CN101243294B - Refrigerating apparatus - Google Patents

Refrigerating apparatus Download PDF

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Publication number
CN101243294B
CN101243294B CN2006800298921A CN200680029892A CN101243294B CN 101243294 B CN101243294 B CN 101243294B CN 2006800298921 A CN2006800298921 A CN 2006800298921A CN 200680029892 A CN200680029892 A CN 200680029892A CN 101243294 B CN101243294 B CN 101243294B
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CN
China
Prior art keywords
cold
accumulator
producing medium
refrigerant
side unit
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Expired - Fee Related
Application number
CN2006800298921A
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Chinese (zh)
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CN101243294A (en
Inventor
竹上雅章
近藤东
谷本宪治
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication of CN101243294A publication Critical patent/CN101243294A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/007—Compression machines, plants or systems with reversible cycle not otherwise provided for three pipes connecting the outdoor side to the indoor side with multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/24—Low amount of refrigerant in the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

A refrigerating apparatus comprising a refrigerant return mechanism (5) for returning a liquid refrigerant in a receiver (17) to a circulation route. Accordingly, the liquid refrigerant in the receiver (17) can be forcibly returned to the circulation route in such an operating state that the circulation route for the refrigerant is formed to return the refrigerant fed from compression mechanisms (11D, 11E) from a second use side unit (20) to the compression mechanisms (11D, 11E) through first use side units (30, 40).

Description

Refrigerating plant
Technical field
The present invention relates to refrigerating plant, particularly relates to a kind of refrigerating plant, its have as refrigerating with and many of idle call utilize the side heat exchanger and can carry out 100% recuperation of heat running between the side heat exchanger respectively utilizing.
Background technology
The refrigerating plant that carries out kind of refrigeration cycle is always known.This refrigerating plant is utilized widely as the air conditioner that makes indoor nice and cool and heating or with the cooler of the showcase of refrigeratings such as food.At the refrigerating plant of this class, some is (for example with reference to the patent documentation 1) that carries out the both sides of air-conditioning and refrigerating.This refrigerating plant for example is arranged on convenience store, a refrigerating plant only is set and can carry out in the shop in air-conditioning with cool off showcase etc.
Described refrigerating plant, showcase of using at refrigerating and idle call indoor set etc. utilize set in the side unit many to utilize side heat exchanger (refrigerating with heat exchanger and idle call heat exchanger), each personal hydraulic fluid side communication pipe arrangement and gas side communication pipe arrangement connect side by side for the heat source side heat exchanger (outdoor heat converter) that is located at outdoor heat source side unit (outdoor unit).
Here, when refrigerant loop has two systems in the second system side loop of the first system side loop that refrigerating uses and idle call, respectively use two communication pipe arrangements at liquid pipe and tracheae usually.On the other hand, wherein also having is at the shared hydraulic fluid side communication of the liquid pipe of two systems pipe arrangement, to reduce the quantity (with reference to patent documentation 2) of communication pipe arrangement.
The refrigerant loop of this device, particularly as shown in figure 13.Among the figure, the 101st, outdoor unit, the 102nd, indoor units, the 103rd, refrigeration showcase (refrigeration unit), the 104th, freezing with showcase (freezing unit).Be provided with compressing mechanism 105,106, outdoor heat converter 107, outdoor expansion valve 108 and accumulator (receiver) 109 at outdoor unit 101, be provided with indoor heat converter (idle call heat exchanger) 110 and indoor expansion valve 111 in indoor units 102.And, refrigeration with showcase 103 be provided with refrigeration with heat exchanger 112 and refrigeration with expansion valve 113, be provided with freezing heat exchanger 114, freezing expansion valve 115 and the booster compressor 116 used used freezing with showcase 104.
The refrigerant loop 120 of this refrigerating plant possesses has refrigerating with the first system side loop and the idle call second system side loop; This refrigerating constitutes with the first system side loop that cold-producing medium carries out unidirectional circulation between outdoor heat converter 107 and refrigerating are with heat exchanger 112,114; This idle call second system side loop constitute that cold-producing medium carries out Reversible Cycle between outdoor heat converter 107 and indoor heat converter 110.And, as the shared hydraulic fluid side communication of the liquid pipe of each system pipe arrangement 121.
At described refrigerating plant, be located at outdoor outdoor heat converter 107 and carry out for thermal source the running of room conditioning and the cooling of each showcase except using, also can not use described outdoor heat converter 107 and with indoor heat converter 110 as condenser and carry out the running of heating installation and refrigerating with 100% recuperation of heat as evaporimeter with heat exchanger 112,114 with refrigerating.
But, making hydraulic fluid side communication pipe arrangement 121 is when carrying out 100% recuperation of heat running in one the structure of described refrigerant loop 120, form following cold-producing medium circulating path at refrigerant loop 120, just: compressing mechanism 105,106 cold-producing mediums that sprayed, after indoor heat converter 110 condenses, evaporate with heat exchanger 112,114 at refrigerating, return the cold-producing medium circulating path of compressing mechanism 105,106 again.In other words, at this moment, be necessary to make that the liquid refrigerant that condenses at indoor heat converter 110 does not flow to the direction of heat source side heat exchanger 107 from accumulator 109, and this cold-producing medium is imported the heat exchanger 112,114 that refrigerating is used.
But, when for example outside air temperature is low, because the pressure in the accumulator 109 descends, hydraulic fluid side communication pipe arrangement 121 pressure inside also descend, the liquid refrigerant that flows out from indoor heat converter 110 flows into accumulators 109 from hydraulic fluid side communication pipe arrangement 121 easily, and therefore flowing to refrigerating may be not enough to some extent with the refrigerant flow of heat exchanger 112,114.And in case the refrigerating refrigerant flow deficiency of heat exchanger 112,114, the ability of then cooling off in each showcase 103,104 storehouse will descend.
Here, in the described refrigerating plant, the refrigerant passage of the pipe arrangement 121 past accumulators 109 of communicating in the hydraulic fluid side is provided with pressure-reducing valve (relief valve) 117.This pressure-reducing valve 117 remains on following state: then open when above when the refrigerant pressure of hydraulic fluid side communication pipe arrangement 121 rises to setting, but till reaching this setting for closing.And, the pressure of the hydraulic fluid side communication pipe arrangement 121 when being higher than 100% recuperation of heat running by the operating pressure of this pressure-reducing valve 117 is set for, prevent that 100% recuperation of heat when running liquid refrigerant from flowing into accumulator 109, can not descend even make that the flow of refrigerant in the refrigerant loop 120 is stablized refrigerating capacity when outside air temperature is low.
And, though also can to carry out with outdoor heat converter 107 at described refrigerating plant be the heating installation running of the kind of refrigeration cycle of evaporimeter, owing to will have an effect in the suction pressure of pressure-reducing valve 117 compressors 106 during situation like this, so pressure-reducing valve 117 will be opened.And during cold air operation, cold-producing medium can not flow through the path that is provided with pressure-reducing valve 117.
[patent documentation 1] TOHKEMY 2001-280749 communique
[patent documentation 2] TOHKEMY 2005-134103 communique
Summary of the invention
Solve problem
Yet, in described device, can not stop cold-producing medium to flow into accumulator sometimes fully even close pressure-reducing valve.Specifically, this is at pressure-reducing valve the situation that cold-producing medium leaks outside to take place, during this situation, because cold-producing medium flows into accumulator gradually, the cold-producing medium that flows in 100% recuperation of heat running can flow out from accumulator hardly, therefore, the refrigerant amount in the accumulator increases, and is then not enough with the cold-producing medium of heat exchanger as the refrigerating that utilizes the side unit.Thus, the ability drop of cooling off in each showcase storehouse will become problem.And, even this class problem can take place similarly in the situation that is provided with the valve system dissimilar with pressure-reducing valve (such as magnetic valve).No matter be the valve system of which kind, under the situation of the cold-producing medium generation effect of higher pressure, will be difficult to separate fully leaking outside of the cold-producing medium that disappears.
And, even stop cold-producing medium to flow under the situation of accumulator, pressure-reducing valve will be opened sometimes when the refrigerant pressure that works at pressure-reducing valve is too high, during this situation, in case be higher than that required cold-producing medium flows in the accumulator and aforementioned in the same manner because the deficiency of cold-producing medium will make ability drop in each showcase storehouse of cooling.
Because it is above-mentioned, the objective of the invention is to: in possessing the refrigerating plant that utilizes the side heat exchanger shared hydraulic fluid side communication of a plurality of liquid pipes simultaneously pipe arrangement of several system, prevent that the increase of the refrigerant amount in accumulator from causing the lack of refrigerant that utilizes the side unit.
Solution
First invention is to be object with following refrigerating plant, this refrigerating plant possesses: the heat source side unit 10 with compressing mechanism 11D, 11E, heat source side heat exchanger 15 and accumulator 17, having first utilizes first of side heat exchanger 31,41 to utilize side unit 30,40, have second and utilize second of side heat exchanger 21 to utilize side unit 20, and connect gas side communication pipe arrangement 51,52 and the hydraulic fluid side communication pipe arrangement 53,54,55 that each unit 10,20,30,40 constitutes refrigerant loop 50; Described gas side communication pipe arrangement 51,52 has first gas side communication pipe arrangement 51 and second gas side communication pipe arrangement 52, this first gas side communication pipe arrangement 51 connects described heat source side unit 10 and described first and utilizes side unit 30,40, and this second gas side communication pipe arrangement 52 connects described heat source side unit 10 and described second and utilizes side unit 20; Described hydraulic fluid side communication pipe arrangement 53,54,55 has set liquid pipe 53, the first difference liquid pipe 54 and the second difference liquid pipe 55, this set liquid pipe 53 connects described heat source side unit 10, the first difference liquid pipe 54 utilizes side unit 30,40 from this set liquid pipe inconsistent connection in 53 fens described first, and this second difference liquid pipe 55 utilizes side unit 20 from this set liquid pipe inconsistent connection in 53 fens described second.And, described refrigerant loop 50 can form following cold-producing medium circulating path, just: described compressing mechanism 11D, the cold-producing medium that 11E sent does not utilize side unit 20 to flow through by described accumulator 17 from described second and first utilizes side unit 30,40 and get back to this compressing mechanism 11D, 11E, and this refrigerating plant is provided with cold-producing medium loopback mechanism 5, this cold-producing medium loopback mechanism 5 is formed with under the operating condition of described circulating path in described refrigerant loop 50, pressurize in by import high-pressure refrigerants to described accumulator 17, send the liquid refrigerants in the described accumulator 17 back to described circulating path by described set liquid pipe 53 described accumulator 17.
Second invention is for having ingress pipe 71 in cold-producing medium loopback mechanism 5 described in first invention, this ingress pipe 71 is to be used for the high-pressure refrigerant from described compressing mechanism 11D, 11E ejection is imported to described accumulator 17, by from this ingress pipe 71 described high-pressure refrigerant being imported described accumulator 17 and makes the liquid refrigerant in this accumulator 17 get back to described circulating path by described set liquid pipe 53 to these accumulator 17 pressurizations.
The 3rd invention is for having communicating pipe 67 in cold-producing medium loopback mechanism 5 described in first invention, this communicating pipe 67 is to be used for making described accumulator 17 to be communicated with the suction side of described compressing mechanism 11D, 11E, is inhaled into described compressing mechanism 11D, 11E and sends back to described circulating path by making the liquid refrigerant in the described accumulator 17 this communicating pipe 67.
