WO2014127667A1 - 一种热泵干衣机膨胀阀的控制方法 - Google Patents
一种热泵干衣机膨胀阀的控制方法 Download PDFInfo
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- WO2014127667A1 WO2014127667A1 PCT/CN2013/089826 CN2013089826W WO2014127667A1 WO 2014127667 A1 WO2014127667 A1 WO 2014127667A1 CN 2013089826 W CN2013089826 W CN 2013089826W WO 2014127667 A1 WO2014127667 A1 WO 2014127667A1
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- Prior art keywords
- expansion valve
- opening
- temperature
- evaporator
- adjustment mode
- Prior art date
Links
- 238000000034 method Methods 0.000 title claims abstract description 26
- 238000001704 evaporation Methods 0.000 claims abstract description 44
- 239000003507 refrigerant Substances 0.000 claims abstract description 16
- 238000001035 drying Methods 0.000 claims description 41
- 230000008020 evaporation Effects 0.000 claims description 40
- 230000007423 decrease Effects 0.000 claims description 14
- 238000009833 condensation Methods 0.000 claims description 8
- 230000005494 condensation Effects 0.000 claims description 8
- 238000005265 energy consumption Methods 0.000 abstract description 3
- 238000001514 detection method Methods 0.000 description 9
- 230000003247 decreasing effect Effects 0.000 description 8
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000007791 dehumidification Methods 0.000 description 2
- 238000010981 drying operation Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
Classifications
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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
- D06F58/32—Control of operations performed in domestic laundry dryers
- D06F58/34—Control of operations performed in domestic laundry dryers characterised by the purpose or target of the control
-
- 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
- D06F2103/28—Air properties
- D06F2103/32—Temperature
-
- 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
- D06F2103/28—Air properties
- D06F2103/36—Flow or velocity
-
- 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
- D06F2103/50—Parameters monitored or detected for the control of domestic laundry washing machines, washer-dryers or laundry dryers related to heat pumps, e.g. pressure or flow rate
-
- 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
- D06F2105/16—Air properties
- D06F2105/24—Flow or velocity
-
- 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
- D06F58/00—Domestic laundry dryers
- D06F58/20—General details of domestic laundry dryers
- D06F58/206—Heat pump arrangements
Definitions
- the invention relates to a drying clothes control method, in particular to a control method of a heat pump dryer heat pump system, in particular to an expansion valve of a heat pump dryer that adjusts the opening degree of the expansion valve according to the detection temperature to improve the drying efficiency.
- Control Method. BACKGROUND OF THE INVENTION
- An existing air pump type clothes drying device is provided with an air circulation passage: heated air heated by a condenser in a heat pump circulation system is sent into a drying chamber containing clothes, and moisture is taken from the clothes. The air is sent back to the evaporator for dehumidification, and the dehumidified air is again heated by the condenser and sent to the drying chamber.
- the pressure of the compressor system is the saturation pressure corresponding to the temperature of the refrigerant corresponding to 60 ⁇ 70 °C.
- the condensation temperature of the compressor will increase with the increase of temperature. Close to the limit of the highest pressure.
- the existing drum type heat pump dryer is designed with an auxiliary condenser and an auxiliary fan to assist the operation of the fan in the late drying stage or in a high temperature environment, and adjust the compressor load. Due to the single control temperature setting, the drying temperature is raised as much as possible in the middle and early stages of drying, which is conducive to the completion of drying in the middle and early stages; but in the later stage, the temperature inside the cylinder has risen and the humidity of the drying air is decreasing. The required condensation point is decreasing.
- the Chinese Patent Application No. 200610153406. 9 discloses a laundry drying apparatus capable of achieving a stable operation of a heat pump that produces dry clothes air circulating between a drying chamber and a heat pump.
- the air heated by the heater in the heat pump is sent into the water tank as a drying chamber, and the air discharged from the water tank passes through the filter unit, returns to the heat pump, is dehumidified by the heat absorber, and then sent to the heater.
- the filter unit is provided with a lint filter, and is provided with a pipe communicating with the air discharge port and the air introduction port.
- Chinese Patent Application No. 200410097855. 7 discloses a laundry drying device comprising: a heat pump device; a air passage for guiding dry clothes air to a heat pump of a heat pump device, a radiator, and a clothes drying chamber; a blower that feeds dry air into the air duct; and a control device.
- the compressor and the blower are operated; when the drying operation is interrupted, the control device stops the compressor for a prescribed time.
- the above-mentioned drying device using the heat pump drying method starts at a high ambient temperature, for example, 35 to 40 ° C.
- the temperature of the air blown into the laundry/drying cylinder rapidly rises above 60 ° C, and the temperature of the air blown from the washing/drying cylinder rises rapidly.
