CN101978227A - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

Info

Publication number
CN101978227A
CN101978227A CN2009801105845A CN200980110584A CN101978227A CN 101978227 A CN101978227 A CN 101978227A CN 2009801105845 A CN2009801105845 A CN 2009801105845A CN 200980110584 A CN200980110584 A CN 200980110584A CN 101978227 A CN101978227 A CN 101978227A
Authority
CN
China
Prior art keywords
compressor
desired value
value
control
heat exchanger
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.)
Pending
Application number
CN2009801105845A
Other languages
Chinese (zh)
Inventor
笠原伸一
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of CN101978227A publication Critical patent/CN101978227A/en
Pending legal-status Critical Current

Links

Images

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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/15—Hunting, i.e. oscillation of controlled refrigeration variables reaching undesirable values
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • 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
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Provided is a freezing apparatus which constitutes an air conditioner (10) including a main controller (60) and auxiliary controllers (70a and 70b). The main controller (60) has a compressor control unit for adjusting the running capacity of a compressor (31), to stop the compressor (31) when the capacity of the air conditioner (10) exceeds a load. When the starts/stops of the compressor (31) by the compressor control unit become highly frequent, a target overheat degree changing unit of the main controller (60) raises a target value of overheat forcibly. In a cooling run, the auxiliary controllers (70a and 70b) then adjust the openings of indoor expansion valves (42 and 47) by using the raised target value of overheat. In a warming run, on the other hand, the main controller (60) adjusts the opening of an outdoor expansion valve (34) by using the raised target value of overheat.

