CN101275789A - Refrigerating apparatus - Google Patents
Refrigerating apparatus Download PDFInfo
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- CN101275789A CN101275789A CNA2008100992162A CN200810099216A CN101275789A CN 101275789 A CN101275789 A CN 101275789A CN A2008100992162 A CNA2008100992162 A CN A2008100992162A CN 200810099216 A CN200810099216 A CN 200810099216A CN 101275789 A CN101275789 A CN 101275789A
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Abstract
The invention relates to a refrigeration unit, comprising: a refrigerant circuit (20) which is provided with using side heat exchangers (101, 111, 131) and heat source side compressors (41, 42, 43) and makes refrigerating fluid process vapor-compression refrigeration cycle; and a cooling fluid loop which is provided with a supercool heat exchanger (210) and removes cooling fluid to a pump institution of the supercool heat exchanger (210). The refrigeration unit supercools the refrigerating fluid which is provided to the using side heat exchangers (101, 111, 131) in the supercool heat exchanger (210) via the cooling fluid. The refrigeration unit is characterized in that: the refrigeration unit comprises a controller (240) for controlling power consumption about the refrigerant circuit (20) and the power consumption about the cooling fluid loop; the controller (240) priority increases the power consumption about the cooling fluid loop relative to the refrigerant circuit (20) when load is increased.
Description
Patent application of the present invention is that international application no is that PCT/JP2005/014122, international filing date are on August 2nd, 2005, the application number that enters the China national stage is 200580001048.3, name is called the dividing an application of application for a patent for invention of " refrigerating plant ".
Technical field
The present invention relates to a kind of refrigerating plant with apparatus for supercooling, this apparatus for supercooling will be delivered to the cold-producing medium supercooling that utilizes the side machine from the heat source side machine.
Background technology
In the past, for example, open shown in the flat 10-185333 communique as the spy, comprise: have supercooling with the 1st refrigerant loop of heat exchanger with have the 2nd refrigerant loop that utilizes side heat exchanger and heat source side compressor, with the 2nd cold-producing medium supercooling of heat exchanger with the 2nd refrigerant loop, the refrigerating plant of seeking to increase refrigerating capacity is well-known by supercooling.
Be the air conditioner of this refrigerating plant, comprise outdoor unit, indoor units and supercooling unit.Specifically, this supercooling unit is set in the way of hydraulic fluid side connecting pipe of outer unit of junction chamber and indoor units, simultaneously, comprises the 1st refrigerant loop (cooling fluid circuit).This supercooling unit constitutes and allows the 1st cold-producing medium circulate in the 1st refrigerant loop to carry out kind of refrigeration cycle, the 2nd refrigerant cools of the air conditioner that will send into from the hydraulic fluid side connecting pipe in heat exchanger in the supercooling of the 1st refrigerant loop.And this supercooling unit hangs down the cold air ability that improves by the enthalpy drop that will deliver to the liquid refrigerant cooling of indoor units from the outdoor unit of air conditioner, and allow the liquid refrigerant of delivering to indoor units.
As mentioned above, above-mentioned supercooling unit is to be used for refrigerating plants such as auxiliary air conditioner machine, increases its refrigerating capacity.Therefore, not in the stopping of refrigerating plant, only do not make the situation of supercooling unit running.And, not having as the heating installation running of air conditioner yet, refrigerating plant makes the situation of supercooling unit running under the state as the heat pump action.Therefore, whether decision should make supercooling unit running, is to wait according to the operating condition of the refrigerating plant that the supercooling unit has been installed and outdoor gas temperature to judge.
So in above-mentioned air conditioner, the control part of the control part of supercooling unit and air conditioner linked together constitutes a control system.Signal from the control part of air conditioner to the control part input of this supercooling unit that represent the operating condition of air conditioner from.And, in this supercooling unit, carry out its running control according to the signal of importing from the control part of air conditioner.
But, in above-mentioned air conditioner (refrigerating plant) in the past, when load increases because of the rising of outdoor gas temperature etc., allow the compressor operation capacity increase of the 2nd refrigerant loop usually, guarantee the cold air ability.
But if only allow circulating mass of refrigerant increase in the 2nd bigger refrigerant loop of the height pressure reduction of kind of refrigeration cycle, then the input for compressor increases the phenomenon that causes the coefficient of performance to reduce sometimes.Its result has the problem that the power consumption of whole device obviously increases.
And, when to contract demand when restricted, particularly from summer electrification excessive, strong request is limited in the summation of electric power that uses in the 1st refrigerant loop and the electric power that uses in the 2nd refrigerant loop.
Summary of the invention
In view of the premises, the objective of the invention is to: by being adjusted in heat source side loop and supercooling balance, allow whole refrigerating plant more effectively turn round, suppress the power consumption of whole device with running capacity in the loop.
The solution that the present invention studied is as follows.
Specifically, the 1st solution is to be prerequisite with such refrigerating plant, comprising: have the side of utilization heat exchanger 101,111,131 and heat source side compressor 41,42,43, the refrigerant loop 20 that allows cold-producing medium circulate to carry out the steam compression type refrigerating circulation; And has supercooling with heat exchanger 210 with will cool off with the fluid conveyance to the cooling fluid circuit 220 of this supercooling with the pump machanism 221 of heat exchanger 210, this refrigerating plant will offer the above-mentioned side heat exchanger 101 that utilizes by cooling with fluid, 111,131 cold-producing medium is in above-mentioned supercooling supercooling in the heat exchanger 210, it is characterized in that: comprise controller 240, this controller 240 is under the condition that does not receive from the signal of above-mentioned refrigerant loop 20, according to the cooling fluid state of using fluid circuit 220 with the refrigerant condition or the cooling of the refrigerant loop 20 that flows in the heat exchanger 210 in above-mentioned supercooling, with outdoor gas temperature, reduce the power consumption of said pump mechanism 221, above-mentioned cooling fluid circuit is to have as the supercooling of pump machanism with compressor 221 and heat source side heat exchanger 222, the supercooling usefulness refrigerant loop 220 that circulates and carry out the steam compression type refrigerating circulation with cold-producing medium with the supercooling of fluid as cooling; Above-mentioned controller 240, constitute supercooling refrigerant condition and the outdoor gas temperature of using refrigerant loop 220 with the refrigerant condition or the supercooling of the refrigerant loop 20 that flows in the heat exchanger 210 according in above-mentioned supercooling, reduce the operating frequency of above-mentioned supercooling, reduce the power consumption of this supercooling thus with compressor 221 with compressor 221.
In above-mentioned solution, use in the refrigerant loop 220 in supercooling, repeat such circulation: from supercooling with the supercooling of compressor 221 ejection with cold-producing medium heat source side heat exchanger 222 for example with air heat exchange, then, supercooling with in the heat exchanger 210 with the cold-producing medium heat exchange of refrigerant loop 20, turn back to supercooling again with compressor 221.With in the heat exchanger 210, supercooling is with cold-producing medium heat absorption and the evaporation of cold-producing medium from refrigerant loop 20, with the refrigerant cools of refrigerant loop 20 in supercooling.
And, controller 240, be not subjected to the signal of relevant operating condition from refrigerant loop 20 side joints, according to supercooling refrigerant condition and the outdoor gas temperature of using refrigerant loop 220 with the refrigerant condition or the supercooling of the refrigerant loop 20 that flows in the heat exchanger 210 in supercooling, reduce the operating frequency of supercooling, allow running capacity reduce with compressor 221.
The 2nd solution is to be prerequisite with such refrigerating plant, comprising: have the side of utilization heat exchanger 101,111,131 and heat source side compressor 41,42,43, the refrigerant loop 20 that allows cold-producing medium circulate to carry out the steam compression type refrigerating circulation; And has supercooling with heat exchanger 210 with will cool off with the fluid conveyance to the cooling fluid circuit 220 of this supercooling with the pump machanism 221 of heat exchanger 210, this refrigerating plant will offer the above-mentioned side heat exchanger 101 that utilizes by cooling with fluid, 111,131 cold-producing medium is in above-mentioned supercooling supercooling in the heat exchanger 210, it is characterized in that: comprise controller 240, this controller 240 is under the condition that does not receive from the signal of above-mentioned refrigerant loop 20, according to the cooling fluid state of using fluid circuit 220 with the refrigerant condition or the cooling of the refrigerant loop 20 that flows in the heat exchanger 210 in above-mentioned supercooling, with outdoor gas temperature, reduce the power consumption of said pump mechanism 221, above-mentioned cooling fluid circuit is to have as the supercooling of pump machanism with compressor 221 and heat source side heat exchanger 222, the supercooling usefulness refrigerant loop 220 that circulates and carry out the steam compression type refrigerating circulation with cold-producing medium with the supercooling of fluid as cooling; Above-mentioned controller 240, constitute supercooling refrigerant condition and the outdoor gas temperature of using refrigerant loop 220 with the refrigerant condition or the supercooling of the refrigerant loop 20 that flows in the heat exchanger 210 according in above-mentioned supercooling, increase the operating frequency of the fan 230 of above-mentioned heat source side heat exchanger 222, reduce the power consumption of above-mentioned supercooling thus with compressor 221.
In above-mentioned solution, use in the refrigerant loop 220 in supercooling, repeat such circulation: the air heat exchange that heat source side heat exchanger 222 and by fan 230, is taken into cold-producing medium with the supercooling of compressor 221 ejection from supercooling, then, supercooling with in the heat exchanger 210 with the cold-producing medium heat exchange of refrigerant loop 20, turn back to supercooling again with compressor 221.
And, controller 240, according to supercooling refrigerant condition and the outdoor gas temperature of using refrigerant loop 220 with the refrigerant condition or the supercooling of the refrigerant loop 20 that flows in the heat exchanger 210 in supercooling, increase the operating frequency of the fan 230 of heat source side heat exchanger 222, allow air quantity increase.At that time, do not allow supercooling change with the running capacity of compressor 221.So, because supercooling uses the supercooling in the refrigerant loop 220 to use the high-pressure of cold-producing medium to descend, so supercooling reduces this supercooling power consumption reduction of compressor 221 with the compression load in the compressor 221.That is to say, with in the compressor 221, spray the workload that pressure reduces compression by reducing in supercooling.
The 3rd solution be the above-mentioned the 1st or the basis of the 2nd solution on, in the refrigerant condition of above-mentioned supercooling, be the supercooling degree of supercooling with the cold-producing medium of the refrigerant loop 20 in the heat exchanger 210 with the refrigerant loop 20 that flows in the heat exchanger 210.
In above-mentioned solution, will detect as the supercooling degree by the refrigerant temperature of the refrigerant loop before the supercooling 20 with by the difference of the refrigerant temperature of the refrigerant loop 20 after the supercooling in heat exchanger 210 in supercooling.And, infer in the refrigerant condition of supercooling with the refrigerant loop 20 that flows the heat exchanger 210 from this supercooling degree.
Specifically, when the supercooling degree is big, from in the cold-producing medium sufficiently cooled phenomenon of supercooling, can judge from refrigerant loop 20 inflow supercooling less with the refrigerant flow of the refrigerant loop 20 of heat exchanger 210 with refrigerant loop 20 heat exchanger 210.Controller 240 can be less from inferring the power consumption that about refrigerant loop 20 here.At this moment, do not reduce the power consumption of pump machanism 221.And at the supercooling degree hour, from supercooling with heat exchanger 210 cold-producing medium of refrigerant loop 20 do not have sufficiently cooled phenomenon, can judge that to flow into supercooling from refrigerant loop 20 more with the refrigerant flow of the refrigerant loop 20 of heat exchangers 210.Can be bigger from inferring the power consumption that about refrigerant loop 20 here.At this moment, controller 240 reduces the power consumption of pump machanism 221, is suppressed in the setting with the power consumption of pump machanism 221 with about the total of the power consumption of refrigerant loop 20.
The 4th solution be the above-mentioned the 1st or the basis of the 2nd solution on, in the refrigerant condition of above-mentioned supercooling, be at the refrigerant flow of supercooling with the refrigerant loop 20 that flows in the heat exchanger 210 with the refrigerant loop 20 that flows in the heat exchanger 210.