- the refrigerant saturation pressure in the evaporator is high, the load on the compressor system is large, and the critical working pressure of the compressor is quickly reached.
- the heat dissipation range of the auxiliary cooling fan and the auxiliary condenser will also be exceeded.
- the compressor will stop working due to excessive pressure and excessive exhaust temperature. During the drying process, the compressor will work intermittently. The performance of the compressor components causes an impact and increases the failure rate. If a compressor system is used, although the compressor will adjust the operating frequency of the compressor by the control system to adjust the compressor working load, the compressor itself has a minimum operating frequency range. The high-load operation of the refrigeration system results in a high failure rate of the compressor motor and a reduced service life.
- the technical problem to be solved by the present invention is to overcome the deficiencies of the prior art, and provide a control of an expansion valve of a heat pump dryer by adjusting the opening degree of the expansion valve to improve the drying efficiency while reducing the heat pump working load and thereby reducing the drying energy consumption. method.
- a control method of a heat pump dryer expansion valve which detects the evaporator temperature of the heat pump system and/or the surface temperature of the condenser and/or the compressor row The gas temperature selects the corresponding expansion valve adjustment mode, and the opening degree of the expansion valve is adjusted in each adjustment mode according to the set mode.
- the evaporator evaporation temperature is a temperature at a phase change position of the refrigerant between the evaporator inlet position and the outlet position;
- the condenser surface temperature is a temperature at a phase change position of the refrigerant between the condenser inlet position and the outlet position.
- control of the expansion valve adjusts the opening of the expansion valve to increase and/or decrease and/or maintain at an interval corresponding to each adjustment mode setting.
- the expansion valve is first controlled to perform a full closing operation to be in a completely closed state, and then the expansion valve is opened to a set initial position, and then the compressor is started, and after the frequency up is completed, the expansion valve is executed at intervals. Control adjustment.
- Controlling the expansion valve to perform the full closing operation is as follows: first, the maximum opening pulse of the expansion valve is closed, and then the first pulse of the setting is turned on and the second pulse of the setting is turned off, the set number of times is completed, and the first setting is performed. The pulse is less than the set second pulse.
- the expansion valve adjustment mode mainly includes:
- the evaporator In the first adjustment mode, the evaporator is in a stage of easy frost formation, and the difference between the compressor discharge temperature and the surface temperature of the condenser reflecting the condensation temperature is greater than a set value, and the mode controls the opening degree of the expansion valve to increase, thereby evaporating Evaporation temperature rises;
- a second adjustment mode which controls the opening degree of the expansion valve to increase, decrease or not change, so that the drying temperature rises and the evaporation temperature of the evaporator rises;
- a third adjustment mode detecting that the evaporator evaporation temperature is greater than the first set value, controlling the opening of the expansion valve to decrease, so that steaming The evaporator evaporation temperature is lowered;
- the second adjustment mode is selected.
- the expansion valve is controlled to increase the set opening degree, and if the expansion valve opening degree is increased multiple times until the maximum opening degree allowed by the expansion valve, or the expansion valve opening degree is continuously increased, The number of times is determined, and it is judged that the heat pump compressor and/or the fan are adjusted under the condition of the first adjustment mode.
- SH>0 increase the expansion valve opening degree, and the increasing amplitude and the A SH value change in a positive direction, that is, the larger the A SH value, the larger the opening degree is, the smaller the A SH value is.
- control expansion valve is controlled to decrease the set opening degree, and if the expansion valve opening degree is decreased multiple times until the minimum opening degree allowed by the expansion valve, or the number of expansion valve opening times is continuously reduced, The number of times is determined to determine that the evaporator evaporation temperature is still greater than the first set value, and then the heat pump compressor and/or the fan are controlled for adjustment.
- the present invention has the following advantageous effects as compared with the prior art.
- the heat pump dryer of the invention increases the function of adjusting the expansion valve to control the working efficiency of the heat pump on the basis of the existing heat pump module, and controls the opening degree of the expansion valve in the corresponding adjustment mode at different evaporation temperatures/ Reduced/maintained, combined with compressor control and / or fan control, improve the efficiency of the heat pump, while reducing energy consumption; In addition, through the opening control of the expansion valve, excessive refrigerant flow into the compressor is avoided. Relatively extended the life of the compressor.
- Figure 1 is a schematic view of a heat pump system according to the present invention
- Figure 2 is a schematic view of the heat pump dryer according to the present invention
- Figure 3 is a control flow chart of the expansion valve according to the present invention
- the heat pump dryer of the present invention comprises a drum 1 and a heat pump drying system provided under the drum, and the hot air generated by the heat pump drying system is passed through the drying duct by the air blowing fan 2.
