WO2017036280A1 - 一种直排式热泵干衣机 - Google Patents

一种直排式热泵干衣机 Download PDF

Info

Publication number
WO2017036280A1
WO2017036280A1 PCT/CN2016/094140 CN2016094140W WO2017036280A1 WO 2017036280 A1 WO2017036280 A1 WO 2017036280A1 CN 2016094140 W CN2016094140 W CN 2016094140W WO 2017036280 A1 WO2017036280 A1 WO 2017036280A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat pump
branch
drying
evaporator
exhaust
Prior art date
Application number
PCT/CN2016/094140
Other languages
English (en)
French (fr)
Inventor
许升
宋华诚
田书君
单世强
Original Assignee
青岛海尔滚筒洗衣机有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 青岛海尔滚筒洗衣机有限公司 filed Critical 青岛海尔滚筒洗衣机有限公司
Priority to JP2018511116A priority Critical patent/JP6704598B2/ja
Priority to KR1020187007659A priority patent/KR102085023B1/ko
Priority to US15/753,477 priority patent/US10662573B2/en
Priority to EP16840709.6A priority patent/EP3346045A4/en
Publication of WO2017036280A1 publication Critical patent/WO2017036280A1/zh

Links

Images

Classifications

    • 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
    • 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
    • D06F58/10—Drying cabinets or drying chambers having heating or ventilating means
    • 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
    • D06F58/30—Drying processes 
    • 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
    • D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • D06F2103/02—Characteristics of laundry or load
    • D06F2103/08—Humidity
    • 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
    • D06F2103/00—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers
    • D06F2103/56—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers related to air ducts, e.g. position of flow diverters
    • 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
    • D06F2105/00—Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
    • D06F2105/26—Heat pumps
    • 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
    • D06F2105/00—Systems or parameters controlled or affected by the control systems of washing machines, washer-dryers or laundry dryers
    • D06F2105/30—Blowers
    • 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 
    • D06F58/24—Condensing arrangements