In above-mentioned solution, directly will detect at the refrigerant flow that supercooling is flowed in heat exchanger 210.Infer from this refrigerant flow in the refrigerant condition of supercooling with the refrigerant loop 20 that flows the heat exchanger 210.And controller 240 according to this refrigerant flow and outdoor gas temperature, reduces the power consumption of pump machanism 221, is suppressed in the setting with the power consumption of pump machanism 221 with about the total of the power consumption of refrigerant loop 20.
The 5th solution be the above-mentioned the 1st or the basis of the 2nd solution on, above-mentioned cooling is with the cooling fluid state of fluid circuit 220, for supercooling with in the heat exchanger 210 with the cold-producing medium supercooling of refrigerant loop 20 before and cooling after the supercooling temperature difference of fluid.
In above-mentioned solution, detect the temperature difference of before cooling is with supercooling in the fluid circuit 220, using fluid with supercooling cooling afterwards.Infer with the temperature difference of fluid from this cooling in the refrigerant condition of supercooling with the refrigerant loop 20 that flows the heat exchanger 210.
Specifically, when the temperature difference of cooling off the usefulness fluid is big, from in the cold-producing medium sufficiently cooled phenomenon of supercooling, can judge in supercooling less with the refrigerant flow of the refrigerant loop 20 that flows in the heat exchanger 210 with refrigerant loop 20 heat exchanger 210.Therefore, controller 240 infers that the power consumption that about refrigerant loop 20 is less, does not reduce the power consumption of pump machanism 221.And in cooling with the temperature difference of fluid hour, from supercooling with heat exchanger 210 cold-producing medium of refrigerant loop 20 do not have sufficiently cooled phenomenon, can judge in supercooling more with the refrigerant flow of the refrigerant loop 20 that flows in the heat exchanger 210.Therefore, controller 240 infers that the power consumption that about refrigerant loop 20 is bigger, reduces the power consumption of pump machanism 221, is suppressed in the setting with the power consumption of pump machanism 221 with about the total of the power consumption of refrigerant loop 20.
The 6th solution be the above-mentioned the 1st or the basis of the 2nd solution on, above-mentioned cooling is with the cooling fluid state of fluid circuit 220, is with the flow of the cooling of flowing in the heat exchanger 210 with fluid in supercooling.
In above-mentioned solution, from using the cooling of flowing the heat exchanger 210 flow of fluid in supercooling, infer in the refrigerant condition of supercooling with the refrigerant loop 20 that flows in the heat exchanger 210.Specifically, when cooling with the flow of fluid more after a little while, can judge in supercooling also less with the refrigerant flow that flows in the heat exchanger 210.At this moment, controller 240 infers that the power consumption that about refrigerant loop 20 is less, does not reduce the power consumption of pump machanism 221.And when cooling with the flow of fluid more for a long time, can judge in supercooling also more with the refrigerant flow that flows in the heat exchanger 210.At this moment, controller 240 infers that the power consumption that about refrigerant loop 20 is bigger, reduces the power consumption of pump machanism 221, is suppressed in the setting with the power consumption of pump machanism 221 with about the total of the power consumption of refrigerant loop 20.
The 7th solution be the above-mentioned the 1st or the basis of the 2nd solution on, above-mentioned cooling fluid circuit is to have as the supercooling of pump machanism with compressor 221 and heat source side heat exchanger 222, the supercooling usefulness refrigerant loop 220 that circulates and carry out the steam compression type refrigerating circulation with cold-producing medium with the supercooling of fluid as cooling.And the supercooling refrigerant condition of above-mentioned supercooling usefulness refrigerant loop 220 is the high-pressure of supercooling with the usefulness of the supercooling in the refrigerant loop 220 cold-producing medium.
In above-mentioned solution, infer with the high-pressure of cold-producing medium in the refrigerant condition of supercooling with the refrigerant loop 20 that flows the heat exchanger 210 from supercooling.That is to say that when its high-pressure is low, judges supercooling and tail off with the heat exchange amount in the heat exchanger 210, the refrigerant flow of refrigerant loop 20 is less, infers that the power consumption that about refrigerant loop 20 is less.And, when high-pressure is higher, controller 240, it is many with the heat exchange quantitative change in the heat exchanger 210 to judge supercooling, and the refrigerant flow of refrigerant loop 20 is more, infers that the power consumption that about refrigerant loop 20 is bigger.Therefore, reduce the power consumption of supercooling with compressor 221.
The 8th solution be the above-mentioned the 1st or the basis of the 2nd solution on, above-mentioned cooling fluid circuit is to have as the supercooling of pump machanism with compressor 221 and heat source side heat exchanger 222, the supercooling usefulness refrigerant loop 220 that circulates and carry out the steam compression type refrigerating circulation with cold-producing medium with the supercooling of fluid as cooling.And the supercooling refrigerant condition of above-mentioned supercooling usefulness refrigerant loop 220 is the supercooling high-pressure of the supercooling usefulness cold-producing medium in the refrigerant loop 220 and the pressure differential of low pressure.
In above-mentioned solution, infer with the high-pressure of cold-producing medium and the pressure differential of low pressure in the refrigerant condition of supercooling with the refrigerant loop 20 that flows the heat exchanger 210 from supercooling.Specifically, when its pressure differential hour, because low pressure almost is maintained by expansion valve etc. and immobilizes, it is low when general therefore to judge high-pressure, judges in supercooling less with the refrigerant flow of the refrigerant loop 20 that flows in the heat exchanger 210.Therefore, infer that the power consumption that about refrigerant loop 20 is less.And, when pressure differential is big, judge high-pressure height when general, judge in supercooling more with the refrigerant flow of the refrigerant loop 20 that flows in the heat exchanger 210.And, infer that the power consumption that about refrigerant loop 20 is bigger, supercooling reduces with the power consumption of compressor 221.
The 9th solution is to be prerequisite with such refrigerating plant, comprising: have the side of utilization heat exchanger 101,111,131 and heat source side compressor 41,42,43, the refrigerant loop 20 that allows cold-producing medium circulate to carry out the steam compression type refrigerating circulation; And has supercooling with heat exchanger 210 with will cool off with the fluid conveyance to the cooling fluid circuit of this supercooling with the pump machanism of heat exchanger 210.This refrigerating plant utilization cooling will offer the above-mentioned cold-producing medium of side heat exchanger 101,111,131 that utilizes in above-mentioned supercooling supercooling in the heat exchanger 210 with fluid.
And, comprising controller 240, control is about the power consumption of above-mentioned refrigerant loop 20 with about the power consumption of above-mentioned cooling with fluid circuit.And above-mentioned controller 240 when load increases, with respect to above-mentioned refrigerant loop 20, preferentially allows increase about the power consumption of above-mentioned cooling with fluid circuit.
In above-mentioned solution, with in the fluid circuit, will offer supercooling usefulness heat exchanger 210 with fluid in order to coolings such as the cold-producing medium of the cold-producing medium of supercooling refrigerant loop 20 and water by pump machanism 221 in cooling.With in the heat exchanger 210, the cold-producing medium of refrigerant loop 20 and cooling exchange with fluid thermal in supercooling.And with in the heat exchanger 210, cooling is with the cold-producing medium heat absorption of fluid from refrigerant loop 20, with the refrigerant cools of refrigerant loop 20 in supercooling.
In this refrigerating plant, when increasing when loading, controller 240 carries out preferentially allowing cooling control with the running of the power consumption increase of fluid circuit with respect to refrigerant loop 20.For example, allow the running capacity of pump machanism increase, make about the power consumption of cooling to increase with fluid circuit.That is to say, with in the fluid circuit,, increase refrigerating capacity by allowing the workload of electrical equipment such as pump machanism increase in cooling.So, even do not allow the power consumption (that is, workload) of the electrical equipment such as heat source side compressor 41,42,43 in the refrigerant loop 20 increase, supercooling also increases with the refrigerating capacity of heat exchanger 210.Therefore,, also be held lower, guaranteed in the refrigerating capacity of utilizing side heat exchanger 101,111,131 towards the enthalpy of the cold-producing medium of the refrigerant loop 20 that utilizes side heat exchanger 101,111,131 even when the load of refrigerating plant increases.
The 10th solution is on the basis of above-mentioned the 9th solution, above-mentioned controller 240, constitute control about the power consumption of above-mentioned cooling with fluid circuit, so that above-mentioned supercooling becomes desired value with the refrigerant temperature in the outlet of heat exchanger 210, and set above-mentioned desired value with the ambient conditions of heat exchanger 210 according to supercooling, so that when load increases, preferentially allow increase about the power consumption of above-mentioned cooling with fluid circuit.
In above-mentioned solution, controller 240 is regulated the desired value of supercooling with the refrigerant outlet temperature of heat exchanger 210 according to the supercooling such as refrigerant flow of outdoor gas temperature and refrigerant loop 20 with the ambient conditions of heat exchanger 210.That is to say that controller 240 is held the load condition of refrigerating plant from supercooling with the ambient conditions of heat exchanger 210, sets above-mentioned desired value according to its load condition.Therefore, corresponding with its load when load increases, with respect to refrigerant loop 20, allow cooling preferentially increase with the power consumption of fluid circuit.
The 11st solution is on the basis of above-mentioned the 9th solution, and above-mentioned controller 240 constitutes by allowing the power consumption of pump machanism increase, and allows preferentially increase about the power consumption of cooling off with fluid circuit.
In above-mentioned solution, controller 240 allows the running capacity of pump machanism increase, and the power consumption of this pump machanism is increased.That is to say, with in the fluid circuit, allow offer the supercooling quantity delivered increase of the cooling of heat exchanger 210, increase the refrigerating capacity of supercooling with heat exchanger 210 with fluid in cooling.
The 12nd solution is on the basis of above-mentioned the 11st solution, above-mentioned cooling fluid circuit be have the supercooling that constitutes pump machanism with compressor 221 and heat source side heat exchanger 222, be provided as the supercooling usefulness refrigerant loop 220 that supercooling that cooling uses with fluid circulates and carries out the steam compression type refrigerating circulation with cold-producing medium.And above-mentioned controller 240 constitutes by allowing above-mentioned supercooling increase with the operating frequency of compressor 221, allows this supercooling increase with the power consumption of compressor 221.
In above-mentioned solution, use in the refrigerant loop 220 in supercooling, repeat such circulation: from supercooling with the supercooling of compressor 221 ejection with cold-producing medium heat source side heat exchanger 222 for example with air heat exchange, then, supercooling with in the heat exchanger 210 with the cold-producing medium heat exchange of refrigerant loop 20, turn back to supercooling again with compressor 221.Absorb heat and evaporation with the cold-producing medium of cold-producing medium with supercooling in the heat exchanger 210 in supercooling, with the refrigerant cools of refrigerant loop 20 from refrigerant loop 20.
In this refrigerating plant, when load increases, allow supercooling increase with the operating frequency (that is running capacity) of compressor 221, allow this supercooling increase, so that supercooling becomes desired value with the outlet refrigerant temperature of heat exchanger 210 with the power consumption of compressor 221.That is to say that with in the heat exchanger 210, supercooling increases with the flow of cold-producing medium in supercooling, refrigerating capacity improves.
The 13rd solution is on the basis of above-mentioned the 9th solution, above-mentioned cooling fluid circuit be have the supercooling that constitutes pump machanism with compressor 221 and heat source side heat exchanger 222, be provided as the supercooling usefulness refrigerant loop 220 that supercooling that cooling uses with fluid circulates and carries out the steam compression type refrigerating circulation with cold-producing medium.And above-mentioned controller 240 constitutes by allowing the operating frequency of fan 230 of above-mentioned heat source side heat exchanger 222 increase, and allows preferentially increase about the power consumption of above-mentioned supercooling with refrigerant loop 220.
In above-mentioned solution, use in the refrigerant loop 220 in supercooling, repeat such circulation: the air heat exchange that heat source side heat exchanger 222 and by fan 230, is taken into cold-producing medium with the supercooling of compressor 221 ejection from supercooling, then, supercooling with in the heat exchanger 210 with the cold-producing medium heat exchange of refrigerant loop 20, turn back to supercooling again with compressor 221.
In this refrigerating plant, when load increases, allow the operating frequency of fan 230 of heat source side heat exchanger 222 increase, increase the power consumption of this fan 230.At that time, do not allow supercooling change with the running capacity of compressor 221.Here, after allowing the operating frequency of fan 230 increase, supercooling reduces with the high-pressure of the supercooling in the refrigerant loop 220 with cold-producing medium, and supercooling is risen with the volume efficiency of compressor 221, increases with the flow of the supercooling of flowing in the heat exchanger 210 with cold-producing medium in supercooling.So, supercooling increases with the refrigerating capacity of heat exchanger 210.That is to say, allow the workload of fan 230 increase, improve refrigerating capacity.
