
During the steady-state process of conventional heat pump clothesdrier, the temperature of the air stream in the exit of evaporimeter is relatively low, for example, be approximately 25 DEG C.The temperature of the air stream of the porch of laundry drum should be relatively high, for example, be approximately 65 DEG C, makes condenser must use relatively high temperature difference heating and cooling agent.Relation between the temperature of air stream need to have the heat exchanger of unfavorable size.
WO2011/080045A1 discloses a kind of household electrical appliance with hothouse and heat pump circuit.Heat pump circuit comprises liquefier, evaporimeter and two additional heat exchangers.Process air is heated by liquefier and is cooled by evaporimeter.Additional cools down cold-producing medium and heating process air.Another additional heat exchanger makes the condensate of cold-producing medium excessively cold, and reduces the mass flow of circulating refrigerant.But heat pump circuit comprises a large amount of parts and complicated control system.
The object of this invention is to provide a kind of clothesdrier with heat pump, the performance that this clothesdrier makes it possible to reduce the drying time of heat pump and improves heat pump due to low-complexity.
Object of the present invention realizes by clothesdrier according to claim 1.
According to the present invention, the heat exchanger that one side is additional and on the other hand the first heat exchanger or the second heat exchanger are formed as a heat exchanger assemblies, and this heat exchanger assemblies comprises an airflow path and at least one coolant channel.
The invention provides the layout of the first heat exchanger in a physics heat exchanger assemblies or the second heat exchanger and additional heat exchanger.Described heat exchanger assemblies comprises a passage or at least two the independent passages for cold-producing medium, and it runs through the passage for air stream.The different piece that is connected to refrigerant loop for the passage of cold-producing medium, wherein, cold-producing medium has different hot states.The heat exchanger assemblies that comprises the first heat exchanger or the second heat exchanger and additional heat exchanger has reduced the complexity of heat pump.
Preferably, heat exchanger assemblies comprises public fin and the airflow path between described fin and at least one coolant channel, this at least one coolant channel and fin are thermally coupled, to limit that side of the first heat exchanger or the second heat exchanger and additional heat exchanger, that side of the first heat exchanger or the second heat exchanger and additional heat exchanger shares public fin.
Preferably, three coolant channels are through public fin.
Preferably, the outlet that the entrance of coolant channel is arranged on the second heat exchanger place and coolant channel is arranged on additional heat exchanger place.
Preferably, the entrance of coolant channel is connected to the outlet of expansion gear, and the outlet of coolant channel is connected to the gateway of compressor.
Preferably, a part of at least extending between entrance and outlet for coolant channel is crossed heat exchanger assemblies, to lead to additional heat exchanger from the second heat exchanger.
Preferably, refrigerant loop comprises inner heat exchanger, wherein, the high-pressure side of described inner heat exchanger interconnects between the first heat exchanger and expansion gear, and the low-pressure side of described inner heat exchanger interconnects between the second heat exchanger and additional heat exchanger, makes additional heat exchanger receive cold-producing medium via the described low-pressure side of inner heat exchanger.
Preferably, the first coolant channel is corresponding with the second heat exchanger, and second refrigerant passage is corresponding with additional heat exchanger, and wherein, the entrance of the first coolant channel is connected to the outlet of expansion gear, the outlet of the first coolant channel is connected to the entrance of the low-pressure side of inner heat exchanger, and the entrance of second refrigerant passage is connected to the outlet of the low-pressure side of inner heat exchanger, and the outlet of second refrigerant passage is connected to the entrance of compressor.
Preferably, the first coolant channel is corresponding with additional heat exchanger and be a part for the low voltage section of refrigerant loop, and second refrigerant passage is corresponding with the first heat exchanger and be a part for the high-voltage section of refrigerant loop.
Preferably, the entrance of the first coolant channel is connected to the refrigerant outlet of evaporimeter, the outlet of the first coolant channel is connected to the entrance of compressor, and the entrance of second refrigerant passage is connected to the outlet of compressor, and the outlet of second refrigerant passage is connected to the entrance of expansion gear.
Preferably, the entrance of the first coolant channel is connected to the outlet of the low-pressure side of inner heat exchanger, the outlet of the first coolant channel is connected to the entrance of compressor, and the entrance of second refrigerant passage is connected to the outlet of compressor, the outlet of second refrigerant passage is connected to the on high-tension side entrance of inner heat exchanger.
Preferably, refrigerant loop comprises bypass line, makes cold-producing medium can completely or partially walk around described additional heat exchanger.
Preferably, bypass line comprises at least one switch valve for opening and closing described bypass line, or bypass line comprises at least one control valve opened continuously for described bypass line, or bypass line comprises at least one triple valve of the refrigerant side for alternately opening and closing described bypass line and additional heat exchanger.