The 4th invention is for being provided with thermal source fan 16 in described heat source side unit 10 in first invention, this thermal source fan 16 is used for carrying air to described heat source side heat exchanger 15, described cold-producing medium loopback mechanism 5 has means of communication 13, this means of communication 13 is to be used for making described accumulator 17 be communicated with described compressing mechanism 11D by described heat source side heat exchanger 15, the ejection side of 11E, under the state that described thermal source fan 16 is stopped, making this accumulator 17 be communicated with described compressing mechanism 11D by this means of communication 13, the ejection side of 11E and make this compressing mechanism 11D, the high-pressure refrigerant that 11E sprayed flows into described accumulator 17, makes the liquid refrigerant in this accumulator 17 get back to described circulating path by described set liquid pipe 53.
The 5th invention is to possess the degree of superheat detector 79,81 of suction and controller 95 in first to the 4th arbitrary invention of inventing; This suction degree of superheat detector the 79, the 81st detects and utilizes side heat exchanger 31,41 to flow to the degree of superheat of the cold-producing medium of described compressing mechanism 11D, 11E suction side from described first; This controller 95 is the described cold-producing medium loopback of control mechanisms 5, makes detected value when described suction degree of superheat detector 79,81 become setting and sends the cold-producing medium in the described accumulator 17 back to described circulating path when above.
The 6th invention is to possess ejection degree of superheat detector 75,76 and controller 95 in arbitrary invention of first to the 4th invention, this ejection degree of superheat detector the 75, the 76th detects the degree of superheat of cold-producing medium of described compressing mechanism 11D, 11E ejection, and this controller 95 is that the described cold-producing medium loopback of control mechanism 5 makes detected values when described ejection degree of superheat detector 75,76 become setting to send the cold-producing medium in the described accumulator 17 back to described circulating path when above.
The 7th invention is to possess ejection refrigerant temperature detector 76 and controller 95 in first to the 4th arbitrary invention of inventing, this ejection refrigerant temperature detector 76 is the temperature that detect the cold-producing medium of described compressing mechanism 11D, 11E ejection, and this controller 95 is that the described cold-producing medium loopback of control mechanism 5 makes detected values when described ejection refrigerant temperature detector 76 become setting to send the cold-producing medium in the described accumulator 17 back to described circulating path when above.
The 8th invention is to be object with following refrigerating plant, this refrigerating plant possesses: the heat source side unit 10 with compressing mechanism 11D, 11E, heat source side heat exchanger 15 and accumulator 17, having first utilizes first of side heat exchanger 31,41 to utilize side unit 30,40, have second and utilize second of side heat exchanger 21 to utilize side unit 20, and connect gas side communication pipe arrangement 51,52 and the hydraulic fluid side communication pipe arrangement 53,54,55 that each unit 10,20,30,40 constitutes refrigerant loop 50; Be provided with thermal source fan 16 in described heat source side unit 10, this thermal source fan 16 is used for carrying air to described heat source side heat exchanger 15; Described gas side communication pipe arrangement 51,52 has first gas side communication pipe arrangement 51 and second gas side communication pipe arrangement 52, this first gas side communication pipe arrangement 51 connects described heat source side unit 10 and described first and utilizes side unit 30,40, and this second gas side communication pipe arrangement 52 connects described heat source side unit 10 and described second and utilizes side unit 20; Described hydraulic fluid side communication pipe arrangement 53,54,55 has set liquid pipe 53, the first difference liquid pipe 54 and the second difference liquid pipe 55, this set liquid pipe 53 connects described heat source side unit 10, this first difference liquid pipe 54 utilizes side unit 30,40 from this set liquid pipe inconsistent connection in 53 fens described first, and this second difference liquid pipe 55 utilizes side unit 20 from this set liquid pipe inconsistent connection in 53 fens described second.Be provided with the switching mechanism 12 that to change first drive manner and second drive manner at described refrigerant loop 50, to be the cold-producing medium sent of described compressing mechanism 11D, 11E utilize side unit 20 to flow through from described second to this first drive manner first utilizes side unit 30,40 to get back to this compressing mechanism 11D, 11E, and this second drive manner is that cold-producing medium that described compressing mechanism 11D, 11E are sent is flowed through after described heat source side heat exchanger 15 flows into accumulators 17 and first utilized side unit 30,40 to get back to this compressing mechanism 11D, 11E; Under the state that described thermal source fan 16 is stopped by described switching mechanism 12, be converted to second drive manner from first drive manner, the liquid refrigerant that accumulates in accumulator 17 in this first drive manner sent back to described first by described set liquid pipe 53 utilize side unit 30,40.
-effect-
In first invention, in the operating condition that is formed with following cold-producing medium circulating path, just: the cold-producing medium that compressing mechanism 11D, 11E are sent utilizes side unit 20 to flow through from second first to utilize side unit 30,40 to get back to the cold-producing medium circulating path of compressing mechanism 11D, 11E, can send the liquid refrigerants in the accumulator 17 back to circulating path forcibly with described cold-producing medium loopback mechanism 5.In other words, even want as described to stop cold-producing medium flow into accumulator 17 sometimes cold-producing medium still can flow into accumulator 17, under these circumstances, the refrigerant amount of circulating path will reduce, but, send the liquid refrigerant in the accumulator 17 back to circulating path with cold-producing medium loopback mechanism 5 in this first invention.
In second invention, when sending the liquid refrigerant in the accumulator 17 back to circulating path, will import accumulator 17 from the high-pressure gas refrigerant of compressing mechanism 11D, 11E ejection by ingress pipe 71.In case import high-pressure gas refrigerant then the liquid refrigerant that interior pressure will rise and it is inner of accumulator 17 will be discharged.Thus, the liquid refrigerant that is discharged from from accumulator 17 is sent back to circulating path by set liquid pipe 53.Thus, the ratio of the gas refrigerant that density is little in the accumulator 17 will increase, and the ratio of the liquid refrigerant that density is big will reduce.And the refrigerant amount in the accumulator 17 reduces, and the refrigerant amount of circulating path increases.
In the 3rd invention, when sending the liquid refrigerant in the accumulator 17 back to circulating path, according to making accumulator 17 be communicated with the suction side of compressing mechanism 11D, 11E communicating pipe 67.In case be communicated with the suction side of compressing mechanism 11D, 11E, then the liquid refrigerant of accumulator 17 inside is inhaled into compressing mechanism 11D, 11E.Thus, the liquid refrigerant in the accumulator 17 is sent back to circulating path forcibly, and the refrigerant amount in the accumulator 17 will reduce, and the refrigerant amount of circulating path increases.
In the 4th invention, when the liquid refrigerant in the accumulator 17 is sent back to circulating path, make accumulator 17 be communicated with the ejection side of compressing mechanism 11D, 11E according to means of communication 13 by heat source side heat exchanger 15, make the gas refrigerant of the high pressure of compressing mechanism 11D, 11E ejection flow into accumulator 17.In case high-pressure gas refrigerant flows into, then to invent in the same manner with described second, the pressurized liquid refrigerant in the inside of accumulator 17 will be discharged from.And, sent back to circulating path by set liquid pipe 53 from the liquid refrigerant that accumulator 17 is discharged from.Thus, the refrigerant amount in the accumulator 17 reduces, and the refrigerant amount of circulating path increases.
And the high-pressure gas refrigerant that compressing mechanism 11D, 11E are sprayed is imported into accumulator 17 by heat source side heat exchanger 15.In this 4th invention, utilize heat source side heat exchanger 15 to be used as being used for the high-pressure gas refrigerant of compressing mechanism 11D, 11E ejection is imported the circulation path of accumulator 17.
In the 5th invention,, then send the liquid refrigerants in the accumulator 17 back to circulating path according to cold-producing medium loopback mechanism 5 in case become more than the setting from first degree of superheat of cold-producing medium of utilizing side heat exchanger 31,41 to flow to the suction side of compressing mechanism 11D, 11E.But, utilize side heat exchanger 31,41 first, refrigerant flow more at least the flow of refrigerant of gas-liquid two-phase state area decreases and zone that single-phase gas refrigerant flows enlarges, therefore, utilize the refrigerant superheat degree that side heat exchanger 31,41 flows out will become big from first.In other words, owing to utilize the refrigerant superheat degree that side heat exchanger 31,41 flows out to reflect that first utilizes the flow of the cold-producing medium of side heat exchanger 31,41 from first, if use the detected value that sucks degree of superheat detector 79,81 can judge suitably that first utilizes the cold-producing medium of side heat exchanger 31,41 whether not enough.
In the 6th invention,, then send accumulator 17 interior liquid refrigerants back to circulating path according to cold-producing medium loopback mechanism 5 in case make the degree of superheat of cold-producing medium of compressing mechanism 11D, 11E ejection become setting when above.Yet as described, first utilizes the refrigerant flow of side heat exchanger 31,41 fewer, utilizes the degree of superheat that side heat exchanger 31,41 flows out the cold-producing medium that is inhaled into compressing mechanism 11D, 11E will become big from first.And the degree of superheat that is inhaled into the cold-producing medium of compressing mechanism 11D, 11E heals greatly, and the degree of superheat of the cold-producing medium that compressing mechanism 11D, 11E are sprayed also becomes big.In other words, because the refrigerant superheat degree that compressing mechanism 11D, 11E are sprayed reflects that first utilizes the refrigerant flow of side heat exchanger 31,41, if use the detected value of ejection degree of superheat detector 75,76 can judge suitably that first utilizes the cold-producing medium of side heat exchanger 31,41 whether not enough.
In the 7th invention,, the refrigerant temperature that makes compressing mechanism 11D, 11E be sprayed sends the cold-producing mediums in the accumulator 17 back to circulating path according to cold-producing medium loopback mechanism 5 in case becoming more than the setting.Yet as described, first utilizes the refrigerant flow of side heat exchanger 31,41 fewer, and the degree of superheat of the cold-producing medium of compressing mechanism 11D, 11E ejection will become big.And the degree of superheat of cold-producing medium greatly just its temperature uprises.In other words, because the refrigerant temperature that compressing mechanism 11D, 11E are sprayed reflects that first utilizes the refrigerant flow of side heat exchanger 31,41, utilize the cold-producing medium of side heat exchanger 31,41 whether not enough if use the detected value of ejection refrigerant temperature detector 76 can suitably judge first.
In the 8th invention,, then convert operating condition to second drive manner from first drive manner in accumulator 17 according to switching mechanism 12 in case liquid refrigerant accumulates in first drive manner.At second drive manner, with described the 4th invention similarly make accumulator 17 internal pressurization because the high-pressure gas refrigerant that sprayed of compressing mechanism 11D, 11E flows into accumulator 17, therefore the liquid refrigerant that is accumulated in first drive manner will be discharged from.And the liquid refrigerant that is discharged from from accumulator 17 is sent back to first by set liquid pipe 53 and is utilized side unit 30,40.