The 14th solution is on the basis of above-mentioned the 10th solution, and above-mentioned supercooling is outdoor gas temperature with the ambient conditions of heat exchanger 210.
In above-mentioned solution, set the desired value of supercooling with the outlet refrigerant temperature of heat exchanger 210 according to outdoor gas temperature.That is to say that controller 240 is inferred the load condition of refrigerating plant according to outdoor gas temperature, after its outdoor gas temperature uprises, judges load and increases.
The 15th solution is on the basis of above-mentioned the 10th solution, and above-mentioned supercooling is the supercooling degree of this supercooling with the cold-producing medium of the refrigerant loop 20 in the heat exchanger 210 with the ambient conditions of heat exchanger 210.
In above-mentioned solution, set the desired value of supercooling with the outlet refrigerant temperature of heat exchanger 210 according to the supercooling degree of the cold-producing medium of refrigerant loop 20.That is to say that controller 240 is inferred the load condition of refrigerating plant according to the supercooling degree of cold-producing medium, after its supercooling degree diminishes, judges load and increases.At this moment, for example, set desired value lower.
The 16th solution is on the basis of above-mentioned the 10th solution, and above-mentioned supercooling is with the ambient conditions of heat exchanger 210, for use the refrigerant flow of the refrigerant loop 20 that flows in the heat exchanger 210 in this supercooling.
In above-mentioned solution, set the desired value of supercooling with the refrigerant flow of heat exchanger 210 with the outlet refrigerant temperature of heat exchanger 210 according to supercooling.That is to say that controller 240 is inferred the load condition of refrigerating plant according to supercooling with the refrigerant flow of heat exchanger 210, after how its refrigerant flow becomes, judge load and increase.At that time, for example, set desired value lower.
The 17th solution is on the basis of above-mentioned the 10th solution, above-mentioned supercooling is with the ambient conditions of heat exchanger 210, for this supercooling with in the heat exchanger 210 with the cold-producing medium supercooling of refrigerant loop 20 before and cooling after the supercooling with the cooling of fluid circuit temperature difference with fluid.
In above-mentioned solution, set the desired value of supercooling with the temperature difference before and after the supercooling of fluid with the outlet refrigerant temperature of heat exchanger 210 according to cooling.That is to say that controller 240 is inferred the load condition of refrigerating plant according to the temperature difference before and after the supercooling of cooling fluid, after its temperature difference diminishes, judges load and increases.At that time, for example, set desired value lower.
The 18th solution is on the basis of above-mentioned the 10th solution, and above-mentioned supercooling is with the ambient conditions of heat exchanger 210, for use the flow of fluid with the cooling of fluid circuit with the cooling of flowing in the heat exchanger 210 in this supercooling.
In above-mentioned solution, set the desired value of supercooling with the cooling of heat exchanger 210 with the flow of fluid with the outlet refrigerant temperature of heat exchanger 210 according to supercooling.That is to say that controller 240 according to cooling off the load condition of inferring refrigerating plant with the flow of fluid, after how its flow becomes, is judged load and increased.At that time, for example, set desired value lower.
The 19th solution is on the basis of above-mentioned the 10th solution, above-mentioned cooling fluid circuit is to have as the supercooling of pump machanism with compressor 221 and heat source side heat exchanger 222, the supercooling usefulness refrigerant loop 220 that circulates and carry out the steam compression type refrigerating circulation with cold-producing medium with the supercooling of fluid as cooling.And the ambient conditions of above-mentioned supercooling usefulness heat exchanger 210 is the high-pressure of supercooling with the usefulness of the supercooling in the refrigerant loop 220 cold-producing medium.
In above-mentioned solution, set the desired value of supercooling with the supercooling of refrigerant loop 220 with the high-pressure of cold-producing medium with the outlet refrigerant temperature of heat exchanger 210 according to supercooling.That is to say that controller 240 is inferred the load condition of refrigerating plant according to supercooling with the high-pressure of cold-producing medium, after its high-pressure uprises, judges load and increases.At that time, for example, set desired value lower.
The 20th solution is on the basis of above-mentioned the 10th solution, above-mentioned cooling fluid circuit is to have as the supercooling of pump machanism with compressor 221 and heat source side heat exchanger 222, the supercooling usefulness refrigerant loop 220 that circulates and carry out the steam compression type refrigerating circulation with cold-producing medium with the supercooling of fluid as cooling.And the ambient conditions of above-mentioned supercooling usefulness heat exchanger 210 is the supercooling high-pressure of the supercooling usefulness cold-producing medium in the refrigerant loop 220 and the pressure differential of low pressure.
In above-mentioned solution, set the desired value of supercooling with the supercooling of refrigerant loop 220 with the high-pressure of cold-producing medium and the pressure differential of low pressure with the outlet refrigerant temperature of heat exchanger 210 according to supercooling.That is to say that controller 240 is inferred the load condition of refrigerating plant according to supercooling with the height pressure reduction of cold-producing medium, its height pressure reduction become big after, judge load and increase.At that time, for example, set desired value lower.
The 21st solution is on the basis of above-mentioned the 14th solution, and above-mentioned controller 240 constitutes along with outdoor gas temperature uprises and makes above-mentioned desired value lower.
In above-mentioned solution, if outdoor gas temperature uprises, then the phenomenon of the load of refrigerating plant increase is set out, even hypothesis does not change desired value, for supercooling is remained desired value with the outlet refrigerant temperature of heat exchanger 210, also must for example allow the running capacity of pump machanism increase.On the other hand, in this solution, along with outdoor gas temperature uprises, controller 240 reduces desired value.And, be lower desired value in order to make supercooling with the outlet refrigerant temperature of heat exchanger 210, must further allow the running capacity of pump machanism increase, that is to say, allow the cooling of pump machanism use the supply workload of fluid to increase.Therefore, in the present invention, when the rising because of outdoor gas temperature, when the load of refrigerating plant increased, controller 240 preferentially increased about the power consumption of cooling with fluid circuit by regulating desired value.
-effect-
Therefore, according to the 1st solution, controller 240 according at refrigerant condition or the cooling cooling of fluid circuit 220 state and the outdoor gas temperature with fluid of supercooling with the refrigerant loop 20 that flows in the heat exchanger 210, reduces the power consumption of pump machanism 221.Therefore, controller 240 can be under situation about not being subjected to from refrigerant loop 20 side joints about the signal of the operating condition of refrigerant loop 20, reduces the power consumption of the pump machanism 221 of compressor etc.So, can make about the power consumption of cooling and reduce, suppress the power consumption of whole refrigerating plant with fluid circuit 220.Its result can positively turn round in the contract electric weight.
And, when adhering to after the usefulness when being contained in refrigerating plant with fluid circuit 220 cooling, communication in order to the signal of giving and accepting needn't be set between refrigerant loop 20 and cooling are with fluid circuit 220 with connecting up.Therefore, can cut down in order to the operation number of cooling with fluid circuit 220 to be installed, in the accident that can also the people when possible trouble prevents because of misroute etc. operation to be set causes, allow refrigerating capacity improve for fault.
And,,, therefore can positively hold about the reduction of cooling with the power consumption of fluid circuit 220 owing to wait the power consumption of inferring relevant refrigerant loop 20 according to the refrigerant condition of refrigerant loop 20 according to the 2nd solution.So, can positively in the contract electric weight, turn round.
And,,, be higher than the evaporating temperature of the cold-producing medium in utilizing side heat exchanger 101,111,131 in the endothermic temperature or the evaporating temperature of supercooling with the usefulness of the cooling in the heat exchanger 210 fluid according to the 9th solution.The cooling cooling of pump machanism 221 front and back of the fluid circuit 220 height pressure reduction of fluid is less than the height pressure reduction of the kind of refrigeration cycle in the refrigerant loop 20.And, refrigerating plant of the present invention, for not being allows circulating mass of refrigerant increase in the bigger refrigerant loop 20 of height pressure reduction, but allow cooling increase in fluid circuit 220 with the flow of fluid in the littler cooling of height pressure reduction, and the power consumption (workload) of increase pump machanism 221 grades, preferential increasing about the power consumption of cooling with fluid circuit 220.That is to say,, come increase corresponding to load by the workload of less pump machanism 221 grades of the original burden of preferential increase.Therefore, can suppress reduction that can the rejection coefficient for increase corresponding to the required input of increase of load.Its result can suppress the increase of the power consumption of whole refrigerating plant.
And, according to the 10th solution, come the target setting value with the ambient conditions of heat exchanger 210 according to the supercooling of outdoor gas temperature and refrigerant flow etc., so as when load to increase preferential the increase about the power consumption of cooling with fluid circuit 220.Therefore, can positively increase about the power consumption of cooling with fluid circuit 220 according to load condition is preferential.
And, infer the load condition of refrigerating plant owing to only being used in cooling with the information that obtains in the fluid circuit 220, so the communication wiring in order to the signal of giving and accepting at refrigerant loop 20 with between cooling off with fluid circuit 220 needn't be set.
And, according to the 12nd or the 13rd solution,, just can allow supercooling increase at an easy rate with the power consumption of refrigerant loop 220 only by regulating the running capacity of supercooling with compressor 221 or fan 230, can suppress the power consumption of whole refrigerating plant.
And,,,, allow cooling preferentially increase with the power consumption of pump machanism 221 grades of fluid circuit 220 with respect to the heat source side compressor 41,42,43 of refrigerant loop 20 etc. along with outdoor gas temperature uprises according to the 21st solution.So,, the reduction of the coefficient of performance of refrigerating plant can be easier and more effectively suppressed, the increase of whole power consumption can be suppressed from can further increasing about the power consumption of cooling with fluid circuit 220 according to load condition is preferential.
The simple declaration of accompanying drawing
Fig. 1 is the piping diagram that shows the structure of the refrigerating plant that comprises the supercooling unit.
Fig. 2 is the piping diagram of the action when showing the cold air operation of refrigerating plant.
Fig. 3 is the piping diagram of action that shows heating installation when running of refrigerating plant.
Fig. 4 is the coordinate diagram that shows the electric quantity change of the outdoor unit among the 1st embodiment.
Fig. 5 is the coordinate diagram that shows the electric quantity change of the outdoor unit in the variation of the 1st embodiment.
Fig. 6 is the flow chart that shows the running control of the controller among the 4th embodiment.
Fig. 7 is the coordinate diagram that shows the target liq refrigerant outlet temperature among the 4th embodiment.
The specific embodiment
Below, with reference to accompanying drawing embodiments of the invention are described in detail.
(the 1st embodiment)
The refrigerating plant 10 of this 1st embodiment is arranged in the convenience store etc., carries out the cooling that air is in harmonious proportion and showcase the is interior shop in.As shown in Figure 1, above-mentioned refrigerating plant 10 has supercooling with heat exchanger 210 and supercooling compressor 221, comprises as the cooling supercooling refrigerant loop 220 of the supercooling of fluid with flow of refrigerant; Utilize side heat exchanger 101,111,131 and refrigerant loop 20 heat source side compressor 41,42,43, that allow flow of refrigerant with having.Refrigerating plant 10 constitutes the cold-producing medium that comes supercooling to flow with the supercooling of refrigerant loop 220 with heat exchanger 210 by supercooling in refrigerant loop 20.That is to say that supercooling constitutes cooling fluid circuit involved in the present invention with refrigerant loop 220.
Below, the structure of refrigerating plant 10 is specified.
In refrigerating plant 10, be provided with outdoor unit 11, air-conditioning unit 12, refrigerator display case 13, refrigerated display case 14, supercharging unit 15 and supercooling unit 200.In this refrigerating plant 10, outdoor unit 11 and supercooling unit 200 is provided with without, remaining air-conditioning unit 12 grades are arranged in the shop of convenience store etc.
Above-mentioned supercooling unit 200, comprise refrigerant passage 205, supercooling with refrigerant loop 220, supercooling with heat exchanger 210 with as the controller 240 of control device.