- the heat pump drying system includes a heat pump module having a compressor 3, a condenser 4, an expansion valve 5, and an evaporator 6, and the condenser 4 is in a refrigerant phase between the condenser inlet position and the outlet position.
- a condenser temperature sensor 7 for detecting the condensation temperature of the condenser is provided at the variable position, and the evaporator 6 is provided with an evaporator temperature sensor 8 for detecting the evaporation temperature of the evaporator at a phase change position of the refrigerant between the evaporator inlet position and the outlet position.
- a compressor temperature sensor 9 for detecting the discharge temperature of the compressor is provided at the exhaust port of the compressor 3.
- the control method of the heat pump dryer expansion valve of the present invention selects a corresponding expansion valve adjustment mode by detecting the evaporator evaporation temperature of the heat pump system and/or the condenser surface temperature and/or the compressor discharge temperature.
- the opening of the expansion valve is increased and/or decreased and/or maintained at a set interval time in each adjustment mode.
- the expansion valve adjustment mode of the present invention is used in conjunction with other procedures for controlling the heat pump system in the drying process, such as compressor control and/or fan control, to facilitate stable operation of the heat pump system.
- the expansion valve first performs a full-closed action. For example, the maximum opening of the expansion valve itself is 500 pulses, then 500 pulses are turned off, and then 5 times of 5 pulses are turned off and 60 pulses are turned off 5 times to ensure that the expansion valve is completely closed. Disabled.
- the expansion valve opens to the initial position of 210 pulses and the compressor starts. After the end of the up-conversion, the compressor is set at a time interval, and the temperature of each detection point of the heat pump system is stabilized before the expansion valve is controlled and adjusted.
- the expansion valve adjustment mode mainly includes the following three types:
- the evaporator In the first adjustment mode, the evaporator is in a stage of easy frost formation, and the difference between the compressor discharge temperature and the surface temperature of the condenser reflecting the condensation temperature is greater than a set value, and the mode controls the opening degree of the expansion valve to increase, thereby evaporating Evaporation temperature rises;
- a second adjustment mode which controls the opening degree of the expansion valve to increase, decrease or not change, so that the drying temperature rises and the evaporation temperature of the evaporator rises;
- a third adjustment mode detecting that the evaporation temperature of the evaporator is greater than the first set value, and controlling the opening degree of the expansion valve to decrease, so that the evaporation temperature of the evaporator is lowered;
- the second adjustment mode is selected.
- the temperature of the clothes is low, if the evaporator temperature sensor senses evaporation of the evaporator If the temperature is less than o°c, it indicates that the evaporator is prone to frost formation. At this time, it is judged whether the difference between the compressor discharge temperature and the condenser surface temperature reflecting the condensation temperature is greater than the set value. If yes, the inside of the evaporator is explained. The refrigerant evaporates completely, belonging to the state corresponding to the first adjustment mode, and the expansion valve is adjusted to run 5 pulses in the direction of large opening.
- the refrigerant in the evaporator evaporates completely according to the temperature of the front and rear surfaces of the evaporator because, under the environment of 0 ° C, even if the refrigerant evaporates completely, the detection result may be consistent with the temperature before and after the evaporator, so The difference between the compressor discharge temperature and the condenser surface temperature is judged, and the result is more accurate.
- the opening degree by adjusting the expansion valve to increase the flow rate of the refrigerant the evaporation temperature is increased; in addition, the increase in the flow rate at the initial stage of drying also increases the compressor load, and the temperature rise process in the drum is accelerated. The above process is cycled at set time intervals.
- the heat pump compressor and/or the fan are controlled for adjustment. If the evaporator temperature sensor senses that the evaporator evaporation temperature is not less than 0 ° C, for example, when the dryer ambient temperature is high, or the difference between the compressor discharge temperature and the condenser surface temperature reflecting the condensation temperature is not greater than If the value is fixed, the first adjustment mode cannot be selected, and the evaporation temperature is compared with the preset first set value, thereby determining whether the second or third adjustment mode is selected.
- SH>0 increase the expansion valve opening degree, and the increasing amplitude and the A SH value change in a positive direction, that is, the larger the A SH value, the larger the opening degree is, the smaller the A SH value is.
- the next adjustment period is judged after 30 seconds; if the detection calculation is as in the above 5-6 case, the next adjustment period is determined after 60 seconds; if the detection calculation is as in the seventh type described above After the situation, the next adjustment period is judged after 10 seconds.
- the third adjustment mode is generally in the late stage of drying. As the drying temperature rises, the evaporation temperature also rises. The smaller the compressor frequency also causes the evaporation temperature to rise, so that the evaporation temperature does not exceed the compressor use range and decreases.