Preferably, bypass line maybe can pass through the temperature control of the cold-producing medium at least one position of refrigerant loop by the temperature control of the cold-producing medium at least one position of refrigerant loop, or bypass line maybe can be by the temperature control of the air stream at least one position in air stream loop by the temperature control of the air stream at least one position in air stream loop.
Preferably, bypass line is by one of the following control or can be by one of the following control,
The temperature of the cold-producing medium at the refrigerant outlet place of the-the second heat exchanger,
The temperature difference of the refrigerant inlet place of the-the second heat exchanger and the cold-producing medium at refrigerant outlet place,
The temperature difference of the temperature of the air stream at the cold-producing medium at the refrigerant outlet place of the-the second heat exchanger and the air outflow port place of the second heat exchanger.
In the situation that cold-producing medium keeps gaseous state, the first heat exchanger is as gas cooler.On the contrary, change into liquid in the situation that at least in part at cold-producing medium from gaseous state, the first heat exchanger is as condenser.
In the situation that cold-producing medium keeps gaseous state, the second heat exchanger is as gas heater.In addition, in the situation that cold-producing medium changes gaseous state into from liquid state at least in part, the second heat exchanger is as evaporimeter.
The novelty and the creative feature that are considered as characteristic of the present invention are stated in claims.
The present invention is described with reference to the accompanying drawings in more detail, in the accompanying drawings,
Fig. 1 shows the schematic diagram of the heat pump for clothesdrier of first embodiment of the invention;
Fig. 2 shows the schematic diagram of the heat pump for clothesdrier second embodiment of the invention;
Fig. 3 shows according to the schematic diagram of the heat pump for clothesdrier of the 3rd embodiment of the present invention;
Fig. 4 shows according to the schematic diagram of the heat pump for clothesdrier of the 4th embodiment of the present invention;
Fig. 5 shows according to the schematic diagram of the heat pump for clothesdrier of the 5th embodiment of the present invention;
Fig. 6 shows according to the schematic diagram of the heat exchanger assemblies for heat pump of the 5th embodiment of the present invention;
Fig. 7 shows according to the schematic diagram of the heat pump for clothesdrier of the 6th embodiment of the present invention;
Fig. 8 shows according to the schematic diagram of the heat exchanger assemblies for heat pump of the 6th embodiment of the present invention;
Fig. 9 shows according to the schematic diagram of the heat pump for clothesdrier of the 7th embodiment of the present invention;
Figure 10 shows according to the schematic diagram of the heat exchanger assemblies for heat pump of the 7th embodiment of the present invention;
Figure 11 shows according to the schematic diagram of the heat pump for clothesdrier of the 8th embodiment of the present invention; And
Figure 12 shows according to the schematic diagram of the heat exchanger assemblies for heat pump of the 8th embodiment of the present invention.
Fig. 1 illustrates the schematic diagram of the heat pump for clothesdrier of first embodiment of the invention.Heat pump comprises that closed refrigerant circuit 10 and dry air flow back to road 12.
Refrigerant loop 10 comprises compressor 14, condenser 16, expansion gear 18, evaporimeter 20 and additional heat exchanger 22.Compressor 14, condenser 16, expansion gear 18, evaporimeter 20 and additional heat exchanger 22 series connection switchings and formation closed loop.Air stream loop 12 comprises evaporimeter 20, additional heat exchanger 22, condenser 16, air stream fan 24 and clothing process chamber 26, and clothing process chamber 26 is preferably rotatable drum.Air stream loop 12 also forms loop.
Cold-producing medium is compressed by compressor 14 and by condenser 16 condensations.Cold-producing medium evaporates by layering and in evaporimeter 20 in expansion gear 18.Then, cold-producing medium is cooled by additional heat exchanger 22 and is inhaled into by compressor 14.Dry air stream is driven by air stream fan 24 and passes laundry drum 26, thereby removes moisture from wet wash.Then, dry air circulation pervaporation device 20 is cooled and dehumidifies and be preheated by additional heat exchanger 22.Finally, dry air stream is heated and is again reintroduced in laundry drum 26 in condenser 16.
Additional heat exchanger 22 is arranged on the inner side, air stream loop between evaporimeter 20 and condenser 16.Cold-producing medium and dry air stream are by additional heat exchanger 22, by evaporimeter 20 and condenser 16 heat connections.In refrigerant loop, additional heat exchanger 22 is arranged between the refrigerant outlet of evaporimeter 20 and the entrance of compressor 14.The cold-producing medium that carrys out flash-pot 20 was cooled by additional heat exchanger 22 before being sucked by compressor 14, and dry air stream is preheated by described additional heat exchanger 22 simultaneously.