On the other hand, be provided with outdoor loop 40 at outdoor unit 11, be provided with air conditioner loop 100, be provided with refrigeration circuit 110 at refrigerator display case 13 at air-conditioning unit 12, be provided with refrigerating circuit 130 at refrigerated display case 14, be provided with boost-up circuit 140 at supercharging unit 15.In refrigerating plant 10, by with pipeline with these loops 40,100 ... link together to constitute with the refrigerant passage 205 of supercooling unit 200 and allow the refrigerant loop 20 of refrigerating plant 10 of flow of refrigerant.
And, be provided with the 1st hydraulic fluid side connecting pipe the 21, the 2nd hydraulic fluid side connecting pipe the 22, the 1st gas side connecting pipe 23 and the 2nd gas side connecting pipe 24 at refrigerant loop 20.
The 1st hydraulic fluid side connecting pipe 21 is connected an end of the refrigerant passage 205 of supercooling unit 200 on the outdoor loop 40.One end of the 2nd hydraulic fluid side connecting pipe 22 is connected the other end of refrigerant passage 205.The other end of the 2nd hydraulic fluid side connecting pipe 22 is divided into 3 branches, is connected on air conditioner loop 100, refrigeration circuit 110 and the refrigerating circuit 130.The branch pipe that is connected refrigerating circuit 130 in the 2nd hydraulic fluid side connecting pipe 22 is provided with hydraulic fluid side shut off valve 25.
One end of the 1st gas side connecting pipe 23 is divided into two branches, is connected on refrigeration circuit 110 and the boost-up circuit 140.The branch pipe that is connected boost-up circuit 140 in the 1st gas side connecting pipe 23 is provided with gas side shut off valve 26.The other end of the 1st gas side connecting pipe 23 is connected on the outdoor loop 40.The 2nd gas side connecting pipe 24 is connected air conditioner loop 100 on the outdoor loop 40.
＜outdoor unit 〉
Be provided with variable displacement compressor the 41, the 1st fixed-capacity compressor 42 and the 2nd fixed-capacity compressor 43 as the heat source side compressor in outdoor loop 40.And, be provided with outdoor heat converter 44, reservoir (receiver) 45 and outdoor expansion valve 46 in outdoor loop 40.And, be provided with 81,82,83,84 and high-pressure gas pipes 66 of 64,65,4 liquid lines of 61,62,63, two bleed pipes of 3 suction lines in outdoor loop 40.And, be provided with 51,52,53, hydraulic fluid side shut off valves 54 of 3 No. four transfer valves and two gas side shut off valves 55,56 in outdoor loop 40.
In this outdoor loop 40, the 1st hydraulic fluid side connecting pipe 21 is connected on the hydraulic fluid side shut off valve 54, the 1st gas side connecting pipe 23 is connected on the 1st gas side shut off valve 55, the 2nd gas side connecting pipe 24 is connected on the 2nd gas side shut off valve 56.
Variable displacement compressor the 41, the 1st fixed-capacity compressor 42 and the 2nd fixed-capacity compressor 43 all are Totally-enclosed-types, high pressure dome type vortex-type compressor.Power to variable displacement compressor 41 by phase inverter (inverter).This variable displacement compressor 41 can change the rotary speed of air compressor motor by allowing the output frequency of phase inverter change, and changes its capacity.And the 1st, the 2nd fixed- capacity compressor 42,43 compressors that always under certain rotary speed, turn round for air compressor motor, its capacity can not change.
The 1st suction line 61, one end are connected on the 1st gas side shut off valve 55.The 1st suction line 61 branches into the 1st branch pipe 61a and the 2nd branch pipe 61b at the other end, and the 1st branch pipe 61a is connected the suction side of variable displacement compressor 41, and the 2nd branch pipe 61b is connected on the 3 No. four transfer valves 53.Be provided with the check valve CV-1 that only allows cold-producing medium to flow to the 3rd No. four transfer valves 53 from the 1st gas side shut off valve 55 at the 2nd branch pipe 61b of the 1st suction line 61.
The 2nd suction line 62, one end are connected on the 3 No. four transfer valves 53, and the other end is connected the suction side of the 1st fixed-capacity compressor 42.
The 3rd suction line 63, one end are connected on the 2 No. four transfer valves 52.This 3rd suction line 63 branches into the 1st branch pipe 63a and the 2nd branch pipe 63b at the other end, and the 1st branch pipe 63a is connected the suction side of the 2nd fixed-capacity compressor 43, and the 2nd branch pipe 63b is connected on the 3 No. four transfer valves 53.Be provided with the check valve CV-2 that only allows cold-producing medium to flow to the 3rd No. four transfer valves 53 from the 2 No. four transfer valves 52 at the 2nd branch pipe 63b of the 3rd suction line 63.
The 1st bleed pipe 64 at one end branches into the 1st branch pipe 64a and the 2nd branch pipe 64b, and the 1st branch pipe 64a is connected the ejection side of variable displacement compressor 41, and the 2nd branch pipe 64b is connected the ejection side of the 1st fixed-capacity compressor 42.The other end of the 1st bleed pipe 64 is connected on the 1 No. four transfer valves 51.Be provided with the check valve CV-3 that only allows cold-producing medium to flow to the 1st No. four transfer valves 51 from the 1st fixed-capacity compressor 42 at the 2nd branch pipe 64b of the 1st bleed pipe 64.
The 2nd bleed pipe 65, the one end is connected the suction side of the 2nd fixed-capacity compressor 43, and the other end is connected the positive front of the 1st No. four transfer valves 51 in the 1st bleed pipe 64.Be provided with the check valve CV-4 that only allows cold-producing medium to flow to the 1st No. four transfer valves 51 from the 2nd fixed-capacity compressor 43 at the 2nd bleed pipe 65.
An end of the 2nd liquid line 82 is connected the bottom of reservoir 45 by shut off valve 58.The other end of the 2nd liquid line 82 is connected on the hydraulic fluid side shut off valve 54.Be provided with the check valve CV-6 that only allows cold-producing medium to flow to hydraulic fluid side shut off valve 54 from reservoir 45 at the 2nd liquid line 82.
One end of the 3rd liquid line 83 is connected between the check valve CV-6 and hydraulic fluid side shut off valve 54 in the 2nd liquid line 82.The other end of the 3rd liquid line 83 is connected the top of reservoir 45 by the 1st liquid line 81.And, be provided with the check valve CV-7 that only allows cold-producing medium to flow to the other end from the one end at the 3rd liquid line 83.
One end of the 4th liquid line 84 is connected between the check valve CV-6 and shut off valve 58 in the 2nd liquid line 82.The other end of the 4th liquid line 84 is connected between the outdoor heat converter 44 and check valve CV-5 in the 1st liquid line 81.And,, be disposed with check valve CV-8 and outdoor expansion valve 46 from the one end towards the other end at the 4th liquid line 84.This check valve CV-8 only allows cold-producing medium to flow to the other end from an end of the 4th liquid line 84.And outdoor expansion valve 46 is made of electric expansion valve.
High-pressure gas pipe 66, one end are connected the positive front of the 1st No. four transfer valves 51 in the 1st bleed pipe 64.High-pressure gas pipe 66 branches into the 1st branch pipe 66a and the 2nd branch pipe 66b at the other end, and the 1st branch pipe 66a is connected the downstream side of the check valve CV-5 in the 1st liquid line 81, and the 2nd branch pipe 66b is connected on the 3 No. four transfer valves 53.The 1st branch pipe 66a at high-pressure gas pipe 66 is provided with magnetic valve SV-7 and check valve CV-9.This check valve CV-9 is arranged in the downstream side of magnetic valve SV-7, only allows cold-producing medium to flow to the 1st liquid line 81 from magnetic valve SV-7.
The 1 No. four transfer valve 51, the 1 passages (port) are connected the terminal of the 1st bleed pipe 64, and the 2nd passage is connected the 2 No. four transfer valve 52, the 3 passages and is connected outdoor heat converter 44, the 4 passages and is connected the 2nd gas side shut off valve 56.The 1 No. four transfer valves 51 can switch to the 1st state (state that Fig. 1 represents with solid line) and the 2nd state (state that Fig. 1 dots), wherein, described the 1st state is that the 1st passage and the 3rd passage are interconnected, the state that the 2nd passage and the 4th passage are interconnected, described the 2nd state is that the 1st passage and the 4th passage are interconnected, the state that the 2nd passage and the 3rd passage are interconnected.
The 2 No. four transfer valve 52, the 1 passages are connected the downstream side of the check valve CV-4 in the 2nd bleed pipe 65, and the 2nd passage is connected the initiating terminal of the 3rd suction line 63, and the 4th passage is connected the 2nd passage of the 1st No. four transfer valves 51.And the 3rd passage of the 2nd No. four transfer valves 52 is sealed.The 2 No. four transfer valves 52 can switch to the 1st state (state that Fig. 1 represents with solid line) and the 2nd state (state that Fig. 1 dots), wherein, above-mentioned the 1st state is that the 1st passage and the 3rd passage are interconnected, the state that the 2nd passage and the 4th passage are interconnected, above-mentioned the 2nd state is that the 1st passage and the 4th passage are interconnected, the state that the 2nd passage and the 3rd passage are interconnected.
The 3 No. four transfer valves 53, the 1st passage is connected the terminal of the 2nd branch pipe 66b of high-pressure gas pipe 66, the 2nd passage is connected the initiating terminal of the 2nd suction line 62, the 3rd passage is connected the terminal of the 2nd branch pipe 61b of the 1st suction line 61, and the 4th passage is connected the terminal of the 2nd branch pipe 63b of the 3rd suction line 63.The 3 No. four transfer valves 53 can switch to the 1st state (state that Fig. 1 represents with solid line) and the 2nd state (state that Fig. 1 dots), wherein, above-mentioned the 1st state is that the 1st passage and the 3rd passage are interconnected, the state that the 2nd passage and the 4th passage are interconnected, above-mentioned the 2nd state is that the 1st passage and the 4th passage are interconnected, the state that the 2nd passage and the 3rd passage are interconnected.
Also be provided with playpipe 85, communicating pipe 87, oil eliminator 75 and oil return pipe 76 in outdoor loop 40.And, also be provided with 4 oil equalizing pipes 71,72,73,74 in outdoor loop 40.
Communicating pipe 87, the one end is connected between the shut off valve 59 and flow control valve 86 in the playpipe 85, and the other end is connected the upstream side of the magnetic valve SV-7 among the 1st branch pipe 66a of high-pressure gas pipe 66.Be provided with the check valve CV-10 that only allows cold-producing medium to flow to the other end from the one end this communicating pipe 87.
The 1st oil equalizing pipe 71, one end are connected on the variable displacement compressor 41, and the other end is connected on the 2nd suction line 62.Be provided with magnetic valve SV-1 at the 1st oil equalizing pipe 71.The 2nd oil equalizing pipe 72, one end are connected on the 1st fixed-capacity compressor 42, and the other end is connected on the 1st branch pipe 63a of the 3rd suction line 63.Be provided with magnetic valve SV-2 at the 2nd oil equalizing pipe 72.The 3rd oil equalizing pipe 73, one end are connected on the 2nd fixed-capacity compressor 43, and the other end is connected on the 1st branch pipe 61a of the 1st suction line 61.Be provided with magnetic valve SV-3 at the 3rd oil equalizing pipe 73.The 4th oil equalizing pipe 74, one end are connected the upstream side of the magnetic valve SV-2 in the 2nd oil equalizing pipe 72, and the other end is connected on the 1st branch pipe 61a of the 1st suction line 61.Be provided with magnetic valve SV-4 at the 4th oil equalizing pipe 74.By suitably opening or closing the magnetic valve SV-1～SV-4 of each oil equalizing pipe 71～74, with the amount of the stockpiling equalization of the refrigerator oil in each compressor 41,42,43.
Also be provided with various sensors and pressure switch in outdoor loop 40, do not illustrate among the figure.
And, be provided with outdoor fan 48 at outdoor unit 11.By this outdoor fan 48 outdoor air is delivered to outdoor heat converter 44.
＜air-conditioning unit 〉
Air-conditioning unit 12 formations are utilized the side machine.Air-conditioning unit 12 comprises air conditioner loop 100.This air conditioner loop 100, that end of its hydraulic fluid side is connected the 2nd hydraulic fluid side connecting pipe 22, and that end of gas side is connected the 2nd gas side connecting pipe 24.