Definitions

  • the invention relates to a clothes drying device in the field of household appliances, in particular to an in-line heat pump dryer.
  • the existing dryers mainly exist in the following two ways:
  • the first type is an in-line type clothes dryer, and its working principle is as follows: air is taken in from the outside atmosphere, and the suction air is heated by a heating wire, and the heated high-temperature drying gas is blown into the outer tube, and the clothes on the clothes are The water is vaporized; the water after the gasification is mixed into the gas to become high-temperature moisture, and the high-temperature moisture is finally discharged to the outer cylinder to achieve the purpose of drying the clothes.
  • the exhaust gas contains a large amount of residual heat, it cannot be recycled, resulting in high energy consumption and low efficiency.
  • the second type is a heat pump type dryer, and its working principle is as follows: the outer tube and the drying air passage are connected end to end to form a circulating air path.
  • the airflow in the drying air duct is heated by the condenser of the heat pump system to form a high-temperature drying gas and flows into the outer cylinder, and the high-temperature drying gas flowing into the outer cylinder vaporizes the moisture on the clothes therein; the vaporized water is mixed into the gas.
  • high-temperature moisture For high-temperature moisture, high-temperature moisture is discharged into the outer cylinder and flows into the drying air duct; the high-temperature moisture flowing into the drying air passage is condensed and precipitated into a low-temperature drying gas by the evaporator; the low-temperature drying gas flows through the evaporator. To complete the air circulation. Through the work of the dryer, the above-mentioned circulating airflow is continuously generated, and finally the purpose of drying the clothes is achieved.
  • the heat pump dryer can recycle the waste heat from the exhaust gas from the outer cylinder, the energy consumption is reduced; however, since the gas inside is always in a closed loop state, the moisture is completely condensed by the evaporator, and the dehumidification speed ratio is Straight row is slow. Therefore, how to combine the heat pump dryer with the in-line dryer to obtain a kind of exhaust gas can be recycled, low energy consumption, high drying efficiency, and high cleanliness after drying.
  • the in-line heat pump dryer has become an urgent problem to be solved.
  • the object of the present invention is to provide an in-line heat pump dryer to realize the effect of preheating and recovering the exhaust airflow by the heat pump system in the direct discharge dryer, and improving the drying. Efficiency and the purpose of reducing energy consumption.
  • Another object of the present invention is to provide an in-line heat pump dryer to achieve different heat pump loads and improve drying efficiency in different drying periods of the dryer.
  • the utility model relates to an in-line heat pump dryer, which comprises an outer cylinder, an intake drying air passage and an exhaust drying air passage which respectively connect the outer cylinder and the outer part; the dryer system is further provided with a heat pump system and a heat pump system.
  • the condenser is arranged in the intake drying air passage, and the evaporator is arranged in the exhaust drying air passage.
  • the exhaust drying air passage includes at least two controllable opening and closing branches, and corresponding evaporators are respectively disposed in each branch to flow the exhaust airflow through the corresponding branch in different drying periods. The purpose of adjusting the power of the heat pump system is achieved.
  • one evaporator is respectively disposed in each of the two branches, and two evaporators are provided with heat exchange fins of different densities; the two evaporators are connected to the same heat pump system through the three-way control valve, and the heat pump system
  • the medium in the cold medium can flow through two evaporators simultaneously or separately.
  • the evaporator includes a first portion and a second portion having different heat exchange fin densities, and the first portion and the second portion are respectively located in different branches of the exhaust drying air passage.
  • the two branches are correspondingly connected in parallel, and the two branches are provided with a damper for controlling the opening and closing of the branch near the outlet end of the outer cylinder.
  • each evaporator is incorporated into the same heat pump system, and the cold medium in the heat pump system can flow through each of the two branches simultaneously or separately.
  • the heat exchange fins on each evaporator have the same density, and the heat exchange fins on the evaporators in the same branch are staggered so that the fins in the two branches have different densities.
  • a partition is provided in a middle portion of the exhaust drying air passage, and the partition divides the corresponding exhaust drying air passage into a first branch and a second branch connected in parallel; the partition is near the outlet end of the outer cylinder There is a damper that controls the two branches to open separately or simultaneously.
  • the damper is mounted on the partition near one end of the outer cylinder, and the damper is connected to the partition via a hinge so that the damper can rotate around the hinge shaft to open the first branch and the second branch separately or simultaneously.
  • the damper when the dryer performs the drying process or when the drying is performed at a higher drying temperature, the damper is in the first state, the first branch is opened, and the second branch is closed, so that the exhaust gas flows only through the first An evaporator having a lower density of heat exchange fins in the branch;
  • the damper When the dryer performs the drying process or the drying is performed at a lower drying temperature, the damper is in the second state, the first branch is closed, and the second branch is opened, so that the exhaust gas flows only through the second branch.
  • the damper when the dryer adopts a special working condition for rapid drying of the clothes, the damper is in the third state, the first branch is opened, and the second branch is opened, so that the exhaust gas flows through the evaporation in the two branches respectively.
  • the discharge of the refrigerant increases the upper limit of the endothermic saturation of the refrigerant; at the same time, in order to match the saturation of the refrigerant, the flow rate of the dry air flow can be increased, so that the drying time of the laundry is shortened.
  • the compressor of the heat pump system is disposed in the intake drying air passage upstream of the condenser to preheat the intake air flow.
  • an auxiliary heating wire is further disposed in the intake drying air path, and the auxiliary heating wire is disposed downstream of the condenser; and the exhaust drying air path is provided with a fan that controls a flow direction of the heat exchange gas, and the fan Located upstream of the damper.
  • a filter screen is disposed in the exhaust drying air path between the fan and the outlet port of the outer cylinder to filter the wire dust in the exhaust gas flow.
  • the exhaust drying air passage includes at least three branches corresponding to the opening and closing dampers, and corresponding evaporators are respectively disposed in each of the branches.
  • the dryer is in the second state in the stage where the drying start temperature is low, and the exhaust airflow passes through the entire evaporator or most of the portions through the fins, which can increase the suction of the evaporator.
  • the thermal effect makes the cold medium mass absorb heat and the heat pump load is large, so as to increase the heating temperature of the intake air flow after passing through the condenser.