The invention effect
Among the present invention, in case be formed with that cold-producing medium flows into accumulator 17 then in the operating condition of the described circulating path that refrigerant amount will reduce, can make accumulator 17 interior liquid refrigerants get back to circulating path by cold-producing medium loopback mechanism 5.In case send the liquid refrigerant in the accumulator 17 back to circulating path, then flow through and respectively utilize the refrigerant amount of side unit 20,30,40 to increase.Therefore, before respectively utilizing side unit 20,30,40 lack of refrigerants, by sending the liquid refrigerant in the accumulator 17 back to circulating path according to cold-producing medium loopback mechanism 5, can prevent at the lack of refrigerant that respectively utilizes side unit 20,30,40, avoid decline in the adjustment ability of respectively utilizing side unit 20,30,40.
And in described the 3rd invention, when sending the liquid refrigerant in the accumulator 17 back to circulating path, compressing mechanism 11D, 11E will suck the liquid refrigerant in the accumulator 17, and therefore, the suction degree of superheat of compressing mechanism 11D, 11E can descend.Therefore, can send cold-producing medium back to circulating path and separate the lack of refrigerant that disappears, simultaneously can suppress to suck the degree of superheat and the input of cutting down compressing mechanism 11D, 11E.
And, in described the 4th invention, utilize in the kind of refrigeration cycle of refrigerant loop 50, to have to be used as being used for the high-pressure gas refrigerant of compressing mechanism 11D, 11E ejection is imported the circulation path of accumulator 17 as evaporimeter or as the heat source side heat exchanger 15 of condenser function.In other words, the part with the structure of refrigerating plant 1 is used to as cold-producing medium loopback mechanism 5.Therefore, can simplify the structure of refrigerating plant 1 with cold-producing medium loopback mechanism 5.
And, in described the 5th invention, be conceived to: can judge first from first degree of superheat of utilizing side heat exchanger 31,41 to flow to the cold-producing medium of compressing mechanism 11D, 11E suction side and utilize the cold-producing medium of side heat exchanger 31,41 whether not enough, make according to the detected value control cold-producing medium loopback mechanism 5 that sucks degree of superheat detector 79,81.Therefore, before first utilizes side heat exchanger 31,41 lack of refrigerants, send the liquid refrigerant in the accumulator 17 back to circulating path suitable opportunity, can positively avoid first and utilize the cooling capacity of side heat exchanger 31,41 to descend.
And, in described the 6th invention, be conceived to: whether the degree of superheat of the cold-producing medium that is sprayed from compressing mechanism 11D, 11E judge first and utilize the cold-producing medium of side heat exchanger 31,41 not enough, makes detected value control cold-producing medium loopback mechanism 5 according to ejection degree of superheat detector 75,76.Therefore, before first utilizes side heat exchanger 31,41 lack of refrigerants, send the liquid refrigerant in the accumulator 17 back to circulating path opportune moment, can positively avoid first decline that utilizes the cooling capacity of side heat exchanger 31,41.
And, in described the 7th invention, be conceived to: judge that from the refrigerant temperature that compressing mechanism 11D, 11E are sprayed first utilizes the cold-producing medium of side heat exchanger 31,41 whether not enough, so that control cold-producing medium loopback mechanism 5 according to the detected value of ejection refrigerant temperature detector 76.Therefore, before first utilizes side heat exchanger 31,41 lack of refrigerants, send the liquid refrigerant in the accumulator 17 back to circulating path opportune moment, can positively avoid first decline that utilizes side heat exchanger 31,41 cooling capacities.
And, in described the 8th invention,, can make that will accumulate in liquid refrigerant in the accumulator 17 in first drive manner sends first back to and utilize side unit 30,40 by converting second drive manner to from first drive manner.Therefore, if according to this 8th invention, in first drive manner, can prevent to avoid decline in the adjustment ability of respectively utilizing side unit 20,30,40 in the quantity not sufficient of respectively utilizing the cold-producing medium that circulates between side unit 20,30,40 and compressing mechanism 11D, the 11E.
Description of drawings
Fig. 1 illustrates the refrigerant loop figure of the refrigerating plant of the embodiment of the invention 1.
Fig. 2 illustrates the refrigerant loop figure of action of the cold air operation of embodiment 1.
Fig. 3 illustrates the refrigerant loop figure of action of the freezing running of embodiment 1.
Fig. 4 illustrates the refrigerant loop figure of action of the freezing running of first cold air of embodiment 1.
Fig. 5 illustrates the refrigerant loop figure of action of the freezing running of second cold air of embodiment 1.
Fig. 6 illustrates the refrigerant loop figure of action of the heating installation running of embodiment 1.
Fig. 7 illustrates the refrigerant loop figure of closed electromagnetic valve state action of hot-gas bypass pipe of the freezing running of first heating installation of embodiment 1.
Fig. 8 illustrates the magnetic valve of hot-gas bypass pipe of the freezing running of first heating installation of embodiment 1 and opens the refrigerant loop figure of state action.
Fig. 9 illustrates the refrigerant loop figure of action of the freezing running of second heating installation of embodiment 1.
Figure 10 illustrates the refrigerant loop figure of action of the freezing running of the 3rd heating installation of embodiment 1.
Figure 11 illustrates the refrigerant loop figure of the refrigerating plant of the embodiment of the invention 2.
Figure 12 illustrates the refrigerant loop figure of the refrigerating plant of the embodiment of the invention 3.
Figure 13 illustrates the refrigerant loop figure of refrigerating plant always.
Symbol description
The 1-refrigerating plant, 5-cold-producing medium loopback mechanism, the outdoor unit of 10-(heat source side unit), the 11D-compressing mechanism, the 11E-compressing mechanism, the 13-second four-way change-over valve means of communication, 15-outdoor heat converter (heat source side heat exchanger), the 17-accumulator, 20-indoor units (second utilizes the side unit), 21-indoor heat converter (second utilizes the side heat exchanger), 30-refrigerates unit (first utilizes the side unit), 31-refrigerates heat exchanger (first utilizes the side heat exchanger), the freezing unit of 40-(first utilizes the side unit), 41-freezing heat-exchanger (first utilizes the side heat exchanger), the 50-refrigerant loop, the 50A-first system side loop, the 50B-second system side loop, 51-first gas side communication pipe arrangement (gas side communication pipe arrangement), 52-second gas side communication pipe arrangement (gas side communication pipe arrangement), 53-gathers liquid pipe (hydraulic fluid side communication pipe arrangement), 54-first difference (liquid pipe hydraulic fluid side communication pipe arrangement), 55-second difference (liquid pipe hydraulic fluid side communication pipe arrangement), 67-liquid injecting tube (communicating pipe), 71-hot-gas bypass pipe (ingress pipe), 75-high-pressure sensor (ejection degree of superheat detector), 76-ejection temperature sensor (ejection degree of superheat detector, ejection refrigerant temperature detector), 79-low-pressure sensor (sucking degree of superheat detector), 81-inlet temperature sensor (sucking degree of superheat detector), the 95-controller
The specific embodiment
Below, describe embodiments of the invention in detail according to accompanying drawing.
" embodiment 1 "
Embodiments of the invention 1 below are described.The refrigerant loop figure of the refrigerating plant 1 that present embodiment 1 is related as shown in Figure 1.This refrigerating plant 1 is provided in a side of convenience store and is used for carrying out changes in temperature gas in cooling refrigeration showcase and refrigerated display case and the supply shop.
Described refrigerating plant 1 possesses: outdoor unit (heat source side unit) 10, indoor units (second utilizes the side unit) 20, refrigeration unit (first utilizes the side unit) 30 and freezing unit (first utilizes the side unit) 40, each unit 10,20,30,40 usefulness gas sides communication pipe arrangement 51,52 is connected with hydraulic fluid side communication pipe arrangement 53,54,55, constitutes the refrigerant loop 50 of steam compression type refrigerating circulation.
Second gas side communication pipe arrangement, 52 formations that gas side communication pipe arrangement 51,52 is communicated pipe arrangement (low pressure tracheae) 51 and has been connected outdoor unit 10 and indoor units 20 by first gas side that has connected outdoor unit 10, refrigeration unit 30 and freezing unit 40.Hydraulic fluid side communication pipe arrangement 53,54,55, by the set liquid pipe 53 that has connected outdoor unit 10, from the inconsistent connection in 53 fens of this set liquid pipe refrigerate the first difference liquid pipe 54 of unit 30 and freezing unit 40 and in 53 fens inconsistent junction chambers of this set liquid pipe the second difference liquid pipe 55 of unit 20 constitute.And the first difference liquid pipe 54 is made of the refrigeration side first difference liquid pipe 54a of refrigeration unit 30 sides and the freezing side first difference liquid pipe 54b of freezing unit 40 sides.In the present embodiment 1,, adopted three-tube type communication matched tube structure by making the set liquid pipe 53 of part of outdoor unit 10 1 sides of hydraulic fluid side communication pipe arrangement 53,54,55 shared for indoor units 20 and refrigerating unit 30,40.
The constituting of described indoor units 20 can be carried out the conversion of cold air operation and heating installation running, for example is set at sales field etc.And described refrigeration unit 30 is arranged on air in refrigeration is used for cooling off this showcase with showcase the storehouse.Described freezing unit 40 is arranged on air in the freezing storehouse that is used for cooling off this showcase with showcase.Though one indoor units 20, refrigeration unit 30 and freezing unit 40 only are shown among the figure,, be 2 in parallel indoor units 20 and 8 in parallel refrigeration unit 30 in the present embodiment 1, and connect one freezing unit 40.
And refrigerant loop 50 has possessed refrigerating with the first system side loop 50A and the idle call second system side loop 50B; By utilizing the refrigeration unit 30 of side unit and freezing unit 40 to constitute as the outdoor unit 10 of heat source side unit and as first, cold-producing medium is unidirectional circulation to this refrigerating with the first system side loop 50A; This idle call second system side loop 50B is by utilizing the indoor units 20 of side unit to constitute as the outdoor unit 10 of heat source side unit with as second, and cold-producing medium is a Reversible Cycle.
＜outdoor unit 〉
Described outdoor unit 10 possesses frequency-changeable compressor 11A as first compressor, as the first invariable frequency compressor 11B of second compressor with as the second invariable frequency compressor 11C of the 3rd compressor, possess first four-way change-over valve 12, second four-way change-over valve 13 and the 3rd four-way change-over valve 14 simultaneously and as the outdoor heat converter 15 of heat source side heat exchanger.And outdoor heat converter 15 is the fin tube heat exchanger of plate-fin for example, is set at as near the outdoor fan 16 of thermal source fan.
Described each compressor 11A, 11B, 11C for example constitute with hermetic type high pressure dome type scroll compressor.Described frequency-changeable compressor 11A is that motor is stage or the variable variable displacement compressor of continuity by Frequency Converter Control, capacity.The described first invariable frequency compressor 11B and the second invariable frequency compressor 11C are the fixed-capacity compressor that motor often drives with certain rotating speed.
Described frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C constitute compressing mechanism 11D, the 11E of this refrigerating plant 1; This compressing mechanism 11D, 11E are made of the compressing mechanism 11D of first system and the compressing mechanism 11E of second system.Specifically, compressing mechanism 11D, 11E, following situation is arranged in the running: constitute the compressing mechanism 11D of first system and constitute the situation of the compressing mechanism 11E of second system by the frequency-changeable compressor 11A and the first invariable frequency compressor 11B, and constitute the compressing mechanism 11D of first system and constitute the situation of the compressing mechanism 11E of second system by the first invariable frequency compressor 11B and the second invariable frequency compressor 11C by frequency-changeable compressor 11A by the second invariable frequency compressor 11C.In other words, it is used that frequency-changeable compressor 11A is fixed as the first system side loop 50A that refrigerating uses, and that the second invariable frequency compressor 11C is fixed as the second system side loop 50B of idle call is used, on the other hand, the first invariable frequency compressor 11B can be converted to the first system side loop 50A and the second system side loop 50B is used.