In evaporimeter 20, dry air stream is cooled with dehumidified, and cold-producing medium is vaporized and heats in evaporimeter 20 simultaneously, and preferably cold-producing medium is by superheated.During steady-state process, the temperature of the air stream at the air outflow port place of laundry drum 26 and the air inflow aperture place of evaporimeter 20 is for example approximately 40 DEG C respectively.The temperature of the air stream at the air outflow port place of evaporimeter 20 is for example approximately 25 DEG C.By contrast, cold-producing medium enters evaporimeter and is arrived up to for example approximately 35 DEG C by superheated by evaporimeter at the temperature of approximately 20 DEG C.Then, air stream is preheated by described overheated cold-producing medium in additional heat exchanger 22.The temperature of the air stream at the air outflow port place of condenser 16 and the air inflow aperture place of laundry drum 26 is for example approximately 65 DEG C respectively.Thereby additional heat exchanger 22 is supported condenser 16 during heated air flow.
Additional heat exchanger 22 has following advantage: higher heating power is transferred into air stream, has made to shorten the heating period of heat pump.In addition, air stream can reach higher temperature during the steady-state process of heat pump.Moreover the in the situation that of other parameter constants of supposition, the temperature of the cold-producing medium of the porch of compressor 14 is lower, makes to have reduced the needed power of compressor 14.
Fig. 2 illustrates the schematic diagram of the heat pump for clothesdrier second embodiment of the invention.The heat pump of the second embodiment comprises the parts identical with the heat pump of the first embodiment.Additionally, the refrigerant loop 10 of the second embodiment comprises bypass line 28.
Bypass line 28 preferably arranges concurrently with additional heat exchanger 22.Bypass line 28 makes cold-producing medium can completely or partially walk around additional heat exchanger 22.When flow of refrigerant is by bypass line 28 and while walking around additional heat exchanger 22, so avoided the too low temperature of the cold-producing medium in the exit of compressor.Described too low temperature will make dry air stream can not be heated to the level of expectation.
Bypass line 28 can switch by one or more valves.Not shown described valve in Fig. 2.For example, bypass line 28 comprises the pair of switches valve of the end that is arranged on described bypass line 28.Alternatively, bypass line 28 can only switch by a switch valve.According to another example, bypass line 28 comprises the pair of control valve of the end that is arranged on described bypass line 28, and wherein, control valve can completely or partially be opened.Alternatively, bypass line 28 can only switch by a control valve.In addition, bypass line 28 can comprise triple valve.
Fig. 3 illustrates according to the schematic diagram of the heat pump for clothesdrier of the 3rd embodiment of the present invention.The heat pump of the 3rd embodiment comprises the parts identical with the heat pump of the first embodiment.Additionally, the refrigerant loop 10 of the 3rd embodiment comprises inner heat exchanger 30.
The condenser 16, evaporimeter 20 and the additional heat exchanger 22 that connect refrigerant loop 10 and air stream loop 12 from heat are different, and inner heat exchanger 30 only works in refrigerant loop 10.Refrigerant loop 10 heat connect high-voltage section and the low voltage section of refrigerant loop 10.High-voltage section extends to the entrance of expansion gear 18 via condenser 16 from the outlet of compressor 14.Low voltage section extends to the entrance of compressor 14 via evaporimeter 20 and additional heat exchanger 22 from the outlet of expansion gear 18.
Inner heat exchanger 30 comprises high-pressure side 32 and low-pressure side 34.High-pressure side 32 is corresponding with the high-voltage section of refrigerant loop 10.Low-pressure side 34 is corresponding with the low voltage section of refrigerant loop 10.
The cold-producing medium that carrys out the outlet of flash-pot 20 is heated in the low-pressure side 34 of inner heat exchanger 30.Then, cold-producing medium is cooled in additional heat exchanger 22.Inner heat exchanger 30 allows air stream in additional heat exchanger 22 to reach heated more as in the first embodiment and the second embodiment too low temperature levels at the cold-producing medium of the porch without compressor 14.
Fig. 4 illustrates according to the schematic diagram of the heat pump for clothesdrier of the 4th embodiment of the present invention.The heat pump of the 4th embodiment comprises the parts identical with the heat pump of the 3rd embodiment.Additionally, the refrigerant loop 10 of the 3rd embodiment comprises bypass line 28.In other words, the 4th embodiment is the combination of the second embodiment and the 3rd embodiment.
Bypass line 28 is preferably arranged to additional heat exchanger 22 parallel.Bypass line 28 allows cold-producing medium can completely or partially pass through additional heat exchanger 22.When flow of refrigerant is by bypass line 28 and while walking around additional heat exchanger 22, so avoided the too low temperature of the cold-producing medium in the exit of compressor.
Bypass line 28 also can switch by one or more valves.Not shown described valve in Fig. 4.For example, bypass line 28 comprises the pair of switches valve of the end that is arranged on described bypass line 28.Alternatively, bypass line 28 can only switch by a switch valve.According to other examples, bypass line 28 comprises the paired control valve of the end that is arranged on described bypass line 28, and wherein, control valve can completely or partially be opened.Alternatively, bypass line 28 can only switch by a control valve.Finally, bypass line 28 can comprise triple valve.