In air conditioner loop 100, be disposed with the heat exchanger of air condition 101 that air-conditioning expansion valve 102 and conduct utilize the side heat exchanger from that end of its hydraulic fluid side towards that end of gas side.Heat exchanger of air condition 101 is the fin tube type heat exchanger of horizontal tab style.In this heat exchanger of air condition 101, between cold-producing medium and room air, carry out heat exchange.On the other hand, air-conditioning expansion valve 102 is made of electric expansion valve.
Be provided with air-conditioning fan 105 at air-conditioning unit 12.By this air-conditioning fan 105 room air in the shop is delivered to heat exchanger of air condition 101.
＜refrigerator display case 〉
In refrigeration circuit 110, be disposed with the refrigeration heat exchanger 111 that refrigeration magnetic valve 114, refrigeration expansion valve 112 and conduct utilize the side heat exchanger from that end of its hydraulic fluid side towards that end of gas side.Refrigeration heat exchanger 111 is the fin tube type heat exchanger of horizontal tab style.In this refrigeration heat exchanger 111, between cold-producing medium and Ku Nei air, carry out heat exchange.Refrigeration expansion valve 112 is made of the temperature automatic expansion valve.The temperature sensing tube 113 of refrigeration expansion valve 112 is installed on the outlet side pipeline of refrigeration heat exchanger 111.
Be provided with freezer internal fan 115 at refrigerator display case 13.By this freezer internal fan 115 air in the storehouse of refrigerator display case 13 is delivered to refrigeration heat exchanger 111.
＜refrigerated display case 〉
In refrigerating circuit 130, be disposed with the freezing heat-exchanger 131 that freezing magnetic valve 134, freezing expansion valve 132 and conduct utilize the side heat exchanger from that end of its hydraulic fluid side towards that end of gas side.Freezing heat-exchanger 131 is the fin tube type heat exchanger of horizontal tab style.In this freezing heat-exchanger 131, between cold-producing medium and Ku Nei air, carry out heat exchange.Freezing expansion valve 132 is made of the temperature automatic expansion valve.The temperature sensing tube 133 of freezing expansion valve 132 is installed on the outlet side pipeline of freezing heat-exchanger 131.
Be provided with freezer internal fan 135 at refrigerated display case 14.By this freezer internal fan 135 air in the storehouse of refrigerated display case 14 is delivered to freezing heat-exchanger 131.
＜supercharging unit 〉
Supercharging unit 15 comprises boost-up circuit 140.Be provided with booster compressor 141, suction line 143, bleed pipe 144 and bypass pipe 150 at this boost-up circuit 140.
Bleed pipe 144, its initiating terminal are connected the ejection side of booster compressor 141, and terminal is connected the 1st gas side connecting pipe 23.At this bleed pipe 144, be disposed with high-pressure switch 148, oil eliminator 145 and ejection side check valve 149 from its initiating terminal towards terminal.149 on ejection side check valve allows cold-producing medium to flow to terminal from the initiating terminal of bleed pipe 144.
＜supercooling unit 〉
As mentioned above, supercooling unit 200 comprises: refrigerant passage 205, supercooling refrigerant loop 220, supercooling heat exchanger 210 and controller 240.
Supercooling is with refrigerant loop 220 loop circuit for successively supercooling being formed by connecting with heat exchanger 210 with expansion valve 223 and supercooling with outdoor heat converter 222, for the supercooling of expansion mechanism with compressor 221, supercooling with pipeline., utilize supercooling to allow the supercooling that is filled circulate and carry out steam compression type refrigerating and circulate with in refrigerant loop 220 in this supercooling with cold-producing medium with compressor 221.That is to say that with in the refrigerant loop 220, the different supercooling of cold-producing medium that transference is flowed circulates with cold-producing medium in this supercooling in the refrigerant loop 20 of above-mentioned refrigerating plant 10.And in the present embodiment, supercooling constitutes pump machanism with compressor 221, and supercooling constitutes the heat source side heat exchanger with outdoor heat converter 222.
Supercooling is the high pressure dome type vortex-type compressor of full seal type with compressor 221.Power with compressor 221 to supercooling by phase inverter.This supercooling can change by the output frequency that makes phase inverter with compressor 221, changes the rotary speed of air compressor motor, changes its capacity.Supercooling is the fin tube type heat exchanger of transverse fin formula with outdoor heat converter 222.With in the outdoor heat converter 222, between supercooling is with cold-producing medium and outdoor air, carry out heat exchange in this supercooling.Supercooling is made of electric expansion valve with expansion valve 223.
Supercooling is made of so-called heat-exchangers of the plate type with heat exchanger 210.Form a plurality of the 1st streams 211 and the 2nd stream 212 in supercooling respectively with heat exchanger 210.Supercooling is connected on the 1st stream 211 with refrigerant loop 220, refrigerant passage 205 is connected on the 2nd stream 212.And this supercooling makes the cold-producing medium heat exchange of the supercooling of circulation the 1st stream 211 with the refrigerating plant 10 of cold-producing medium and circulation the 2nd stream 212 with heat exchanger 210.
Be provided with various sensors and pressure switch at supercooling unit 200.Specifically, the supercooling in refrigerant passage 205 is provided with temperature sensor 237,238 as Temperature Detector with the both sides of heat exchanger 210.In refrigerant passage 205,, promptly be provided with outlet side refrigerant temperature sensors 237 near the part that is connected the end of the 2nd hydraulic fluid side connecting pipe 22 near the part of supercooling with heat exchanger 210 other ends.And, in this refrigerant passage 205,, promptly be provided with entrance side refrigerant temperature sensors 238 near the part that is connected the end of the 1st hydraulic fluid side connecting pipe 21 near the part of supercooling with heat exchanger 210 1 ends.
And, be provided with the outer air-temperature sensor 231 and the outdoor fan 230 of gas temperature outside the sensing chamber at supercooling unit 200.By this outdoor fan 230 outdoor air is delivered to supercooling outdoor heat converter 222.
To the detected value of controller 240 input outlet side refrigerant temperature sensors 237, the detected value of entrance side refrigerant temperature sensors 238, the detected value of outer air-temperature sensor 231 etc.And this controller 240 constitutes according to the detected value of the sensor that is transfused to and controls supercooling with the starting of compressor 221 with stop.Come the signal of the refrigerating plant 10 of formations such as free off-premises station group 11 and air-conditioning unit 12 all not to be input in this controller 240.That is to say that only according to the detected value etc. of the sensor that is arranged on supercooling unit 200, the information that obtains in the inside of supercooling unit 200 is carried out the running capacity control of supercooling with compressor 221 to controller 240.
The running action of-refrigeration system-
Main action in the running action that above-mentioned refrigerating plant 10 is carried out is illustrated.
＜cold air operation 〉
Cold air operation carries out the cooling of room air for to carry out the cooling of air in the storehouse in refrigerator display case 13 and refrigerated display case 14 in air-conditioning unit 12, with the running of freezing in the shop.
As shown in Figure 2, in cold air operation, the 1 No. four transfer valves 51, the 2 No. four transfer valves 52 and the 3 No. four transfer valves 53 are set at the 1st state respectively.And,, on the other hand, suitably regulate the aperture of air-conditioning expansion valve 102, refrigeration expansion valve 112 and freezing expansion valve 132 with outdoor expansion valve 46 Close Alls.Under this state, make variable displacement compressor the 41, the 1st fixed-capacity compressor the 42, the 2nd fixed-capacity compressor 43 and booster compressor 141 runnings.In this cold air operation, supercooling unit 200 becomes operating condition.Running action to supercooling unit 200 later on is illustrated.
Be sent to outdoor heat converter 44 from the cold-producing medium of variable displacement compressor the 41, the 1st fixed-capacity compressor 42 and the ejection of the 2nd fixed-capacity compressor 43 by the 1 No. four transfer valves 51.In outdoor heat converter 44, cold-producing medium is to outdoor air heat release, condensation.Condensed refrigerant flows into the 1st hydraulic fluid side connecting pipe 21 by the 1st liquid line 81, reservoir 45 and the 2nd liquid line 82 successively in outdoor heat converter 44.
The cold-producing medium that flows into the 1st hydraulic fluid side connecting pipe 21 flows into the refrigerant passage 205 of supercooling unit 200.Flow into the cold-producing medium of refrigerant passage 205, during by 2nd stream 212 of supercooling, further be cooled with heat exchanger 210.The liquid refrigerant (supercooling cold-producing medium) of the supercooling state that is cooled in heat exchanger 210 in supercooling is assigned to air conditioner loop 100, refrigeration circuit 110 and refrigerating circuit 130 by the 2nd hydraulic fluid side connecting pipe 22.
The cold-producing medium that flows into air conditioner loop 100 is depressurized the back and imports heat exchanger of air condition 101 by air-conditioning expansion valve 102 time.In heat exchanger of air condition 101, cold-producing medium absorbs heat from room air, evaporation.At that time, in heat exchanger of air condition 101, the cold-producing medium evaporating temperature is set at for example about 5 ℃.In air-conditioning unit 12, the room air that will be cooled in heat exchanger of air condition 101 provides in the shop.
The cold-producing medium of evaporation in heat exchanger of air condition 101 flows into outdoor loop 40 by the 2nd gas side connecting pipe 24, then, flows into the 3rd suction line 63 by the 1 No. four transfer valves 51 and the 2 No. four transfer valves 52 successively.Flow into the cold-producing medium of the 3rd suction line 63, its part sucks the 2nd fixed-capacity compressor 43 by the 1st branch pipe 63a, remaining is inhaled into the 1st fixed-capacity compressor 42 by the 2nd branch pipe 63b, the 3 No. four transfer valves 53 and the 2nd suction line 62 successively.
The cold-producing medium that flows into refrigeration circuit 110 is depressurized the back and imports refrigeration heat exchanger 111 by refrigeration expansion valve 112 time.In refrigeration heat exchanger 111, cold-producing medium is the air heat absorption in the storehouse, evaporation.At that time, in refrigeration heat exchanger 111, the cold-producing medium evaporating temperature for example is set at about-5 ℃.The cold-producing medium of evaporation flows into the 1st gas side connecting pipe 23 in refrigeration heat exchanger 111.Air offers in the storehouse in the storehouse that will be cooled in refrigeration heat exchanger 111 in refrigerator display case 13, and storehouse temperature is remained on for example about 5 ℃.
The cold-producing medium that flows into refrigerating circuit 130 is depressurized the back and imports freezing heat-exchanger 131 by freezing expansion valve 132 time.In freezing heat-exchanger 131, cold-producing medium is the air heat absorption in the storehouse, evaporation.At that time, at freezing heat-exchanger 131 the cold-producing medium evaporating temperature for example is set at about-30 ℃.Air offers in the storehouse in the storehouse that will be cooled in freezing heat-exchanger 131 in refrigerated display case 14, and storehouse temperature is for example remained on about-20 ℃.
The cold-producing medium of evaporation in freezing heat-exchanger 131 flows into boost-up circuit 140, is inhaled into booster compressor 141.Refrigerant compressed flows into the 1st gas side connecting pipe 23 by bleed pipe 144 in booster compressor 141.
In the 1st gas side connecting pipe 23, cold-producing medium of sending into from refrigeration circuit 110 and the cold-producing medium interflow of sending into from boost-up circuit 140.And these cold-producing mediums flow into the 1st suction line 61 in outdoor loop 40 by the 1st gas side connecting pipe 23.The cold-producing medium that flows into the 1st suction line 61 is inhaled into variable displacement compressor 41 by its 1st branch pipe 61a.
＜heating installation running 〉
Heating installation operates as the cooling of carrying out air in the storehouse in refrigerator display case 13 and refrigerated display case 14, carries out the heating of room air in air-conditioning unit 12, gives the running of heating in the shop.
As shown in Figure 3, in outdoor loop 40, the 1 No. four transfer valves 51 are set at the 2nd state, the 2 No. four transfer valves 52 are set at the 1st state, the 3 No. four transfer valves 53 are set at the 1st state.And,, on the other hand, suitably regulate the aperture of air-conditioning expansion valve 102, refrigeration expansion valve 112 and freezing expansion valve 132 with outdoor expansion valve 46 Close Alls.Under this state, make variable displacement compressor 41 and booster compressor 141 runnings, the 1st fixed-capacity compressor 42 and the 2nd fixed-capacity compressor 43 are stopped.And outdoor heat converter 44 becomes halted state when not being admitted to cold-producing medium.In the running of the 1st heating installation, supercooling unit 200 becomes halted state.