Each bleed pipe 56a, 56b, the 56c of described frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C is connected to a high-pressure air pipe (ejection pipe arrangement) 57.Be respectively arranged with non-return valve CV1, CV2 at the bleed pipe 56b of the described first invariable frequency compressor 11B and the bleed pipe 56c of the second invariable frequency compressor 11C.
Described high-pressure air pipe 57 is connected to the first valve port P1 of first four-way change-over valve 12.The gas side end of described outdoor heat converter 15 connects the second valve port P2 of first four-way change-over valve 12 by the outdoor first tracheae 58a.The 3rd valve port P3 at first four-way change-over valve 12 is connected with second gas side communication pipe arrangement 52 by the outdoor second tracheae 58b.The 4th valve port P4 of first four-way change-over valve 12 connects second four-way change-over valve 13.
The first valve port P1 of described second four-way change-over valve 13 is by the bleed pipe 56c of the auxiliary tracheae 59 connections second invariable frequency compressor 11C.The second valve port P2 of second four-way change-over valve 13 is made of the sealing valve port that is closed.The 3rd valve port P3 of second four-way change-over valve 13 is by the 4th valve port P4 of described first four-way change-over valve 12 of tube connector 60 connections.And the 4th valve port P4 of second four-way change-over valve 13 connects the suction line 61c of the second invariable frequency compressor 11C.Because therefore the second valve port P2 of second four-way change-over valve 13 also can use triple valve to be replaced for the sealing valve port.
Described first four-way change-over valve 12 constitute first state of can changing and second state; First state is that the first valve port P1 and the second valve port P2 are communicated with, and the 3rd valve port P3 and the 4th valve port P4 are communicated with (state shown in Fig. 1 solid line); Second state is that the first valve port P1 and the 3rd valve port P3 are communicated with, and the second valve port P2 and the 4th valve port P4 are communicated with (state shown in Fig. 1 dotted line).
And, described second four-way change-over valve 13 constitute first state of can changing and second state; First state is that the first valve port P1 and the second valve port P2 are communicated with, and the 3rd valve port P3 and the 4th valve port P4 are communicated with (state shown in Fig. 1 solid line); Second state is that the first valve port P1 and the 3rd valve port P3 are communicated with, and the second valve port P2 and the 4th valve port P4 are communicated with (state shown in Fig. 1 dotted line).
Be connected with a end as the outdoor liquid pipe 62 of liquid pipe in the end, hydraulic fluid side of described outdoor heat converter 15.At the accumulator 17 that being provided with of outdoor liquid pipe 62 accumulated liquid refrigerant midway, the other end of outdoor liquid pipe 62 connects the set liquid pipe 53 of hydraulic fluid side communication pipe arrangement 53,54,55.
Described accumulator 17 is by allowing the first inflow pipe 63a that cold-producing medium thermotropism source heat exchanger 15 flows into, allow the first effuser 63b that cold-producing medium flows out to hydraulic fluid side communication pipe arrangement 53,54,55, allow the second inflow pipe 63c that cold-producing medium flows into from hydraulic fluid side communication pipe arrangement 53,54,55 and allowing that the second effuser 63d that cold-producing medium flows out to outdoor heat converter 15 is connected heat source side heat exchanger 15 and the hydraulic fluid side pipe arrangement 53,54,55 of communicating.
The suction line 61a of described frequency-changeable compressor 11A is by low pressure tracheae 64 connections first gas side communication pipe arrangement 51 of the first system side loop 50A.The suction line 61c of the second invariable frequency compressor 11C is by the low pressure tracheae (outdoor first tracheae 58a or the outdoor second tracheae 58b) of first, second four-way change-over valve 12,13 connections second system side loop 50B.And the suction line 61b of the first invariable frequency compressor 11B connects the suction line 61a of frequency-changeable compressor 11A or the suction line 61c of the second invariable frequency compressor 11C by the 3rd four-way change-over valve 14.
Specifically, be connected with branch pipe 61d, be connected with branch pipe 61e at the suction line 61c of the second invariable frequency compressor 11C at the suction line 61a of frequency-changeable compressor 11A.And, the branch pipe 61d of the suction line 61a of frequency-changeable compressor 11A connects the first valve port P1 of the 3rd four-way change-over valve 14 by non-return valve CV3, the suction line 61b of the first invariable frequency compressor 11B connects the second valve port P2 of the 3rd four-way change-over valve 14, and the branch pipe 61e of the suction line 61c of the second invariable frequency compressor 11C connects the 3rd valve port P3 of the 3rd four-way change-over valve 14 by non-return valve CV4.Only allow refrigerant flow direction the 3rd four-way change-over valve 14 at described branch pipe 61d, 61e set non-return valve CV3, CV4, and forbid flowing of rightabout cold-producing medium.And,, be connected with the high pressure ingress pipe of the high-pressure that is used for importing refrigerant loop 50 at the 4th valve port P4 of the 3rd four-way change-over valve 14 though omit in the accompanying drawings.
Described the 3rd four-way change-over valve 14 constitute first state of can changing and second state; First state is that the first valve port P1 and the second valve port P2 are communicated with, and the 3rd valve port P3 and the 4th valve port P4 are communicated with (state shown in Fig. 1 solid line); Second state is that the first valve port P1 and the 4th valve port P4 are communicated with, and the second valve port P2 and the 3rd valve port P3 are communicated with (state shown in Fig. 1 dotted line).
The set liquid pipe 53 of first gas side communication pipe arrangement 51 and second gas side communication pipe arrangement 52 and described communication liquid pipe 53,54,55 is to extend to the outside from outdoor unit 10, is provided with draught excluder 18a, 18b, the 18c corresponding with it in outdoor unit 10.
At described outdoor liquid pipe 62, be connected with auxiliary liquid pipe 65 (the second effuser 63d) and the liquid branch pipe 66 (the second inflow pipe 63c) of walking around accumulator 17 jointly.Auxiliary liquid pipe 65 mainly is that cold-producing medium flows through, is provided with the outdoor expansion valve 19 as expansion mechanism when greenhouse.One end of auxiliary liquid pipe 65 is connected to (the first inflow pipe 63a) between outdoor heat converter 15 and the accumulator 17, and the other end of auxiliary liquid pipe 65 is connected between accumulator 17 and the draught excluder 18c.Be provided with the non-return valve CV5 that only allows refrigerant flow direction accumulator 17 between auxiliary liquid pipe 65 in outdoor liquid pipe 62 and the tie point of outdoor heat converter 15 1 sides and the accumulator 17.
And,, be provided with non-return valve CV6 and pressure-reducing valve 107 in order from draught excluder 18c one side at liquid branch pipe 66.Non-return valve CV6 be only allow cold-producing medium from draught excluder 18c one effluent to accumulator 17.And when in a single day the refrigerant pressure of work became authorized pressure such as 1.5MPa, pressure-reducing valve 107 will be opened automatically, on the other hand, till surpassing this authorized pressure liquid branch pipe 66 was remained on closed condition.One end of liquid branch pipe 66 is connected between non-return valve CV5 and the accumulator 17, and the other end is connected between the tie point and draught excluder 18c auxiliary liquid pipe 65 and draught excluder 18c one side in the outdoor liquid pipe 62.
And, outdoor liquid pipe 62 and the tie point of auxiliary liquid pipe 65 and draught excluder 18c one side and and the tie point of liquid branch pipe 66 and draught excluder 18c one side between (the first effuser 63b) be provided with non-return valve CV7.This non-return valve CV7 only allows that cold-producing medium flows to draught excluder 18c from accumulator 17.
And, between the accumulator 17 of outdoor liquid pipe 62 and non-return valve CV5, be connected with a end as the hot-gas bypass pipe 71 of ingress pipe.The other end of hot-gas bypass pipe 71 is connected between the draught excluder 18b and first four-way change-over valve 12 of the outdoor second tracheae 58b, and the way is provided with magnetic valve SV1 therein.Hot-gas bypass pipe 71 and magnetic valve SV1 have constituted cold-producing medium loopback of the present invention mechanism 5.
And, being connected with liquid injecting tube 67 at liquid branch pipe 66, an end of this liquid injecting tube 67 is connected with the connecting portion of low pressure tracheae 64 with suction line 61a.The other end of liquid injecting tube 67 is connected between non-return valve CV6 and the pressure-reducing valve 107.Be provided with the electric expansion valve 67a that is used for adjusting flow at this liquid injecting tube 67.
＜indoor units 〉
Described indoor units 20 has as second utilizes the indoor heat converter (heat exchanger of air condition) 21 of side heat exchanger and as the indoor expansion valve 22 of expansion mechanism.The gas side of described indoor heat converter 21 connects second gas side communication pipe arrangement 52.And the hydraulic fluid side of described indoor heat converter 21 connects the second difference liquid pipe 55 of hydraulic fluid side communication pipe arrangement 53,54,55 by indoor expansion valve 22.And described indoor heat converter 21 is the fin tube heat exchanger of plate-fin for example, is installed in as near the indoor fan 23 that utilizes the crosswind fan.And indoor expansion valve 22 is made of electric expansion valve.
＜refrigeration unit 〉
Described refrigeration unit 30 has as first and utilizes the refrigeration heat exchanger 31 of side heat exchanger and as the refrigeration expansion valve 32 of expansion mechanism.The hydraulic fluid side of described refrigeration heat exchanger 31 connects the first difference liquid pipe 54 (the refrigeration side first difference liquid pipe 54a) of hydraulic fluid side communication pipe arrangement 53,54,55 by magnetic valve SV2 and refrigeration expansion valve 32.This magnetic valve SV2 is used for stopping to flow of cold-producing medium when stopping running.On the other hand, the gas side of described refrigeration heat exchanger 31 is connected with from 51 fens inconsistent refrigeration side difference tracheae 51a of first gas side communication pipe arrangement.
Refrigeration heat exchanger 31 is communicated with the suction side of frequency-changeable compressor 11A, and on the other hand, described indoor heat converter 21 is communicated with the suction side of the second invariable frequency compressor 11C when cold air operation.The refrigerant pressure of described refrigeration heat exchanger 31 (evaporating pressure) will be lower than the refrigerant pressure (evaporating pressure) of indoor heat converter 21.Specifically, the cold-producing medium evaporating temperature of described refrigeration heat exchanger 31 is-10 ℃ for example, and the cold-producing medium evaporating temperature of indoor heat converter 21 is+5 ℃ for example, and refrigerant loop 50 constitutes the loop of different temperature evaporation.
And described refrigeration expansion valve 32 is thermal expansion valves, and temperature sensing tube is installed in the gas side of refrigeration heat exchanger 31.Therefore, refrigeration expansion valve 32 is adjusted aperture according to the refrigerant temperature of refrigeration heat exchanger 31 outlet sides.Described refrigeration heat exchanger 31 is the fin tube heat exchanger of plate-fin for example, is installed in as near the refrigeration fan 33 of cooling fan.