Description

Refrigerating plant
Technical field
The present invention relates to a kind of refrigerating plant, this refrigerating plant carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure.
Background technology
Up to now, the refrigerating plant that cold-producing medium is circulated carry out kind of refrigeration cycle is known.In patent documentation 1 disclosed refrigerating plant, the high pressure of the kind of refrigeration cycle of carrying out in the refrigerant loop is configured to be higher than the value of cold-producing medium critical pressure.That is to say, in the refrigerant loop of this refrigerating plant, carry out so-called overcritical circulation.
Also have, in patent documentation 2 disclosed airconditions, carry out the general kind of refrigeration cycle that high pressure is configured to be lower than the value of cold-producing medium critical pressure.In the aircondition of this patent documentation 2, for the frequency that reduces compressor start and stop, the desired value during to the running of control aircondition is regulated.Patent documentation 1: a day disclosure special permission communique spy opens 2001-116376 communique patent documentation 2: a day disclosure special permission communique spy opens the 2002-061925 communique
Summary of the invention
-invent technical problem to be solved-
In the refrigerating plant that carries out so-called overcritical circulation, also to make compressor start and stop sometimes for the ability of regulating refrigerating plant.For example, even if be under the situation of variable displacement compressor at compressor, even also can exist capacity to be made as minimum of a value sometimes with compressor, the still excessive situation of ability relative load of refrigerating plant.Under these circumstances, will allow compressor stop.
Compare with general kind of refrigeration cycle, the high pressure of overcritical circulation is higher.For this reason, the general kind of refrigeration cycle that is lower than the cold-producing medium critical pressure with high pressure is compared, in the refrigerating plant that carries out overcritical circulation, start behind the compressor reach appropriate value to the high pressure of kind of refrigeration cycle or low pressure till needed power more.However, in the refrigerating plant that carries out overcritical circulation, but fully do not take so far in order to reduce the countermeasure of compressor start and stop frequency.
The present invention invents in view of described problem, and its purpose is: in the refrigerating plant that carries out so-called overcritical circulation, reduce the start-stop time of compressor, improve the running efficiency of refrigerating plant.-in order to the technical scheme of technical solution problem-
The invention of first aspect is an object with following refrigerating plant, this refrigerating plant comprises refrigerant loop 20 and control device 80, in this refrigerant loop 20, be provided with compressor 31, expansion mechanism 34,42,47, heat source side heat exchanger 33 and utilize side heat exchanger 41,46, this refrigerant loop 20 carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, and 80 pairs of described compressors 31 of this control device and described expansion mechanism 34,42,47 are controlled.Described control device 80 constitutes and carries out: regulate the capacity of described compressor 31, make the physical quantity of the duty that is illustrated in the kind of refrigeration cycle of carrying out in the described refrigerant loop 20 become the volume controlled action of controlling desired value; Regulate flow, make the flow-control action that becomes degree of superheat desired value from described heat source side heat exchanger 33 and the described degree of superheat of utilizing the side heat exchanger 41,46 heat exchanger as evaporator operation to flow to the cold-producing medium of described compressor 31 by the cold-producing medium of described expansion mechanism 34,42,47; And when described compressor 31 being stopped, improving the degree of superheat desired value change action of described degree of superheat desired value by force by described volume controlled action.
The invention of second aspect is an object with following refrigerating plant, this refrigerating plant comprises refrigerant loop 20 and control device 80, in this refrigerant loop 20, be provided with compressor 31, expansion mechanism 34,42,47, heat source side heat exchanger 33 and utilize side heat exchanger 41,46, this refrigerant loop 20 carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, 80 pairs of described compressors 31 of this control device are controlled, and this refrigerating plant carries out described heat source side heat exchanger 33 at least as gas cooler work and the described side heat exchanger 41 that utilizes, 46 cooling runnings as evaporator operation.Described control device 80 constitutes and carries out: with the low pressure of the described kind of refrigeration cycle of utilizing the evaporating temperature of the cold-producing medium in the side heat exchanger 41,46 or in described refrigerant loop 20, carrying out as the control parameter, regulate the capacity of described compressor 31, make this control parameter become the volume controlled action of control desired value; And start the described control desired value of reliefs at described compressor 31 and descend gradually, make when described compressor 31 starts, counting and passed through the control desired value change action that described control desired value after the stipulated time becomes the specified standard desired value.
The invention of the third aspect is an object with following refrigerating plant, this refrigerating plant comprises refrigerant loop 20 and control device 80, in this refrigerant loop 20, be provided with compressor 31, expansion mechanism 34,42,47, heat source side heat exchanger 33 and utilize side heat exchanger 41,46, this refrigerant loop 20 carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, 80 pairs of described compressors 31 of this control device are controlled, and this refrigerating plant carries out the described side heat exchanger 41 that utilizes at least, 46 as the heat run that adds as evaporator operation of gas cooler work and described heat source side heat exchanger 33.Described control device 80 constitutes and carries out: the high pressure of the kind of refrigeration cycle that will carry out in described refrigerant loop 20 is regulated the capacity of described compressor 31 as the control parameter, makes this control parameter become the volume controlled action of control desired value; And start the described control desired value of reliefs at described compressor 31 and rise gradually, make when described compressor 31 starts, counting and passed through the control desired value change action that described control desired value after the stipulated time becomes the specified standard desired value.
The invention of fourth aspect is an object with following refrigerating plant, this refrigerating plant comprises refrigerant loop 20 and control device 80, in this refrigerant loop 20, be provided with compressor 31, expansion mechanism 34,42,47, heat source side heat exchanger 33 and utilize side heat exchanger 41,46, this refrigerant loop 20 carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, and 80 pairs of described compressors 31 of this control device are controlled.Described control device 80 constitutes and carries out: according to the physical quantity of using the duty that is illustrated in the kind of refrigeration cycle of carrying out in the described refrigerant loop 20 and the command value that ride gain is calculated, regulate the capacity of described compressor 31, make this physical quantity become the volume controlled action of control desired value; And the load of described refrigerating plant is more little, just makes the more little gain-adjusted action of described ride gain.
In the invention of first aspect, second aspect, the third aspect and fourth aspect various aspects, cold-producing medium circulates and carries out kind of refrigeration cycle in refrigerant loop 20.At this moment, the critical pressure that is higher than this cold-producing medium from the pressure of the cold-producing medium of compressor 31 ejection.Also have, be arranged on the heat source side heat exchanger 33 in the refrigerant loop 20 and utilize a heat exchanger in the side heat exchanger 41,46, and another heat exchanger is as evaporator operation as gas cooler work.
In the invention of first aspect, control device 80 carries out the volume controlled action.Under this volume controlled action, regulate the capacity of compressor 31, make the physical quantity of regulation become the control desired value.Though depart from the control desired value if become the physical quantity of regulation, can't further reduce the state of compressor 31 capacity again, control device 80 just makes compressor 31 stop.If by the volume controlled action compressor 31 is stopped, control device 80 just carries out degree of superheat desired value change action, improves degree of superheat desired value by force.If afterwards compressor 31 entry into service again, control device 80 just utilizes the degree of superheat desired value that has been improved by degree of superheat desired value change action to carry out flow-control and moves.That is to say that control device 80 is regulated the flow by the cold-producing medium of expansion mechanism 34,42,47, the degree of superheat desired value that the degree of superheat that flows to the cold-producing medium of compressor 31 from the heat exchanger 33,41,46 as evaporator operation is become be enhanced.
In the invention of first aspect, it is high more that expansion mechanism 34,42,47 is configured to degree of superheat desired value, and the flow of the cold-producing medium by this expansion mechanism is few more state just.If compare under the identical situation of compressor 31 capacity, then because degree of superheat desired value is high more, the circulating mass of refrigerant in the refrigerant loop 20 is just few more, so the ability of refrigerating plant 10 just can reduce.That is to say that degree of superheat desired value is high more, the lower limit of the ability of refrigerating plant 10 is just low more.For this reason, control device 80 has to allow under the situation that compressor 31 stops before improving the target degree of superheat, and the possibility that the running of compressor 31 is continued increases.
In the invention of second aspect, control device 80 carries out volume controlled action and control desired value change action in the cooling operation process.Under this volume controlled action, control device 80 will utilize the evaporating temperature of the cold-producing medium in the side heat exchanger 41,46 or the low pressure of the kind of refrigeration cycle of in refrigerant loop 20, carrying out as the control parameter, regulate the capacity of compressor 31, make the control parameter become the control desired value.Though if become control parameter drift-out control desired value, can't further reduce the state of compressor 31 capacity again, control device 80 just allows compressor 31 stop.As if compressor 31 entry into service again, control device 80 is just controlled desired value change action afterwards.Under this control desired value change action, control device 80 with compressor 31 again that control desired value constantly of entry into service be made as the value higher than standard mesh scale value, from this time, be carved into through reducing the control desired value gradually during this section till the stipulated time, make this control desired value desired value that constantly is near the mark.During this, under the volume controlled action, utilize the control desired value that has regulated by control desired value change action, the capacity of compressor 31 is regulated.
At this, soon, the control parameter is that the actual measured value of low pressure of the evaporating temperature of cold-producing medium or kind of refrigeration cycle and the difference of standard mesh scale value just can increase after compressor 31 starts.For this reason, to keep the standard mesh scale value constant if control desired value soon after compressor 31 starts, and then in order to make the control parameter desired value that is near the mark as early as possible, the capacity of compressor 31 will be increased suddenly.And, if the cooling capacity of refrigerating plant 10 increases suddenly with increasing suddenly of compressor 31 capacity, will become at compressor 31 and start back cooling capacity surplus in the short time, and the state that allows compressor 31 stop once more of having to.
With respect to this, the control device 80 in the invention of second aspect after compressor 31 starts soon during this period of time in will control desired value and be made as the value higher than standard mesh scale value.Therefore, though after compressor 31 starts soon, the control parameter is that the actual measured value of low pressure of the evaporating temperature of cold-producing medium or kind of refrigeration cycle is also little than this difference of keeping under the constant situation of standard mesh scale value in the control desired value with the difference of control desired value.Consequently, the capacity that can be suppressed at compressor 31 startup back compressors 31 increases suddenly, and the cooling capacity of refrigerating plant 10 also can change lentamente.For this reason, it is constant to keep the standard mesh scale value in hypothesis control desired value, control device 80 has to allow under the situation that compressor 31 stops, if control device 80 makes the control desired value be higher than the standard mesh scale value as this is invented, and the possibility increase that the running of compressor 31 is continued.