  • the damper when the temperature of the dryer is high in the middle and late stages of drying, the damper is in the first state, so that all or most of the air passes through the fins and the sparse part of the evaporator to reduce the heat absorption of the evaporator, so that the heat pump system
  • the condensing temperature is kept close to or slightly lower than 70 ° C to save energy.
  • the accumulation of swarf on the surface of the evaporator fins can be avoided. Since the inner part of the outer cylinder is relatively dry and the clothes are easily worn when the drying process is performed at the later stage of the drying process, the swarf formed after the wear is discharged with the exhaust gas flow. Although most of the thread will be filtered by the filter, some of the very fine chips will pass through the filter to the evaporator position. If the damper is operated at a later stage, the exhaust gas flow passes through the evaporator with a lower density of the heat exchange fins, which makes the wire easier to pass through the evaporator without being trapped and accumulated.
  • the invention has simple structure and remarkable effect, and is suitable for popularization and use.
  • FIG. 1 is a schematic structural view of a clothes dryer in an embodiment of the present invention
  • FIG. 2 is a schematic structural view of an exhaust drying air passage corresponding to a first state in a damper according to an embodiment of the present invention
  • FIG. 3 is a schematic structural view of an exhaust drying air passage corresponding to a second state in a damper according to an embodiment of the present invention
  • FIG. 4 is a schematic structural view of an exhaust drying air passage corresponding to a third state in a damper according to an embodiment of the present invention.
  • Figure 5 is a schematic structural view of a clothes dryer in another embodiment of the present invention.
  • Fig. 6 is a structural schematic view showing an exhaust drying air passage in still another embodiment of the present invention.
  • Main components 1 - outer cylinder, 2 - intake drying air duct, 3 - exhaust drying air duct, 4 - condenser, 5 - evaporator, 6 - auxiliary heating wire, 7 - filter, 8 - Fan, 9-compressor, 10-throttle device, 11-first branch, 12-second branch, 13-first part, 14-second part, 15-first evaporator, 16-second evaporation , 17 - partition, 18 - hinge, 19 - damper, 20 - air inlet, 21 - outlet, 22 - air inlet, 23 - air outlet, 25 - three-way control valve, 26 - first damper, 27—Second damper, 28—third branch, 29—third.
  • an embodiment of the present invention introduces an in-line heat pump dryer, which includes an outer cylinder 1, an intake drying air passage 2, and an exhaust drying air passage 3; One end of the air drying air passage 2 is in communication with the air inlet 22 of the outer cylinder, and the other end is an air inlet end 20 communicating with the atmosphere; the end of the exhaust drying air passage 3 is connected to the air outlet 23 of the outer cylinder. The other end is an air outlet end 21 that communicates with the atmosphere.
  • the dryer is further provided with a heat pump system, and the heat pump system comprises at least a condenser 4, a throttling device 10, an evaporator 5 and a compressor 9 connected end by end through a pipeline to constitute a circulating flow of the refrigerant. Flow channel.
  • the condenser 4 is disposed in the intake drying air passage 2, and the evaporator 4 is disposed in the exhaust drying air passage 3.
  • the outlet end of the compressor 9 is an end for the refrigerant to flow out of the compressor, and the outlet end is connected to the condenser 4 via a pipeline;
  • the inlet end of the compressor 9 is an end for the refrigerant to flow into the compressor, the inlet The end pipe is connected to the evaporator 5.
  • the cold medium in the heat pump system is circulated in the direction from the outlet end of the compressor to the inlet of the condenser to the throttle device to the evaporator to the inlet of the compressor under the action of the compressor, so as to achieve a flow through the condenser.
  • the intake airflow is heated to heat up, and the purpose of sucking heat and cooling the exhaust gas flowing through the evaporator is to achieve the purpose of drying the clothes in the outer tub.
  • the compressor 9 in order to improve the working efficiency of the heat pump system, the compressor 9 is disposed in the intake drying air passage 2 upstream of the condenser 4 to pre-intake the intake air flow by utilizing the heat dissipation amount during the working process of the compressor. heating.
  • the auxiliary heating air duct 2 is provided with an auxiliary heating wire 6 for electrically heating the flowing airflow; further preferably, the The auxiliary heating wire 6 is provided in the intake drying air path 2 downstream of the condenser 4 to improve electric heating efficiency.
  • the air intake and/or exhaust drying air passage is provided with a fan 8 for controlling the direction of the airflow in the air passage.
  • a fan 8 is disposed in the exhaust drying air passage 3, and the fan 8 is disposed upstream of the evaporator 5, so that the airflow direction in the intake air drying duct 2 is the self-intake end 20
  • the flow direction of the air inlet 22 flows, and the airflow direction in the outer cylinder 1 flows from the air inlet 22 to the air outlet 23, and the airflow direction in the exhaust air passage 3 flows from the air outlet 23 toward the air outlet end 21.
  • the exhaust drying air passage 3 is provided with a filter net 7 for filtering the wire debris in the exhaust gas flow, and the filter net 7 is disposed upstream of the fan 8 and close to the air outlet 23. Exhaust air to dry the wind road 3.
  • the in-line heat pump dryer using the above method has the following problems: when the dryer is dried or when the temperature is dried, the temperature and humidity of the discharged air gradually increase, and when the upper limit of the heat pump system is reached, It is necessary to reduce the input power of the heating wire or to make the heating intermittently work to avoid the heat pump load exceeding the limit. However, this is equivalent to limiting the input of heating energy, which is not conducive to drying of clothes from the evaluation of drying time.
  • the exhaust drying air passage 3 includes at least two branches corresponding to the opening and closing dampers 19, and corresponding evaporators are respectively disposed in each branch. 5.
  • the density of the heat exchange fins on the evaporator 5 in each branch is different, so that the exhaust gas flow of the dryer during different working periods is discharged separately or simultaneously through the corresponding branch to control the heat absorption rate of the evaporator, thereby avoiding In the late drying or high-temperature drying, it is necessary to reduce the heat input of the auxiliary heating wire to achieve the effect of shortening the drying time of the dryer; at the same time, the purpose of minimizing the exhaust resistance and improving the drying efficiency of the dryer is achieved.
  • a partition 17 is disposed in the exhaust drying air passage 3 between the fan 8 and the air outlet end 21 , and the partition 17 is along the axis of the exhaust drying air passage 3 .
  • the parallel direction extends to make the corresponding portion of the exhaust drying air passage 3 into two corresponding parallel branches, which are the first branch 11 and the second branch 12, respectively.
  • the evaporator 5 of the heat pump system is correspondingly disposed in the first branch 11 and the second branch 12.
  • the evaporator 5 extends in a direction perpendicular to the axis of the exhaust drying air passage 3 and is disposed through the partition plate 17, so that the first portion 13 of the evaporator 5 is disposed in the first branch 11 and the second portion 14 is provided.
  • the second branch 12 In the second branch 12 .