＜freezing unit 〉
Described freezing unit 40 has as first freezing heat-exchanger 41 that utilizes the side heat exchanger, as the freezing expansion valve 42 of expansion mechanism with as the booster compressor 43 of refrigerant condenser.The hydraulic fluid side of described freezing heat-exchanger 41 is connected the first difference liquid pipe 54 (the freezing side first difference liquid pipe 54b) of hydraulic fluid side communication pipe arrangement 53,54,55 with freezing expansion valve 42 by magnetic valve SV3.
The suction side of the gas side of described freezing heat-exchanger 41 and booster compressor 43 connects by being connected tracheae 68.Ejection side at booster compressor 43 is connected with from 51 fens inconsistent freezing side difference tracheae 51b of first gas side communication pipe arrangement.Be provided with non-return valve CV8 and oil eliminator 44 at freezing side difference tracheae 51b.Between oil eliminator 44 and connection tracheae 68, connect oil return pipe 69 with capillary 45.
Described booster compressor 43 and the compressing mechanism 11D of first system between with the compression of cold-producing medium twin-stage, make the evaporating temperature of cold-producing medium of freezing heat-exchanger 41 be lower than the evaporating temperature of the cold-producing medium of refrigeration heat exchanger 31.The evaporating temperature of the cold-producing medium of described freezing heat-exchanger 41 for example is set to-35 ℃.
And described freezing expansion valve 42 is thermal expansion valves, and temperature sensing tube is installed in the gas side of freezing heat-exchanger 41.Described freezing heat-exchanger 41 is the fin tube heat exchanger of plate-fin for example, is installed in as near the freezing fan 46 of cooling fan.
And, between the connection tracheae 68 and oil eliminator 44 and non-return valve CV8 among the freezing side difference tracheae 51b of the suction side of described booster compressor 43, be connected with the bypass pipe 70 of non-return valve CV9.The constituting of this bypass pipe 70 makes cold-producing medium walk around this booster compressor 43 when booster compressor 43 faults etc. stop to flow.
＜control system 〉
Be provided with various sensors and various switch at described refrigerant loop 50.High-pressure air pipe 57 at described outdoor unit 10 is provided with high-pressure sensor 75 that detects high-pressure refrigerant pressure and the ejection temperature sensor 76 that detects the high-pressure refrigerant temperature.Be provided with the ejection temperature sensor 77 that detects the high-pressure refrigerant temperature at the bleed pipe 56c of the described second invariable frequency compressor 11C.And; each bleed pipe 56a, 56b, 56c at described frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C are respectively equipped with the pressure switch 78 that high voltage protective is used, and the pressure switch 78 that this high voltage protective is used is that compressor 11A, 11B, 11C are stopped.
Be provided with low- pressure sensor 79,80 that detects low pressure refrigerant pressure and the inlet temperature sensor 81,82 that detects the low pressure refrigerant temperature at each suction line 61a, 61c of the described frequency-changeable compressor 11A and the second invariable frequency compressor 11C.The low-pressure sensor 79 of frequency-changeable compressor 11A one side and inlet temperature sensor 81 have constituted suction degree of superheat detector of the present invention.
Be provided with outdoor heat exchange sensor 83 at described outdoor heat converter 15, this outdoor heat exchange sensor 83 is to be used for detecting in the refrigerant temperature of outdoor heat converter 15, just evaporating temperature or adiabatic condensation temperature.And, be provided with the outer air-temperature sensor 84 that detects outside air temperature at described outdoor unit 10.
Be provided with indoor heat exchange sensor 85 at described indoor heat converter 21, this indoor heat exchange sensor 85 is to be used for detecting in the refrigerant temperature of indoor heat converter 21, just adiabatic condensation temperature or evaporating temperature, is provided with the air-temperature sensor 86 that detects the gas refrigerant temperature at gas side simultaneously.And, be provided with the temperature sensor 87 that detects indoor air temperature in described indoor units 20.
Be provided with the refrigerated storage temperature sensor 88 of detection refrigeration at described refrigeration unit 30 with the storehouse temperature in the showcase.Be provided with the freezing cryogenic temperature sensor 89 of detection at described freezing unit 40 with the storehouse temperature in the showcase.And, being provided with the pressure switch 90 that high voltage protective is used in the ejection side of booster compressor 43, this is then to open and make this compressor 43 stop when the ejection refrigerant pressure becomes setting.
The output signal of described various sensor and various switches is output to the controller 95 as control mode.The running that constitutes control refrigerant loop 50 of this controller 95 is so that can change eight kinds of drive manners described later.And, controller 95, control in the running frequency-changeable compressor 11A startup, stop and volume controlled or the startup of the first invariable frequency compressor 11B and the second invariable frequency compressor 11C and stop, controlling further the aperture adjusting etc. of outdoor expansion valve 19 and indoor expansion valve 22, also control the conversion of each four-way change-over valve 12,13,14 or the aperture control of the electric expansion valve 67a of liquid injecting tube 67 etc. simultaneously.
And controller 95 when the freezing running of first heating installation described later, also carries out the switch control to the magnetic valve SV1 of hot-gas bypass pipe 71.Specifically, carry out following control when the freezing running of first heating installation that is formed with circulating path, aforesaid this circulating path is: the cold-producing medium that compressing mechanism 11D sent utilizes the refrigeration unit 30 of side unit and freezing unit 40 and returns compressing mechanism 11D as first from utilizing the indoor units 20 of side unit to flow through as second.
At first, the detected value of the detected value of controller 95 usefulness low-pressure sensors 79 and inlet temperature sensor 81 detects from as first degree of superheat of utilizing the cold-producing medium of the refrigeration heat exchanger 31 of side heat exchanger and the suction side that freezing heat-exchanger 41 flows to compressing mechanism 11D.And when this detected degree of superheat becomes setting when above, controller 95 opens solenoid valve SV1 are when the degree of superheat is closed magnetic valve SV1 during less than setting.
Whether controller 95 is judged from the degree of superheat of the cold-producing medium that is inhaled into compressing mechanism 11D and is being utilized the cold-producing medium of the refrigeration heat exchanger 31 of side heat exchanger and freezing heat-exchanger 41 not enough as first.When in a single day controller 95 judges that when refrigerating the lack of refrigerant of heat exchanger 31 and freezing heat-exchanger 41, then opens solenoid valve SV1 is so that send the cold-producing mediums in the accumulator 17 back to circulating path.
-running action-
Then, the running action that relevant refrigerating plant 1 is carried out is illustrated according to each running.It constitutes and can set eight kinds of drive manners in the present embodiment 1.Specifically,＜i〉only carry out the cold air operation of indoor units 20 cold air,＜ii〉only refrigerate the freezing running of the cooling of unit 30 and freezing unit 40,＜iii〉carry out the cold air of indoor units 20 simultaneously, and the freezing running of first cold air of the cooling of refrigeration unit 30 and freezing unit 40,＜iv〉the freezing running of second cold air of running when the cold air scarce capacity of first cold air indoor units 20 of freezing when running,＜v〉only carry out the heating installation running of the heating installation of indoor units 20,＜vi〉do not use outdoor heat converter 15 to carry out the heating installation of indoor units 20 with 100% recuperation of heat running, and the freezing running of first heating installation of the cooling of refrigeration unit 30 and freezing unit 40,＜vii〉the freezing running of second heating installation when the heating installation ability of the freezing running indoor units 20 of first heating installation is superfluous, carried out, and＜viii〉the freezing running of the 3rd heating installation when the heating installation scarce capacity of the freezing running indoor units 20 of first heating installation, carried out.
Below, specify the action of each running.
＜cold air operation 〉
This cold air operation is the running of only carrying out indoor units 20 cold air.During this cold air operation, as shown in Figure 2, constitute the compressing mechanism 11D of first system by frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C constitute the compressing mechanism 11E of second system.And, only drive the first invariable frequency compressor 11B and the second invariable frequency compressor 11C of second 11E of system compresses mechanism.
And shown in Fig. 2 solid line, first four-way change-over valve 12 and second four-way change-over valve 13 are converted to first state respectively, and the 3rd four-way change-over valve 14 is converted to second state.And the electric expansion valve 67a of outdoor expansion valve 19, liquid injecting tube 67, the magnetic valve SV1 of hot-gas bypass pipe 71, the magnetic valve SV2 of refrigeration unit 30 and the magnetic valve SV3 of freezing unit 40 close.
In this state, the cold-producing medium that the first invariable frequency compressor 11B and the second invariable frequency compressor 11C are sprayed flows to outdoor heat converter 15 through the outdoor first tracheae 58a and condenses from first four-way change-over valve 12.This liquid refrigerant that condenses flows through outdoor liquid pipe 62, and process accumulator 17 flows to indoor heat converter 21 evaporations by the set liquid pipe 53 and the second difference liquid pipe 55 of hydraulic fluid side communication pipe arrangement 53,54,55 from indoor expansion valve 22.The vaporized gas cold-producing medium flows through the suction line 61c of the second invariable frequency compressor 11C from second gas side communication pipe arrangement 52 and the outdoor second tracheae 58b, through first four-way change-over valve 12 and second four-way change-over valve 13.The part of this low-pressure refrigerant gas is got back to the second invariable frequency compressor 11C, and remaining gas refrigerant is diverted to branch pipe 61e from the suction line 61c of the second invariable frequency compressor 11C, gets back to the first invariable frequency compressor 11B by the 3rd four-way change-over valve 14.Repeating above-mentioned circulation by cold-producing medium makes in the shop nice and cool.
And this operating condition is loaded according to indoor cold air and is controlled the startup of the first invariable frequency compressor 11B and the second invariable frequency compressor 11C and stop or the aperture of indoor expansion valve 22 etc.One compressor 11B, 11C also can only turn round.
＜freezing running 〉
Freezing running is the running that only refrigerates the cooling of unit 30 and freezing unit 40.During this freezing running, as shown in Figure 3, constitute the compressing mechanism 11D of first system, constitute the compressing mechanism 11E of second system by the second invariable frequency compressor 11C by the frequency-changeable compressor 11A and the first invariable frequency compressor 11B.And, drive as the frequency-changeable compressor 11A of the compressing mechanism 11D of first system and drive the first invariable frequency compressor 11B, also drive booster compressor 43 simultaneously, and stop the second invariable frequency compressor 11C.
And first four-way change-over valve 12, second four-way change-over valve 13 and the 3rd four-way change-over valve 14 shown in Fig. 3 solid line, are converted to first state separately.Further, the magnetic valve SV2 of refrigeration unit 30 and the magnetic valve SV3 of freezing unit 40 open, and the magnetic valve SV1 of hot-gas bypass pipe 71, outdoor expansion valve 19 and indoor expansion valve 22 are closed.And the electric expansion valve 67a of liquid injecting tube 67 is configured to full cut-off or sets become the regulation aperture so that the liquid refrigerant of regulation flow can circulate according to operating condition.
In this state, the cold-producing medium that the frequency-changeable compressor 11A and the first invariable frequency compressor 11B are sprayed flows to outdoor heat converter 15 from first four-way change-over valve 12 through the outdoor first tracheae 58a and condenses.This liquid refrigerant that condenses flows through outdoor liquid pipe 62 through accumulator 17, and the set liquid pipe 53 of the pipe arrangement 53,54,55 of communicating from the hydraulic fluid side is diverted to refrigeration side first difference liquid pipe 54a and the freezing side first difference liquid pipe 54b.