- the evaporator surface temperature when detecting that the evaporator evaporation temperature is greater than the first set value, reducing the opening degree of the five pulse signals of the expansion valve, and circulating the above process at a set time interval, if the expansion valve opening degree is decreased multiple times
- the heat pump compressor and/or the fan are controlled to be adjusted until the minimum opening allowed by the expansion valve, or the number of times the expansion valve opening is continuously reduced, reaches the set number, and it is judged that the evaporator evaporation temperature is still greater than the first set value.
- the synchronous drying judgment program when the dry clothes condition is satisfied, stops the drying, otherwise, the control program of the expansion valve is repeated.
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- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Drying Of Solid Materials (AREA)
- Control Of Washing Machine And Dryer (AREA)
Abstract
一种热泵干衣机膨胀阀(5)的控制方法,通过检测热泵系统蒸发器(6)蒸发温度和/或冷凝器(4)表面温度和/或压缩机(3)排气温度选择对应的膨胀阀(5)调节模式,各调节模式下按照设定的方式调节膨胀阀(5)的开度。蒸发器(6)蒸发温度为蒸发器(6)入口位置到出口位置之间制冷剂发生相变位置处的温度;冷凝器(4)表面温度为冷凝器(4)入口位置到出口位置之间制冷剂发生相变位置处的温度。膨胀阀(5)的控制以对应各调节模式设定的间隔时间调节膨胀阀(5)的开度增大和/或减小和/或维持不变。本发明配合压缩机(3)控制和/或风机控制,提高了热泵工作效率,同时降低了能耗;另外通过膨胀阀(5)的开度控制,避免了过量的制冷剂流入压缩机(3),相对延长了压缩机(3)的使用寿命。
Description
一种热泵干衣机膨胀阀的控制方法 技术领域
本发明涉及一种干衣控制方法, 具体是一种热泵干衣机热泵系统的控制方法, 尤其是一 种热泵干衣机根据检测温度调节膨胀阀开度大小以提高烘干效率的膨胀阀的控制方法。 背景技术 现有热泵式衣物干燥装置中设置有如下的空气循环通道: 由热泵循环系统中的冷凝器进 行过加热的加热空气被送入装有衣物的干燥室内, 从衣物中夺取了水分的湿空气被送回到蒸 发器处进行除湿, 除湿后的空气再次由冷凝器加热, 并送入干燥室中。 热泵干衣机烘干系统, 压縮机系统耐受的压力为制冷剂对应 60〜70°C间温度对应的饱和 压力, 在烘干后期, 随温度的升高, 压縮机的冷凝温度会接近最高压力的限值。 现有滚筒式 热泵干衣机, 设计有辅助冷凝器和辅助风机, 以使在烘干后期或者在高温环境中辅助风机动 作, 对压縮机负荷进行调节。 由于采用单控制温度设置, 在烘干的中前期, 都尽可能的提升 烘干温度, 在中前期利于烘干的完成; 但在后期, 筒内温度已经升高, 烘干空气湿度在减小, 需要的凝露点在降低, 尽管湿度减小会使蒸发器的负荷降低, 温度也降低, 但由于压縮机的 功率负荷在高值运行, 进入滚筒的热量并没有减少, 蒸发器温度的下降小于空气露点温度的 下降; 而冷凝风机的使用, 则使热量更多的进入环境中, 结果是在烘干后期增大了功率消耗, 降低除湿效率。 