Import the heat exchanger of air condition 101 of air conditioner loops 100 successively by the 1 No. four transfer valves 51 and the 2nd gas side connecting pipe 24 from the cold-producing medium of variable displacement compressor 41 ejection, to the room air heat release, condensation.In air-conditioning unit 12, indoor air heated is provided in the shop in heat exchanger of air condition 101.Condensed refrigerant is distributed to refrigeration circuit 110 and refrigerating circuit 130 by the 2nd hydraulic fluid side connecting pipe 22 in heat exchanger of air condition 101.
In refrigerator display case 13 and refrigerated display case 14, the same during with above-mentioned cold air operation, carry out the cooling of air in the storehouse.The cold-producing medium evaporation back in refrigeration heat exchanger 111 that flows into refrigeration circuit 110 flows into the 1st gas side connecting pipe 23.On the other hand, after the cold-producing medium of inflow refrigerating circuit 130 evaporates in freezing heat-exchanger 131, in booster compressor 141, be compressed, flow into the 1st gas side connecting pipe 23 then.Flow into the cold-producing medium of the 1st gas side connecting pipe 23,, be inhaled into variable displacement compressor 41, be compressed by behind the 1st suction line 61.
So, in the running of the 1st heating installation, cold-producing medium heat absorption in refrigeration heat exchanger 111 and freezing heat-exchanger 131, cold-producing medium heat release in heat exchanger of air condition 101.And the heat of cold-producing medium utilization absorption of air in the storehouse heats in the shop in refrigeration heat exchanger 111 and freezing heat-exchanger 131.
In addition, in the heating installation running, also can make 42 runnings of the 1st fixed-capacity compressor.Whether making 42 runnings of the 1st fixed-capacity compressor is what to decide according to the cooling load in refrigerator display case 13 and the refrigerated display case 14.
So, because in heating installation running, outdoor gas temperature is lower, only uses refrigerating plant 10 just can bring into play the ability of regulation fully, use the situation of supercooling usefulness compressor 221 when therefore not having as cold air operation.
The running action of-supercooling unit-
Running action to supercooling unit 200 is illustrated.Under the operating condition of supercooling unit 200, supercooling is suitably regulated the aperture of supercooling with expansion valve 223 simultaneously with compressor 221 runnings.
As shown in Figure 2, use the outdoor heat converter 222 to outdoor air heat release, condensation in supercooling with cold-producing medium with the supercooling of compressor 221 ejections from supercooling.At the supercooling cold-producing medium of supercooling,, flow into the 1st stream 211 of supercooling usefulness heat exchanger 210 then being depressurized during with expansion valve 223 by supercooling with condensation in the outdoor heat converter 222.With in the 1st stream 211 of heat exchanger 210, supercooling is evaporated with the cold-producing medium heat absorption of cold-producing medium from the 2nd stream 212 in supercooling.Supercooling with heat exchanger 210 in the supercooling of evaporation be inhaled into supercooling with compressor 221 with cold-producing medium, be compressed.
Detected value, the detected value of outlet side refrigerant temperature sensors 237 and the detected value of entrance side refrigerant temperature sensors 238 of air-temperature sensor 231 outside above-mentioned controller 240 inputs.Controller 240, the detected value of supercooling with two refrigerant temperature sensors 237,238 in the running of compressor 221 compared, infer from this comparative result to be the supercooling degree of refrigerant condition with the refrigerant loop 20 that flows the heat exchanger 210 in supercooling.Constituting to decide according to this supercooling degree with by outer air-temperature sensor 231 detected outdoor gas temperatures allows supercooling continue or to stop with the running of compressor 221.
Control value action to this controller 240 is illustrated.
At first, from inferring in the refrigerant condition of supercooling with the refrigerant loop 20 that flows the heat exchanger 210 by the supercooling degree of the cold-producing medium of said temperature detector 237,238 detected refrigerant loops 20.Served as cooling degree when big, from the cold-producing medium of refrigerant loop 20 by supercooling with the sufficiently cooled phenomenon of heat exchanger 210, can judge that to flow into supercooling from refrigerant loop 20 less with the cold-producing medium of the refrigerant loop 20 of heat exchanger 210.Controller 240 can be less from inferring the power consumption that about refrigerant loop 20 here.
And served as cooling degree hour, from the cold-producing medium of refrigerant loop 20 not by supercooling with the sufficiently cooled phenomenon of heat exchanger 210, can judge that to flow into supercooling from refrigerant loop 20 more with the cold-producing medium of the refrigerant loop 20 of heat exchangers 210.Can be bigger from inferring the power consumption that about refrigerant loop 20 here.
Specifically, as shown in Figure 4, use pre-prepd supposition curve, controller 240 is inferred the electric weight of outdoor unit 11 from supercooling degree and outdoor gas temperature.And, calculate the electric weight of outdoor unit 11 and supercooling total with the electric weight of compressor 221, judge that it adds up to whether in limits value.This limits value is so long as to be no more than the contract electric weight just passable with the total of other power consumption machine.
In addition, in the present embodiment, though by allowing supercooling stop, the electric weight of whole freezing system is reduced in the limits value with the running of compressor 221, but also can allow supercooling descend, reduce the electric weight of whole refrigerating plant 10 with the operating frequency of compressor 221.That is to say that the present invention reduces the power consumption of this supercooling with compressor 221 by directly reducing the operating frequency of supercooling with compressor 221.
The effect of-Di 1 embodiment-
In above-mentioned supercooling unit 200, controller 240, according to the detected value that is arranged on the sensor in the supercooling unit 200 etc., only the information that obtains in supercooling unit 200 is controlled the running of supercooling with compressor 221.That is to say, in this supercooling unit 200, even and do not carry out giving and accepting of signal etc. between the refrigerant loop 20, also can control the running of supercooling according to the operating condition of refrigerant loop 20 with compressor 221.Therefore, for example, when being installed in above-mentioned supercooling unit 200 in the refrigerant loop 20, as long as the refrigerant passage 205 of supercooling unit 200 is connected on the 1st, the 2nd hydraulic fluid side connecting pipe 21,22 of refrigerant loop 20, the communication wiring in order to the signal of giving and accepting needn't be set between refrigerant loop 20 and supercooling unit 200.
Therefore, use the present invention, can cut down the operation number when being installed in supercooling unit 200 in the refrigerating plant 10, the accident that people when can also possible trouble preventing because of misroute etc. operation to be set causes for fault, simultaneously, the apparatus for supercooling that can turn round in contract demand on one side suppresses the electric weight of whole refrigerating plant 10, Yi Bian improve its refrigerating capacity.
Each variation of-Di 1 embodiment-
Each variation (the 1st variation～the 5th variation) is for inferring the example of the electric weight of outdoor unit 11 according to the various parameters beyond the supercooling degree of the cold-producing medium of refrigerant loop 20.
-Di 1 variation-
In the supercooling unit 200 of this 1st variation, also can be provided as the flow sensor of flow detector in refrigerant passage 205, turn round the control supercooling with compressor 221 according to the flow of the detected refrigerant passage 205 of this flow sensor.That is to say that the detection flowmeter of flow sensor is shown in the refrigerant condition of supercooling with the refrigerant loop 20 that flows in the heat exchanger 210.
Specifically, in this supercooling unit 200, to the detected value of controller 240 input flow rate sensors and outside the detected value of air-temperature sensor 231.As shown in Figure 5, use pre-prepd supposition curve, control value device 240, from the detected value of flow sensor and outside the detected value of air-temperature sensor 231 infer the electric weight of outdoor unit 11.And, calculate this electric weight of inferring the outdoor unit 11 that and supercooling total with the electric weight of compressor 221, judge that it adds up to whether in limits value.This limits value is as long as to be no more than the contract electric weight just passable with the total of other power consumption machine.
-Di 2 variation-
In the supercooling unit 200 of this 2nd variation, also can use the both sides of heat exchanger 210 in supercooling with the supercooling in the refrigerant loop 220, just the last downstream side of the 1st stream 211 is provided as the temperature sensor of supercooling with the Temperature Detector of cold-producing medium, turns round according to the detected detected temperatures difference of these two temperature sensors and controls supercooling compressor 221.That is to say, the above-mentioned detected supercooling temperature difference of cold-producing medium, for with before the cold-producing medium supercooling of refrigerant loop 20 and the supercooling after the supercooling with the temperature difference of cold-producing medium, the state of cold-producing medium is used in the expression supercooling with the supercooling in the refrigerant loop 220.
In this supercooling unit 200, to the detected value of each temperature sensor of controller 240 input and outside the detected value of air-temperature sensor 231.Control value device 240 uses pre-prepd supposition curve, from the difference of the detected value of each temperature sensor and outside the detected value of air-temperature sensor 231 infer and the electric weight of outdoor unit 11 do not illustrate among the figure.For example, when the difference of the detected value of each temperature sensor is big, from use the sufficiently cooled phenomenon of cold-producing medium of refrigerant loop 20 heat exchanger 210 in supercooling, it is less with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210 to judge supercooling, infers that the power consumption that about refrigerant loop 20 is less.And, when the difference of the detected value of each temperature sensor hour, from supercooling with heat exchanger 210 cold-producing medium of refrigerant loop 20 do not have sufficiently cooled phenomenon, it is more with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210 to judge supercooling, infers that the power consumption that about refrigerant loop 20 is bigger.
-Di 3 variation-
In the supercooling unit 200 of this 3rd variation, the also flow sensor that can be provided as flow detector with the supercooling in the refrigerant loop 220 with the entrance side or the outlet side of heat exchanger 210 in supercooling turns round the control supercooling with compressor 221 according to this detected flow.That is to say that detected flowmeter is shown the flow of the supercooling of flowing of supercooling usefulness refrigerant condition with cold-producing medium in supercooling usefulness heat exchanger 210.
In this supercooling unit 200, to the detected value of controller 240 input flow rate sensors and outside the detected value of air-temperature sensor 231.Control value device 240 uses pre-prepd supposition curve, from the detected value of flow sensor and outside the detected value of air-temperature sensor 231 infer and the electric weight of outdoor unit 11 do not illustrate among the figure.For example, when the detected value of flow sensor hour, it is less with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210 to judge supercooling, infers that the power consumption that about refrigerant loop 20 is less.And when the detected value of flow sensor was big, it was more with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210 to judge supercooling, infers that the power consumption that about refrigerant loop 20 is bigger.
-Di 4 variation-
In the supercooling unit 200 of this 4th variation, also can be provided as and detect supercooling with the pressure sensor of the supercooling in the refrigerant loop 220, turn round the control supercooling with compressor 221 according to this detected pressure with the pressure detector of the high-pressure of cold-producing medium.That is to say the detected pressure representative supercooling state of cold-producing medium.
In this supercooling unit 200, to the detected value of controller 240 input pressure sensors and outside the detected value of air-temperature sensor 231.Control value device 240 uses pre-prepd supposition curve, from the detected value of pressure sensor and outside the detected value of air-temperature sensor 231 infer and the electric weight of outdoor unit 11 do not illustrate among the figure.For example, when the detected value of pressure sensor hour, it is less with the flow of cold-producing medium with the supercooling in the heat exchanger 210 with outdoor heat converter 222 and supercooling to judge supercooling, and supercooling is also less with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210.Therefore, infer that the power consumption that about refrigerant loop 20 is less.And, when the detected value of pressure sensor is big, it is more with the flow of cold-producing medium with the supercooling in the heat exchanger 210 with outdoor heat converter 222 and supercooling to judge supercooling, and supercooling is also more with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210.So, infer that the power consumption that about refrigerant loop 20 is bigger.
-Di 5 variation-
In the supercooling unit 200 of this 5th variation, also can be provided as and detect supercooling with two pressure sensors of the supercooling in the refrigerant loop 220, turn round the control supercooling with compressor 221 according to these two detected pressure differentials with the pressure detector of the high-pressure of cold-producing medium and low pressure.That is to say that this detected pressure differential is represented the state of supercooling with cold-producing medium.
