EP2535669A2 - Système de conditionnement d'air de type multi-divisions - Google Patents

Système de conditionnement d'air de type multi-divisions Download PDF

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Publication number
EP2535669A2
EP2535669A2 EP12171591A EP12171591A EP2535669A2 EP 2535669 A2 EP2535669 A2 EP 2535669A2 EP 12171591 A EP12171591 A EP 12171591A EP 12171591 A EP12171591 A EP 12171591A EP 2535669 A2 EP2535669 A2 EP 2535669A2
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EP
European Patent Office
Prior art keywords
opening degree
electronic expansion
outdoor unit
expansion valve
outdoor
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP12171591A
Other languages
German (de)
English (en)
Other versions
EP2535669A3 (fr
Inventor
Makoto Sato
Kinichi Takemoto
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Ltd
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Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2535669A2 publication Critical patent/EP2535669A2/fr
Publication of EP2535669A3 publication Critical patent/EP2535669A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention relates to a multi-split type air conditioning system in which a plurality of indoor units are connected in parallel to one outdoor unit.
  • each indoor unit has an electronic expansion valve (EEV).
  • EEV electronic expansion valve
  • a multi-room type air conditioner disclosed in Patent Literature 1 indicated below maintains an appropriate amount of refrigerant circulation according to the number of multiple indoor units being in operation and a refrigerant discharging temperature, to prevent rise in discharging temperature and lack of capacity.
  • Patent Literature 2 indicated below prevents refrigerant oil from accumulating inside a refrigeration cycle to lead to oil exhaustion in a compressor, even when the refrigerant oil that is weakly soluble in the refrigerant is used, while avoiding generation of a lot of liquid flowing back to the compressor, even without an accumulator.
  • a method for operating a multi-room type air conditioner disclosed in Patent Literature 3 secures the amount of refrigerant circulation in the refrigeration cycle during a cooling operation by preventing the liquid refrigerant from accumulating in a receiver, thereby enabling an appropriate operation without lack of capacity.
  • the problem of surplus refrigerant of this kind becomes particularly significant when the six indoor units include one that requires large heat exchange capacity, or more specifically, include a master type one that is for a large space, such as a living room.
  • the surplus refrigerant accumulates at the condenser in the heating operation, the degree of supercooling at the refrigerant becomes large. In this state, in order to satisfy the performance requirement for heating operation, it is necessary to increase the number of rotation of the inverter-controlled compressor, resulting in an operation in an extremely inefficient operating point.
  • the present invention is made to solve the above-described problems, and an object of the present invention is to provide a multi-split type air conditioning system that achieves operation with a high COP by rapidly achieving the optimal operating point in the heating operation to stabilize the number of rotation of the inverter-controlled compressor.
  • the multi-split type air conditioning system according to present invention comprises:
  • the multi-split type air conditioning system according to the present invention comprises:
  • the in-heating-operation opening degree control mode performs the open-loop control for a predetermined time period when the heating operation is activated and when the number of the indoor units being in operation changes, and thereafter transits to a zone control, and in the open-loop control for a second or latter time that is initiated after the number of the indoor units being in operation changes, a value obtained by adding a zone control integrated value obtained at a zone control that is performed last time before the open loop control is initiated to a calculated value of the outdoor unit electronic expansion valve interim opening degree. This makes it possible to optimize the outdoor unit electronic expansion valve interim opening degree in the open-loop control for the second or latter time in consideration for the operation state.
  • multi-split air conditioner multi-split air conditioner
  • the multi-split air conditioner described hereafter has an exemplary configuration in which six indoor units are connected in parallel. However, the number of indoor units to be connected will not be limited to six.
  • a multi-split air conditioner AC of an embodiment shown in Fig. 1 has a closed-circuit refrigeration cycle in which six indoor units 30A to 30F are connected in parallel to one outdoor unit 10.
  • This multi-split air conditioner AC comprises a control unit 50 that performs various operation control of the outdoor unit 10 and the indoor units 30A to 30F, and can perform a cooling operation or a heating operation by selecting and switching the direction of flow of the refrigerant circulating in the refrigeration cycle.
  • Arrows in Fig. 1 show the direction of flow of the refrigerant in a heating operation.