According to other embodiment of the present invention, the low-pressure side 34 of inner heat exchanger 30 is arranged on the downstream of additional heat exchanger 22.After cold-producing medium is cooling by the air stream in the heat exchanger 22 adding, cold-producing medium is heated in the low-pressure side 34 of inner heat exchanger 30, has made to avoid the too low temperature levels at the entrance and exit place of compressor 14.This embodiment does not preferably need bypass line 28, because the suitable temperature levels at the entrance and exit place of compressor 14 has been guaranteed in the position of the low-pressure side 34 of inner heat exchanger 30.
According to the temperature levels of air stream and/or cold-producing medium, can control valve or multiple valve of bypass line 28.In the time that dry cycle starts, evaporimeter 20 can be filled or cold-producing medium can be by superheated, can be lower than the temperature of air stream in the temperature of the cold-producing medium at the refrigerant outlet place of evaporimeter 20.Thereby cold-producing medium can not heat the air stream in additional heat exchanger 22 and walk around described additional heat exchanger 22.
Bypass line 28 is opened and additional heat exchanger 22 is not worked in the following cases:
The temperature of the cold-producing medium at the refrigerant outlet place of-evaporimeter 20 is lower than predetermined value,
The temperature difference of the cold-producing medium at the refrigerant inlet of-evaporimeter 20 and refrigerant outlet place is lower than predetermined value, and/or
The temperature of the cold-producing medium at the refrigerant outlet place of-evaporimeter 20 is lower than the temperature of the air stream at the air outflow port place of evaporimeter 20.
In the transition stage of dry cycle or after the heating period, if the air stream of the porch of laundry drum 26 can not remain on higher level place, can walk around additional heat exchanger 22.This situation may occur in the beginning of steady-state process.If the predeterminated level of the temperature at the refrigerant outlet place of the refrigerant inlet of evaporimeter 20 or the cold-producing medium in exit or condenser 16 when starting corresponding to dry cycle, and the temperature of air stream of porch of laundry drum 26 or the temperature of the cold-producing medium in the exit of compressor 14, lower than another predeterminated level, can completely or partially be passed through additional heat exchanger 22 so simultaneously.In the time that air stream reaches desired value, so additional heat exchanger 22 is started again.Thereby additional heat exchanger 22 is worked under switching mode.
Fig. 5 shows according to the schematic diagram of the heat pump for clothesdrier of the 5th embodiment of the present invention.The difference of the 5th embodiment and the first embodiment is, evaporimeter 20 and additional heat exchanger 22 are formed by heat exchanger assemblies 36.
Described heat exchanger assemblies 36 comprise public fin 38 and with the hot linked coolant channel 44 of fin 38, to be defined for the vaporizer side 20 of cooling-air stream and heating and cooling agent and to flow and the additional heat exchanger side 22 of cooling refrigeration agent for preheated air.
Fig. 6 shows according to the schematic diagram of the heat exchanger assemblies 36 for heat pump of the 5th embodiment of the present invention.Heat exchanger assemblies 36 comprises multiple fin 38.Heat exchanger assemblies 36 comprises the public airflow path 40 for evaporimeter 20 and additional heat exchanger 22, and wherein, airflow path 40 is first by evaporimeter 20, then by additional heat exchanger 22.Coolant channel 42 runs through airflow path 40 and thermally coupled with fin, and preferably, coolant channel 42 is through public fin 38.Coolant channel 42 is preferably snakelike.The entrance 48 of coolant channel 42 is connected to the outlet of expansion gear 18.The outlet 50 of coolant channel 42 is connected to the gateway of compressor 14.
The entrance 48 of coolant channel 42 is arranged on the vaporizer side place of heat exchanger assemblies, and the outlet 50 of coolant channel 42 is arranged on the additional heat exchanger side place of heat exchanger assemblies.
At least a portion between entrance 48 and outlet 50 of coolant channel 42 is crossed heat exchanger assemblies, to lead to additional interchanger side 22 from vaporizer side 20.
In the vaporizer side 20 of heat exchanger assemblies 36, air stream is cooled and dehumidifies.In the additional heat exchanger side 22 of heat exchanger assemblies 36, air stream is preheated.In the vaporizer side 20 of heat exchanger assemblies 36, cold-producing medium is vaporized and superheated.In the additional heat exchanger side 22 of heat exchanger assemblies 36, cold-producing medium is cooled.
Fig. 7 shows according to the schematic diagram of the heat pump for clothesdrier of the 6th embodiment of the present invention.The difference of the 6th embodiment and the 3rd embodiment is, evaporimeter 20 and additional heat exchanger 22 are formed by heat exchanger assemblies 36.Described heat exchanger assemblies 36 comprise public fin 38 and with hot linked two coolant channels 44,46 of fin 38, to be defined for the vaporizer side 20 of cooling-air stream and heating and cooling agent and to flow and the additional heat exchanger side 22 of cooling refrigeration agent for preheated air.