In this supercooling unit 200, to the detected value of each pressure sensor of controller 240 input and outside the detected value of air-temperature sensor 231.Control value device 240 uses pre-prepd supposition curve, from the difference of the detected value of each pressure sensor and outside the detected value of air-temperature sensor 231 infer and the electric weight of outdoor unit 11 do not illustrate among the figure.For example, when the difference of the detected value of each pressure sensor hour, because by the aperture control of supercooling with expansion valve 223, low pressure almost is maintained and immobilizes, therefore it is lower than usually to judge high-pressure, it is less with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210 to judge supercooling, as mentioned above.So, infer that the power consumption that about refrigerant loop 20 is less.And, when the difference of the detected value of each pressure sensor is big, judge high-pressure than high usually, it is also more with the refrigerant flow of the refrigerant loop 20 in the heat exchanger 210 to judge supercooling, as mentioned above.Therefore, infer that the power consumption that about refrigerant loop 20 is bigger.
(the 2nd embodiment)
The refrigerating plant 10 of this 2nd embodiment, by allowing supercooling increase with the operating frequency of the outdoor fan 230 of outdoor heat converter 222, reduce the power consumption of supercooling with compressor 221, replace above-mentioned the 1st embodiment directly to allow supercooling stop, reducing the power consumption of this supercooling with compressor 221 with the running of compressor 221.That is to say that in the present embodiment, supercooling immobilizes with the operating frequency of compressor 221.
Specifically, controller 240 when the supercooling degree of the cold-producing medium of refrigerant loop 20 is big, infers that the power consumption that about refrigerant loop 20 is less, does not allow the operating frequency of outdoor fan 230 change.And controller 240 has served as cooling degree hour, infers that the power consumption that about refrigerant loop 20 is bigger, allows the operating frequency of outdoor fan 230 increase and is big air quantity.So, supercooling reduces with the high-pressure of the supercooling in the refrigerant loop 220 with cold-producing medium.That is to say that supercooling reduces with the ejection pressure of compressor 221.Therefore, with in the compressor 221, owing to the compression work amount reduces, so power consumption reduces in supercooling.Its result, even not and carry out giving and accepting of signal etc. between the refrigerant loop 20, also can be according to the running of the operating condition of refrigerant loop 20 control supercooling with compressor 221, can make the electric weight of outdoor unit 11 and supercooling being aggregated in the limits value with the electric weight of compressor 221.
In addition, in the present embodiment, though after allowing the operating frequency of outdoor fan 230 increase, the power consumption of outdoor fan 230 increases, but supercooling is far longer than its increase with the reduction of the power consumption in the compressor 221, can positively reduce the power consumption of supercooling unit 200.And, in each variation of above-mentioned the 1st embodiment, if infer that the power consumption that refrigerant loop 20 is bigger, then with the above-mentioned the same control room external fan 230 that turns round.
(the 3rd embodiment)
The refrigerating plant 10 of this 3rd embodiment is made of the chilled(cooling) water return (CWR) of flow of cooling water, replaces being made of with the refrigerant loop that cold-producing medium circulates in cooling off with fluid circuit supercooling in above-mentioned the 1st embodiment, does not illustrate among the figure.Specifically, this chilled(cooling) water return (CWR) comprises supercooling with heat exchanger 210 and pump, the cooling water of cooling tower by this pump conveyance to supercooling usefulness heat exchanger 210.And with in the heat exchanger 210, the cold-producing medium heat exchange of cooling water and refrigerant passage 205 is with this refrigerant cools in above-mentioned supercooling.That is to say that use in the fluid circuit in the cooling of present embodiment, cooling water flows with fluid as cooling.
At this moment, controller 240 is according to the supercooling degree of the cold-producing medium of refrigerating plant 10 and the running capacity that outdoor gas temperature is regulated pump.Specifically, controller 240 has served as cooling degree when big, does not allow the operating frequency of pump change.And, served as cooling degree hour, allow the operating frequency of pump reduce, reduce the running capacity of pump.So, can allow the power consumption of pump reduce.Its result, though and refrigerant loop 20 between do not carry out giving and accepting of signal etc., also can the electric weight of whole refrigerating plant 10 can be suppressed in the limits value according to the running of the operating condition control pump of its refrigerant loop 20.
(the 4th embodiment)
The refrigerating plant 10 of this 4th embodiment, by the preferential power consumption that increases supercooling unit 200 when load increases, the power consumption that suppresses whole refrigerating plant 10, replace above-mentioned the 1st embodiment by reducing the power consumption of supercooling with compressor 221, limit the power consumption of supercooling unit 200, suppress the power consumption of whole refrigerating plant 10.
Specifically, the outdoor gas temperature Ta of the detected value of air-temperature sensor 231 and be the liquid refrigerant outlet temperature Tout of the detected value of outlet side refrigerant temperature sensors 237 outside the controller 240 of present embodiment is input as.And controller 240 decides according to above-mentioned outdoor gas temperature Ta and to continue supercooling with the running of compressor 221 or stop.That is to say, in the present embodiment, outdoor gas temperature Ta is used as the ambient conditions of supercooling with heat exchanger 210.
Control action to this controller 240 is illustrated.
As shown in Figure 6, be set with target liq refrigerant outlet temperature Eom as preprepared desired value.According to this target liq refrigerant outlet temperature Eom, the controller 240 control supercooling running capacity of compressor 221.This target liq refrigerant outlet temperature Eom is set to along with outdoor gas temperature Ta uprises and step-down.
Specifically, target liq refrigerant outlet temperature Eom, when outdoor gas temperature Ta is 25 ℃≤Ta≤40 ℃, Eom=-(Ta-40)+10 ℃.And, during Ta＜25 ℃, Eom=25 ℃ (immobilizing), during Ta＞40 ℃, Eom=10 ℃ (immobilizing).
Secondly, utilize Fig. 7 that the supercooling of controller 240 control with the running capacity of compressor 221 is illustrated.
At first, supercooling is the frequency of defined with the frequency of compressor 221.And in step S1, controller 240 calculates liquid refrigerant outlet temperature Tout and target liq refrigerant outlet temperature Eom poor (Tout-Eom), when this difference during less than-1.0 ℃ (regional A of Fig. 7), transfers to step S2.And, when this difference is more than-1.0 and is discontented with 1.0 (with the area B of figure), finish.And, when this difference surpasses-1.0 ℃ (with zone C of figure), transfer to step S4.
In step S2, controller 240 judges whether supercooling is low-limit frequencies with the frequency of compressor 221.And, if low-limit frequency just finishes, if not low-limit frequency is just transferred to step S3.
In step S3, make the one-level of supercooling with the frequency reduction defined of compressor 221, finish.
And in step S4, judge whether supercooling is highest frequencies with the frequency of compressor 221.And, if highest frequency just finishes, if not highest frequency is just transferred to step S5.
In step S5, make the one-level of supercooling with the frequency increase defined of compressor 221, finish.
So, along with outdoor gas temperature Ta uprises, controller 240 is set target liq refrigerant outlet temperature Eom lower.And, in order to allow liquid refrigerant outlet temperature Tout, must allow supercooling use the operating frequency of compressor 221 to rise near lower target liq refrigerant outlet temperature Eom, further increase running capacity.Therefore, in the present embodiment, when the rising because of outdoor gas temperature Ta, when the load of refrigerating plant 10 increased, controller 240 allowed supercooling preferentially increase with the running capacity of compressor 221 by regulating target liq refrigerant outlet temperature Eom.Its result, supercooling increases with the power consumption of compressor 221, and supercooling preferentially increases with the power consumption of refrigerant loop 220.
In addition, in the supercooling unit 200 of present embodiment, though when the difference of liquid refrigerant outlet temperature Tout and target liq refrigerant outlet temperature Eom is more than 1.0 ℃ or 1.0 ℃ the time, allow supercooling change by controller 240 with the running capacity of compressor 221, but also can have ± during 1.5 ℃ and ± 2.0 ℃ poor, allowing its variation.
(effect of the 4th embodiment)
As mentioned above, in the supercooling evaporating temperature of the supercooling of heat exchanger 210, be higher than the evaporating temperature of the cold-producing medium in utilizing side heat exchanger 101,111,131 with cold-producing medium.At the height pressure reduction of supercooling, less than height pressure reduction in the kind of refrigeration cycle of refrigerant loop 20 with the kind of refrigeration cycle of refrigerant loop 220.And, the refrigerating plant 10 of present embodiment, for not being allows circulating mass of refrigerant increase in the bigger refrigerant loop 20 of the height pressure reduction of kind of refrigeration cycle, but allow supercooling increase in refrigerant loop 220 with the internal circulating load of cold-producing medium in the littler supercooling of the height pressure reduction of kind of refrigeration cycle, and allow supercooling increase with the operating frequency of compressor 221, preferentially increase its power consumption (workload).That is to say that the running capacity by the less supercooling usefulness compressor 221 of the original burden of preferential increase comes the increase corresponding to load.Therefore, can suppress decline that can the rejection coefficient for increase corresponding to the required input of increase of load.Its result can suppress the increase of the power consumption of whole refrigerating plant 10.
And, in the present embodiment,,, allow supercooling preferentially increase with the running capacity of compressor 221 with respect to heat source side compressor 41,42,43 along with outdoor gas temperature uprises.So, since can according to the variation of the height pressure reduction of the corresponding kind of refrigeration cycle of outdoor gas temperature, allow supercooling preferentially increase with the running capacity of compressor 221, therefore the decline of the coefficient of performance of refrigerating plant 10 can be suppressed easier and effectively, the recruitment of whole power consumption can be suppressed.
Each variation of-Di 4 embodiment-
Each variation (the 1st variation～the 6th variation) for according to the ambient conditions of the various parameters beyond the outdoor gas temperature as supercooling usefulness heat exchanger 210, is set the example of supercooling with the desired value of the refrigerant temperature in the outlet of heat exchanger 210.
-Di 1 variation-
In this 1st variation, will use the ambient conditions of heat exchanger 210 as supercooling with the supercooling degree of the cold-producing medium of the refrigerant loop 20 that flows in the heat exchanger 210 in supercooling.At this moment, the temperature sensor of the Temperature Detector that the supercooling in refrigerant passage 205 is provided as cold-producing medium with the entrance side and the outlet side of heat exchanger 210 does not illustrate among the figure.The detected temperatures of these temperature sensors is transfused to controller 240, and its detected temperatures difference is used as the supercooling degree.And, in controller 240, come target setting liquid refrigerant outlet temperature Eom according to the supercooling degree of cold-producing medium.That is to say that along with the supercooling degree diminishes, infer that load increases, Eom sets lowlyer with target liq refrigerant outlet temperature.
-Di 2 variation-
In the refrigerating plant 10 of this 2nd variation, will use the ambient conditions of heat exchanger 210 as supercooling with the refrigerant flow of the refrigerant loop 20 that flows in the heat exchanger 210 in supercooling.At this moment, be provided as the flow sensor of the flow detector of cold-producing medium, do not illustrate among the figure, should detect flow and be input to controller 240 in refrigerant passage 205.And, in controller 240, according to refrigerant flow target setting liquid refrigerant outlet temperature Eom.That is to say that along with refrigerant flow becomes many, infer that load increases, Eom sets lowlyer with target liq refrigerant outlet temperature.
-Di 3 variation-
In the refrigerating plant 10 of this 3rd variation, supercooling is used as the ambient conditions of supercooling with heat exchanger 210 with the supercooling in the heat exchanger 210 with the temperature difference before and after the supercooling of cold-producing medium.At this moment, be provided as the temperature sensor of supercooling with the entrance side of heat exchanger 210 and outlet side, do not illustrate among the figure with the Temperature Detector of cold-producing medium in supercooling.The detected temperatures of these temperature sensors is input to controller 240, its detected temperatures difference is used the temperature difference of the supercooling front and back of cold-producing medium as supercooling.And, in controller 240, according to the temperature difference target setting liquid refrigerant outlet temperature Eom of supercooling with cold-producing medium.That is to say that along with its temperature difference diminishes, infer that load increases, Eom sets lowlyer with target liq refrigerant outlet temperature.
-Di 4 variation-
In the refrigerating plant 10 of this 4th variation, will use the flow of cold-producing medium as the ambient conditions of supercooling with the supercooling of flowing in the heat exchanger 210 in supercooling with heat exchanger 210.At this moment, be provided as the flow sensor of supercooling with the entrance side of heat exchanger 210 or outlet side, do not illustrate among the figure, should detect flow and be input to controller 240 with the flow detector of cold-producing medium in supercooling.And, in controller 240, according to detecting flow set target liq refrigerant outlet temperature Eom.That is to say that along with its supercooling is many with the flow change of cold-producing medium, infer that load increases, Eom sets lowlyer with target liq refrigerant outlet temperature.