  • the evaporator 5 is arranged with a plurality of heat exchange fins arranged at intervals along the axis parallel to the axis of the exhaust drying air passage; preferably, the distance between the heat exchange fins disposed on the first portion 13 is greater than
  • the heat transfer fins disposed on the second portion 14 are spaced apart such that the heat exchange fins on the first portion 13 and the second portion 14 are arranged at different densities, making them suitable for different working periods of the dryer.
  • the two branches are provided near the end of the outer cylinder air outlet 23, and a damper 19 for controlling the opening and closing of the branch is provided.
  • a damper 19 for controlling the opening and closing of the branch is provided.
  • one end of the damper 19 is connected to the partition 17 near the air inlet end via a hinge 18, so that the damper 19 can be rotated around the hinge to open or close the first branch 11 and the second branch 12 respectively.
  • the damper 19 has the following states:
  • the damper 19 is in the first state, opening the first branch 11 and closing the second branch 12. At this time, the exhaust gas flow is discharged through the first branch 11 and exchanges heat with the first portion 13 of the evaporator having a small heat exchange fin density, which is suitable for the dryer to perform the drying process or adopt a higher drying temperature. Drying.
  • the damper 19 is in the second state, closing the first branch 11 and opening the second branch 12; at this time, the exhaust gas flow is discharged through the second branch 12, and the heat exchange fin has a higher density.
  • the second portion 14 of the evaporator is heat exchanged and is suitable for drying the dryer at the beginning of the drying process or at a lower drying temperature.
  • the damper 19 also has a third state, opening the first branch 11 and opening the second branch 12.
  • the exhaust gas stream is simultaneously discharged through the first and second branches, and exchanges heat with the first and second portions of the evaporator, so that the exhaust gas stream is simultaneously discharged through the evaporators in the two branches, respectively.
  • the flow rate of the drying air flow can be increased, so that the drying time of the clothes is shortened, which is suitable for the dry drying machine under the special conditions of rapid drying.
  • the dryer is in the second state in the stage where the drying start temperature is low, and the exhaust airflow passes through the entire evaporator or most of the portions through the fins, which can increase the suction of the evaporator.
  • the thermal effect makes the cold medium mass absorb heat and the heat pump load is large, so as to increase the heating temperature of the intake air flow after passing through the condenser.
  • the damper when the temperature of the dryer is high in the middle and late stages of drying, the damper is in the first state, so that all or most of the air passes through the fins and the sparse part of the evaporator to reduce the heat absorption of the evaporator, so that the heat pump system
  • the condensing temperature is kept close to or slightly lower than 70 ° C to save energy.
  • the damper is in the third state, so that the exhaust air flow is simultaneously discharged through the parallel first branch and the second branch to increase the heat absorption rate of the evaporator. Increase the temperature of the Jinfeng airflow flowing through the condenser to achieve the purpose of reducing the drying time.
  • the difference between this embodiment and the first embodiment is that a first evaporator 15 is disposed in the first branch 11 of the exhaust drying air passage 3, and a second is disposed in the second branch 12 Evaporator 16.
  • the density of the heat exchange fins provided on the first evaporator 15 is smaller than the density of the heat exchange fins provided on the second evaporator 16.
  • the air inlet ends of the first evaporator 15 and the second evaporator 16 are in communication with the throttle device 10 via a three-way control valve 25, and the first evaporator 15 and the second evaporator 16 are The outlet end is in communication with the compressor 9 via another three-way control valve 25.
  • the cold medium can be caused to flow through the first evaporator 15 and the second evaporator 16 separately or simultaneously to achieve control of the flow direction of the refrigerant.
  • the cold medium in the three-way control valve 25 flows into the first evaporator 15 and does not flow into the second evaporator 16;
  • the evaporator in the exhaust gas branch is prevented from flowing through the refrigerant to reduce the energy consumption of the heat pump system and improve the refrigerant exchange. Thermal efficiency. At the same time, it is convenient to maintain the evaporator in different branches to improve the maintenance cost of the dryer.
  • an evaporator is provided in the first branch; at least two evaporators are disposed in the second branch, so that the heat exchange fin of the evaporator in the first branch
  • the sheet density is less than the heat exchange fin density of the evaporator in the second branch (not noted in the drawings).
  • the difference between the embodiment and the above-mentioned first to third embodiments is that the exhaust drying air passage 3 includes at least three branches corresponding to the opening and closing dampers, and correspondingly corresponding to each of the branches Evaporator 5.
  • the rationality of the evaporator arrangement is further improved, and more power options are provided for the dryer to further match the heat pump power corresponding to different time periods, thereby achieving the purpose of improving drying efficiency and reducing energy consumption.
  • two exhausting partitions 17 are disposed in the exhaust drying air passage 3 between the fan 8 and the air outlet end 21, and the partitions 17 are all baked along the exhaust.
  • the axis of the dry wind road extends in parallel to the corresponding portion of the exhaust drying air passage 3 as three corresponding parallel branches, respectively being the first branch 11, the second branch 12 and the third branch 28 .
  • the evaporator 5 of the heat pump system extends in a direction perpendicular to the axis of the exhaust drying air passage 3, and is sequentially disposed through the two partitions 17, so that the first portion 13 of the evaporator 5 is disposed in the first branch.
  • the second portion 14 is disposed in the second branch 12 and the third portion 29 is disposed in the third branch 28.
  • the spacing distance of the heat exchange fins disposed on the first portion 13 is greater than the spacing distance of the heat exchange fins disposed on the second portion 14 is greater than the spacing distance of the heat exchange fins disposed on the third portion 29, so that The heat exchange fins on the portion 13, the second portion 14, and the third portion 29 are arranged at different densities, making them suitable for different working periods of the dryer.
  • the first damper 26 is disposed on the partition between the first branch 11 and the second branch 12, and the second partition 12 and the third branch 13 are provided with a second partition. Damper 27.
  • the first damper 26 has three states: a first state, opening the first branch, closing the second branch; a second state, closing the first branch, opening the second branch; and the third state, opening the first One road, open the second branch.
  • the second damper 27 has the following three states: a first state, opening a second branch, closing a third branch; a second state, closing a second branch, opening a third branch; and a third state, opening the first The second branch opens the third branch.
  • the first branch, the second branch and the third branch can be opened separately or simultaneously to achieve a reasonable deployment of the exhaust airflow, thereby improving the working efficiency of the dryer, Reduce the purpose of energy consumption.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