In the invention of the third aspect, control device 80 carries out volume controlled action and control desired value change action in the heating operation process.Under this volume controlled action, the high pressure of the kind of refrigeration cycle that control device 80 will carry out in refrigerant loop 20 is regulated the capacity of compressor 31 as the control parameter, makes the control parameter become the control desired value.Though if become control parameter drift-out control desired value, can't further reduce the state of compressor 31 capacity again, control device 80 just allows compressor 31 stop.As if compressor 31 entry into service again, control device 80 is just controlled desired value change action afterwards.Under this control desired value change action, control device 80 with compressor 31 again that control desired value constantly of entry into service be made as the value lower than standard mesh scale value, from this time, be carved into through improving the control desired value gradually during this section till the stipulated time, make this control desired value desired value that constantly is near the mark.During this, under the volume controlled action, utilize the control desired value that has regulated by control desired value change action, the capacity of compressor 31 is regulated.
At this, soon, the control parameter is that the actual measured value of high pressure of kind of refrigeration cycle and the difference of standard mesh scale value just can increase after compressor 31 starts.For this reason, to keep the standard mesh scale value constant if control desired value soon after compressor 31 starts, and then in order to make the control parameter desired value that is near the mark as early as possible, the capacity of compressor 31 will be increased suddenly.And, if the heating efficiency of refrigerating plant 10 sharply increases with increasing suddenly of compressor 31 capacity, will become at compressor 31 and start back heating efficiency surplus in the short time, and the state that allows compressor 31 stop once more of having to.
With respect to this, the control device 80 in the invention of the third aspect after compressor 31 starts soon during this period of time in will control desired value and be made as the value lower than standard mesh scale value.Therefore, though after compressor 31 starts soon, the control parameter is that the actual measured value of high pressure of kind of refrigeration cycle is also little than this difference of keeping under the constant situation of standard mesh scale value in the control desired value with the difference of control desired value.Consequently, the capacity that can be suppressed at compressor 31 startup back compressors 31 increases suddenly, and the heating efficiency of refrigerating plant 10 also can change lentamente.For this reason, it is constant to keep the standard mesh scale value in hypothesis control desired value, control device 80 has to allow under the situation that compressor 31 stops, if control device 80 makes the control desired value be lower than the standard mesh scale value as this is invented, and the possibility increase that the running of compressor 31 is continued.
In the invention of fourth aspect, control device 80 carries out volume controlled action and gain-adjusted action.Under this volume controlled action, regulate the capacity of compressor 31, make the physical quantity of regulation become the control desired value.Though depart from the control desired value if become the physical quantity of regulation, can't further reduce the state of compressor 31 capacity again, control device 80 just allows compressor 31 stop.On the other hand, control device 80 carries out the gain-adjusted action, constantly is reduced in the value of employed ride gain in the volume controlled action along with reducing of refrigerating plant 10 loads.
At this, although the load of refrigerating plant 10 reduces, ride gain is still bigger, and then the variable quantity of the capacity of fixed compressor 31 with the difference of control desired value of physical quantity according to the rules will increase.Consequently, the ability relative load surplus of refrigerating plant 10 has to allow the possibility of this state that compressor 31 stops to increase and be absorbed in.
With respect to this, the control device 80 in the invention of fourth aspect constantly reduces the value of ride gain along with reducing of refrigerating plant 10 loads.Consequently, be that this command value under certain situation is little with the physical quantity of regulation and the command value calculated of ride gain than ride gain.For this reason, keep certain in the hypothesis ride gain, control device 80 has to allow under the situation that compressor 31 stops, if control device 80 reduces ride gain as this is invented, and the possibility increase that the running of compressor 31 is continued.
The effect of-invention-
As mentioned above, in the invention of described first aspect, reduce the lower limit of the ability of refrigerating plant 10, thereby make owing to the superfluous possibility that causes compressor 31 to stop of the ability relative load of refrigerating plant 10 reduces by improving degree of superheat desired value.Also have, in the invention of described second aspect, be set at higher value by the control parameter that after compressor 31 starts, will cool off soon in the operation process, thereby make owing to the superfluous possibility that causes compressor 31 to stop of the cooling capacity relative load of refrigerating plant 10 reduces.Also have, in the invention of the described third aspect, be set at lower value by the control parameter that after compressor 31 starts, will heat soon in the operation process, thereby make owing to the superfluous possibility that causes compressor 31 to stop of the heating efficiency relative load of refrigerating plant 10 reduces.Also have, in the invention of described fourth aspect, when the load of refrigerating plant 10 hour is made as less value with ride gain, thereby make because the superfluous possibility reduction that causes compressor 31 to stop of the ability relative load of refrigerating plant 10.
So, according to the present invention, in the refrigerating plant 10 that carries out so-called overcritical circulation, can make owing to the superfluous possibility that causes compressor 31 to stop of the ability relative load of refrigerating plant 10 reduces.That is to say, in the refrigerating plant 10 of the overcritical circulation of this characteristic, can make the number of times minimizing that allows compressor 31 start and to stop in order to carry out capacity adjustment with " needed power is more till starting compressor 31 backs to reach appropriate value to the high pressure of kind of refrigeration cycle or low pressure ".Therefore,, be used for carrying out the start-stop time of the compressor 31 of capacity adjustment by minimizing, and can reduce the power that in the operation process of refrigerating plant 10, consumes, the running efficiency of refrigerating plant 10 is improved according to the present invention.
Description of drawings
Fig. 1 is the refrigerant loop figure of the schematic configuration of the air conditioner in expression first embodiment.Fig. 2 is the master controller of expression in first embodiment and the block diagram of the structure of submaster controller.Fig. 3 is the block diagram of the structure of the master controller in expression second embodiment.Fig. 4 is the block diagram of the structure of the master controller in expression the 3rd embodiment.
-symbol description-
10 air conditioners, (refrigerating plant) 20 refrigerant loops 31 compressors 33 outdoor heat converters, (heat source side heat exchanger) 34 outdoor expansion valves, (expansion mechanism) 41 indoor heat converters, (utilizing the side heat exchanger) 42 indoor expansion valves, (expansion mechanism) 46 indoor heat converters, (utilizing the side heat exchanger) 47 indoor expansion valves, (expansion mechanism) 60 master controller 70a submaster controller 70b submaster controllers 80 control device
The specific embodiment
Below, with reference to accompanying drawing embodiments of the present invention are described in detail.Below Shuo Ming each embodiment all is the air conditioner 10 that is made of refrigerating plant.
(first embodiment of invention) as shown in Figure 1, the air conditioner 10 of present embodiment comprises an outdoor unit 11 and two indoor units 12,13.Outdoor unit 11 is arranged on outdoor.Each indoor units 12,13 is arranged on indoor.The platform number of outdoor unit of enumerating here in addition, 11 and indoor units 12,13 only is an example.Also have, this air conditioner 10 comprises master controller 60 and submaster controller 70a, 70b.Master controller 60 and submaster controller 70a, 70b constitute control device 80.
In the air conditioner 10 of present embodiment, with hydraulic fluid side connecting pipe 21 and gas side connecting pipe 22 the outdoor loop 30 of outdoor unit 11 and the indoor loop 40,45 of Ge Tai indoor units 12,13 are coupled together, thereby form refrigerant loop 20.In this refrigerant loop 20, filling arbon dioxide (CO 2) make cold-producing medium.Also have, it is the taller value of critical pressure of carbon dioxide that the high pressure of the kind of refrigeration cycle of carrying out in this refrigerant loop 20 is configured to than cold-producing medium.
In outdoor unit 11, taken in an outdoor loop 30.In outdoor loop 30, be provided with compressor 31, four-way change-over valve 32, as the outdoor heat converter 33 of heat source side heat exchanger, outdoor expansion valve 34, liquid reservoir 35, hydraulic fluid side stop valve 36 and gas side stop valve 37 as expansion mechanism.Also have, in outdoor unit 11, be provided with and be used for outdoor air is sent to the outdoor fan 16 of outdoor heat converter 33.
In outdoor loop 30, the ejection side of compressor 31 is connected with first valve port of four-way change-over valve 32, and its suction side is connected with second valve port of four-way change-over valve 32.The gas side of outdoor heat converter 33 is connected with the 3rd valve port of four-way change-over valve, and its liquid side is connected with an end of outdoor expansion valve 34.The other end of outdoor expansion valve 34 is connected with hydraulic fluid side stop valve 36 via liquid reservoir 35.The 4th valve port of four-way change-over valve 32 is connected with gas side stop valve 37.
In each indoor units 12,13, respectively taken in an indoor loop 40,45.In each indoor loop 40,45, one couples together as 41,46 and indoor expansion valves 42,47 as expansion mechanism of the indoor heat converter that utilizes the side heat exchanger.In each indoor loop 40,45, indoor heat converter 41,46 and 42,47 series connection of indoor expansion valve.Also have, in each indoor units 12,13, respectively be provided with an indoor fan 17,18 that is used for room air is sent to indoor heat converter 41,46.
In refrigerant loop 20, an end of hydraulic fluid side connecting pipe 21 is connected with hydraulic fluid side stop valve 36.The other end of hydraulic fluid side connecting pipe 21 is divided into two, and is connected with the end of indoor expansion valve 42,47 1 sides in each indoor loop 40,45.On the other hand, an end of gas side connecting pipe 22 is connected with gas side stop valve 37.The other end of gas side connecting pipe 22 is divided into two, and is connected with the end of indoor heat converter 41,46 1 sides in each indoor loop 40,45.That is to say, in this refrigerant loop 20, two indoor loop 40,45 relative outdoor loop 30 parallel connections.
Compressor 31 is totally-enclosed type compressors of taking in compressing mechanism and motor in a housing.Outdoor heat converter 33 and each indoor heat converter 41,46 all are to constitute to make cold-producing medium and air carry out the pipe type air heat exchanger of heat exchange.Outdoor expansion valve 34 and each indoor expansion valve 42,47 all are the variable electric expansion valves of aperture.Four-way change-over valve 32 switches between first valve port is communicated with the 3rd valve port and second valve port is communicated with the 4th valve port first state (state among Fig. 1 shown in the solid line) and first valve port is communicated with the 4th valve port and second valve port is communicated with the 3rd valve port second state (state shown in dotted lines in Figure 1).
In outdoor unit 11, be provided with a high-pressure sensor 51, low-pressure sensor 52, inlet temperature sensor 53, an outdoor gas side temperature sensor 54 and an outside air temperature sensor 58.High-pressure sensor 51 is connected between first valve port of the ejection side of compressor 31 in the refrigerant loop 20 and four-way change-over valve 32, measures from the pressure of the cold-producing medium of compressor 31 ejections.Low-pressure sensor 52 is connected between second valve port of the suction side of compressor 31 in the refrigerant loop 20 and four-way change-over valve 32, and measurement will be inhaled into the pressure of the cold-producing medium of compressor 31.Inlet temperature sensor 53 is arranged between second valve port of the suction side of compressor 31 in the refrigerant loop 20 and four-way change-over valve 32, and measurement will be inhaled into the temperature of the cold-producing medium of compressor 31.Outdoor gas side temperature sensor 54 is arranged near the gas side end of outdoor heat converter 33 in the outdoor loop 30, measures the temperature of passing through cold-producing medium herein.The temperature that outside air temperature sensor 58 is measured by the outdoor air before the outdoor heat converter 33.
In each indoor units 12,13, respectively be provided with indoor temperature transmitter 55a, a 55b, indoor gas side temperature sensor 56a, a 56b and indoor liquid side temperature sensor 57a, a 57b. Indoor temperature transmitter 55a, 55b measure the temperature by the room air before the indoor heat converter 41,46.Indoor gas side temperature sensor 56a, 56b are arranged in each indoor loop 40,45 near indoor heat converter 41,46 and the ends indoor expansion valve 42,47 opposite sides, measure the temperature of the cold-producing medium by herein.Indoor liquid side temperature sensor 57a, 57b are arranged near the end of indoor expansion valve 42,47 1 sides of indoor heat converter 41,46 in each indoor loop 40,45, measure the temperature of passing through cold-producing medium herein.