Flowing through refrigerates the liquid refrigerant of the side first difference liquid pipe 54a, flows to refrigeration heat exchanger 31 through refrigeration expansion valve 32 and evaporates and flow through refrigeration side difference tracheae 51a.On the other hand, the liquid refrigerant of the freezing side first difference liquid pipe 54b that flows through flows to freezing heat-exchanger 41 evaporations through freezing expansion valve 42.Being inhaled into booster compressor 43 at these freezing heat-exchanger 41 vaporized gas cold-producing mediums is compressed and is ejected into freezing side difference tracheae 51b.
At described refrigeration heat exchanger 31 vaporized gas cold-producing mediums with from the gas refrigerant of booster compressor 43 ejection, get back to the frequency-changeable compressor 11A and the first invariable frequency compressor 11B by low pressure tracheae 64 at first gas side communication pipe arrangement, 51 interflow.Repeat above-mentioned circulation by cold-producing medium and come cooling refrigeration showcase and freezing with in the storehouse of showcase.
At the refrigerant pressure of described freezing heat-exchanger 41, owing to be attracted at booster compressor 43, therefore the refrigerant pressure at refrigeration heat exchanger 31 becomes low pressure.As a result, for example the refrigerant temperature (evaporating temperature) at freezing heat-exchanger 41 becomes-35 ℃, and becomes-10 ℃ in the refrigerant temperature (evaporating temperature) of refrigeration heat exchanger 31.
When this freezing running, for example control the startup of the first invariable frequency compressor 11B according to low-pressure sensor 79 detected low pressure refrigerant pressure (LP) and stop or controlling frequency-changeable compressor 11A startup, stop or volume controlled is carried out the running of corresponding freezing load.
For example increase the control of compressing mechanism 11D capacity, at first the state-driven frequency-changeable compressor 11A that stops at the first invariable frequency compressor 11B.Frequency-changeable compressor 11A rises to after the heap(ed) capacity in case load drives the first invariable frequency compressor 11B when further increasing and makes frequency-changeable compressor 11A be reduced to lowest capacity simultaneously.If load further increase, the capacity of frequency-changeable compressor 11A risen thereafter.When reducing the control of compressor capacity, then carry out increasing the opposite action of control with this.
And the aperture of described refrigeration expansion valve 32 and freezing expansion valve 42 is carried out the degree of superheat control according to temperature sensing tube.Relevant this point also is identical in each following running.
The freezing running of＜the first cold air 〉
The freezing running of this first cold air is the running of carrying out the cooling of the cold air of indoor units 20 and refrigeration unit 30 and freezing unit 40 simultaneously.During the freezing running of this first cold air, as shown in Figure 4, constitute the compressing mechanism 11D of first system, constitute the compressing mechanism 11E of second system by the second invariable frequency compressor 11C by the frequency-changeable compressor 11A and the first invariable frequency compressor 11B.And, drive frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C, also drive booster compressor 43 simultaneously.
And first four-way change-over valve 12, second four-way change-over valve 13 and the 3rd four-way change-over valve 14 shown in the solid line, are converted to first state as Fig. 4 separately.Further, the magnetic valve SV2 of refrigeration unit 30 and the magnetic valve SV3 of freezing unit 40 open, and on the other hand, the magnetic valve SV1 and the outdoor expansion valve 19 of hot-gas bypass pipe 71 are closed.And the electric expansion valve 67a of liquid injecting tube 67 is set to full cut-off according to operating condition or is set at the regulation aperture suction side of the compressing mechanism 11D so that the cold-producing medium of regulation flow is flowed through.
In this state, the cold-producing medium that frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C are sprayed at high-pressure air pipe 57 interflow, flows to outdoor heat converter 15 from first four-way change-over valve 12 through the outdoor first tracheae 58a and condenses.The liquid refrigerant that this condenses flows through outdoor liquid pipe 62, through accumulator 17, flows to the set liquid pipe 53 of hydraulic fluid side communication pipe arrangement 53,54,55.
The part of liquid refrigerant of set liquid pipe 53 of described hydraulic fluid side communication pipe arrangement 53,54,55 of flowing through is diverted to the second difference liquid pipe 55, flows to indoor heat converter 21 evaporations through indoor expansion valve 22.This vaporized gas cold-producing medium flows through suction line 61c and gets back to the second invariable frequency compressor 11C through first four-way change-over valve 12 and second four-way change-over valve 13 from second gas side communication pipe arrangement 52 and the outdoor second tracheae 58b.
On the other hand, the liquid refrigerant that flows to the set liquid pipe 53 of described hydraulic fluid side communication pipe arrangement 53,54,55 is diverted to refrigeration side first difference liquid pipe 54a and the freezing side first difference liquid pipe 54b.The liquid refrigerant of the refrigeration side of the flowing through first difference liquid pipe 54a flows to 31 evaporations of refrigeration heat exchanger through refrigeration expansion valve 32 and flows through refrigeration side difference tracheae 51a.And the liquid refrigerant of the freezing side first difference liquid pipe 54b that flows through flows to freezing heat-exchanger 41 evaporations through freezing expansion valve 42.At these freezing heat-exchanger 41 vaporized gas cold-producing mediums, be pressurized compressor 43 and attract compression, be ejected into freezing side difference tracheae 51b.
At described refrigeration heat exchanger 31 vaporized gas cold-producing mediums with from the gas refrigerant of booster compressor 43 ejection,, get back to the frequency-changeable compressor 11A and the first invariable frequency compressor 11B by low pressure tracheae 64 at first gas side communication pipe arrangement, 51 interflow.
Repeat above-mentioned circulation by cold-producing medium and feel nice and cool in the shop, cooling refrigeration is with showcase and freezing with in the storehouse of showcase simultaneously.
The freezing running of＜the second cold air 〉
The freezing running of second cold air is the running when the cold air scarce capacity of described first cold air indoor units 20 of freezing when running, the first invariable frequency compressor 11B is converted to the running of air-conditioning side.The setting in this second cold air freezing when running, identical during basically with the freezing running of first cold air as shown in Figure 5, still, this point that is converted to second state at the 3rd four-way change-over valve 14 is different with the freezing running of first cold air.
Therefore, when the freezing running of this second cold air, with the freezing running of first cold air similarly, condense at outdoor heat converter 15 from the cold-producing medium of frequency-changeable compressor 11A, the first invariable frequency compressor 11B and second invariable frequency compressor 11C ejection, and in indoor heat converter 21, refrigeration heat exchanger 31 and freezing heat-exchanger 41 evaporations.
And, get back to the first invariable frequency compressor 11B and the second invariable frequency compressor 11C at the cold-producing medium of described indoor heat converter 21 evaporations, then get back to frequency-changeable compressor 11A at the cold-producing medium of refrigeration heat exchanger 31 and freezing heat-exchanger 41 evaporations.By use two compressor 11B, 11C to remedy the deficiency of cold air ability in the air-conditioning side.
＜heating installation running 〉
This heating installation running is the running of only carrying out the heating installation of indoor units 20.During the running of this heating installation, as shown in Figure 6, constitute the compressing mechanism 11D of first system, constitute the compressing mechanism 11E of second system by the first invariable frequency compressor 11B and the second invariable frequency compressor 11C by frequency-changeable compressor 11A.And, only drive the first invariable frequency compressor 11B and the second invariable frequency compressor 11C of the compressing mechanism 11E of second system.
And shown in Fig. 6 solid line, first four-way change-over valve 12 is converted to second state, and second four-way change-over valve 13 is converted to first state, and the 3rd four-way change-over valve 14 is converted to second state.On the other hand, the magnetic valve SV1 of the electric expansion valve 67a of liquid injecting tube 67, hot-gas bypass pipe 71, the magnetic valve SV2 of refrigeration unit 30 and the magnetic valve SV3 of freezing unit 40 close.And indoor expansion valve 22 is set to standard-sized sheet, and described outdoor expansion valve 19 is controlled in the regulation aperture.
In this state, the cold-producing medium of the first invariable frequency compressor 11B and second invariable frequency compressor 11C ejection flows to indoor heat converter 21 from first four-way change-over valve 12 through the outdoor second tracheae 58b and second gas side communication pipe arrangement 52 and condenses.This liquid refrigerant that condenses is flowed through from the second difference liquid pipe 55 of hydraulic fluid side communication pipe arrangement 53,54,55 and is gathered liquid pipe 53, further flows into accumulators 17 by liquid branch pipe 66.Thereafter, described liquid refrigerant flows through outdoor heat converter 15 evaporations through the outdoor expansion valve 19 of auxiliary liquid pipe 65.This vaporized gas cold-producing medium is from the outdoor first tracheae 58a, get back to the first invariable frequency compressor 11B and the second invariable frequency compressor 11C through the flow through suction line 61c of the second invariable frequency compressor 11C of first four-way change-over valve 12 and second four-way change-over valve 13.By repeat this circulate heat indoor.
And and similarly also can only turn round one compressor 11B, 11C of cold air operation.
The freezing running of＜the first heating installation 〉
The freezing running of this first heating installation is not use outdoor heat converter 15 with the turn round cooling of the heating installation that carries out indoor units 20 and refrigeration unit 30 and freezing unit 40 of 100% recuperation of heat.The freezing running of this first heating installation as shown in Figure 7, constitutes the compressing mechanism 11D of first system by the frequency-changeable compressor 11A and the first invariable frequency compressor 11B, is made of the compressing mechanism 11E of second system the second invariable frequency compressor 11C.And, drive frequency-changeable compressor 11A and drive the first invariable frequency compressor 11B, also drive booster compressor 43 simultaneously.And the second invariable frequency compressor 11C is stopped.
And shown in Fig. 7 solid line, first four-way change-over valve 12 is converted to second state, and second four-way change-over valve 13 and the 3rd four-way change-over valve 14 are converted to first state.And the magnetic valve SV2 of refrigeration unit 30 and the magnetic valve SV3 of freezing unit 40 open, and outdoor expansion valve 19 is closed.And the magnetic valve SV1 of hot-gas bypass pipe 71 is according to coming gauge tap from the detected value of low-pressure sensor 79 and the detected degree of superheat that flows through the cold-producing medium of suction line 61a of detected value of inlet temperature sensor 81.And the electric expansion valve 67a of liquid injecting tube 67 controls aperture according to the detected value of the described degree of superheat and ejection temperature sensor 76.
In this state, the cold-producing medium of frequency-changeable compressor 11A and first invariable frequency compressor 11B ejection flows to indoor heat converter 21 from first four-way change-over valve 12 through the outdoor second tracheae 58b and second gas side communication pipe arrangement 52 and condenses.This liquid refrigerant that condenses is diverted to refrigeration side first difference liquid pipe 54a and the freezing side first difference liquid pipe 54b from the second difference liquid pipe 55 of hydraulic fluid side communication pipe arrangement 53,54,55 before set liquid pipe 53.
Flowing through refrigerates the liquid refrigerant of the side first difference liquid pipe 54a, flows to refrigeration heat exchanger 31 through refrigeration expansion valve 32 and evaporates and the refrigeration side difference tracheae 51a that flows through.And the liquid refrigerant that flows through the freezing side first difference liquid pipe 54b flows to freezing heat-exchanger 41 evaporations through freezing expansion valve 42.At these freezing heat-exchanger 41 vaporized gas cold-producing mediums, be pressurized compressor 43 and attract compression, be ejected into freezing side difference tracheae 51b.