一种直排式热泵干衣机，其包括：外筒、将外筒（1）与外部分别相连通的进气烘干风路（2）、排气烘干风路（3）；所述干衣机上还设有热泵系统，热泵系统的冷凝器（4）设于进气烘干风路（2）中，蒸发器（5）设于排气烘干风路（3），所述排气烘干风路（3）包括至少两个可控开闭的支路，各支路中分别设有对应的蒸发器（5）。所述干衣机可以在不同干燥阶段，使排气气流分别或同时流经不同支路，合理调节热泵的工作状态，提高干衣机的烘干效率。

Description

一种直排式热泵干衣机 技术领域
本发明涉及家电领域的一种干衣设备，尤其涉及一种直排式热泵干衣机。
背景技术
现有的干衣机主要存在如下两种方式：
第一种为直排式干衣机，其工作原理如下：自外界大气吸入空气，并利用加热丝对吸入空气进行加热，加热后的高温干燥气体吹入外筒中，并将其内衣物上的水分气化；气化后的水分混合入气体中变为高温湿气，高温湿气最后排出外筒，以实现对衣物烘干的目的。但是，上述方式中，因排出气体中含有大量余热，不能被回收利用，造成能耗较大、效率低下。
第二种为热泵式干衣机，其工作原理如下：外筒与烘干风道首尾相连构成循环风路。烘干风道中的气流经热泵系统的冷凝器加热后形成高温干燥气体并流入外筒，流入外筒中的高温干燥气体将其内衣物上的水分气化；气化后的水分混合入气体中变为高温湿气，高温湿气排出外筒并流入烘干风道；流入烘干风道中的高温湿气经蒸发器作用使水汽冷凝析出变为低温干燥气体；低温干燥气体再流经蒸发器，以完成气流循环。通过干衣机工作中不断生成上述循环气流，最终实现对衣物进行烘干的目的。
虽然，热泵式干衣机可对自外筒排出气体中的余热可被回收利用，降低了能耗；但是因其内气体始终处于封闭循环状态，湿气完全靠蒸发器进行冷凝，除湿速度比直排式慢。因此，如何将热泵干衣机与直排式干衣机结合起来得出一种可对排气进行回收利用、能耗较低、烘干效率较高、且烘干后衣物洁净度较高的直排式热泵干衣机就成了急需解决的问题。
有鉴于此，特提出本发明。
发明内容
本发明的目的在于提供一种直排式热泵干衣机，以实现直排式干衣机利用热泵系统对排气气流中预热回收、对进气气流预加热的效果，并达到提高烘干效率、降低能耗的目的。
本发明的另一目的在于提供一种直排式热泵干衣机，以实现干衣机不同烘干时期对应不同热泵负荷，提高烘干效率的目的。
为实现发明目的，采用如下技术方案：
一种直排式热泵干衣机，其包括，外筒，将外筒与外部分别相连通的进气烘干风路、排气烘干风路；干衣机上还设有热泵系统，热泵系统的冷凝器设于进气烘干风路中，蒸发器设于排气烘干风路。
进一步，所述排气烘干风路包括至少两个可控开闭的支路，各支路中分别设有对应的蒸发器，以在不同烘干时期使排气气流流经对应支路，达到调整热泵系统功率的目的。
进一步，两个支路中分别各设有一个蒸发器，且两个蒸发器上设有不同密度的换热翅片；两个蒸发器经三通控制阀并连入同一热泵系统中，热泵系统中的冷媒介质可同时或分别流经两个蒸发器。
进一步，所述的蒸发器包括换热翅片密度不同的第一部分和第二部分，第一部分和第二部分分别处于排气烘干风路的不同支路中。
进一步，两个支路相对应的并联，且两个支路靠近外筒出风口端设有控制支路开闭的风门。
进一步，两个支路中分别设有不同数量的蒸发器，各蒸发器均并入同一热泵系统中，热泵系统中的冷媒介质可同时或分别流经两个支路中的各蒸发器。
优选的，各蒸发器上所述换热翅片的密度相同设置，且同一支路中的各蒸发器上换热翅片相交错设置，使两个支路中的翅片密度不同。
进一步，排气烘干风路的中部设有隔板，隔板将对应的排气烘干风路分为并连的第一支路和第二支路；在隔板靠近外筒出风口端设有控制两个支路分别或同时开启的风门。
优选的，所述的风门安装于隔板靠近外筒一端，所述风门与隔板经铰链相连接，使得风门可绕铰链轴旋转，以分别或同时打开第一支路和第二支路。
进一步，在干衣机执行烘干程序后期或采用较高烘干温度进行烘干时，风门处于第一状态，打开第一支路、闭合第二支路，令排气气流只流经第一支路中换热翅片密度较小的蒸发器；
在干衣机执行烘干程序前期或采用较低烘干温度进行烘干时，风门处于第二状态，闭合第一支路、打开第二支路，令排气气流只流经第二支路中换热翅片密度较大的蒸发器。
进一步，在干衣机采用对衣物快速烘干的特殊工况时，风门处于第三状态，打开第一支路、打开第二支路，以使排气气流分别经两个支路中的蒸发器同时排出，增加冷媒的吸热饱和上限；同时，为了配合冷媒吸热饱和度，可增加烘干气流的流动速率，使得衣物的烘干时间得到缩短。
进一步，热泵系统的压缩机设于冷凝器上游的进气烘干风路中，以对进气气流进行预加热。
进一步，进气烘干风路中还设有辅助加热丝，所述辅助加热丝设于冷凝器的下游；所述排气烘干风路中设有控制换热气体流向的风机，所述风机设于风门的上游。所述风机与外筒出气口之间的排气烘干风路中设有过滤网，以对排气气流中的线屑进行过滤。
进一步，所述排气烘干风路包括至少三个对应设有开闭风门的支路，各支路中分别设有对应的蒸发器。
采用上述技术方案，本发明较现有技术的优势在于：
通过上述设置和方法，使得干衣机在干燥开始温度较低的阶段，风门处于第二状态，使排气气流通过整个蒸发器或大部分通过翅片较密集的部分，可以增加蒸发器的吸热效果，使冷媒介质较大负载吸热、令热泵负荷较大，以提高经过冷凝器后进气气流的加热温度。同时，干衣机在干燥中后期温度较高的时候，风门处于第一状态，使空气全部或大部分通过翅片较稀疏部分蒸发器，以减小蒸发器的吸热量，使热泵系统的冷凝温度保持接近或略低于70℃，以达到节约能耗的目的。
通过这种方式，可以在干衣机执行烘干程序后期，避免为降低热泵负荷，需执行将辅助加热丝关闭或压缩机关闭的步骤，提高干衣机干燥后期的热量输入，合理分配干衣机不同时期干燥速度的提升。
同时，可以避免线屑在蒸发器翅片表面的积存。由于在干衣机执行烘干程序后期，排气气流温度较高的时候，外筒内部较为干燥，衣物容易磨损，磨损后形成的线屑会随排气气流排出。虽然大部分线屑会被过滤网过滤，但一部分极细小的线屑会透过过滤器到达蒸发器位置。如果在后期动作风门，使排气气流穿过蒸发器的换热翅片密度较小部分，会令线屑更容易经过蒸发器而不会被拦截造成积累。
本发明结构简单，效果显著，适宜推广使用。
附图说明
图1本发明实施例中干衣机的结构示意图；
图2本发明实施例中风门处于第一状态对应的排气烘干风路的结构示意图；
图3本发明实施例中风门处于第二状态对应的排气烘干风路的结构示意图；
图4本发明实施例中风门处于第三状态对应的排气烘干风路的结构示意图；
图5本发明另一实施例中干衣机的结构示意图；
图6本发明再一实施例中排气烘干风路的结构示意图。
主要元件说明：1—外筒，2—进气烘干风路，3—排气烘干风路，4—冷凝器，5—蒸发器，6—辅助加热丝，7—过滤网，8—风机，9—压缩机，10—节流装置，11—第一支路,12—第二支路，13—第一部分，14—第二部分，15—第一蒸发器，16—第二蒸发器，17—隔板，18—铰链，19—风门，20—进风端，21—出风端，22—进风口，23—出风口，25—三通控制阀，26—第一风门，27—第二风门，28—第三支路，29—第三部分。
具体实施方式
下面结合实施例对本发明进行进一步详细的说明。
如图1所示，本发明实施例中介绍了一种直排式热泵干衣机，其包括，外筒1，进气烘干风路2、排气烘干风路3；所述的进气烘干风路2一端与外筒的进风口22相连通、另一端为与大气相连通的进风端20；所述的排气烘干风路3一端与外筒的出风口23相连通、另一端为与大气相连通的出风端21。所述的干衣机上还设有热泵系统，所述的热泵系统至少包括，经管路依次首尾连接的冷凝器4、节流装置10、蒸发器5和压缩机9，以构成供冷媒循环流动的流动通道。
本发明实施例中，所述的冷凝器4设于进气烘干风路2中，所述的蒸发器4设于排气烘干风路3中。所述压缩机9的出口端为供冷媒介质流出压缩机的一端，该出口端经管路与冷凝器4相连接；所述压缩机9的进口端为供冷媒介质流入压缩机的一端，该进口端经管路与蒸发器5相连接。从而，使得热泵系统中的冷媒介质，在压缩机作用下，沿自压缩机的出口端至冷凝器至节流装置至蒸发器至压缩机的进口端的方向循环流动，以实现对流经冷凝器的进气气流加热升温、对流经蒸发器的排气气流吸热降温的目的，进而实现对外桶内衣物进行烘干的目的。