Master controller 60 is arranged in the outdoor unit 11.As shown in Figure 2, in master controller 60, be provided with low voltage target value configuration part 61, high pressure desired value configuration part 62, compressor control portion 63, outdoor expansion valve control part 64 and degree of superheat desired value changing unit 65.Measured value to master controller 60 input high-pressure sensors 51, low-pressure sensor 52, inlet temperature sensor 53, outdoor gas side temperature sensor 54, each indoor temperature transmitter 55a, 55b and outside air temperature sensor 58.
In each indoor units 12,13, respectively be provided with submaster controller 70a, a 70b.As shown in Figure 2, in each submaster controller 70a, 70b, be provided with indoor expansion valve control part 71a, 71b.Measured value to each submaster controller 70a, 70b input low-pressure sensor 52.Also have, be arranged on indoor gas side temperature sensor 56a, 56b in the same indoor units 12,13 and the measured value of indoor liquid side temperature sensor 57a, 57b to each submaster controller 70a, 70b input and this each submaster controller.
Master controller 60 and submaster controller 70a, 70b utilize from the measured value of each sensor input the running of air conditioner 10 are controlled.Hereinafter, the detailed in addition explanation of control action that master controller 60 and submaster controller 70a, 70b are carried out.
The air conditioner 10 of the running action-present embodiment of-air conditioner is selected as the cooling operation of cooling running with as a kind of running in the running of heating that adds heat run, and carries out this running.By operation four-way change-over valve 32, carry out cooling operation and heat switching between the running.
(cooling operation) describes the working condition of the air conditioner in the cooling operation process 10.When cooling operation, four-way change-over valve 32 is set to first state (state among Fig. 1 shown in the solid line).Also have, when cooling operation, outdoor expansion valve 34 is set to full open position, and the aperture of each indoor expansion valve 42,47 is suitably regulated.
In refrigerant loop 20, cold-producing medium circulates and carries out kind of refrigeration cycle.In the refrigerant loop 20 when being in cooling operation, outdoor heat converter 33 is as gas cooler work, and each indoor heat converter 41,46 is as evaporator operation.
Specifically, be sent to outdoor heat converter 33 by four-way change-over valve 32 from the cold-producing medium of the supercriticality of compressor 31 ejection, and towards the outdoor air heat release.The cold-producing medium that flows out from outdoor heat converter 33 passes through outdoor expansion valve 34 and liquid reservoir 35 influent side connecting pipes 21, is assigned to each indoor loop 40,45 afterwards.
The cold-producing medium that has flowed into each indoor loop 40,45 was depressurized by indoor expansion valve and becomes the gas-liquid two-phase state in 42,47 o'clock, evaporated from the room air heat absorption in indoor heat converter 41,46 then.The room air that each indoor units 12,13 will be cooled in indoor heat converter 41,46 feeds to indoor.Cold-producing medium inflow gas side connecting pipe 22 by each indoor heat converter 41,46 and converging is sucked by compressor 31 by four-way change-over valve 32 then.After 31 pairs of cold-producing mediums that sucked of compressor compress this cold-producing medium is sprayed.
(heating running) describes the working condition that heats the air conditioner 10 in the operation process.When heating running, four-way change-over valve 32 is set to second state (state shown in dotted lines in Figure 1).Also have, when heating running, the aperture of outdoor expansion valve 34 and each indoor expansion valve 42,47 obtains suitable adjusting.
In refrigerant loop 20, cold-producing medium circulates and carries out kind of refrigeration cycle.In the refrigerant loop 20 when heating running, each indoor heat converter 41,46 is as gas cooler work, and outdoor heat converter 33 is as evaporator operation.
Specifically, by four-way change-over valve 32 inflow gas side connecting pipes 22, be assigned to each indoor loop 40,45 from the cold-producing medium of the supercriticality of compressor 31 ejection then.The cold-producing medium that has flowed into each indoor loop 40,45 in indoor heat converter 41,46 towards the room air heat release.The room air that each indoor units 12,13 will be heated in indoor heat converter 41,46 feeds to indoor.The cold-producing medium that flows out from indoor heat converter 41,46 flows into outdoor loop 30 then by indoor expansion valve 42,47 back influent side connecting pipes 21.
The cold-producing medium that has flowed into outdoor loop 30 is sent to outdoor expansion valve 34 after by liquid reservoir 35, and is depressurized by outdoor expansion valve 34 time and becomes the gas-liquid two-phase state.Cold-producing medium by outdoor expansion valve 34 is sent to outdoor heat converter 33, and from outdoor air the heat absorption and evaporate.The cold-producing medium that flows out from outdoor heat converter 33 is sucked by compressor 31 by four-way change-over valve 32.After 31 pairs of cold-producing mediums that sucked of compressor compress this cold-producing medium is sprayed.
The working condition of-master controller and submaster controller-as mentioned above, master controller 60 and submaster controller 70a, 70b utilize from the measured value of each sensor input the running of air conditioner 10 are controlled.
(cooling operation) describes being in master controller 60 in the cooling operation process and the working condition of submaster controller 70a, 70b.In the cooling operation process, at master controller 60, low voltage target value configuration part 61, compressor control portion 63 and 65 work of degree of superheat desired value changing unit.Also have, in master controller 60, the work that outdoor expansion valve control part 64 only makes the aperture of outdoor expansion valve 34 keep full open position, high pressure desired value configuration part 62 is in halted state.Have, in each submaster controller 70a, 70b, separately indoor expansion valve control part 71a, 71b carry out work again.
Indoor expansion valve control part 71a, the 71b of each submaster controller 70a, 70b regulate the aperture that is arranged on the indoor expansion valve 42,47 in the respective chambers unit 12,13.That is to say that in first indoor units 12, the aperture that the indoor expansion valve control part 71a of submaster controller 70a regulates the first indoor expansion valve 42 makes the refrigerant superheat degree in first indoor heat converter, 41 exits become the degree of superheat desired value of regulation.Also have, in second indoor units 13, the aperture that the indoor expansion valve control part 71b of submaster controller 70b regulates the second indoor expansion valve 47 makes the refrigerant superheat degree in second indoor heat converter, 46 exits become the degree of superheat desired value of regulation.
The detailed in addition explanation of control action that each indoor expansion valve control part 71a, 71b are carried out.Deduct the saturation temperature of the cold-producing medium corresponding in indoor expansion valve control part 71a, 71b the detected value, calculate the refrigerant superheat degree in indoor heat converter 41,46 exits that are arranged in the respective chambers unit 12,13 with the detected value of low-pressure sensor 52 by indoor gas side temperature sensor 56a, 56b from be arranged on corresponding indoor units 12,13.And, the aperture that is arranged on the indoor expansion valve 42,47 in the respective chambers unit 12,13 is regulated, make the calculated value of this degree of superheat become degree of superheat desired value.Indoor expansion valve control part 71a, 71b are general FEEDBACK CONTROL realizations such as passing ratio integral differential (PID) control to the aperture control of indoor expansion valve 42,47.
Specifically, under the situation of calculated value less than degree of superheat desired value of the degree of superheat, indoor expansion valve control part 71a, 71b are in order to increase the refrigerant superheat degree in indoor heat converter 41,46 exits, and reduce the aperture of indoor expansion valve 42,47, the flow of the cold-producing medium by indoor heat converter 41,46 is reduced.Also have, under the situation of calculated value greater than degree of superheat desired value of the degree of superheat, indoor expansion valve control part 71a, 71b are in order to reduce the refrigerant superheat degree in indoor heat converter 41,46 exits, and strengthen the aperture of indoor expansion valve 42,47, the flow of the cold-producing medium by indoor heat converter 41,46 is increased.In addition, in indoor expansion valve control part 71a, 71b, except changed the situation of degree of superheat desired value by degree of superheat desired value changing unit 65, this degree of superheat desired value all is configured to certain standard value (for example 5 ℃).
Low voltage target value configuration part 61 constitutes: carry out low voltage target value and set action.Set under the action in this low voltage target value, the desired value of the low pressure of kind of refrigeration cycle is the corresponding value of cooling load of the indoor units 12,13 of low voltage target value when being configured to cooling operation.
Specifically, the indoor design temperature of low voltage target value configuration part 61 during according to the measured value of each indoor temperature transmitter 55a, 55b, refrigeration etc. judge that the refrigerating capacity of indoor units 12,13 is surplus or deficiency.And when the refrigerating capacity of judging indoor units 12,13 was not enough, low voltage target value configuration part 61 reduced low voltage target value for refrigerating capacity is increased.Also have, when the refrigerating capacity of judging indoor units 12,13 was superfluous, low voltage target value was improved in low voltage target value configuration part 61 for refrigerating capacity is reduced.
Compressor control portion 63 constitutes: carry out the volume controlled action.Under this volume controlled action, regulate the running capacity of compressor 31, make the measured value (that is the actual measured value of the low pressure of kind of refrigeration cycle) of low-pressure sensor 52 become low voltage target value.That is to say that the low pressure of compressor control portion 63 usefulness kind of refrigeration cycle is regulated the running capacity of compressor 31 as the control parameter, makes this control parameter become low voltage target value.
Specifically, compressor control portion 63 changes the rotary speed by electric motor driven compressing mechanism by changing the frequency of the alternating current of supplying with to the motor of compressor 31, changes the running capacity of compressor 31 thus.And when the measured value of low-pressure sensor 52 was higher than low voltage target value, compressor control portion 63 reduced for the low pressure that makes kind of refrigeration cycle, and improved the rotary speed of the motor of compressor 31, and the running capacity of compressor 31 is increased.Also have, when the measured value of low-pressure sensor 52 was lower than low voltage target value, compressor control portion 63 raise for the low pressure that makes kind of refrigeration cycle, and reduced the rotary speed of the motor of compressor 31, and the running capacity of compressor 31 is reduced.
At this moment, compressor control portion 63 utilizes the measured value of low-pressure sensor 52 and the ride gain of regulation, calculates the command value of the variable quantity of the ac frequency of supplying with to the motor of compressor 31.Specifically, in compressor control portion 63, the measured value of low-pressure sensor 52 and the difference of low voltage target value are big more, the command value of the variable quantity of ac frequency just becomes big more value, the measured value of low-pressure sensor 52 and the difference of low voltage target value are more little, and the command value of the variable quantity of ac frequency just becomes more little value.
Also have, although the frequency of the alternating current of supplying with to the motor of compressor 31 reaches lower limit, but the measured value of low-pressure sensor 52 is lower than the words that the state of low voltage target value has still continued the stipulated time, compressor control portion 63 just is judged as the relative cooling load surplus of refrigerating capacity, just allows compressor 31 stop.And then if the difference of the measured value of indoor temperature transmitter 55a, the 55b indoor design temperature during with refrigeration etc. reaches more than a certain degree, compressor control portion 63 just is judged as and need cools off indoor, just starts compressor 31.
Degree of superheat desired value changing unit 65 constitutes: carry out degree of superheat desired value change action.Under this degree of superheat desired value change action, the number of times that 65 pairs of compressor control portions 63 of degree of superheat desired value changing unit stop compressor 31 is counted.And, if compressor control portion 63 make number of times that compressor stops at the appointed time (for example in 15 minutes) reach setting (for example twice), degree of superheat desired value changing unit 65 just makes degree of superheat desired value begin to rise from standard value (for example 5 ℃) by force.After degree of superheat desired value changing unit 65 had improved degree of superheat desired value by force, indoor expansion valve control part 71a, 71b utilized the degree of superheat desired value that improves up from standard value, and the aperture of indoor expansion valve 42,47 is regulated.