  • the outdoor unit 10 comprises a variable-power operated type compressor (hereafter referred to as "compressor") 11, which is driven by, for example, an inverter-controlled electric motor, an outdoor heat exchanger 12 that performs heat exchange between the refrigerant and the outdoor air, and a four-way valve 13 for performing a cooling operation and a heating operation by selecting and switching the circulation direction of the refrigerant supplied from the compressor 11.
  • compressor variable-power operated type compressor
  • the compressor 11 and the four-way valve 13 are configured so that the number of rotation and the direction of refrigerant circulation are controlled by receiving a control signal from the control unit 50.
  • a discharge thermal sensor 14 that detects a discharge pipe sensor temperature Td of the refrigerant.
  • a suction thermal sensor 15 that detects a suction pipe sensor temperature Ts of the refrigerant.
  • an outdoor heat exchange thermal sensor 16 that detects an outdoor heat exchanging fluid tube sensor temperature TO. Temperature detection values (Td, Ts, TO) detected respectively by the discharge thermal sensor 14, the suction thermal sensor 15 and the outdoor heat exchange thermal sensor 16 are input to the control unit 50 and used for a variety of operation control.
  • the indoor units 30A to 30F comprise indoor heat exchangers 31A to 31F respectively.
  • Each of the indoor units 30A to 30F is provided with refrigerant pipes 33A to 33F that branch out of headers 32A and 32B and are connected thereto in parallel.
  • the refrigerant pipes 33A to 33F have electronic expansion valves 34A to 34F on one side of the indoor units 30A to 30F and on-off valves 35A to 35F on the other side of the indoor units 30A to 30F.
  • the electronic expansion valves 34A to 34F are installed downstream of the indoor units 30A to 30F in the direction of refrigerant flow in the heating operation, and the on-off valves 35A to 35F are installed upstream thereof.
  • a remotely controllable element such as a solenoid valve
  • the on-off valves 35A to 35F open and close according to the operating/stop state of the indoor units 30 by receiving a control signal from the control unit 50.
  • the electronic expansion valves 34A to 34F receive individual control signals from the control unit 50 so that the opening degree control is performed.
  • indoor heat exchange thermal sensors 36A to 36F are provided that detect indoor heat exchanging fluid tube sensor temperature TR of each of the indoor units. Each detection value of the indoor heat exchanging fluid tube sensor temperatures TR detected by the indoor heat exchange thermal sensors 36A to 36F is input to the control unit 50 and used for a variety of operation control.
  • the multi-split air conditioner AC of the present embodiment comprises a receiver 20 and an outdoor unit electronic expansion valve 21 upstream of the outdoor heat exchanger 12 that serves as an evaporator in the heating operation. Since the outdoor unit electronic expansion valve 21 in this case is disposed between the receiver 20 and the outdoor heat exchanger 12, the receiver 20 is located upstream of the outdoor unit electronic expansion valve 21 in the direction of refrigerant flow in the heating operation.
  • the receiver 20 is a receptacle that has a function to hold surplus refrigerant in heating operation.
  • the receiver 20 is a receptacle for temporarily reserving liquid refrigerant liquefied in the indoor heat exchanger 31 that serves as a condenser in the heating operation.
  • the outdoor unit electronic expansion valve 21 is provided for adjusting an operating point of the whole system of the multi-split air conditioner AC, besides the above-described electronic expansion valve 34 for each of the indoor units 30.
  • This outdoor unit electronic expansion valve 21 by performing the aperture control (opening degree adjustment) by receiving from the control unit 50 the control signal on which below-described correction is performed, adjusts surplus refrigerant that accumulates in the receiver 20 disposed upstream of the direction of refrigerant flow in the heating operation.
  • the adjustment of the opening degree of the outdoor unit electronic expansion valve 21 is performed in accordance with the state of the heating operation (number of the indoor units 30 being in operation or the like), it is possible to adjust the amount of the liquid refrigerant accumulating in the receiver 20. Therefore it becomes possible to prevent increase of the degree of supercooling caused by the surplus refrigerant accumulation in the indoor units 30.
  • the control unit 50 performs a variety of operation control, such as switching between the cooling operation and the heating operation and an operation according to a temperature setting.