本发明实施例中，为了提高热泵系统的工作效率，将压缩机9设于冷凝器4上游的进气烘干风路2中，以利用压缩机工作过程中的散热量对进气气流进行预加热。为了提高进风气流的加热速率及流入外筒中进风气流的温度，优选的，进气烘干风路2中设有辅助加热丝6，以对流经气流进行电加热；进一步优选的，所述的辅助加热丝6设于冷凝器4下游的进气烘干风路2中，以提高电加热效率。
本发明实施例中，所述的进气和/或排气烘干风路中设有控制风路中气流方向的风机8。优选的，仅在排气烘干风路3中设有一风机8，所述风机8设于蒸发器5的上游，就可实现进风烘干风路2中的气流方向为自进风端20向进风口22方向流动、外筒1中的气流方向为自进风口22向出风口23方向流动、排气烘干风路3中的气流方向为自出风口23向出风端21方向流动。
本发明实施例中，所述的排气烘干风路3中设有过滤排气气流中线屑杂物的过滤网7，所述的过滤网7设于风机8上游的、靠近出风口23的排风烘干风路3中。
但是，采用上述方式的直排式热泵干衣机存在如下问题：在干衣机烘干后期或采用高温烘干时，随排出的空气温度和湿度逐渐升高，当达到热泵系统负荷上限时，需要降低加热丝的输入功率或者使加热间断性工作，以避免热泵负荷超出限制。但是，这相当于限制了加热能量的输入，从干燥时间的考核上，不利于衣物干燥。
如图1至图6所示，本发明实施例中，所述排气烘干风路3包括至少两个对应设有开闭风门19的支路，各支路中分别设有对应的蒸发器5。各支路中蒸发器5上所设换热翅片的密度不相同，令干衣机不同工作时段的排气气流分别或同时经对应支路排出，以控制蒸发器的吸热速率，避免了烘干后期或高温烘干时需降低辅助加热丝热量输入的情况，以实现缩短干衣机烘干时间的效果；同时，达到了尽量降低排气阻力，提高干衣机烘干效率的目的。
实施例一
如图1所示，本实施例中，风机8与出风端21之间的排气烘干风路3中设有隔板17，所述隔板17沿排气烘干风路3轴线相平行方向延伸，以将排气烘干风路3对应部分为两个相对应并联的支路，分别为第一支路11和第二支路12。
本实施例中，热泵系统的蒸发器5对应设于第一支路11和第二支路12中。所述蒸发器5沿与排气烘干风路3轴线相垂直方向延伸，并穿过隔板17设置，使蒸发器5的第一部分13设于第一支路11中，第二部分14设于第二支路12中。所述蒸发器5上排布有沿排气烘干风路轴线平行方向延伸的、间隔排布的多片换热翅片；优选的，第一部分13上所设换热翅片的间隔距离大于第二部分14上所设换热翅片的间隔距离，以使得第一部分13和第二部分14上的换热翅片排布密度不同，使其适用于干衣机的不同工作时段。
本实施例中，两个支路靠近外筒出风口23端设有控制支路开闭的风门19。优选的，所述风门19一端与隔板17靠近进风口端经铰链18相连接，使风门19可绕铰链旋转，以分别将第一支路11、第二支路12对应打开或关闭。
本实施例中，所述风门19具有如下状态：
如图2所示，风门19处于第一状态，打开第一支路11、闭合第二支路12。此时，排气气流经第一支路11排出，并与换热翅片密度较小的蒸发器第一部分13进行热交换，适用于干衣机执行烘干程序后期或采用较高烘干温度进行烘干。
如图3所示，风门19处于第二状态，闭合第一支路11、打开第二支路12；此时，排气气流经第二支路12排出，并与换热翅片密度较大的蒸发器第二部分14进行热交换，适用于干衣机执行烘干程序初期或采用较低烘干温度进行烘干。
优选的，如图4所示，所述风门19还具有第三状态，打开第一支路11、打开第二支路12。此时，排气气流同时经第一和第二支路排出，并与蒸发器的第一和第二部分进行热交换，以使排气气流分别经两个支路中的蒸发器同时排出，增加冷媒的吸热饱和上限；同时，为了配合冷媒吸热饱和度，可增加烘干气流的流动速率，使得衣物的烘干时间得到缩短，适用于干衣机采用快速烘干特殊工况下。
通过上述设置和方法，使得干衣机在干燥开始温度较低的阶段，风门处于第二状态，使排气气流通过整个蒸发器或大部分通过翅片较密集的部分，可以增加蒸发器的吸热效果，使冷媒介质较大负载吸热、令热泵负荷较大，以提高经过冷凝器后进气气流的加热温度。同时，干衣机在干燥中后期温度较高的时候，风门处于第一状态，使空气全部或大部分通过翅片较稀疏部分蒸发器，以减小蒸发器的吸热量，使热泵系统的冷凝温度保持接近或略低于70℃，以达到节约能耗的目的。
通过这种方式，可以避免为降低热泵负荷，需执行将辅助加热丝关闭或压缩机关闭的步骤，提高干衣机干燥后期的热量输入，合理分配干衣机不同时期干燥速度的提升。
同时，在干衣机需对衣物快速烘干时，将风门处于第三状态，以使排风气流同时经并联的第一支路和第二支路外排，以提高蒸发器的吸热速率，增加流经冷凝器的金凤气流温度，达到缩减烘干时间的目的。
实施例二
如图5所示，本实施例与上述实施例一的区别在于：排气烘干风路3的第一支路11中设有第一蒸发器15，第二支路12中设有第二蒸发器16。所述第一蒸发器15上所设换热翅片的密度小于第二蒸发器16上所设换热翅片的密度。
本实施例中，所述的第一蒸发器15和第二蒸发器16的进风端经一三通控制阀25与节流装置10相连通，第一蒸发器15和第二蒸发器16的出风端经另一三通控制阀25与压缩机9相连通。从而，使得冷媒介质可分别或同时流经第一蒸发器15、第二蒸发器16，以实现对冷媒流向的控制。
三通控制阀25和风门19的对应状态如下：
当风门19处于第一状态时，三通控制阀25中的冷媒介质流入第一蒸发器15，不流入第二蒸发器16；
当风门19处于第二状态时，三通控制阀25中的冷媒介质流入第二蒸发器16，不流入第一蒸发器15；
当风门19处于第三状态时，三通控制阀25中的冷媒介质同时流入第一蒸发器15和第二蒸发器16。
通过在两个支路中分别设置单独的蒸发器，以控制冷媒的流经部位，避免不存在排气气流支路中的蒸发器流经冷媒，以降低热泵系统的能耗，提高冷媒的换热效率。同时，便于不同支路中蒸发器的维修，以提高干衣机的后期维护成本。
实施例三
本实施例与上述实施例二的区别在于：在第一支路中设有一个蒸发器；第二支路中设有至少两个蒸发器，以使得第一支路中蒸发器的换热翅片密度小于第二支路中蒸发器的换热翅片密度(未在附图中注明)。
实施例四
如图6所示，本实施例与上述实施例一至三的区别在于：所述排气烘干风路3包括至少三个对应设有开闭风门的支路，各支路中分别设有对应的蒸发器5。
通过上述设置，以进一步提高蒸发器排布的合理度，为干衣机提供更多的功率选择，以进一步匹配不同时段所对应的热泵功率，实现提高烘干效率、降低能耗的目的。
如图6所示，本实施例中，风机8与出风端21之间的排气烘干风路3中设有两个相平行的隔板17，所述隔板17均沿排气烘干风路3轴线相平行方向延伸，以将排气烘干风路3对应部分为三个相对应并联的支路，分别为第一支路11、第二支路12和第三支路28。
本实施例中，热泵系统的蒸发器5沿与排气烘干风路3轴线相垂直方向延伸，并依次穿过两个隔板17设置，使蒸发器5的第一部分13设于第一支路11中，第二部分14设于第二支路12中，第三部分29设于第三支路28中。
优选的，第一部分13上所设换热翅片的间隔距离大于第二部分14上所设换热翅片的间隔距离大于第三部分29上所设换热翅片的间隔距离，以使得第一部分13、第二部分14和第三部分29上的换热翅片排布密度不同，使其适用于干衣机的不同工作时段。
本实施例中，第一支路11和第二支路12之间的隔板上设有第一风门26，第二支路12和第三支路13之间的隔板上设有第二风门27。
所述第一风门26具有如下三个状态：第一状态，打开第一支路、闭合第二支路；第二状态，闭合第一支路、打开第二支路；第三状态，打开第一支路、打开第二支路。
所述第二风门27具有如下三个状态：第一状态，打开第二支路、闭合第三支路；第二状态，闭合第二支路、打开第三支路；第三状态，打开第二支路、打开第三支路。
通过第一风门和第二风门的配合，使得第一支路、第二支路和第三支路可分别或同时打开，以实现对排气气流的合理调配，达到提高干衣机工作效率、降低能耗的目的。
上述实施例中的实施方案可以进一步组合或者替换，且实施例仅仅是对本发明的优选实施例进行描述，并非对本发明的构思和范围进行限定，在不脱离本发明设计思想的前提下，本领域中专业技术人员对本发明的技术方案作出的各种变化和改进，均属于本发明的保护范围。