But, if the degree of superheat of the cold-producing medium that flows out from indoor heat converter 41,46 in the cooling operation process is too high, the degree of superheat of cold-producing medium that compressor 31 just might occur sucking is too high, and from compressor 31 condition of overhigh temperature of the cold-producing medium of ejection.For this reason, in degree of superheat desired value changing unit 65, configure the higher limit that the change action of degree of superheat desired value makes the ascensional range that degree of superheat desired value rises, avoid too high from the temperature of the cold-producing medium of compressor 31 ejections.
(heating running) describes being in the master controller 60 that heats in the operation process and the working condition of submaster controller 70a, 70b.In heating operation process, at master controller 60, high pressure desired value configuration part 62, compressor control portion 63, outdoor expansion valve control part 64 and 65 work of degree of superheat desired value changing unit, low voltage target value configuration part 61 is in halted state.Have, in each submaster controller 70a, 70b, separately indoor expansion valve control part 71a, 71b carry out work again.
Indoor expansion valve control part 71a, the 71b of each submaster controller 70a, 70b regulate the aperture that is arranged on the indoor expansion valve 42,47 in the respective chambers unit 12,13.This point is identical with the action in the cooling operation process.But, heat the aperture of expansion valve 42,47 in indoor expansion valve control part 71a in the operation process, the 71b conditioning chamber so that be arranged on the indoor liquid side temperature sensor 57a in the respective chambers unit 12,13, the detected value of 57b becomes the desired value of regulation.That is to say, heat the aperture of expansion valve 42,47 in indoor expansion valve control part 71a in the operation process, the 71b conditioning chamber, make the desired value that becomes regulation as the temperature of the cold-producing medium in indoor heat converter 41,46 exits of gas cooler work.Indoor expansion valve control part 71a, 71b are general FEEDBACK CONTROL realizations such as passing ratio integral differential (PID) control to the aperture control of indoor expansion valve 42,47.
Specifically, detected value at indoor liquid side temperature sensor 57a, 57b is higher than under the situation of desired value, indoor expansion valve control part 71a, 71b are in order to reduce the refrigerant temperature in indoor heat converter 41,46 exits, and reduce the aperture of indoor expansion valve 42,47, the flow of the cold-producing medium by indoor heat converter 41,46 is reduced.Also have, detected value at indoor liquid side temperature sensor 57a, 57b is lower than under the situation of desired value, indoor expansion valve control part 71a, 71b are in order to improve the refrigerant temperature in indoor heat converter 41,46 exits, and strengthen the aperture of indoor expansion valve 42,47, the flow of the cold-producing medium by indoor heat converter 41,46 is increased.
High pressure desired value configuration part 62 constitutes: carry out the high pressure desired value and set action.Set under the action in this high pressure desired value, the desired value of the high pressure of kind of refrigeration cycle be the indoor units 12,13 of high pressure desired value when being configured to and heating running heat the corresponding value of load.
Specifically, high pressure desired value configuration part 62 judges that according to the measured value of each indoor temperature transmitter 55a, 55b, the indoor design temperature when heating etc. the heating capacity of indoor units 12,13 is surplus or deficiency.And when the heating capacity of judging indoor units 12,13 was not enough, the high pressure desired value was improved in high pressure desired value configuration part 62 for heating capacity is increased.Also have, when the heating capacity of judging indoor units 12,13 was superfluous, high pressure desired value configuration part 62 reduced the high pressure desired value for heating capacity is reduced.
Compressor control portion 63 constitutes: carry out the volume controlled action.Under this volume controlled action, regulate the running capacity of compressor 31, make the measured value (that is the actual measured value of the high pressure of kind of refrigeration cycle) of high-pressure sensor 51 become the high pressure desired value.That is to say that the high pressure of compressor control portion 63 usefulness kind of refrigeration cycle is regulated the running capacity of compressor 31 as the control parameter, makes this control parameter become the high pressure desired value.
Specifically, compressor control portion 63 changes the rotary speed by electric motor driven compressing mechanism by changing the frequency of the alternating current of supplying with to the motor of compressor 31, changes the running capacity of compressor 31 thus.And, being lower than under the situation of high pressure desired value at the measured value of high-pressure sensor 51, compressor control portion 63 rises for the high pressure that makes kind of refrigeration cycle, and improves the rotary speed of the motor of compressor 31, and the running capacity of compressor 31 is increased.Also have, be higher than under the situation of high pressure desired value at the measured value of high-pressure sensor 51, compressor control portion 63 is in order to make the high drops of kind of refrigeration cycle, and reduces the rotary speed of the motor of compressor 31, and the running capacity of compressor 31 is reduced.
At this moment, compressor control portion 63 utilizes the measured value of high-pressure sensor 51 and the ride gain of regulation, calculates the command value of the variable quantity of the ac frequency of supplying with to the motor of compressor 31.Specifically, in compressor control portion 63, the difference of the measured value of high-pressure sensor 51 and high pressure desired value is big more, the command value of the variable quantity of ac frequency just becomes big more value, the difference of the measured value of high-pressure sensor 51 and high pressure desired value is more little, and the command value of the variable quantity of ac frequency just becomes more little value.
Outdoor expansion valve control part 64 constitutes: carry out the flow-control action.Under this flow-control action, the aperture of regulating outdoor expansion valve 34 makes in heating operation process the degree of superheat as the cold-producing medium in outdoor heat converter 33 exits of evaporator operation become degree of superheat desired value.That is to say that outdoor expansion valve control part 64 is controlled the flow by the cold-producing medium of outdoor expansion valve 34 by regulating the aperture of outdoor expansion valve 34.The aperture control of 64 pairs of outdoor expansion valves 34 of outdoor expansion valve control part is general FEEDBACK CONTROL realizations such as passing ratio integral differential control.
Outdoor expansion valve control part 64 is calculated the refrigerant superheat degree in outdoor heat converter 33 exits by deduct the saturation temperature of the cold-producing medium corresponding with the detected value of low-pressure sensor 52 from the detected value of outdoor gas side temperature sensor 54.And the aperture of regulating outdoor expansion valve 34 makes the calculated value of this degree of superheat become degree of superheat desired value.Specifically, under the situation of calculated value less than degree of superheat desired value of the degree of superheat, outdoor expansion valve control part 64 is in order to increase the refrigerant superheat degree in outdoor heat converter 33 exits, and reduces the aperture of outdoor expansion valve 34, and the flow of the cold-producing medium by outdoor heat converter 33 is reduced.Under the situation of calculated value greater than degree of superheat desired value of the degree of superheat, outdoor expansion valve control part 64 is in order to reduce the refrigerant superheat degree in outdoor heat converter 33 exits, and the aperture of increasing outdoor expansion valve 34 makes the flow increase by the cold-producing medium of outdoor heat converter 33.
Degree of superheat desired value changing unit 65 constitutes: carry out degree of superheat desired value change action.That is to say that identical with the cooling operation process, if the number of times that compressor control portion 63 stops compressor reaching setting at the appointed time, degree of superheat desired value changing unit 65 just makes degree of superheat desired value begin to rise from standard value (for example 5 ℃) by force.After degree of superheat desired value changing unit 65 had improved degree of superheat desired value by force, outdoor expansion valve control part 64 utilized the degree of superheat desired value that improves up from standard value, regulates the aperture of outdoor expansion valve 34.
But, if the degree of superheat of the cold-producing medium that flows out from outdoor heat converter 33 in heating operation process is too high, the degree of superheat of cold-producing medium that compressor 31 just might occur sucking is too high, and the condition of overhigh temperature of the cold-producing medium that sprays from compressor 31.For this reason, in degree of superheat desired value changing unit 65, configure the higher limit that the change action of degree of superheat desired value makes the ascensional range that degree of superheat desired value rises, avoid too high from the temperature of the cold-producing medium of compressor 31 ejections.
The effect of-the first embodiment-in the present embodiment, if the ability surplus of air conditioner 10, the frequency that compressor control portion 63 stops compressor 31 improves, and the degree of superheat desired value changing unit 65 of master controller 60 just makes degree of superheat desired value begin to rise from standard value by force.In the cooling operation process, the aperture of expansion valve 42,47 in the indoor expansion valve control part 71a of submaster controller 70a, 70b, 71b conditioning chamber, the degree of superheat desired value that the degree of superheat that flows to the cold-producing medium of compressor 31 from indoor heat converter 41,46 is reached be enhanced.In heating operation process, the aperture that the outdoor expansion valve control part of master controller 60 64 is regulated outdoor expansion valves 34, the degree of superheat desired value that the degree of superheat that flows to the cold-producing medium of compressor 31 from outdoor heat converter 33 is reached be enhanced.
At this, the temperature, flow of supposing to be sent to the air of evaporimeter be for certain, and then the flow of the cold-producing medium by evaporimeter is few more, and the refrigerant superheat degree at evaporator outlet place is just high more.Therefore, degree of superheat desired value is high more, and the aperture of indoor expansion valve 42,47, outdoor expansion valve 34 is just more little.That is to say that indoor expansion valve 42,47, outdoor expansion valve 34 become refrigerant flow less state by this expansion valve (that is, its aperture set lessly state).For this reason, as if comparing under the identical situation of the rotary speed of the compressing mechanism in being arranged at compressor 31, then degree of superheat desired value is high more, and the circulating mass of refrigerant in the refrigerant loop 20 is just few more, and consequently the ability of air conditioner 10 is just low more.
That is to say that degree of superheat desired value is high more, the lower limit of the ability of air conditioner 10 is just low more.For this reason, compressor control portion 63 has to allow under the situation that compressor 31 stops before improving the target degree of superheat, and the possibility that the running of compressor 31 is continued increases.
So, according to present embodiment, in the air conditioner 10 that carries out so-called overcritical circulation, can make owing to the superfluous possibility that causes compressor 31 to stop of the ability relative load of air conditioner 10 reduces.That is to say, in the air conditioner 10 of the overcritical circulation of this characteristic, can make the number of times minimizing that allows compressor 31 start and to stop in order to carry out capacity adjustment with " needed power is more till starting compressor 31 backs to reach appropriate value to the high pressure of kind of refrigeration cycle or low pressure ".Therefore,, be used for carrying out the start-stop time of the compressor 31 of capacity adjustment by minimizing, and can reduce the power that in the operation process of air conditioner 10, consumes, the running efficiency of air conditioner 10 is improved according to present embodiment.
(second embodiment of invention) describes second embodiment of the present invention.Present embodiment has changed the structure of master controller 60 on the basis of the air conditioner 10 of described first embodiment.
As shown in Figure 3, in the master controller 60 of present embodiment, be provided with control desired value changing unit 66, to replace the degree of superheat desired value changing unit 65 of described first embodiment.In addition, in the master controller 60 of present embodiment, the action of low voltage target value configuration part 61, high pressure desired value configuration part 62, compressor control portion 63 and outdoor expansion valve control part 64 is identical with the action in described first embodiment.
Control desired value changing unit 66 constitutes: control desired value change action.Under this control desired value change action, the number of times that 66 pairs of compressor control portions 63 of control desired value changing unit stop compressor 31 is counted.And, if compressor control portion 63 make number of times that compressor stops at the appointed time (for example in 15 minutes) reach setting (for example twice), control desired value changing unit 66 just changes compressor control portion 63 employed control desired values by force.