Fig. 8 shows according to the schematic diagram of the heat exchanger assemblies 36 for heat pump of the 6th embodiment of the present invention.Heat exchanger assemblies 36 comprises multiple fin 38 and the airflow path 40 between described fin 38.Then first airflow path 40 pass through additional heat exchanger 22 sides of heat exchanger assemblies 36 by evaporimeter 20 sides.The first coolant channel 44 and second refrigerant passage 46 run through airflow path 40.The first coolant channel 44 and second refrigerant passage 46 are preferably snakelike.
The first coolant channel 44 in Fig. 8 is corresponding with evaporimeter 20 sides of heat exchanger assemblies 36.Second refrigerant passage 46 in Fig. 8 is corresponding with additional heat exchanger 22 sides of heat exchanger assemblies 36.The entrance 52 of the first coolant channel 44 is connected to the outlet of expansion gear 18.The outlet 54 of the first coolant channel 44 is connected to the entrance of the low-pressure side 34 of inner heat exchanger 30.The entrance 56 of second refrigerant passage 46 is connected to the outlet of the low-pressure side 34 of inner heat exchanger 30.The outlet 58 of second refrigerant passage 46 is connected to the entrance of compressor 14.
Between the first coolant channel 44 and second refrigerant passage 46, cold-producing medium is by the low-pressure side 34 of inner heat exchanger 30.
Fig. 9 shows according to the schematic diagram of the heat pump for clothesdrier of the 7th embodiment of the present invention.The difference of the 7th embodiment and the first embodiment is, additional heat exchanger 22 and condenser 16 are formed by heat exchanger assemblies 36.Described heat exchanger assemblies 36 comprise public fin 38 and with hot linked two coolant channels 44,46 of fin 38, preheat the additional heat exchanger side 22 of air stream and cooling refrigeration agent and the condenser side 16 for heated air flow and cooling refrigeration agent to be defined for.
Figure 10 shows according to the schematic diagram of the heat exchanger assemblies 36 for heat pump of the 7th embodiment of the present invention.Heat exchanger assemblies 36 comprises multiple fin 38.Heat exchanger assemblies 36 comprises the public airflow path 40 for additional heat exchanger side 22 and condenser side 16, and wherein, airflow path 40 is first by additional heat exchanger 22 and condenser 16.Be preferably the first snakelike coolant channel 44 and be preferably snakelike second refrigerant passage 46 and run through airflow path 40.
The first coolant channel 44 in Figure 10 is corresponding with additional heat exchanger side 22.Second refrigerant passage 46 in Figure 10 is corresponding with condenser side 16.
Refrigerant loop 10 is subdivided into high-voltage section and low voltage section.High-voltage section extends to the entrance of expansion gear 18 via condenser 16 from the outlet of compressor 14.Low voltage section extends to the entrance of compressor 14 via evaporimeter 20 from the outlet of expansion gear 18.
A part for the low voltage section that the first coolant channel 44 is refrigerant loop, and a part for the high-voltage section that second refrigerant passage 46 is refrigerant loop.
The entrance 52 of the first coolant channel 44 is connected to the refrigerant outlet of evaporimeter 20.The outlet 54 of the first coolant channel 44 is connected to the entrance of compressor 14.The entrance 56 of second refrigerant passage 46 is connected to the outlet of compressor 14.The outlet 58 of second refrigerant passage 46 is connected to the entrance of expansion gear 18.
In the additional heat exchanger side 22 of heat exchanger assemblies 36, dry air stream is preheated, and cold-producing medium is cooled simultaneously.In condenser side 16, cold-producing medium is cooled, and air stream is preheated simultaneously.
Additionally, the cold-producing medium flow that the thermal conductivity of fin 38 permits flow in additional heat exchanger side 22 carries out cooling to the cold-producing medium in condenser side 16.On the contrary, the cold-producing medium flow flowing in condenser 16 heats to the cold-producing medium in additional heat exchanger 22, thereby has improved the efficiency of heat pump.
Figure 11 shows according to the schematic diagram of the heat pump for clothesdrier of the 8th embodiment of the present invention.The difference of the 8th embodiment and the 3rd embodiment is, additional heat exchanger 22 and condenser 16 are formed by heat exchanger assemblies 36.
Described heat exchanger assemblies 36 comprise public fin 38 and with hot linked two coolant channels 44,46 of fin 38, preheat the additional heat exchanger side 22 of air stream and cooling refrigeration agent and the condenser side 16 for heated air flow and cooling refrigeration agent to be defined for.