Claims (10)

  1. 一种直排式热泵干衣机，其包括，外筒，将外筒(1)与外部分别相连通的进气烘干风路(2)、排气烘干风路(3)，其特征在于：干衣机上还设有热泵系统，热泵系统的冷凝器(4)设于进气烘干风路(2)中，蒸发器(5)设于排气烘干风路(3)；所述排气烘干风路(3)包括至少两个可控开闭的支路，各支路中分别设有对应的蒸发器(5)。
  2. 根据权利要求1所述的一种直排式热泵干衣机，其特征在于：两个支路中分别各设有一个蒸发器(5)，且两个蒸发器(5)上设有不同密度的换热翅片；两个蒸发器(5)经三通控制阀(25)并连入同一热泵系统中，热泵系统中的冷媒介质可同时或分别流经两个蒸发器(5)。
  3. 根据权利要求1所述的一种直排式热泵干衣机，其特征在于：热泵系统的蒸发器(5)包括换热翅片密度不同的第一部分(13)和第二部分(14)，第一部分(13)和第二部分(14)分别处于排气烘干风路(3)的不同支路中。
  4. 根据权利要求1所述的一种直排式热泵干衣机，其特征在于：两个支路中分别设有不同数量的蒸发器，各蒸发器均并入同一热泵系统中，热泵系统中的冷媒介质可同时或分别流经两个支路中的各蒸发器(5)。
  5. 根据权利要求1至4任一所述的一种直排式热泵干衣机，其特征在于：排气烘干风路(3)的中部设有隔板(17)，隔板(17)将对应的排气烘干风路(3)分为并连的第一支路(11)和第二支路(12)；在隔板(17)靠近外筒出风口端设有控制两个支路分别或同时开启的风门(19)。
  6. 根据权利要求5所述的一种直排式热泵干衣机，其特征在于：在干衣机执行烘干程序后期或采用较高烘干温度进行烘干时，风门(19)处于第一状态，打开第一支路(11)、闭合第二支路(12)，令排气气流只流经第一支路中换热翅片密度较小的蒸发器。
  7. 根据权利要求5所述的一种直排式热泵干衣机，其特征在于：在干衣机执行烘干程序前期或采用较低烘干温度进行烘干时，风门(19)处于第二状态，闭合第一支路(11)、打开第二支路(12)，令排气气流只流经第二支路中换热翅片密度较大的蒸发器。
  8. 根据权利要求5所述的一种直排式热泵干衣机，其特征在于：在干衣机采用对衣物快速烘干的特殊工况时，风门(19)控制打开第一支路(11)和第二支路(12)。
  9. 根据权利要求1所述的一种直排式热泵干衣机，其特征在于：热泵系统的压缩机(9)设于冷凝器(4)上游的进气烘干风路(2)中，以对进气气流进行预加热。
  10. 根据权利要求1所述的一种直排式热泵干衣机，其特征在于：进气烘干风路(2)中还设有辅助加热丝(6)，所述辅助加热丝(6)设于冷凝器(4)的下游；所述排气烘干风路(3)中设有控制气体流向的风机(8)，所述风机(8)设于风门(19)的上游。
PCT/CN2016/094140 2015-08-31 2016-08-09 一种直排式热泵干衣机 WO2017036280A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2018511116A JP6704598B2 (ja) 2015-08-31 2016-08-09 直接排出式ヒートポンプ衣類乾燥機
KR1020187007659A KR102085023B1 (ko) 2015-08-31 2016-08-09 배기식 히트펌프형 의류 건조기
US15/753,477 US10662573B2 (en) 2015-08-31 2016-08-09 Vented heat pump dryer
EP16840709.6A EP3346045A4 (en) 2015-08-31 2016-08-09 Vented heat pump dryer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510548113.XA CN106480681B (zh) 2015-08-31 2015-08-31 一种直排式热泵干衣机
CN201510548113.X 2015-08-31

Publications (1)

Publication Number Publication Date
WO2017036280A1 true WO2017036280A1 (zh) 2017-03-09

Family

ID=58186714

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/094140 WO2017036280A1 (zh) 2015-08-31 2016-08-09 一种直排式热泵干衣机

Country Status (6)

Country Link
US (1) US10662573B2 (zh)
EP (1) EP3346045A4 (zh)
JP (1) JP6704598B2 (zh)
KR (1) KR102085023B1 (zh)
CN (1) CN106480681B (zh)
WO (1) WO2017036280A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019129614A1 (en) * 2017-12-26 2019-07-04 Arcelik Anonim Sirketi A heat exchanger
CN113532043A (zh) * 2020-04-18 2021-10-22 杭州富阳康华制药机械有限公司 一种连续式热泵烘房及其使用方法

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10480116B2 (en) * 2017-10-06 2019-11-19 Whirlpool Corporation Drying appliance that performs after-care cycle on a load of laundry after completion of a primary drying cycle and method for performing the after-care cycle
CN110438777B (zh) * 2018-05-04 2023-07-21 青岛海尔洗涤电器有限公司 一种烘干模块加热管结构及洗干一体机或干衣机
CN109028916A (zh) * 2018-07-30 2018-12-18 上海伯涵热能科技有限公司 一种采用不同面积风量比进风预冷高效除湿模块的热泵烘干装置
US10816266B2 (en) 2018-08-30 2020-10-27 Whirlpool Corporation Low pressure laundry treating appliance
CN111748981B (zh) * 2020-06-16 2021-09-03 广东天美洗涤有限公司 一种贯通式烘干设备
CN114234462A (zh) * 2020-09-08 2022-03-25 广东美的白色家电技术创新中心有限公司 热交换系统和电器设备
US20230193551A1 (en) * 2021-12-21 2023-06-22 Whirlpool Corporation Dryer with external vent