(working condition in the cooling operation process) in the cooling operation process, control desired value changing unit 66 will change the action of low voltage target value by force as control desired value change action, and carry out this action.Specifically, if compressor control portion 63 number of times that compressor is stopped reaches the number of times of regulation at the appointed time, control desired value changing unit 66 just allows the compressor control portion 63 employed low voltage target value be that the standard mesh scale value begins to rise from the value by 61 decisions of low voltage target value configuration part.And when compressor 31 started, compressor control portion 63 utilized by controlling the low voltage target value that 66 raisings of desired value changing unit come up, and regulates the running capacity of compressor 31 afterwards.Also have, compressor control portion 63 allows the value of low voltage target value reduce gradually, make when compressor 31 starts, count passed through stipulated time (for example 4 minutes) that constantly low voltage target value become the standard mesh scale value.
At this, soon, the difference of the measured value of low-pressure sensor 52 and standard mesh scale value just can increase after compressor 31 starts.For this reason, if after compressor 31 starts soon low voltage target value to keep the standard mesh scale value constant, then for the measured value that the makes low-pressure sensor 52 as soon as possible desired value that is near the mark, the capacity of compressor 31 will be increased suddenly.And, if the refrigerating capacity of air conditioner 10 increases suddenly with increasing suddenly of compressor 31 capacity, will become compressor 31 start the back in the short time indoor air themperature be lower than design temperature, and the state that allows compressor 31 stop once more of having to.
With respect to this, the control desired value changing unit 66 of present embodiment after compressor 31 starts soon during this period of time in low voltage target value is made as the value higher than standard mesh scale value.Therefore, though after compressor 31 starts soon, the measured value of low-pressure sensor 52 is also little than this difference of keeping in low voltage target value under the constant situation of standard mesh scale value with the difference of low voltage target value.Consequently, the capacity that can suppress compressor 31 startup back compressors 31 increases suddenly, and the refrigerating capacity of air conditioner 10 also can change lentamente.For this reason, it is constant to keep the standard mesh scale value in the hypothesis low voltage target value, compressor control portion 63 has to allow under the situation that compressor 31 stops, if as present embodiment, control desired value changing unit 66 and make low voltage target value be higher than the standard mesh scale value, the possibility increase that the running of compressor 31 is continued.
(heating the working condition in the operation process) in heating operation process, control desired value changing unit 66 will change the action of high pressure desired value by force as control desired value change action, and carry out this action.Specifically, if compressor control portion 63 number of times that compressor is stopped reaches the number of times of regulation at the appointed time, control desired value changing unit 66 just allows the compressor control portion 63 employed high pressure desired values be that the standard mesh scale value begins to reduce from the value by 62 decisions of high pressure desired value configuration part.And afterwards when compressor 31 starts, compressor control portion 63 utilizes the high pressure desired value that has been reduced by control desired value changing unit 66, regulates the running capacity of compressor 31.Also have, compressor control portion 63 allows the value of high pressure desired value raise gradually, make when compressor 31 starts, count passed through stipulated time (for example 4 minutes) that constantly high pressure desired value become the standard mesh scale value.
At this, soon, the difference of the measured value of high-pressure sensor 51 and standard mesh scale value just can increase after compressor 31 starts.For this reason, if after compressor 31 starts soon the high pressure desired value to keep the standard mesh scale value constant, then for the measured value that the makes high-pressure sensor 51 as soon as possible desired value that is near the mark, the capacity of compressor 31 will be increased suddenly.If the heating capacity of air conditioner 10 increases suddenly with increasing suddenly of compressor 31 capacity, will become compressor 31 start the back in the short time indoor air themperature be higher than design temperature, and the state that allows compressor 31 stop once more of having to.
With respect to this, the control desired value changing unit 66 of present embodiment after compressor 31 starts soon during this period of time in the high pressure desired value is made as the value lower than standard mesh scale value.Therefore, though after compressor 31 starts soon, the measured value of high-pressure sensor 51 is also little than this difference of keeping under the constant situation of standard mesh scale value in the high pressure desired value with the difference of high pressure desired value.Consequently, the capacity that can suppress compressor 31 startup back compressors 31 increases suddenly, and the heating capacity of air conditioner 10 also can change lentamente.For this reason, it is constant to keep the standard mesh scale value in hypothesis high pressure desired value, compressor control portion 63 has to allow under the situation that compressor 31 stops, if as present embodiment, control desired value changing unit 66 and make the high pressure desired value be lower than the standard mesh scale value, the possibility increase that the running of compressor 31 is continued.
The effect of-the second embodiment-, in the air conditioner 10 that carries out so-called overcritical circulation, can make owing to the superfluous possibility that causes compressor 31 to stop of the ability relative load of air conditioner 10 reduces according to present embodiment.Therefore, identical with described first embodiment, according to present embodiment, be used for carrying out the start-stop time of the compressor 31 of capacity adjustment by minimizing, and can reduce the power that in the operation process of air conditioner 10, consumes, the running efficiency of air conditioner 10 is improved.
The compressor control portion 63 of the variation-present embodiment of-the second embodiment also can constitute: the control parameter of the evaporating temperature that is used as the cold-producing medium in the indoor heat converter 41,46 of evaporator operation during as cooling operation.In the master controller 60 of this variation, be provided with evaporating temperature desired value configuration part to replace low voltage target value configuration part 61.The desired value of the cold-producing medium evaporating temperature in the indoor heat converter 41,46 is set in evaporating temperature desired value configuration part according to the cooling load of air conditioner 10.Also have, as the change of the control desired value in cooling operation process action, it is that the standard mesh scale value begins to rise from the value by the decision of evaporating temperature desired value configuration part that the control desired value changing unit 66 of this variation makes compressor control portion 63 employed evaporating temperature desired values, and allow the value of evaporating temperature desired value descend lentamente, make when compressor 31 starts, count passed through the stipulated time that constantly evaporating temperature desired value become the standard mesh scale value.
(the 3rd embodiment of invention) describes the 3rd embodiment of the present invention.Present embodiment has changed the structure of master controller 60 on the basis of the air conditioner 10 of described first embodiment.
As shown in Figure 4, in the master controller 60 of present embodiment, be provided with gain-adjusted portion 67 to replace the degree of superheat desired value changing unit 65 in described first embodiment.In addition, in the master controller 60 of present embodiment, the action of low voltage target value configuration part 61, high pressure desired value configuration part 62, compressor control portion 63 and outdoor expansion valve control part 64 is identical with the action in described first embodiment.
Gain-adjusted portion 67 constitutes: carry out the gain-adjusted action.Under the action of this gain-adjusted, gain-adjusted portion 67 is poor according to the measured value (that is, the actual measured value of outside air temperature) of outside air temperature sensor 58 and indoor design temperature, adjusting compressor control portion 63 employed ride gains.
In the cooling operation process, the measured value of 67 pairs of outside air temperature sensors 58 of gain-adjusted portion and indoor design temperature compare.In the cooling operation process, indoor cooling load is along with deduct reducing of resulting value behind the indoor design temperature from the measured value of outside air temperature sensor 58 and reduce.So, from the measured value of outside air temperature sensor 58, deduct indoor design temperature after resulting value more little, gain-adjusted portion 67 just is set at more little value with compressor control portion 63 employed ride gains.
In the cooling operation process, the compressor control portion 63 of present embodiment utilizes the ride gain of the smaller value of being set by gain-adjusted portion 67, and the capacity of compressor 31 is regulated.Specifically, compressor control portion 63 utilizes the measured value of low-pressure sensor 52 and the difference and the ride gain of low voltage target value, calculates the command value of variable quantity of the ac frequency of the motor that feeds to compressor 31.If compare under the identical situation of the difference of the measured value of low-pressure sensor 52 and low voltage target value, then in compressor control portion 63, the value of ride gain is more little, and the command value of the variable quantity of ac frequency is just more little.
In heating operation process, gain-adjusted portion 67 also compares the measured value of outside air temperature sensor 58 and indoor design temperature.In heating operation process, indoor heat load along with the measured value that from indoor design temperature, deducts outside air temperature sensor 58 after reducing of resulting value and reducing.So, from indoor design temperature, deduct the measured value of outside air temperature sensor 58 after resulting value more little, gain-adjusted portion 67 just is set at more little value with compressor control portion 63 employed ride gains.
In heating operation process, the compressor control portion 63 of present embodiment utilizes the ride gain of the smaller value of being set by gain-adjusted portion 67, and the capacity of compressor 31 is regulated.Specifically, compressor control portion 63 utilizes the measured value of high-pressure sensor 51 and the difference and the ride gain of high pressure desired value, calculates the command value of variable quantity of the ac frequency of the motor that feeds to compressor 31.If compare under the measured value of high-pressure sensor 51 situation identical with the difference of high pressure desired value, then in compressor control portion 63, the value of ride gain is more little, and the command value of the variable quantity of ac frequency is just more little.
At this, although the load of air conditioner 10 reduces, but compressor control portion 63 employed ride gains are still bigger, then according to the difference of the measured value of the poor or high-pressure sensor 51 of the measured value of low-pressure sensor 52 and low voltage target value and high pressure desired value and the command value of the variable quantity of fixed ac frequency will increase.Consequently, the ability relative load surplus of air conditioner 10 has to allow the possibility of this state that compressor 31 stops to increase and be absorbed in.
With respect to this, the gain-adjusted portion 67 of present embodiment constantly reduces the value of ride gain along with reducing of air conditioner 10 loads.Consequently, be that this command value under certain situation is little with the measured value of low-pressure sensor 52 or high-pressure sensor 51 and command value that ride gain is calculated than ride gain.Therefore, keep certain in the hypothesis ride gain, compressor control portion 63 has to allow under the situation that compressor 31 stops, if gain-adjusted portion 67 reduces ride gains as present embodiment, and the possibility increase that the running of compressor 31 is continued.
The effect of-Di three embodiments-, in the air conditioner 10 that carries out so-called overcritical circulation, can make owing to the superfluous possibility that causes compressor 31 to stop of the ability relative load of air conditioner 10 reduces according to present embodiment.Therefore, identical with described first embodiment, according to present embodiment, be used for carrying out the start-stop time of the compressor 31 of capacity adjustment by minimizing, and can reduce the power that in the operation process of air conditioner 10, consumes, the running efficiency of air conditioner 10 is improved.
-industrial applicability-
In sum, to be configured to be higher than the refrigeration device of kind of refrigeration cycle of value of the critical pressure of refrigeration agent very useful to carrying out high pressure in the present invention.