申请号为 200610153406. 9 的中国专利公开了一种能够使产生在干燥室与热泵之间循环 的干衣空气的热泵实现稳定操作的衣物干燥装置。 其中, 由热泵中的加热器进行过加热的空 气送入作为干燥室的盛水桶中, 从盛水桶排出的空气穿过过滤器单元后回到热泵, 由吸热器 除湿之后再送至加热器, 形成空气循环通道。 过滤器单元中设有线屑过滤器, 并且设有与空 气排出口及空气导入口相连通的管道。 申请号为 200410097855. 7的中国专利公开了一种衣物干燥装置,包括: 热泵装置; 将干 衣空气引导至热泵装置的吸热器、 放热器和装有衣物的干衣室的风道; 向所述风道中送入干 衣空气的鼓风机; 和控制装置。 在干衣操作过程中, 压縮机和鼓风机进行操作; 当干衣操作 发生中断时, 控制装置使压縮机停止规定的时间。 上述采用热泵烘干方式的干衣装置, 在环境温度较高, 比如 35〜40°C环境下, 烘干开始
阶段, 吹入洗衣 /干衣筒内的空气温度迅速上升到 60°C以上, 从洗衣 /干衣筒内吹出的空气温 度, 湿度也迅速上升。 这种情况下, 蒸发器内的制冷剂饱和压力较高, 压縮机系统的负荷大, 很快达到压縮机的临界工作压力。 对定频压縮机系统, 也会超出辅助散热风机和辅助冷凝器 的散热范围, 压縮机会由于压力过高和排气温度过高停止工作, 烘干过程中压縮机间断工作, 会对压縮机部件性能造成冲击, 增加故障率。 若采用压縮机系统, 虽然压縮机会由控制系统 调整压縮机的工作频率, 对压縮机工作负荷进行调节, 但压縮机自身也有个最低工作频率范 围。 制冷系统的高负荷工作, 导致压縮机电机故障率极高, 降低使用寿命。
有鉴于此特提出本发明。 发明内容
本发明要解决的技术问题在于克服现有技术的不足, 提供一种通过调整膨胀阀的开度来 提高烘干效率同时降低热泵工作负荷进而降低烘干能耗的热泵干衣机膨胀阀的控制方法。
为解决上述技术问题, 本发明采用技术方案的基本构思是: 一种热泵干衣机膨胀阀的控 制方法, 通过检测热泵系统蒸发器蒸发温度和 /或冷凝器表面温度和 /或压縮机排气温度选择 对应的膨胀阀调节模式, 各调节模式下按照设定的方式调节膨胀阀的开度。
进一步的, 蒸发器蒸发温度为蒸发器入口位置到出口位置之间制冷剂发生相变位置处的 温度; 冷凝器表面温度为冷凝器入口位置到出口位置之间制冷剂发生相变位置处的温度。
进一步的, 膨胀阀的控制以对应各调节模式设定的间隔时间调节膨胀阀的开度增大和 / 或减小和 /或维持不变。
进一步的, 开始, 先控制膨胀阀执行全闭动作使其处于完全关闭状态, 然后打开膨胀阀 至设定的初始位置, 再启动压縮机, 升频结束后间隔设定时间再执行膨胀阀的控制调节。
控制膨胀阀执行全闭动作为: 先关闭膨胀阀的最大开度脉冲, 然后反复执行开启设定的 第一脉冲、 关闭设定的第二脉冲上述动作, 完成设定次数, 设定的第一脉冲小于设定的第二 脉冲。
本发明所述的控制方法, 膨胀阀调节模式主要包括:
第一调节模式, 蒸发器处于易结霜阶段, 且压縮机排气温度与反映冷凝温度的冷凝器表 面温度的差值大于设定值, 该模式控制膨胀阀的开度增大, 使得蒸发器蒸发温度上升;
第二调节模式, 该模式控制膨胀阀的开度增大、 减小或不变, 使得烘干温度上升进而蒸 发器蒸发温度上升;
第三调节模式, 检测蒸发器蒸发温度大于第一设定值, 控制膨胀阀的开度减小, 使得蒸
发器蒸发温度降低;
若检测蒸发器蒸发温度不大于第一设定值且检测温度不对应第一调节模式, 则选择第二 调节模式。
进一步的, 在第一调节模式下, 控制膨胀阀增大设定的开度, 若多次增大膨胀阀开度直 至膨胀阀允许的最大开度, 或者连续增大膨胀阀开度次数达到设定次数, 判断仍在第一调节 模式条件下, 则控制热泵压縮机和 /或风机进行调节。
进一步的, 在第二调节模式下, 检测蒸发器出口温度 TS与蒸发器蒸发温度 Te计算蒸发 过热度 TS- Te , 与设定的目标过热度 TSH进行比较, 求值过热度差异 SH = TS_ Te- TSH, 及 过热度差异变化值 A SH = S — Sh^ , i、 i-1 为调节次数, Sh。 = 0 ; SH=0, 判断调节周期为 N1秒 /次; SH = 0, 且 A SH = 0时, 判断调节周期为 N2秒 /次; 其它情况判断调节周期为 N3秒 /次, N1 N3 N2, 每次判断后根据 SH及 A SH的值调节膨胀阀开度增大或减小或维持不变。