Figure 12 shows according to the schematic diagram of the heat exchanger assemblies for heat pump of the 8th embodiment of the present invention.Heat exchanger assemblies 36 comprises the public airflow path 40 for additional heat exchanger side 22 and condenser side 16, and wherein, airflow path 40 is first by additional heat exchanger 22 and condenser 16.Be preferably the first snakelike coolant channel 44 and be preferably snakelike second refrigerant passage 46 and run through airflow path 40.
The first coolant channel 44 in Figure 12 is corresponding with additional heat exchanger side 22.Second refrigerant passage 46 in Figure 12 is corresponding with condenser side 16.A part for the downforce portion that the first coolant channel 44 is refrigerant loop, and a part for the high-voltage section that second refrigerant passage 46 is refrigerant loop.
The entrance 52 of the first coolant channel 44 is connected to the outlet of the low-pressure side 34 of inner heat exchanger 30.The outlet 54 of the first coolant channel 44 is connected to the entrance of compressor 14.The entrance 56 of second refrigerant passage 46 is connected to the outlet of compressor 14.The outlet 58 of second refrigerant passage 46 is connected to the entrance of the high-pressure side 32 of inner heat exchanger 30.
In the additional heat exchanger 22 of heat exchanger assemblies 36, air stream is preheated, and cold-producing medium is cooled simultaneously.In condenser 16, cold-producing medium is cooled, and air stream is heated.
Heat exchanger assemblies 36 is realized by single parts.Described single parts are the heat exchanger of air to liquid, and this air comprises for passage of air stream with for, two or more passages of cold-producing medium the heat exchanger of liquid.Final result is the high-efficiency heating that is conducive to air stream.
For example, if cold-producing medium (carbon dioxide) at least operates in the low voltage section of refrigerant loop 10 under critical pressure, cold-producing medium always remains under gaseous state so.In this case, do not evaporate generation and evaporimeter 20 as gas heater.
Preferably, air stream loop 12 is closed loop, and in this closed loop, air stream flows through laundry drum 26 continuously.But a part for air stream can be discharged from air stream loop 12.The air of having discharged can use fresh air, for example surrounding air to replace.The air of preferably, having discharged and fresh air form the smaller portions of air stream.In addition, air stream loop 12 can temporarily be opened, and wherein, the time of opening air stream loop 12 is sub-fractions of total processing time.Under any circumstance, at least a portion air stream always passes through condenser 16 after passing through evaporimeter 20.
The heat pump that has additional heat exchanger 22 and have alternatively an inner heat exchanger 30 makes to reduce and improved the performance of heat pump drier drying time.
In other embodiment, in refrigerant loop, can be provided with auxiliary condenser especially between main condenser 16 and expansion gear 18.
Although described exemplary embodiment of the present invention herein with reference to the accompanying drawings, but be to be understood that, the invention is not restricted to these accurate embodiments, and do not departing from the scope of the present invention or spirit in the situation that, those of ordinary skill in the art can implement various other variation and remodeling.It is of the present invention as by claims limited range that all these variations and remodeling are intended to be included in.
Reference numerals list
10 refrigerant loops
12 air stream loops
14 compressors
16 first heat exchangers, condenser, gas cooler
18 expansion gears
20 second heat exchangers, evaporimeter, gas heater
22 additional heat exchangers
24 air stream fans
26 laundry drums
28 bypass lines
30 inner heat exchangers
32 high-pressure sides
34 low-pressure sides
36 heat exchanger assemblies
38 fin
40 airflow paths
42 coolant channels
44 first coolant channels
46 second refrigerant passages
The entrance of 48 coolant channels
The outlet of 50 coolant channels
The entrance of 52 first coolant channels
The outlet of 54 first coolant channels
The entrance of 56 second refrigerant passages
The outlet of 58 second refrigerant passages
Claims (15)
1. have a clothesdrier for heat pump, described heat pump comprises: the air stream loop (12) of flowing for the refrigerant loop (10) of cold-producing medium with for dry air, wherein
-described refrigerant loop (10) comprises the compressor (14), the first heat exchanger (16), expansion gear (18), the second heat exchanger (20) and the additional heat exchanger (22) that are connected in series and form loop
-described air stream loop (12) comprises at least one the air stream fan (24), clothing process chamber (26), described the second heat exchanger (20), described additional heat exchanger (22) and described the first heat exchanger (16) that are connected in series and form loop
-described refrigerant loop (10) and described air stream loop (12) connect by described the first heat exchanger (16), described the second heat exchanger (20) and described additional heat exchanger (22) heat
-described the first heat exchanger (16) is provided for the described air stream of heating and cooling described cold-producing medium,
-described the second heat exchanger (24) is provided for cooling described air stream and the described cold-producing medium of heating, and
-described additional heat exchanger (22) is arranged between described the first heat exchanger (16) and described the second heat exchanger (24), in order to preheat described air stream and cooling described cold-producing medium,
It is characterized in that,
The described additional heat exchanger of one side (22) and on the other hand described the first heat exchanger (16) or described the second heat exchanger (20) are formed as a heat exchanger assemblies (36), and described heat exchanger assemblies (36) comprises an airflow path (40) and at least one coolant channel (42,44,46).