  • the control unit 50 controls the opening degree of the outdoor unit electronic expansion valve 21 (hereafter referred to as "EEVH opening degree"), in the manner as shown in Fig. 2 .
  • the EEVH opening degree in the heating operation is adjusted by an in-heating-operation opening degree control mode provided in the control unit 50.
  • an eventual operating point of the EEVH opening degree is determined by the open-loop control and the zone control.
  • the in-heating-operation opening degree control mode comprises an open-loop control that performs an operation when the heating operation is activated and when a number of the indoor units being in operation changes, for a predetermined time period with an outdoor unit electronic expansion valve interim opening degree set corresponding to the actual number of rotation (N) of the compressor 11 determined by the number of the indoor units 30 being in operation and the outdoor air condition.
  • This open-loop control employs an outdoor air temperature, a total heat exchange capacity value of the indoor heat exchangers 31, the number of indoor heat exchangers 31 that are stopped, a suction superheating SH and discharge superheating TDSH of the compressor 11 as parameters for calculating the outdoor unit electronic expansion valve interim opening degree.
  • the mode transits to the zone control that controls the operating point to the discharge superheating TDSH corresponding to actual number of rotation (N) of the compressor 11. This zone control is continued until a change occurs in the number of the indoor units 30 being in operation.
  • This control mode includes an open-loop control and a zone control, and in the shut-down state of the multi-split air conditioner AC, the EEVH opening degree is in the initial condition in which the EEV is full open.
  • an outdoor unit electronic expansion valve interim opening degree R1 is calculated by the open-loop control.
  • the opening degree is fixed to the calculated outdoor unit electronic expansion valve interim opening degree R1, and the heating operation is continued until a predetermined time (for example, 3 minutes or so) elapses.
  • the opening degree (OP) of the outdoor unit electronic expansion valve is calculated as the outdoor unit electronic expansion valve interim opening degree R1 by correcting the actual number of rotation (N) of the compressor 11 based on the below-indicated formula at the open-loop control in the heating operation.
  • correction coefficients a, b according to the external temperature, and the heat exchange capacity, and a correction coefficient Z 4 determined based on the presence or absence of the master type indoor unit and the total value of the capacities of the heat exchangers are newly added correction coefficients.
  • that part of the formula to calculate opening degree of the outdoor unit electronic expansion valve, in which the other correction coefficients, Z 2 and Z 3 are used is conventionally used.
  • EEVH OP (a ⁇ N + b + c) ⁇ Z 2 ⁇ Z 3 ⁇ Z 4
  • a, b are correction coefficients based on the external temperature and the heat exchange capacity
  • c is the sum of ⁇ pulses of all of the stop units
  • Z 2 is a correction coefficient for retaining appropriate suction superheating of the whole of the system, which particularly aims at stabilizing the open-loop control in the transit period
  • Z 3 is a correction coefficient for retaining appropriate discharge superheating of the whole of the system
  • Z 4 is a correction coefficient determined by the presence or absence of the master type indoor unit and the total value of the capacities of the heat exchangers (see values in Table 5)
  • N is an actual number of rotation of the compressor (where a value rounded off to the closest whole number is used for calculating the opening degree).
  • Table 1 and Table 2 show examples of correction coefficients a, b selected based on the outdoor air temperature and the total value of the capacities of the heat exchangers.
  • Correction coefficients a, b used at the open-loop control in the heating operation are, for example, as illustrated in Table 1 and Table 2, determined based on the total value of the heat exchanger capacities of the indoor units 30 that are connected (total value of the capacities of the heat exchangers that serve as condensers) and the outdoor air temperature.
  • the correction coefficient a illustrated in Table 1 and the correction coefficient b illustrated in Table 2 are predetermined values determined based on experiments or the like.
  • Table 3 shows one example of heat exchange performance capacities determined for respective indoor units.
  • the above-described total value of the capacities of the heat exchangers of the indoor units 30 is calculated by using for example, performance values illustrated in Table 3.
  • the heat exchanger capacities illustrated in Table 3 are values of a variety of indoor heat exchangers 31 installed in a variety of indoor units 30.