-Di 5 variation-
In the refrigerating plant 10 of this 5th variation, supercooling is used the ambient conditions of heat exchanger 210 as supercooling with the high-pressure of cold-producing medium with the supercooling in the refrigerant loop 220.At this moment, be provided as the pressure sensor of pressure detector with the ejection side of compressor 221, do not illustrate among the figure, this detected pressures is input to controller 240 in supercooling.And, in controller 240, according to detected pressures target setting liquid refrigerant outlet temperature Eom.That is to say that along with the high-pressure of its supercooling with cold-producing medium uprises, infer that load increases, Eom sets lowlyer with target liq refrigerant outlet temperature.
-Di 6 variation-
In the refrigerating plant 10 of this 6th variation, supercooling is used as the ambient conditions of supercooling with heat exchanger 210 with the supercooling in the refrigerant loop 220 with the high-pressure of cold-producing medium and the pressure differential of low pressure.At this moment, with the pressure sensor that the spout side and the suction side of compressor 221 is provided as pressure detector, do not illustrate among the figure, those detected pressures are input to controller 240 in supercooling.And, in controller 240, according to the pressure differential target setting liquid refrigerant outlet temperature Eom of each detected pressures.That is to say that along with its pressure differential becomes big, infer that load increases, Eom sets lowlyer with target liq refrigerant outlet temperature.
(the 5th embodiment)
The refrigerating plant 10 of this 5th embodiment, by allowing supercooling increase with the operating frequency of the outdoor fan 230 of outdoor heat converter 222, supercooling is increased with the power consumption of refrigerant loop 220, replace above-mentioned the 4th embodiment directly to make the operating frequency rising of supercooling, this supercooling is increased with the power consumption of compressor 221 with compressor 221.That is to say, in the present embodiment,, also do not allow supercooling change with the operating frequency of compressor 221 even load increases.
Specifically, if allow the operating frequency of above-mentioned outdoor fan 230 increase, then supercooling increases with the flow of the supercooling in the heat exchanger 210 with cold-producing medium, and refrigerating capacity increases.That is to say that if allow the operating frequency of outdoor fan 230 increase, then supercooling reduces with the high-pressure of the supercooling in the refrigerant loop 220 with cold-producing medium, supercooling improves with the volume efficiency of compressor 221, and the internal circulating load of cold-producing medium increases.Therefore, liquid refrigerant outlet temperature Tout reduces.Its result, the power consumption of outdoor fan 230 increases, and supercooling preferentially increases with the power consumption of refrigerant loop 220.
In addition, in the present embodiment, though for supercooling is improved with the running efficiency of compressor 221, its power consumption is reduced, the increase of the power consumption of outdoor fan 230 is extremely big, and therefore the power consumption of whole supercooling unit 200 rises really.
At present embodiment, the control action of controller 240 is as follows.In the step S2 of Fig. 6, judge whether the frequency of outdoor fan 230 is low-limit frequency.And,,, then transfer to step S3 if be not low-limit frequency if low-limit frequency then finishes.In step S3, the frequency of outdoor fan 230 is reduced the one-level of defined, finish.
And in step S4, judge whether the frequency of outdoor fan 230 is highest frequency.And,,, then transfer to step S5 if be not highest frequency if highest frequency then finishes.In step S5,, finish the one-level of supercooling with the frequency increase defined of compressor 221.Controller 240 was that unit carries out above-mentioned degree with 30 seconds.
So, when the rising because of outdoor gas temperature Ta, when the load of refrigerating plant 10 increased, controller 240 allowed the running capacity of outdoor fan 230 preferentially increase by regulating target liq refrigerant outlet temperature Eom.Its result, supercooling preferentially increases with the power consumption of refrigerant loop 220, has suppressed the recruitment of the power consumption of whole refrigerating plant 10.Other structure, effect and effect are the same with the 4th embodiment.
(the 6th embodiment)
The refrigerating plant 10 of this 6th embodiment uses the chilled(cooling) water return (CWR) by flow of cooling water to constitute, and replaces being made of with the refrigerant loop that cold-producing medium circulates in cooling off with fluid circuit supercooling in above-mentioned the 1st embodiment, does not illustrate among the figure.Specifically, this chilled(cooling) water return (CWR) comprises supercooling heat exchanger 210 and pump, and the cooling water of cooling tower is arrived supercooling heat exchanger 210 by this pump by conveyance.And with in the heat exchanger 210, the cold-producing medium heat exchange of cooling water and refrigerant passage 205 is with this refrigerant cools in above-mentioned supercooling.That is to say that use in the fluid circuit in the cooling of present embodiment, cooling water flows with fluid as cooling.
At this moment, controller 240 when the load of refrigerating plant 10 increases, allows the running capacity of pump increase, so that liquid refrigerant outlet temperature Tout becomes target liq refrigerant outlet temperature Eom.Its result, the power consumption of pump increases, and preferentially increases about the power consumption of chilled(cooling) water return (CWR), has suppressed the recruitment of the power consumption of whole refrigerating plant 10.Other structure, effect and effect are the same with the 4th embodiment.
In addition, the foregoing description and variation thereof, for be suitable for example of the present invention in nature, the present invention does not painstakingly limit its suitable thing or its purposes scope.
(practicality)
As mentioned above, the present invention is to using in supercooling in the heat exchanger the overcooled refrigeration dress of cold-producing medium Be equipped with usefulness.
Claims (13)
1, a kind of refrigerating plant comprises: have the side of utilization heat exchanger (101,111,131) and heat source side compressor (41,42,43), allow cold-producing medium circulate and carry out the refrigerant loop (20) that steam compression type refrigerating circulates; And have supercooling usefulness heat exchanger (210) and will cool off the cooling fluid circuit of using the pump machanism of heat exchanger (210) with the fluid conveyance to this supercooling, this refrigerating plant will offer the above-mentioned cold-producing medium that utilizes side heat exchanger (101,111,131) in above-mentioned supercooling supercooling in the heat exchanger (210) by cooling with fluid, it is characterized in that:
Comprise controller (240), control is about the power consumption of above-mentioned refrigerant loop (20) with about the power consumption of above-mentioned cooling with fluid circuit:
Above-mentioned controller (240) when load increases, with respect to above-mentioned refrigerant loop (20), preferentially allows increase about the power consumption of above-mentioned cooling with fluid circuit.
2, refrigerating plant according to claim 1 is characterized in that:
Above-mentioned controller (240), constitute control about the power consumption of above-mentioned cooling with fluid circuit, so that above-mentioned supercooling becomes desired value with the refrigerant temperature in the outlet of heat exchanger (210), and set above-mentioned desired value with the ambient conditions of heat exchanger (210) according to supercooling, so that when load increases, preferentially allow increase about the power consumption of above-mentioned cooling with fluid circuit.
3, refrigerating plant according to claim 1 is characterized in that:
Above-mentioned controller (240) constitutes by allowing the power consumption of pump machanism increase, and preferentially allows increase about the power consumption of cooling with fluid circuit.
4, refrigerating plant according to claim 3 is characterized in that:
Above-mentioned cooling fluid circuit be have the supercooling that constitutes pump machanism with compressor (221) and heat source side heat exchanger (222), be provided as supercooling that cooling uses with fluid with the cold-producing medium circulation, carry out the supercooling refrigerant loop (220) that steam compression type refrigerating circulates;
Above-mentioned controller (240) constitutes by allowing above-mentioned supercooling increase with the operating frequency of compressor (221), allows this supercooling increase with the power consumption of compressor (221).
5, refrigerating plant according to claim 1 is characterized in that:
Above-mentioned cooling fluid circuit be have the supercooling that constitutes pump machanism with compressor (221) and heat source side heat exchanger (222), be provided as supercooling that cooling uses with fluid with the cold-producing medium circulation, carry out the supercooling refrigerant loop (220) that steam compression type refrigerating circulates;
Above-mentioned controller (240) constitutes the operating frequency by the fan (230) that increases above-mentioned heat source side heat exchanger (222), preferentially allows increase about the power consumption of above-mentioned supercooling with refrigerant loop (220).
6, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned supercooling is outdoor gas temperature with the ambient conditions of heat exchanger (210).
7, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned supercooling is the supercooling degree of this supercooling with the cold-producing medium of the refrigerant loop (20) in the heat exchanger (210) with the ambient conditions of heat exchanger (210).
8, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned supercooling is with the ambient conditions of heat exchanger (210), for use the refrigerant flow of the refrigerant loop (20) that flows in the heat exchanger (210) in this supercooling.
9, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned supercooling is with the ambient conditions of heat exchanger (210), for this supercooling with heat exchanger (210) in the cold-producing medium supercooling of refrigerant loop (20) before and cooling fluid circuit after the supercooling) the cooling temperature difference of fluid.
10, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned supercooling is used the flow of fluid with the ambient conditions of heat exchanger (210) for use the cooling of flowing in the heat exchanger (210) in this supercooling with the cooling of fluid circuit.
11, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned cooling fluid circuit be have the supercooling that constitutes pump machanism with compressor (221) and heat source side heat exchanger (222), be provided as supercooling that cooling uses with fluid and follow, encircle with cold-producing medium and carry out the supercooling usefulness refrigerant loop (220) that steam compression type refrigerating circulates;
The ambient conditions of above-mentioned supercooling usefulness heat exchanger (210) is the high-pressure of supercooling with the usefulness of the supercooling in the refrigerant loop (220) cold-producing medium.
12, refrigerating plant according to claim 2 is characterized in that:
Above-mentioned cooling fluid circuit be have the supercooling that constitutes pump machanism with compressor (221) and heat source side heat exchanger (222), be provided as supercooling that cooling uses with fluid and circulate with cold-producing medium and carry out the supercooling usefulness refrigerant loop (220) that steam compression type refrigerating circulates;
The ambient conditions of above-mentioned supercooling usefulness heat exchanger (210) is the supercooling high-pressure of the supercooling usefulness cold-producing medium in the refrigerant loop (220) and the pressure differential of low pressure.
13, refrigerating plant according to claim 6 is characterized in that:
Above-mentioned controller (240) constitutes along with outdoor gas temperature uprises and above-mentioned desired value is reduced.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004225997 | 2004-08-02 | ||
| JP2004-225997 | 2004-08-02 | ||
| JP2004225997 | 2004-08-02 | ||
| JP2004-379512 | 2004-12-28 | ||
| JP2004379512 | 2004-12-28 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800010483A Division CN100436961C (en) | 2004-08-02 | 2005-08-02 | Refrigeration unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101275789A true CN101275789A (en) | 2008-10-01 |
| CN100562695C CN100562695C (en) | 2009-11-25 |
Family
ID=37031145
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800010483A Expired - Fee Related CN100436961C (en) | 2004-08-02 | 2005-08-02 | Refrigeration unit |
| CNB2008100992162A Expired - Fee Related CN100562695C (en) | 2004-08-02 | 2005-08-02 | Refrigerating plant |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800010483A Expired - Fee Related CN100436961C (en) | 2004-08-02 | 2005-08-02 | Refrigeration unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN100436961C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103032980A (en) * | 2011-09-29 | 2013-04-10 | 艾默生网络能源有限公司 | Water chilling unit |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2841855B1 (en) * | 2012-04-27 | 2021-04-14 | Carrier Corporation | Cooling system and method of controlling said cooling system |
| JP6323508B2 (en) * | 2016-08-04 | 2018-05-16 | ダイキン工業株式会社 | Refrigeration equipment |
-
2005
- 2005-08-02 CN CNB2005800010483A patent/CN100436961C/en not_active Expired - Fee Related
- 2005-08-02 CN CNB2008100992162A patent/CN100562695C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103032980A (en) * | 2011-09-29 | 2013-04-10 | 艾默生网络能源有限公司 | Water chilling unit |
| CN103032980B (en) * | 2011-09-29 | 2016-01-06 | 艾默生网络能源有限公司 | A kind of handpiece Water Chilling Units |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100436961C (en) | 2008-11-26 |
| CN100562695C (en) | 2009-11-25 |
| CN1842681A (en) | 2006-10-04 |
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