At described refrigeration heat exchanger 31 vaporized gas cold-producing mediums with from the gas refrigerant of booster compressor 43 ejection,, get back to the frequency-changeable compressor 11A and the first invariable frequency compressor 11B by low pressure tracheae 64 at first gas side communication pipe arrangement, 51 interflow.Repeat above-mentioned circulation by cold-producing medium and come in the heating shop, simultaneously cooling refrigeration showcase and freezing with in the storehouse of showcase.In the freezing running of this first heating installation, the cooling capacity (evaporation heat) that makes refrigeration unit 30 and freezing unit 40 averages out with the heating installation ability (heat condenses) of indoor units 20 and carries out 100% recuperation of heat.Form following cold-producing medium circulating path in the freezing running of this first heating installation, just: the cold-producing medium that compressing mechanism 11D sent is flowed through refrigeration unit 30 and freezing unit 40 and is got back to compressing mechanism 11D from indoor units 20.In this circulating path, do not get back to outdoor unit 10 and flow directly into refrigeration unit 30 and freezing unit 40 at the cold-producing medium that indoor units 20 is condensed.
And, though in the freezing running of this first heating installation pressure-reducing valve 107 cuts out, the pressure owing to hydraulic fluid side communication pipe arrangement 53,54,55 becomes too high and makes pressure-reducing valve 107 open at the refrigerant pressure that pressure-reducing valve 107 acts on above authorized pressure such as 1.5MPa sometimes.And, even pressure-reducing valve 107 cuts out, cold-producing medium also can take place sometimes leak outside.During such situation, the cold-producing medium of circulating path flows into accumulators 17 from set liquid pipe 53 by liquid branch pipe 66, and the cold-producing medium of circulating path will reduce.In case the cold-producing medium of circulating path reduces, to tail off gradually at refrigeration heat exchanger 31 and freezing heat-exchanger 41 refrigerant flows, the zone that the cold-producing medium of gas-liquid two-phase state is flowed through will be reduced, and the zone of single phase gas flow of refrigerant will enlarge, and the degree of superheat that flows to the cold-producing medium of compressing mechanism 11D from refrigeration heat exchanger 31 and freezing heat-exchanger 41 will become big gradually.
Become more than the setting in the degree of superheat, then controller 95 opens solenoid valve SV1 according to the cold-producing medium of the detected suction line 61a that flows through of detected value of the detected value of low-pressure sensor 79 and inlet temperature sensor 81.In case magnetic valve SV1 opens, then as shown in Figure 8, the gas refrigerant of the high pressure of compressing mechanism 11D ejection will be imported into accumulator 17 by hot-gas bypass pipe 71, and the interior pressure of accumulator 17 will rise.Thus, the liquid refrigerant in the accumulator 17 is forced to discharge, is sent back to circulating path from set liquid pipe 53.Gas refrigerant is fed into accumulator 17 from circulating path, but because liquid refrigerant will be discharged from, and the refrigerant amount in the accumulator 17 will reduce as a result, and the refrigerant amount of circulating path increases.Thus, can prevent the lack of refrigerant at refrigeration unit 30 and freezing unit 40, the cooling capacity that therefore can avoid at refrigeration unit 30 and freezing unit 40 descends.
And the liquid refrigerant in the accumulator 17 is sent back to circulating path and the refrigerant amount increase in a single day of circulating path, and the degree of superheat of the cold-producing medium of the suction line 61a that flows through will reduce gradually.And, in a single day become less than setting according to the degree of superheat of the detected cold-producing medium of the detected value of the detected value of low-pressure sensor 79 and inlet temperature sensor 81, then controller 95 cuts out magnetic valve SV1.
The freezing running of＜the second heating installation 〉
The freezing running of this second heating installation is the running of carrying out when the heating installation ability of indoor units 20 in the freezing running of described first heating installation is superfluous.During the freezing running of this second heating installation, as shown in Figure 9, constitute the compressing mechanism 11D of first system, constitute the compressing mechanism 11E of second system by the second invariable frequency compressor 11C by the frequency-changeable compressor 11A and the first invariable frequency compressor 11B.And, drive the frequency-changeable compressor 11A and the first invariable frequency compressor 11B, also drive booster compressor 43 simultaneously.And the second invariable frequency compressor 11C is stopped.
The freezing running of this second heating installation, shown in Fig. 9 solid line, except second four-way change-over valve 13 was converted to second state, the setting of valve etc. were identical with the freezing running of described first heating installation.
Therefore, from the part of the cold-producing medium of frequency-changeable compressor 11A and first invariable frequency compressor 11B ejection, with the freezing running of described first heating installation similarly, flow to indoor heat converter 21 and condense.This liquid refrigerant that condenses flows to the first difference liquid pipe 54 (refrigeration side first difference liquid pipe 54a and the freezing side first difference liquid pipe 54b) from the second difference liquid pipe 55 of hydraulic fluid side communication pipe arrangement 53,54,55 in set liquid pipe 53 fronts.
On the other hand, from other cold-producing mediums of described frequency-changeable compressor 11A and first invariable frequency compressor 11B ejection, condense at outdoor heat converter 15 through second four-way change-over valve 13 and the first four-way change-over valve 12 outdoor first tracheae 58a that flows through from auxiliary tracheae 59.The liquid refrigerant that this condenses, by accumulator 17, flow to first difference liquid pipe 54 (refrigeration side first difference liquid pipe 54a and the freezing side first difference liquid pipe 54b) and cold-producing medium interflow when flowing through outdoor liquid pipe 62 from the second difference liquid pipe 55 through the set liquid pipe 53 of hydraulic fluid side communication pipe arrangement 53,54,55.
Thereafter, the flow through liquid refrigerant of the described refrigeration side first difference liquid pipe 54a flows to 31 evaporations of refrigeration heat exchanger and flows through refrigeration side difference tracheae 51a.And the liquid refrigerant of the freezing side first difference liquid pipe 54b that flows through flows to freezing heat-exchanger 41 evaporations, is pressurized compressor 43 and sucks compression, is ejected into freezing side difference tracheae 51b.Collaborate at first gas side communication pipe arrangement 51 at described refrigeration heat exchanger 31 vaporized gas cold-producing mediums with from the gas refrigerant that booster compressor 43 sprays, get back to the frequency-changeable compressor 11A and the first invariable frequency compressor 11B by low pressure tracheae 64.
During the freezing running of this second heating installation, repeat above-mentioned circulation by cold-producing medium and come in the heating shop, cooling refrigeration is with showcase and freezing with in the storehouse of showcase simultaneously.At this moment, do not make the cooling capacity (evaporation heat) of refrigeration unit 30 and freezing unit 40 and the heating installation ability (heat condenses) of indoor units 20 average out, discharge the unnecessary heat of condensation outdoor at outdoor heat converter 15.
The freezing running of＜the three heating installation 〉
The running of being carried out when the freezing running of this 3rd heating installation is the heating installation scarce capacity of indoor units 20 in the freezing running of described first heating installation.The freezing running of this 3rd heating installation as shown in figure 10, constitutes the compressing mechanism 11D of first system by the frequency-changeable compressor 11A and the first invariable frequency compressor 11B, is made of the compressing mechanism 11E of second system the second invariable frequency compressor 11C.And, drive described frequency-changeable compressor 11A, the first invariable frequency compressor 11B and the second invariable frequency compressor 11C, also drive booster compressor 43 simultaneously.
The freezing running of this 3rd heating installation, except following this point: the aperture of control outdoor expansion valve 19, do not control the open and close of magnetic valve SV1 and closed and drive the second invariable frequency compressor 11C, other setting is identical with the freezing running of described first heating installation.
Therefore, from the cold-producing medium of frequency-changeable compressor 11A, the first invariable frequency compressor 11B and second invariable frequency compressor 11C ejection, with the freezing running of described first heating installation similarly, flow to indoor heat converter 21 through second gas side communication pipe arrangement 52 and condense.The liquid refrigerant that this condenses, the second difference liquid pipe 55 of the liquid pipe 53,54,55 of communicating from the hydraulic fluid side are diverted to first difference liquid pipe 54 (refrigeration side first difference liquid pipe 54a and the freezing side first difference liquid pipe 54b) and set liquid pipe 53.
The liquid refrigerant of the refrigeration side of the flowing through first difference liquid pipe 54a flows to 31 evaporations of refrigeration heat exchanger, and flows to refrigeration side difference tracheae 51a.And the liquid refrigerant of the freezing side first difference liquid pipe 54b that flows through flows to freezing heat-exchanger 41 evaporations, is inhaled into booster compressor 43 compressions, and is ejected into freezing side difference tracheae 51b.At described refrigeration heat exchanger 31 vaporized gas cold-producing mediums with from the gas refrigerant of booster compressor 43 ejection,, get back to the frequency-changeable compressor 11A and the first invariable frequency compressor 11B by low pressure tracheae 64 at first gas side communication pipe arrangement, 51 interflow.
On the other hand, the liquid refrigerant of the set liquid pipe 53 of flowing through after indoor heat converter 21 condenses flows through liquid branch pipe 66 and inflow accumulator 17, and process outdoor expansion valve 19 is flowed through outdoor heat converter 15 and evaporated further.This vaporized gas cold-producing medium outdoor first tracheae 58a that flows through, the suction line 61c that flows through the second invariable frequency compressor 11C through first four-way change-over valve 12 and second four-way change-over valve 13 gets back to this second invariable frequency compressor 11C.
When the freezing running of this 3rd heating installation, come in the heating shop by the cold-producing medium repetitive cycling, simultaneously cooling refrigeration showcase and freezing with in the storehouse of showcase.At this moment, refrigeration unit 30 and the cooling capacity (evaporation heat) of freezing unit 40 and the heating installation ability (heat condenses) of indoor units 20 are averaged out, obtain not enough heat of evaporation from outdoor heat converter 15.
The effect of-embodiment 1-
In the present embodiment 1, in case be formed with that cold-producing medium flows into accumulator 17 then in the freezing running of first heating installation of the described circulating path that refrigerant amount will reduce, making the unlatching of the magnetic valve SV1 by hot-gas bypass pipe 71 to send the liquid refrigerants in the accumulator 17 back to circulating path.In case send the liquid refrigerant in the accumulator 17 back to circulating path, the conduct of then flowing through utilizes the refrigerant amount of indoor units 20, refrigeration unit 30 and the freezing unit 40 of side unit to increase.Therefore, before the lack of refrigerant that respectively utilizes side unit 20,30,40,, can prevent deficiency at the cold-producing medium that respectively utilizes side unit 20,30,40 by sending the liquid refrigerant in the accumulator 17 back to circulating path with cold-producing medium loopback mechanism 5.
And, in the present embodiment 1, be conceived to: can judge deficiency from the degree of superheat of cold-producing medium that refrigeration heat exchanger 31 and freezing heat-exchanger 41 flow to the suction side of compressing mechanism 11D, make the magnetic valve SV1 that controls hot-gas bypass pipe 71 according to the detected value of the detected value of low-pressure sensor 79 and inlet temperature sensor 81 at the cold-producing medium of refrigeration unit 30 and freezing unit 40.Therefore, before the lack of refrigerant of refrigeration unit 30 and freezing unit 40, send the liquid refrigerant in the accumulator 17 back to circulating path, can positively avoid decline in the cooling capacity of refrigeration unit 30 and freezing unit 40 suitable opportunity.