  • heat exchanger capacity proportions for respective types of shape (EXT-1 to 4) are shown by being listed in columns, for each of model-specific capacities (EXD-1 to 4) listed in rows, with a reference model-specific capacity being assumed to be 100.
  • the model-specific capacities in the rows mean, for example, performances required for indoor heat exchangers 31 for use in rooms with a variety of capacities, such as a room with a small capacity of space, e.g. a child's room, and a living room with a large capacity of space.
  • types of shape in the columns mean that the heat exchanger capacity proportion varies depending on the installation structure of the indoor units 30 such as wall-hanging type, ceiling-mounted type and free-standing type, even with the same model-specific capacity.
  • the heat exchanger capacity proportion of the indoor units with the model-specific capacity of EXD-1 and the type of shape EXT-1, which is the reference model is 100; the heat exchanger capacity proportion of the indoor units with the model-specific capacity of EXD-2 and the type of shape EXT-2 is 63; and the heat exchanger capacity proportion of the indoor unit with the model-specific capacity of EXD-4 and the type of shape EXT-4 is 125.
  • the total value of the capacities of the heat exchangers in this case is calculated according to the below-indicated formula.
  • the above-described indoor unit with the model-specific capacity EXD-4 and the type of shape EXT-4 is what is called a master type, being for use in a large space, such as a living room.
  • the value of heat exchanger capacity proportion is set to be equal to or greater than the reference value 100.
  • Table 4 shows one example of a correction pulse ⁇ necessary for determining the correction coefficient c.
  • the correction pulse ⁇ is determined according to the heat exchanger capacity proportion of one indoor unit 30 being in the shut-down state for example, in the manner as illustrated in Table 4. After that, for all indoor units 30 being in the shut-down state, correction pulses ⁇ determined according to Table 4 are summed to yield the correction coefficient c.
  • Table 4 Heat exchanger capacity proportion of indoor exchanger being in shut-down state ⁇ 90 91 ⁇ 110 111 ⁇ ⁇ 3 5 10
  • the indoor unit 30 with the model-specific capacity EXD-1 and the type of shape EXT-1 and another one indoor unit with the model-specific capacity EXD-2 and the type of shape EXT-2 has a heat exchanger capacity proportion of 100. Therefore, correction pulse ⁇ is 5.
  • the correction coefficient Z 2 is a value for retaining an appropriate suction superheating SH in the whole of the multi-split air conditioner AC, and this is a correction value that has been used also in the conventional control techniques.
  • the suction superheating SH is equal to or greater than the discharge superheating TDSH, and moreover, the suction superheating SH fluctuates earlier. Therefore, a control is performed to correct the opening degree (OP) of the outdoor unit electronic expansion valve by determining the correction coefficient Z 2 with the suction superheating SH being used as the parameter.
  • the correction coefficient Z 3 is a value for retaining an appropriate discharge superheating TDSH in the whole of the multi-split air conditioner AC, and this is a correction value that has been used also in the conventional control techniques.
  • Td temperature difference
  • the indoor heat exchanging fluid tube sensor temperature TR the highest temperature (maximum value) from among the indoor units 30 performing the heating operation is used.
  • the correction coefficient Z 3 is determined with the discharge superheating TDSH as a parameter to perform a control to correct the opening degree (OP) of the outdoor unit electronic expansion valve.
  • the correction coefficient Z 4 is a correction coefficient determined based on the presence or absence of the master type (the type shown in Table 3 with the model-specific capacity EXD-4 and the type of shape EXT-4) and the above-described total value of the capacities of the heat exchangers, and is determined in the manner shown in, for example, Table 5.
  • Table 5 shows one example of the correction coefficient Z 4 that varies depending on the conditions. In the example shown in Table 5, where the connected units of the indoor units 30 do not include any master type one, the correction coefficient Z 4 is set to be 1.0 and the correction is thereby not performed.
  • the correction coefficient Z 4 is provided that varies depending on whether the total value of the capacities of the heat exchangers calculated using Table 3 is equal to or greater than a predetermined value (for example 400). In the example shown in Table 5, where the calculated total value of the capacities of the heat exchangers is less than 400, the correction coefficient Z 4 is set to be 1.3, and where the calculated total value of the capacities of the heat exchangers is equal to or greater than 400, the correction coefficient Z 4 is set to be 1.5.