2. clothesdrier according to claim 1, wherein, described heat exchanger assemblies (36) comprise public fin (38) and be positioned at airflow path (40) between described fin (38) and with hot linked at least one coolant channel (42 of described fin (38), 44, 46), to limit described the first heat exchanger (16) or described the second heat exchanger (20) and described additional heat exchanger side (22), described the first heat exchanger (16) or described the second heat exchanger (20) and described additional heat exchanger side (22) share described public fin (38).
3. clothesdrier according to claim 2, wherein, described coolant channel (42,44,46) is through described public fin (38).
4. according to the clothesdrier described in any one in aforementioned claim, wherein, the entrance (48) of described coolant channel (42) is arranged on described the second heat exchanger (20) and locates, and locates and the outlet (50) of described coolant channel (42) is arranged on described additional heat exchanger (22).
5. clothesdrier according to claim 4, wherein, the described entrance (48) of described coolant channel (42) is connected to the outlet of described expansion gear (18), and the outlet (50) of described coolant channel (42) is connected to the gateway of described compressor (14).
6. according to the clothesdrier described in claim 4 or 5, wherein, at least a portion of extending between described entrance (48) and described outlet (50) of described coolant channel (42) is crossed described heat exchanger assemblies (36), to lead to described additional heat exchanger (22) from described the second heat exchanger (20).
7. according to the clothesdrier described in any one in aforementioned claim, wherein, described refrigerant loop (10) comprises inner heat exchanger (30), wherein, the high-pressure side (32) of described inner heat exchanger (30) interconnects between described the first heat exchanger (16) and described expansion gear (18), and the low-pressure side (34) of described inner heat exchanger (30) interconnects between described the second heat exchanger (20) and described additional heat exchanger (22), make described additional heat exchanger (22) receive described cold-producing medium via the described low-pressure side (34) of described inner heat exchanger (30).
8. according to the clothesdrier described in any one in claim 7, wherein, the first coolant channel (44) is corresponding with described the second heat exchanger (20), and second refrigerant passage (46) is corresponding with described additional heat exchanger (22), and wherein, the entrance (52) of described the first coolant channel (44) is connected to the described outlet of described expansion gear (18), the outlet (54) of described the first coolant channel (44) is connected to the entrance of the described low-pressure side (34) of described inner heat exchanger (30), and the entrance (56) of described second refrigerant passage (46) is connected to the outlet of the described low-pressure side (34) of described inner heat exchanger (30), the outlet (58) of described second refrigerant passage (46) is connected to the entrance of described compressor (14).
9. according to any one in aforementioned claims 1 to 3 or clothesdrier claimed in claim 7, wherein, the first coolant channel (44) is corresponding with described additional heat exchanger (22) and be a part for the described low voltage section of described refrigerant loop (10), and described second refrigerant passage (46) is corresponding with described the first heat exchanger (16) and be a part for the described high-voltage section of described refrigerant loop.
10. clothesdrier according to claim 9, wherein, the described entrance (52) of described the first coolant channel (44) is connected to the refrigerant outlet of described evaporimeter (20), the described outlet (54) of described the first coolant channel (44) is connected to the entrance of described compressor (14), and the described entrance (56) of described second refrigerant passage (46) is connected to the outlet of described compressor (14), the described outlet (58) of described second refrigerant passage (46) is connected to the entrance of described expansion gear (18).
11. according to the clothesdrier described in claim 10 and 7, wherein, the described entrance (52) of described the first coolant channel (44) is connected to the outlet of the described low-pressure side (34) of described inner heat exchanger (30), the described outlet (54) of described the first coolant channel (44) is connected to the described entrance of described compressor (14), and the described entrance (56) of described second refrigerant passage (46) is connected to the described outlet of described compressor (14), the described outlet (58) of described second refrigerant passage (46) is connected to the described entrance of the described high-pressure side (32) of described inner heat exchanger (30).
12. according to the clothesdrier described in any one in aforementioned claim, wherein, described refrigerant loop (10) comprises bypass line (28), makes described cold-producing medium can completely or partially walk around described additional heat exchanger (22).
13. clothesdriers according to claim 12, wherein, described bypass line (28) comprises at least one switch valve for opening and closing described bypass line (28), or described bypass line (28) comprises at least one control valve opened continuously for described bypass line (28), or described bypass line (28) comprises at least one triple valve of the refrigerant side for alternately opening and closing described bypass line (28) and described additional heat exchanger (22).