Claims (4)

1. refrigerating plant, comprise refrigerant loop (20) and control device (80), in this refrigerant loop (20), be provided with compressor (31), expansion mechanism (34,42,47), heat source side heat exchanger (33) and utilize side heat exchanger (41,46), this refrigerant loop (20) carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, this control device (80) is controlled described compressor (31) and described expansion mechanism (34,42,47), it is characterized in that:
Described control device (80) constitutes and carries out:
Volume controlled is moved, and regulates the capacity of described compressor (31), makes the physical quantity of the duty that is illustrated in the kind of refrigeration cycle of carrying out in the described refrigerant loop (20) become the control desired value,
The flow-control action, regulate flow by the cold-producing medium of described expansion mechanism (34,42,47), making from the described heat source side heat exchanger (33) and the described degree of superheat of utilizing the side heat exchanger (41,46) heat exchanger as evaporator operation to flow to the cold-producing medium of described compressor (31) becomes degree of superheat desired value, and
Degree of superheat desired value change action making described compressor (31) when stopping by described volume controlled action, improves described degree of superheat desired value by force.
2. refrigerating plant, comprise refrigerant loop (20) and control device (80), in this refrigerant loop (20), be provided with compressor (31), expansion mechanism (34,42,47), heat source side heat exchanger (33) and utilize side heat exchanger (41,46), this refrigerant loop (20) carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, this control device (80) is controlled described compressor (31), this refrigerating plant carries out described heat source side heat exchanger (33) at least as gas cooler work and the described side heat exchanger (41 that utilizes, 46) as the cooling running of evaporator operation, it is characterized in that:
Described control device (80) constitutes and carries out:
The volume controlled action, with the low pressure of the described kind of refrigeration cycle of utilizing the evaporating temperature of the cold-producing medium in the side heat exchanger (41,46) or in described refrigerant loop (20), carrying out as the control parameter, regulate the capacity of described compressor (31), make this control parameter become the control desired value, and
The change action of control desired value starts the described control desired value of relief at described compressor (31) and descends gradually, make when described compressor (31) starts, count passed through the stipulated time after described control desired value become the specified standard desired value.
3. refrigerating plant, comprise refrigerant loop (20) and control device (80), in this refrigerant loop (20), be provided with compressor (31), expansion mechanism (34,42,47), heat source side heat exchanger (33) and utilize side heat exchanger (41,46), this refrigerant loop (20) carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, this control device (80) is controlled described compressor (31), this refrigerating plant carries out the described side heat exchanger (41 that utilizes at least, 46) as gas cooler work and described heat source side heat exchanger (33) as the heat run that adds of evaporator operation, it is characterized in that:
Described control device (80) constitutes and carries out:
Volume controlled action, the high pressure of the kind of refrigeration cycle that will carry out in described refrigerant loop (20) are regulated the capacity of described compressor (31) as the control parameter, make this control parameter become the control desired value, and
The change action of control desired value starts the described control desired value of relief at described compressor (31) and rises gradually, make when described compressor (31) starts, count passed through the stipulated time after described control desired value become the specified standard desired value.
4. refrigerating plant, comprise refrigerant loop (20) and control device (80), in this refrigerant loop (20), be provided with compressor (31), expansion mechanism (34,42,47), heat source side heat exchanger (33) and utilize side heat exchanger (41,46), this refrigerant loop (20) carries out the kind of refrigeration cycle that high pressure is configured to be higher than the value of cold-producing medium critical pressure, this control device (80) is controlled described compressor (31), it is characterized in that:
Described control device (80) constitutes and carries out:
The volume controlled action according to the physical quantity of using the duty that is illustrated in the kind of refrigeration cycle of carrying out in the described refrigerant loop (20) and the command value that ride gain is calculated, is regulated the capacity of described compressor (31), makes this physical quantity become the control desired value, and
The gain-adjusted action, the load of described refrigerating plant is more little, just makes described ride gain more little.
CN2009801105845A 2008-03-24 2009-03-11 Refrigeration apparatus Pending CN101978227A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2008-076250 2008-03-24
JP2008076250A JP2009229012A (en) 2008-03-24 2008-03-24 Refrigerating device
PCT/JP2009/001097 WO2009119023A1 (en) 2008-03-24 2009-03-11 Freezing apparatus