在第二调节模式下, SH〉0, 增大膨胀阀开度, 增大的幅度与 A SH值呈正方向变化, 即 A SH值越大, 增加的开度越大, A SH值越小, 增加的开度越小; SH<0, 减小膨胀阀开度, 减小的幅度与 A SH值呈反方向变化, 即 A SH值越小, 减小的开度越大, A SH值越大, 减小 的开度越小; SH = 0 时, 若 A SH<0, 则减小开度, 若 A SH〉0, 则增大开度, 变化幅度与 A SH值对应; SH = 0, 且 A SH = 0时, 维持开度不变。
进一步的, 在第三调节模式下, 控制膨胀阀减小设定的开度, 若多次减小膨胀阀开度直 至膨胀阀允许的最小开度, 或者连续减小膨胀阀开度次数达到设定次数, 判断蒸发器蒸发温 度仍大于第一设定值, 则控制热泵压縮机和 /或风机进行调节。
采用上述技术方案后, 本发明与现有技术相比具有以下有益效果。
本发明热泵干衣机在现有热泵模块的基础上, 增加了对膨胀阀的调节以控制热泵工作效 率的功能, 在不同的蒸发温度下, 以对应的调节模式控制膨胀阀开度增大 /减小 /保持不变, 配合压縮机控制和 /或风机控制, 提高了热泵工作效率, 同时降低了能耗; 另外通过膨胀阀的 开度控制, 避免了过量的制冷剂流入压縮机, 相对延长了压縮机的使用寿命。
附图说明
图 1是本发明所述的热泵系统示意图;
图 2是本发明所述的热泵干衣机示意图; 图 3是本发明所述的膨胀阀控制流程图;
1 滚筒、 2 送风风扇、 3 压縮机、 4 冷凝器、 5 膨胀阀、 6 蒸发器、 7 冷凝器温度传感
器、 8 蒸发器温度传感器、 9 压縮机温度传感器 具体实施方式
下面结合附图对本发明的具体实施方式作进一步详细的描述。
如图 1和图 2所示, 本发明所述的热泵干衣机包括滚筒 1和设有滚筒下方的热泵干衣系 统, 由送风风扇 2将热泵干衣系统产生的热风通过干衣风道导入到滚筒内干燥衣物, 热泵干 衣系统包括具有压縮机 3、冷凝器 4、膨胀阀 5及蒸发器 6的热泵模块, 冷凝器 4在冷凝器入 口位置到出口位置之间制冷剂发生相变位置处设有检测冷凝器冷凝温度的冷凝器温度传感器 7,蒸发器 6在蒸发器入口位置到出口位置之间制冷剂发生相变位置处设有检测蒸发器蒸发温 度的蒸发器温度传感器 8, 于压縮机 3排气口处设有检测压縮机排气温度的压縮机温度传感 器 9。
如图 3所示, 本发明热泵干衣机膨胀阀的控制方法, 通过检测热泵系统蒸发器蒸发温度 和 /或冷凝器表面温度和 /或压縮机排气温度选择对应的膨胀阀调节模式, 各调节模式下以设 定的间隔时间调节膨胀阀的开度增大和 /或减小和 /或维持不变。
本发明膨胀阀调节模式与干衣过程其它控制热泵系统的程序如压縮机控制和 /或风机控 制配合使用, 更利于热泵系统的稳定运行。 开始时, 膨胀阀首先执行全闭动作, 例如膨胀阀本身的最大开度为 500脉冲, 则关 500 脉冲, 然后以开 5个脉冲、 关 60个脉冲的频率反复 5次, 保证膨胀阀处于完全关闭状态。 完 成后, 膨胀阀打开至初始位置 210脉冲, 压縮机启动。 压縮机在升频结束后, 间隔一设定时 间, 待热泵系统各检测点温度平稳后再进行膨胀阀的控制调节。
膨胀阀调节模式主要包括下述三种:
第一调节模式, 蒸发器处于易结霜阶段, 且压縮机排气温度与反映冷凝温度的冷凝器表 面温度的差值大于设定值, 该模式控制膨胀阀的开度增大, 使得蒸发器蒸发温度上升;
第二调节模式, 该模式控制膨胀阀的开度增大、 减小或不变, 使得烘干温度上升进而蒸 发器蒸发温度上升;
第三调节模式, 检测蒸发器蒸发温度大于第一设定值, 控制膨胀阀的开度减小, 使得蒸 发器蒸发温度降低;
若检测蒸发器蒸发温度不大于第一设定值且检测温度不对应第一调节模式, 则选择第二 调节模式。
一般干衣过程中, 在烘干初期, 衣物温度较低, 如果蒸发器温度传感器感知蒸发器蒸发