14. according to the clothesdrier described in claim 12 or 13, wherein, described bypass line (28) is controlled maybe and can be controlled by the temperature of the described cold-producing medium at least one position of described refrigerant loop (10) by the temperature of the described cold-producing medium at least one position of described refrigerant loop (10), or described bypass line (28) is controlled maybe and can be controlled by the temperature of the described air stream at least one position in described air stream loop (12) by the temperature of the described air stream at least one position in described air stream loop (12).
15. according to the clothesdrier described in any one in aforementioned claim 12 to 14, and wherein, described bypass line (28) is by one of the following control or can be by one of the following control,
The temperature of the described cold-producing medium at the described refrigerant outlet place of-described the second heat exchanger (20),
The temperature difference of the refrigerant inlet place of-described the second heat exchanger (20) and the described cold-producing medium at described refrigerant outlet place,
The temperature difference of the temperature of the described air stream at the described cold-producing medium at the described refrigerant outlet place of-described the second heat exchanger (20) and the described air outflow port place of described the second heat exchanger (20).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP11189889.6 | 2011-11-21 | ||
| EP11189889.6A EP2594688B1 (en) | 2011-11-21 | 2011-11-21 | A laundry dryer with a heat pump system |
| PCT/EP2012/072690 WO2013075997A1 (en) | 2011-11-21 | 2012-11-15 | A laundry dryer with a heat pump system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103946441A true CN103946441A (en) | 2014-07-23 |
| CN103946441B CN103946441B (en) | 2016-12-14 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280057032.4A Active CN103946441B (en) | 2011-11-21 | 2012-11-15 | There is the clothesdrier of heat pump |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2594688B1 (en) |
| CN (1) | CN103946441B (en) |
| WO (1) | WO2013075997A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106245266A (en) * | 2016-08-30 | 2016-12-21 | 无锡小天鹅股份有限公司 | Clothes dryer systems and there is its dryer, washing-drying integral machine |
| CN114514347A (en) * | 2019-09-25 | 2022-05-17 | Bsh家用电器有限公司 | Appliance for drying laundry and method for operating such an appliance |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102302326B1 (en) | 2014-10-28 | 2021-09-15 | 엘지전자 주식회사 | Laundry Machine |
| CN108468193B (en) * | 2018-04-28 | 2023-12-19 | 海信冰箱有限公司 | Heat pump clothes dryer |
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| CN1667178A (en) * | 2004-03-10 | 2005-09-14 | 三洋电机株式会社 | Drying machine |
| WO2009016173A1 (en) * | 2007-08-02 | 2009-02-05 | Arcelik Anonim Sirketi | A washer/dryer |
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| DE202006018205U1 (en) * | 2006-11-06 | 2007-02-15 | V-Zug Ag | Clothes dryer with a drum and a heat pump circuit comprising a condenser, a throttle, an evaporator and a compressor comprises an auxiliary heat exchanger between the condenser and the throttle |
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- 2011-11-21 EP EP11189889.6A patent/EP2594688B1/en active Active
-
2012
- 2012-11-15 WO PCT/EP2012/072690 patent/WO2013075997A1/en active Application Filing
- 2012-11-15 CN CN201280057032.4A patent/CN103946441B/en active Active
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| CN1667178A (en) * | 2004-03-10 | 2005-09-14 | 三洋电机株式会社 | Drying machine |
| EP2143839A1 (en) * | 2007-05-31 | 2010-01-13 | Panasonic Corporation | Cloth dryer |
| WO2009016173A1 (en) * | 2007-08-02 | 2009-02-05 | Arcelik Anonim Sirketi | A washer/dryer |
| JP2010088659A (en) * | 2008-10-08 | 2010-04-22 | Toshiba Corp | Washing/drying machine |
| EP2261416A1 (en) * | 2009-06-09 | 2010-12-15 | Electrolux Home Products Corporation N.V. | Heat exchanger for a dryer, especially for a domestic dryer |
| WO2011080045A1 (en) * | 2009-12-22 | 2011-07-07 | BSH Bosch und Siemens Hausgeräte GmbH | Domestic appliance with heat pump circuit |
| EP2385169A1 (en) * | 2010-05-03 | 2011-11-09 | Electrolux Home Products Corporation N.V. | A laundry machine with heat pump system and a method for operating the laundry machine |
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| CN106245266A (en) * | 2016-08-30 | 2016-12-21 | 无锡小天鹅股份有限公司 | Clothes dryer systems and there is its dryer, washing-drying integral machine |
| CN114514347A (en) * | 2019-09-25 | 2022-05-17 | Bsh家用电器有限公司 | Appliance for drying laundry and method for operating such an appliance |
| CN114514347B (en) * | 2019-09-25 | 2024-02-06 | Bsh家用电器有限公司 | Appliance for drying laundry and method for operating such an appliance |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2594688A1 (en) | 2013-05-22 |
| WO2013075997A1 (en) | 2013-05-30 |
| EP2594688B1 (en) | 2016-08-31 |
| CN103946441B (en) | 2016-12-14 |
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