Publications (1)

Publication Number Publication Date
CN101978227A true CN101978227A (en) 2011-02-16

Family

ID=41113237

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2009801105845A Pending CN101978227A (en) 2008-03-24 2009-03-11 Refrigeration apparatus

Country Status (5)

Country Link
US (1) US20110011125A1 (en)
EP (1) EP2261580A1 (en)
JP (1) JP2009229012A (en)
CN (1) CN101978227A (en)
WO (1) WO2009119023A1 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102745039A (en) * 2011-04-21 2012-10-24 株式会社电装 Refrigerant cycle device
CN104254742A (en) * 2012-04-26 2014-12-31 三菱电机株式会社 Air conditioning apparatus
CN104662381A (en) * 2012-08-23 2015-05-27 丹佛斯公司 A method for controlling a vapour compression system during start-up
WO2015149356A1 (en) * 2014-04-04 2015-10-08 Emerson Climate Technologies, Inc. Compressor temperature control systems and methods
CN104976119A (en) * 2014-04-04 2015-10-14 艾默生环境优化技术有限公司 Temperature control system and method of compressor
CN105378392A (en) * 2013-05-27 2016-03-02 三菱电机株式会社 air conditioner
CN105526670A (en) * 2014-10-15 2016-04-27 力博特公司 Apparatus and method for subcooling control based on superheat setpoint control
CN106813322A (en) * 2015-11-30 2017-06-09 青岛海尔空调电子有限公司 A kind of air conditioning pressure protection system and air conditioner refrigerating, heat pressure guard method
CN114739081A (en) * 2022-03-29 2022-07-12 青岛海尔空调电子有限公司 Air conditioning unit control method and system and air conditioning unit

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011080801A1 (en) * 2009-12-28 2011-07-07 ダイキン工業株式会社 Heat pump system
KR20110092147A (en) * 2010-02-08 2011-08-17 삼성전자주식회사 Air conditioner and control method thereof
KR101727034B1 (en) * 2010-03-11 2017-04-14 엘지전자 주식회사 Air conditioner
JP4947221B2 (en) 2010-05-11 2012-06-06 ダイキン工業株式会社 Operation control device for air conditioner and air conditioner having the same
JP5752135B2 (en) * 2010-09-14 2015-07-22 三菱電機株式会社 Air conditioner
JP5797022B2 (en) * 2011-06-09 2015-10-21 三菱重工業株式会社 Multi-type air conditioner and control method thereof
JP5594267B2 (en) * 2011-09-12 2014-09-24 ダイキン工業株式会社 Refrigeration equipment
EP2674697B1 (en) * 2012-06-14 2018-09-12 Alfa Laval Corporate AB A plate heat exchanger
US10174977B2 (en) * 2012-11-21 2019-01-08 Vertiv Corporation Apparatus and method for subcooling control based on superheat setpoint control
JP2014190554A (en) * 2013-03-26 2014-10-06 Fujitsu General Ltd Air conditioner
JP6205871B2 (en) * 2013-06-05 2017-10-04 ソニー株式会社 Magnetic recording medium
WO2015029206A1 (en) * 2013-08-30 2015-03-05 三菱電機株式会社 Refrigeration cycle apparatus
GB2521469B (en) * 2013-12-20 2019-10-16 Hubbard Products Ltd Evaporator Control
JP6412325B2 (en) * 2014-03-27 2018-10-24 日立ジョンソンコントロールズ空調株式会社 Cooling system
JP6455752B2 (en) * 2014-07-31 2019-01-23 パナソニックＩｐマネジメント株式会社 Refrigeration system
JP6628972B2 (en) * 2015-03-26 2020-01-15 三菱重工サーマルシステムズ株式会社 Air conditioning system control device, air conditioning system, air conditioning system control program, and air conditioning system control method
JP6619572B2 (en) * 2015-07-01 2019-12-11 サンデン・オートモーティブクライメイトシステム株式会社 Air conditioner for vehicles
EP3196569A1 (en) * 2016-01-21 2017-07-26 Vaillant GmbH Sensor arramgement in a heat pump system
US10473377B2 (en) * 2016-09-26 2019-11-12 Carrier Corporation High outdoor ambient and high suction pressure oil pump out mitigation for air conditioners
US10921012B1 (en) * 2017-03-06 2021-02-16 EnTouch Controls Inc. System and method for compressor optimization and system cycling using ambient air for cooling or heating
CN110360729A (en) * 2018-04-09 2019-10-22 珠海格力电器股份有限公司 Unit high-fall pressure control method and device and air conditioning equipment
JP6879322B2 (en) * 2019-03-12 2021-06-02 ダイキン工業株式会社 Refrigerator
CN115247858B (en) * 2022-05-16 2024-04-26 美的集团武汉暖通设备有限公司 Air conditioner, control method thereof and computer readable storage medium

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6314047A (en) * 1986-06-28 1988-01-21 三菱重工業株式会社 Refrigerant flow controller for air conditioner for automobile
JP2932922B2 (en) * 1993-12-28 1999-08-09 三菱電機株式会社 Refrigeration / air conditioning system
JP3614330B2 (en) 1999-10-20 2005-01-26 シャープ株式会社 Supercritical vapor compression refrigeration cycle
JP2002061925A (en) 2000-08-23 2002-02-28 Daikin Ind Ltd Air conditioner
WO2003036184A1 (en) * 2001-10-25 2003-05-01 Zexel Valeo Climate Control Corporation Control device of variable displacement compressor and variable displacement control device of refrigerating cycle

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102745039A (en) * 2011-04-21 2012-10-24 株式会社电装 Refrigerant cycle device
CN104254742B (en) * 2012-04-26 2017-03-08 三菱电机株式会社 Air conditioning apparatus
CN104254742A (en) * 2012-04-26 2014-12-31 三菱电机株式会社 Air conditioning apparatus
CN104662381A (en) * 2012-08-23 2015-05-27 丹佛斯公司 A method for controlling a vapour compression system during start-up
US9791174B2 (en) 2012-08-23 2017-10-17 Danfoss A/S Method for controlling an expansion device of a vapor compression system during start-up using rates of change of an evaporator inlet and outlet temperature
CN104662381B (en) * 2012-08-23 2016-11-02 丹佛斯公司 For the method controlling vapor compression system in start-up course
CN105378392B (en) * 2013-05-27 2018-10-26 三菱电机株式会社 air conditioner
CN105378392A (en) * 2013-05-27 2016-03-02 三菱电机株式会社 air conditioner
CN104976119A (en) * 2014-04-04 2015-10-14 艾默生环境优化技术有限公司 Temperature control system and method of compressor
CN104976119B (en) * 2014-04-04 2017-01-18 艾默生环境优化技术有限公司 Temperature control system and method of compressor
WO2015149356A1 (en) * 2014-04-04 2015-10-08 Emerson Climate Technologies, Inc. Compressor temperature control systems and methods
US10180138B2 (en) 2014-04-04 2019-01-15 Emerson Climate Technologies, Inc. Compressor temperature control systems and methods
CN105526670A (en) * 2014-10-15 2016-04-27 力博特公司 Apparatus and method for subcooling control based on superheat setpoint control
CN105526670B (en) * 2014-10-15 2021-06-15 维谛公司 Apparatus and method for subcooling control based on superheat set point control
CN106813322A (en) * 2015-11-30 2017-06-09 青岛海尔空调电子有限公司 A kind of air conditioning pressure protection system and air conditioner refrigerating, heat pressure guard method
CN106813322B (en) * 2015-11-30 2019-08-20 青岛海尔空调电子有限公司 A kind of air conditioning pressure protection system and air conditioner refrigerating, heating pressure protection method
CN114739081A (en) * 2022-03-29 2022-07-12 青岛海尔空调电子有限公司 Air conditioning unit control method and system and air conditioning unit
CN114739081B (en) * 2022-03-29 2024-08-09 青岛海尔空调电子有限公司 Air conditioning unit control method and control system and air conditioning unit

Also Published As

Publication number Publication date
JP2009229012A (en) 2009-10-08
US20110011125A1 (en) 2011-01-20
WO2009119023A1 (en) 2009-10-01
EP2261580A1 (en) 2010-12-15

Similar Documents

Publication Publication Date Title
CN101978227A (en) Refrigeration apparatus
CN101960232B (en) Refrigeration device
CN101981389B (en) Refrigerating device
EP2496897B1 (en) Pressure spike reduction for refrigerant systems incorporating a microchannel heat exchanger
CN100380059C (en) Multi-air conditioning system and valve opening controlling method thereof
CN102734971B (en) Refrigeration device
KR100837498B1 (en) Freezing apparatus
TWI573969B (en) Cascade floating intermediate temperature heat pump system
US7600390B2 (en) Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor
CN103038584B (en) Air conditioning device
CN108139132B (en) Method for controlling a vapor compression system with variable receiver pressure set point
EP1637818B1 (en) Refrigerator
CN112283903B (en) Air conditioner and control method of expansion valve
CN103380334B (en) Freezing cycle device
WO2004063642A1 (en) Refrigeration apparatus
DK1938028T3 (en) Automatiseret styring til ventilator og kølemiddelsystem
CN101512248A (en) Air conditioner
CN101765749A (en) Refrigeration cycle device
EP1614983A2 (en) Air conditioner
US11137164B2 (en) Control systems and methods for heat pump systems
EP3104102B1 (en) Air conditioner and operation method of the same
KR100758901B1 (en) Multi-type air conditioner
KR101250551B1 (en) Air conditioner and control method of the same
JP6507598B2 (en) Air conditioning system
JP2003042582A (en) Freezing cycle device

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C02 Deemed withdrawal of patent application after publication (patent law 2001)
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20110216