温度小于 o°c, 表明蒸发器会容易发生结霜, 此时判断压縮机排气温度与反映冷凝温度的冷 凝器表面温度的差值是否大于设定值, 如果是, 说明蒸发器里面的制冷剂蒸发完全, 属于第 一调节模式对应的状态, 调节膨胀阀往开度大的方向运行 5个脉冲。 此处判断蒸发器里面的 制冷剂是否蒸发完全没有按照蒸发器前后表面的温度是因为, 在 0°C环境以下, 即使制冷剂 蒸发完全, 检测结果也可能蒸发器前后温度趋于一致, 因此采用压縮机排气温度与冷凝器表 面温度的差值进行判断, 结果会更准确。 通过调节膨胀阀增大开度以增加制冷剂的流量, 使 蒸发温度上升; 另外, 在烘干初期流量增加也会使压縮机负荷增加, 滚筒内升温过程加快。 以设定的时间间隔循环上述过程, 若多次增大膨胀阀开度直至膨胀阀允许的最大开度, 或者 连续增大膨胀阀开度次数达到设定次数, 此时判断仍在上述第一调节模式条件下, 则控制热 泵压縮机和 /或风机进行调节。 如果蒸发器温度传感器感知蒸发器蒸发温度不小于 0°C, 例如, 干衣机环境温度较高时, 或者, 压縮机排气温度与反映冷凝温度的冷凝器表面温度的差值不大于设定值, 则不能选择 第一调节模式, 将蒸发温度与预设的第一设定值比较, 进而判断选择第二或第三调节模式。
在第二调节模式下, 检测蒸发器出口温度 TS与蒸发器蒸发温度 Te计算蒸发过热度 TS- Te, 与设定的目标过热度 TSH进行比较, 求值过热度差异 SH = TS_ Te- TSH, 及过热度差异 变化值 A SH = S — ShH, i、 i-1为调节次数, Sh0 = 0; SH=0, 判断调节周期为 N1秒 /次; SH = 0, 且 A SH = 0时, 判断调节周期为 N2秒 /次; 其它情况判断调节周期为 N3秒 /次, N1 N3 ^N2 , 每次判断后根据 SH及 Δ SH的值调节膨胀阀开度增大或减小或维持不变。
在第二调节模式下, SH〉0, 增大膨胀阀开度, 增大的幅度与 A SH值呈正方向变化, 即 A SH值越大, 增加的开度越大, A SH值越小, 增加的开度越小; SH<0, 减小膨胀阀开度, 减小的幅度与 A SH值呈反方向变化, 即 A SH值越小, 减小的开度越大, A SH值越大, 减小 的开度越小; SH = 0 时, 若 A SH<0, 则减小开度, 若 A SH〉0, 则增大开度, 变化幅度与 A SH值对应; SH = 0, 且 A SH = 0时, 维持开度不变。 第二调节模式一般在烘干中间时期起作用, 此时, 检测蒸发器蒸发温度不大于第一设定 值, 则检测蒸发器出口温度 TS与蒸发器蒸发温度 Te, 与目标过热度 TSH=5K进行比较, 如果 SH=0, 判断调节周期为 60秒 /次; 如果 SH=0, 且 A SH=0时, 判断调节周期为 10秒 /次; 其它 情况判断调节周期为 30秒 /次。
1、 SH=5, 说明过热度比目标过热度大 5K, A SH=-3, 说明目前检测过热度前回检测过热 度变小 3K, 则膨胀阀调大 2个脉冲开度;
2、 SH=5, 说明过热度比目标过热度大 5K, A SH=3, 说明目前检测过热度前回检测过热 度变大 3K, 则膨胀阀调大 9个脉冲开度;
3、 SH=-5, 说明过热度比目标过热度小 5K, A SH=-3, 说明目前检测过热度前回检测过 热度变小 3K, 则膨胀阀调小 9个脉冲开度;
4、 SH=-5, 说明过热度比目标过热度小 5K, A SH=3, 说明目前检测过热度前回检测过热 度变大 3K, 则膨胀阀调小 2个脉冲开度;
5、 SH=0, 说明过热度与目标过热度一致, A SH=-3, 说明目前检测过热度前回检测过热 度变小 3K, 则膨胀阀调小 1脉冲开度进行微调;
6、 SH=0, 说明过热度与目标过热度一致, A SH=3, 说明目前检测过热度前回检测过热度 变大 3K, 则膨胀阀调大 1脉冲开度进行微调;
7、 SH=0, 说明过热度与目标过热度一致, A SH=0, 说明目前检测过热度前回检测过热度 没有变化, 则保持膨胀阀开度不变。
若检测计算如上述 1-4情况后, 则 30秒后判断下次调节周期; 若检测计算如上述 5-6情 况后, 则 60秒后判断下次调节周期; 若检测计算如上述第 7种情况后, 则 10秒后判断下次 调节周期。 第三调节模式一般在烘干后期, 随烘干温度的上升, 蒸发温度也在上升, 压縮机频率的 变小也会使蒸发温度上升, 为使蒸发温度不超过压縮机使用范围和降低蒸发器表面温度, 在 检测蒸发器蒸发温度大于第一设定值时, 减小膨胀阀 5个脉冲信号的开度, 以设定的时间间 隔循环上述过程, 若多次减小膨胀阀开度直至膨胀阀允许的最小开度, 或者连续减小膨胀阀 开度次数达到设定次数, 判断蒸发器蒸发温度仍大于第一设定值, 则控制热泵压縮机和 /或风 机进行调节。 本发明膨胀阀的控制过程中, 同步干衣判断程序, 当满足干衣条件时, 则停止干衣, 否 则, 重复上述膨胀阀的控制程序。 上述实施方案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