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101259362A (zh) * 2007-03-07 2008-09-10 三洋电机株式会社 干燥空气供给装置和干燥机
CN101460672A (zh) * 2006-06-06 2009-06-17 Bsh博世和西门子家用器具有限公司 用于烘干衣物的装置和方法
CN201364007Y (zh) * 2009-03-02 2009-12-16 东莞市康源节能科技有限公司 一种空气源高温热泵烘干机
CN102587074A (zh) * 2012-03-30 2012-07-18 常熟南师大发展研究院有限公司 一种热泵复用式洗衣干衣机
KR20120086153A (ko) * 2011-01-25 2012-08-02 위니아만도 주식회사 히트펌프 의류건조기
CN104420145A (zh) * 2013-09-04 2015-03-18 杭州三花微通道换热器有限公司 一种热泵干衣机及其控制方法
CN104532522A (zh) * 2014-08-22 2015-04-22 上海伯涵热能科技有限公司 一种空气开路循环热泵干衣柜

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008029654A (ja) 2006-07-31 2008-02-14 Sharp Corp 洗濯乾燥機
JP2008086424A (ja) * 2006-09-29 2008-04-17 Sanyo Electric Co Ltd 乾燥機
JP2008173330A (ja) * 2007-01-19 2008-07-31 Toshiba Corp 衣類乾燥機
JP4986662B2 (ja) * 2007-03-15 2012-07-25 三洋電機株式会社 乾燥機
JP4889545B2 (ja) * 2007-03-30 2012-03-07 三洋電機株式会社 乾燥装置及びこの装置を備えた洗濯乾燥機
JP5268527B2 (ja) * 2008-09-29 2013-08-21 三洋電機株式会社 ヒートポンプ式乾燥機
KR101142776B1 (ko) * 2010-01-11 2012-05-18 위니아만도 주식회사 히트펌프형 의류건조기
EP2550390B1 (en) 2010-08-09 2016-10-05 LG Electronics Inc. Clothes dryer
JP2012125352A (ja) * 2010-12-14 2012-07-05 Samsung Electronics Co Ltd 衣類乾燥機
JP2015024116A (ja) 2013-06-18 2015-02-05 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 衣類乾燥機
US9879372B2 (en) * 2013-06-18 2018-01-30 Samsung Electronics Co., Ltd. Clothes dryer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101460672A (zh) * 2006-06-06 2009-06-17 Bsh博世和西门子家用器具有限公司 用于烘干衣物的装置和方法
CN101259362A (zh) * 2007-03-07 2008-09-10 三洋电机株式会社 干燥空气供给装置和干燥机
CN201364007Y (zh) * 2009-03-02 2009-12-16 东莞市康源节能科技有限公司 一种空气源高温热泵烘干机
KR20120086153A (ko) * 2011-01-25 2012-08-02 위니아만도 주식회사 히트펌프 의류건조기
CN102587074A (zh) * 2012-03-30 2012-07-18 常熟南师大发展研究院有限公司 一种热泵复用式洗衣干衣机
CN104420145A (zh) * 2013-09-04 2015-03-18 杭州三花微通道换热器有限公司 一种热泵干衣机及其控制方法
CN104532522A (zh) * 2014-08-22 2015-04-22 上海伯涵热能科技有限公司 一种空气开路循环热泵干衣柜

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019129614A1 (en) * 2017-12-26 2019-07-04 Arcelik Anonim Sirketi A heat exchanger
CN113532043A (zh) * 2020-04-18 2021-10-22 杭州富阳康华制药机械有限公司 一种连续式热泵烘房及其使用方法

Also Published As

Publication number Publication date
US10662573B2 (en) 2020-05-26
JP6704598B2 (ja) 2020-06-03
EP3346045A1 (en) 2018-07-11
US20180237980A1 (en) 2018-08-23
EP3346045A4 (en) 2018-08-29
KR102085023B1 (ko) 2020-03-05
KR20180042330A (ko) 2018-04-25
CN106480681A (zh) 2017-03-08
CN106480681B (zh) 2019-08-27
JP2018526100A (ja) 2018-09-13

Similar Documents

Publication Publication Date Title
WO2017036280A1 (zh) 一种直排式热泵干衣机
CN102206916B (zh) 一种用于滚筒干衣的热泵烘干系统及控制方法
WO2017036281A1 (zh) 一种高效的直排式热泵干衣机
CN107724027B (zh) 干衣机
CN207422789U (zh) 一种高效节能烘干机
CN105222566B (zh) 一种带抽湿和废热利用的热泵烘干系统
CN107642925B (zh) 一种带旁通管路的多级热泵干燥除湿系统
CN210374330U (zh) 一种带蒸发除湿和换气除湿的空气源热泵烘干系统
CN205957367U (zh) 除湿机系统
CN113446673A (zh) 一种直膨式转轮复合深度除湿新风系统
CN205119755U (zh) 一种带抽湿和废热利用的热泵烘干系统
CN211932517U (zh) 一种带冷凝除湿功能的闭式循环烟叶烘烤房
CN209537262U (zh) 一种热泵型分温区干燥系统
CN110057169B (zh) 一种水产品热泵型干燥装置
CN111288784A (zh) 一种多级除湿加热开闭环一体热泵机组
CN215112979U (zh) 一种直膨式转轮复合深度除湿新风系统
CN206368284U (zh) 一种高效型一体式烘干装置
CN105361233A (zh) 一种便于安装的智能节能除湿一体式烤烟装置
CN104807314A (zh) 一种箱式换向通风干燥机的余热回收装置及方法
CN211346085U (zh) 一种全仓微速静态烘干装置
CN212299865U (zh) 一种空气能热泵烘干机
CN207050339U (zh) 一种空气源一体式烘干抽湿机及系统
CN212678295U (zh) 一种桑葚果干加工装置
CN110595169A (zh) 一种全仓微速静态烘干装置
CN115925219B (zh) 一种全热回收温度分布式污泥干化装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16840709

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 15753477

Country of ref document: US

ENP Entry into the national phase

Ref document number: 2018511116

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 20187007659

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2016840709

Country of ref document: EP