  • the zone control is continued to transit eventually to an operating point that meets the dilution ratio and the working pressure restriction of the compressor 11.
  • the mode transits again to the open-loop control.
  • the opening degree (OP) which is to be outdoor unit electronic expansion valve interim opening degree R2 after the number of the indoor units 30 being in operation changes, is calculated by performing correction based on the formula that is the same as the above-described correction performed after the activation.
  • the opening degree of the outdoor unit electronic expansion valve 21 to actually be set is the outdoor unit electronic expansion valve interim opening degree Rr that is a value in which the state of operation before the change in the number of the indoor units being in operation occurred is reflected. After the heating operation is continued with the opening degree being fixed to this value for a predetermined time period, the mode transits again to the above-described zone control.
  • the control of opening degree of the outdoor unit electronic expansion valve 21 is performed such that, after the operation is continued for a predetermined time period with the outdoor unit electronic expansion valve interim opening degree R1 being set in the initial open-loop control, the zone control and the open-loop control are repeated until shut-down.
  • Performing such an EEVH opening degree control for an in-heating-operation opening degree control mode makes it possible to secure a stable operating point for the number of rotation of the compressor 11 driven by an inverter-controlled electric motor, construct an operating point with a high COP and improve the efficiency of the system by rapidly achieving the optimal operating point in heating operation of the multi-split air conditioner AC.
  • the above-described in-heating-operation opening degree control mode of the present embodiment is suitable when the plurality of indoor units include a master type one, and particularly, it is suitable for a multi-split air conditioner AC in which five or more indoor units 30 are connected in parallel.
  • the present invention is not limited to the above-described embodiment. Modifications may be appropriately made within the scope of the present invention without departing from the gist of the present invention.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP12171591.6A 2011-06-17 2012-06-12 Système de conditionnement d'air de type multi-divisions Withdrawn EP2535669A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011134778A JP5835958B2 (ja) 2011-06-17 2011-06-17 マルチ形空気調和装置

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EP2535669A2 true EP2535669A2 (fr) 2012-12-19
EP2535669A3 EP2535669A3 (fr) 2014-04-16

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CN104101052A (zh) * 2014-07-02 2014-10-15 广东美芝制冷设备有限公司 一拖多空调器系统及其启动控制装置和启动控制方法
CN104214905A (zh) * 2013-05-31 2014-12-17 日立空调·家用电器株式会社 空调器及其控制方法
CN105605753A (zh) * 2016-01-26 2016-05-25 上海交通大学 基于多联机与新风机复合空调系统的新风送风温控系统
CN104101052B (zh) * 2014-07-02 2016-11-30 广东美芝制冷设备有限公司 一拖多空调器系统及其启动控制装置和启动控制方法
CN107676922A (zh) * 2017-10-31 2018-02-09 广东美的暖通设备有限公司 空调器的控制方法及空调器
WO2018053728A1 (fr) * 2016-09-21 2018-03-29 广东美的暖通设备有限公司 Procédé de commande pour système de climatisation à divisions multiples
CN109974223A (zh) * 2019-04-01 2019-07-05 珠海格力电器股份有限公司 根据天气预报调整空调工作的空调控制方法及装置
CN110836433A (zh) * 2018-08-16 2020-02-25 青岛海尔空调电子有限公司 一拖多空调器的控制方法及控制装置
WO2020164228A1 (fr) * 2019-02-13 2020-08-20 青岛海尔空调电子有限公司 Système de climatisation à divisions multiples et procédé de calcul de capacité d'échange de chaleur associé
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CN114688689A (zh) * 2022-03-31 2022-07-01 安徽奥克斯智能电气有限公司 一种电子膨胀阀的开度调节方法、装置及多联式空调器
CN114811863A (zh) * 2022-05-16 2022-07-29 美的集团武汉暖通设备有限公司 多联机空调器的控制方法、控制器、空调器及介质

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WO2020164228A1 (fr) * 2019-02-13 2020-08-20 青岛海尔空调电子有限公司 Système de climatisation à divisions multiples et procédé de calcul de capacité d'échange de chaleur associé
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