1、 一种热泵干衣机膨胀阀的控制方法, 其特征在于: 通过检测热泵系统蒸发器蒸发温 度和 /或冷凝器表面温度和 /或压縮机排气温度选择对应的膨胀阀调节模式, 各调节模式下 按照设定的方式调节膨胀阀的开度。
2、 根据权利要求 1所述的控制方法, 其特征在于: 蒸发器蒸发温度为蒸发器入口位置 到出口位置之间制冷剂发生相变位置处的温度; 冷凝器表面温度为冷凝器入口位置到出口 位置之间制冷剂发生相变位置处的温度。
3、 根据权利要求 1所述的控制方法, 其特征在于: 膨胀阀的控制以对应各调节模式设 定的间隔时间调节膨胀阀的开度增大和 /或减小和 /或维持不变。
4、 根据权利要求 1所述的控制方法, 其特征在于: 开始, 先控制膨胀阀执行全闭动作 使其处于完全关闭状态, 然后打开膨胀阀至设定的初始位置, 再启动压縮机, 升频结束后 间隔设定时间再执行膨胀阀的控制调节。
5、 根据权利要求 4所述的控制方法, 其特征在于: 控制膨胀阀执行全闭动作为: 先关 闭膨胀阀的最大开度脉冲, 然后反复执行开启设定的第一脉冲、 关闭设定的第二脉冲上述 动作, 完成设定次数, 设定的第一脉冲小于设定的第二脉冲。
6、 根据权利要求 1所述的控制方法, 其特征在于: 膨胀阀调节模式主要包括: 第一调节模式, 蒸发器处于易结霜阶段, 且压縮机排气温度与反映冷凝温度的冷凝器 表面温度的差值大于设定值, 该模式控制膨胀阀的开度增大, 使得蒸发器蒸发温度上升; 第二调节模式, 该模式控制膨胀阀的开度增大、 减小或不变, 使得烘干温度上升进而 蒸发器蒸发温度上升;
第三调节模式, 检测蒸发器蒸发温度大于第一设定值, 控制膨胀阀的开度减小, 使得 蒸发器蒸发温度降低;
若检测蒸发器蒸发温度不大于第一设定值且检测温度不对应第一调节模式, 则选择第 二调节模式。
7、 根据权利要求 6所述的控制方法, 其特征在于: 在第一调节模式下, 控制膨胀阀增 大设定的开度, 若多次增大膨胀阀开度直至膨胀阀允许的最大开度, 或者连续增大膨胀阀 开度次数达到设定次数, 判断仍在第一调节模式条件下, 则控制热泵压縮机和 /或风机进行 调节。
8、 根据权利要求 6所述的控制方法, 其特征在于: 在第二调节模式下, 检测蒸发器出 口温度 TS与蒸发器蒸发温度 Te计算蒸发过热度 TS- Te, 与设定的目标过热度 TSH进行比 较, 求值过热度差异 SH = TS_ Te- TSH, 及过热度差异变化值 Δ SH = S — Sh^, i、 i_l为
调节次数, ShQ = 0; SH=0, 判断调节周期为 Nl秒 /次; SH = 0, 且 ASH = 0时, 判断调节周 期为 N2秒 /次; 其它情况判断调节周期为 N3秒 /次, N1 N3 N2, 每次判断后根据 SH及 Δ SH的值调节膨胀阀开度增大或减小或维持不变。
9、 根据权利要求 8所述的控制方法, 其特征在于: SH〉0, 增大膨胀阀开度, 增大的 幅度与 ASH值呈正方向变化, 即 ASH值越大, 增加的开度越大, ASH值越小, 增加的开度 越小; SH<0, 减小膨胀阀开度, 减小的幅度与 ASH值呈反方向变化, 即 ASH值越小, 减 小的开度越大, ASH值越大, 减小的开度越小; SH = 0时, 若 ASH<0, 则减小开度, 若 A SH〉0, 则增大开度, 变化幅度与 ASH值对应; SH = 0, 且 ASH = 0时, 维持开度不变。
10、 根据权利要求 6所述的控制方法, 其特征在于: 在第三调节模式下, 控制膨胀阀 减小设定的开度, 若多次减小膨胀阀开度直至膨胀阀允许的最小开度, 或者连续减小膨胀 阀开度次数达到设定次数, 判断蒸发器蒸发温度仍大于第一设定值, 则控制热泵压縮机和 / 或风机进行调节。
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