" embodiment 2 "
Embodiments of the invention 2 below are described.The refrigerant loop figure of the refrigerating plant 1 of relevant this embodiment 2 as shown in figure 11.The refrigerating plant 1 of this embodiment 2, it is different with described embodiment 1 at hot-gas bypass pipe 71 magnetic valve SV1 this point not to be set, has constituted cold-producing medium loopback mechanism 5 as second four-way change-over valve 13 of means of communication.
Below the action of circulating path is sent the liquid refrigerant in the accumulator 17 back in explanation in the freezing running of first heating installation.Refrigerating plant 1 at this embodiment 2, when from the detected value of low-pressure sensor 79, and the degree of superheat of the cold-producing medium of the detected suction line 61a that flows through of the detected value of inlet temperature sensor 81 in a single day become setting when above, then second four-way change-over valve 13 is converted to second state.
If second four-way change-over valve 13 is set to second state, the part of the high-pressure gas refrigerant of compressing mechanism 11D ejection will be from auxiliary tracheae 59 through second four-way change-over valve 13 and the first four-way change-over valve 12 outdoor first tracheae 58a that flows through, further from flow through outdoor liquid pipe 62 and flow into accumulator 17 of outdoor heat converter 15.At this moment, outdoor fan 16 is a halted state.Thus, press liter in the accumulator 17, the liquid refrigerant in the accumulator 17 will be discharged forcibly from set liquid pipe 53 is sent back to circulating path.
And second four-way change-over valve 13 is set to the state of second state in the freezing running of first heating installation, and this is the same operating condition of the freezing running of second heating installation with embodiment 1.But, the freezing running of second heating installation of embodiment 1 is to be used for reducing the running that the heating installation ability of indoor units 20 is carried out, relatively, the freezing running of first heating installation of this embodiment 2 is for the liquid refrigerant in the accumulator 17 being sent back to forcibly the running of circulating path.And, the freezing running of second heating installation at embodiment 1, though in order to make refrigerant condenses and drive chamber's external fan 16 at outdoor heat converter 15, but, the freezing running of first heating installation at embodiment 2, just utilize outdoor heat converter 15 as being used for the circulation path that high-pressure gas refrigerant with compressing mechanism 11D ejection imports to accumulator 17, liquid refrigerant will be directed to accumulator 17 in case cold-producing medium condenses, refrigerant amounts in the accumulator 17 will be difficult to reduce, therefore drive chamber's external fan 16 not.
At present embodiment 2, owing to outdoor heat converter 15 is used to as the circulation path that high-pressure gas refrigerant is imported accumulator 17, the circulation path that connects accumulator 17 and compressing mechanism 11D ejection side can be set in addition sends the liquid refrigerant in the accumulator 17 back to circulating path.Thus, the structure of this refrigerating plant 1 will be simplified.
" embodiment 3 "
Embodiments of the invention 3 below are described.The refrigerant loop figure of the refrigerating plant 1 of relevant this embodiment 3 as shown in figure 12.These embodiment 3 refrigerating plants 1, at the link position that hot-gas bypass pipe 71 and magnetic valve SV1 this point and liquid injecting tube 67 are not set, different with described embodiment 1.
One end of liquid injecting tube 67 is connected to the connecting portion of suction line 61a and low pressure tracheae 64, and the other end of liquid injecting tube 67 is connected between the tie point and accumulator 17 of auxiliary liquid pipe 65 in outdoor liquid pipe 62 and draught excluder 18c one side.Liquid injecting tube 67 is in order accumulator 17 to be communicated with the communicating pipe of the suction side of compressing mechanism 11D, to constitute cold-producing medium loopback mechanism 5 with electric expansion valve 67a.
The below relevant action of in the freezing running of first heating installation, the liquid refrigerant in the accumulator 17 being sent back to circulating path of explanation.In the refrigerating plant 1 of this embodiment 3, in case become setting when above according to the degree of superheat of the cold-producing medium of the detected suction line 61a that flows through of the detected value of the detected value of low-pressure sensor 79 and inlet temperature sensor 81, then controller 95 is opened electric expansion valve 67a.Thus, be communicated with the suction side of accumulator 17 and compressing mechanism 11D, therefore, the liquid refrigerant in the accumulator 17 will by compressing mechanism 11D forcibly sucking-off get back to circulating path.
And,, even in the freezing running of first heating installation, open electric expansion valve 67a, be high pressure in the set liquid pipe 53, so the liquid refrigerant in the accumulator 17 can not flow out from accumulator 17 at the refrigerating plant 1 of described embodiment 1 and embodiment 2.
At present embodiment 3, when sending the liquid refrigerant in the accumulator 17 back to circulating path,, therefore, can make the suction degree of superheat of compressing mechanism 11D descend because compressing mechanism 11D will suck the liquid refrigerant in the accumulator 17.Therefore, can send cold-producing medium back to circulating path and separate the lack of refrigerant that disappears, can suppress to suck the input that the degree of superheat is cut down compressing mechanism 11D simultaneously.
" other embodiment "
Relevant described embodiment also can be following structure.
At described embodiment, though controller 95 is being controlled cold-producing medium loopback mechanism 5 according to the detected value of low-pressure sensor 79 and the detected value of inlet temperature sensor 81, but, also can be so that control cold-producing medium loopback mechanism 5 according to the detected value of high-pressure sensor 75 and ejection temperature sensor 76.In case the degree of superheat according to the ejection cold-producing medium of the compressing mechanism 11D that detected value calculated of the detected value of high-pressure sensor 75 and ejection temperature sensor 76 becomes more than the setting, then controller 95 carries out the liquid refrigerants in the accumulator 17 are sent back to the action of circulating path.High-pressure sensor 75 and ejection temperature sensor 76 constitute ejection degree of superheat detector.
And controller 95 also can be controlled cold-producing medium loopback mechanism 5 according to the detected value of the ejection temperature sensor 76 that detects the refrigerant temperature that compressing mechanism 11D sprayed.In case the detected value of ejection temperature sensor 76 becomes setting when above, then controller 95 carries out accumulator 17 interior liquid refrigerants are sent back to the action of circulating path.Ejection temperature sensor 76 constitutes ejection refrigerant temperature detector.
And controller 95 can be controlled cold-producing medium loopback mechanism 5 according to the aperture of the electric expansion valve 67a of liquid injecting tube 67.In case the aperture of electric expansion valve 67a is when to be 400 pulses when becoming regulation aperture electric expansion valve above, for example 480 pulses above, then controller 95 carries out accumulator 17 interior liquid refrigerants are sent back to the action of circulating path.And in case the aperture of electric expansion valve 67a when to be 350 pulses when becoming regulation aperture electric expansion valve following, for example 480 pulses following, then controller 95 finishes accumulator 17 interior liquid refrigerants are sent back to the action of circulating path.
And electric expansion valve 67a controls aperture according to the degree of superheat from the cold-producing medium of the detected suction line 61a of the detected value of the detected value of detected value, the low-pressure sensor 79 of ejection temperature sensor 76 and inlet temperature sensor 81.For example, in case the detected value of ejection temperature sensor 76 becomes the condition more than 90 ℃ or when which condition that the degree of superheat of the cold-producing medium of suction line 61a becomes the condition more than 5 ℃ was set up, then controller 95 enlarged the aperture of electric expansion valve 67a.
And controller 95 also can be controlled cold-producing medium loopback mechanism 5 according to the degree of superheat of the outlet of refrigeration heat exchanger 31 that becomes evaporimeter and freezing heat-exchanger 41.Under this situation, in the outlet of refrigeration heat exchanger 31 and the outlet of freezing heat-exchanger 41 temperature sensor and pressure sensor are set in order to detect the degree of superheat.For example, when in the outlet of refrigeration heat exchanger 31 or in the outlet of freezing heat-exchanger 41, the duration that the degree of superheat of cold-producing medium becomes the state more than 10 ℃ surpasses 10 minutes, and then controller 95 carries out the liquid refrigerant in the accumulator 17 is sent back to the action of circulating path.And, the duration that the degree of superheat of relevant cold-producing medium becomes the state more than 10 ℃ has surpassed 10 minutes evaporimeter, surpass 1 minute in case become the duration of the state below 7 ℃ in the degree of superheat of the cold-producing medium of its outlet, then controller 95 finishes the liquid refrigerants in the accumulator 17 are sent back to the action of circulating path.And, the control of cold-producing medium loopback mechanism 5, do not need to carry out, as long as the unit of the state that is difficult to flow into according to liquid refrigerant, the degree of superheat of cold-producing medium of outlet that for example is configured the evaporimeter of pinnacled unit are carried out just passable according to refrigerant superheat degree at all outlet ports of the evaporimeter of refrigeration unit 30 and freezing unit 40.
And controller 95 also can be controlled cold-producing medium loopback mechanism 5 according to the detected value of high-pressure sensor 75.During this situation, the high-pressure of kind of refrigeration cycle is to change according to indoor units 20 set interior space temperatures, therefore, carries out the control of cold-producing medium loopback mechanism 5 according to the saturation temperature in the detected pressures of high-pressure sensor 75.For example, surpass 10 minutes in case the difference of saturation temperature and interior space temperature becomes the duration of the state below 15 ℃, then controller 95 carries out the liquid refrigerant in the accumulator 17 is sent back to the action of circulating path.And, in case becoming the duration of the state more than 15 ℃, the difference of described temperature surpasses 1 minute, then controller 95 finishes the liquid refrigerant in the accumulator 17 is sent back to the action of circulating path.
And controller 95 also can be controlled cold-producing medium loopback mechanism 5 according to the detected value of low-pressure sensor 79.For example, surpass 10 minutes in case the detected value of low-pressure sensor 79 becomes the duration of the following state of 0.15MPa, then controller 95 carries out the liquid refrigerant in the accumulator 17 is sent back to the action of circulating path.And, in case becoming the duration of the above state of 0.2MPa, the detected value of low-pressure sensor 79 surpasses 1 minute, then controller 95 finishes the liquid refrigerant in the accumulator 17 is sent back to the action of circulating path.
And controller 95 also can be controlled cold-producing medium loopback mechanism 5 according to a plurality of conditions the detected value of the detected value of the degree of superheat of the cold-producing medium of the aperture of the electric expansion valve 67a of the temperature of the degree of superheat of the degree of superheat of the cold-producing medium of the suction side that flows to compressing mechanism 11D from refrigeration heat exchanger 31 and freezing heat-exchanger 41, cold-producing medium that compressing mechanism 11D is sprayed, cold-producing medium that compressing mechanism 11D is sprayed, liquid injecting tube 67, evaporator outlet, high-pressure sensor 75 and low-pressure sensor 79.During this situation,, any condition carries out the liquid refrigerant in the accumulator 17 is sent back to the action of circulating path in case setting up.
And, in case when carrying out the freezing running of first heating installation of 100% recuperation of heat and continuing more than 30 minutes, then controller 95 also can carry out the liquid refrigerants in the accumulator 17 are sent back to the action of circulating path.And, during the situation of outdoor air low temperature below for example-10 ℃, owing to accumulate low pressure liquid refrigerant easily in the accumulator 17, when therefore in a single day the freezing fortune of first heating installation continues more than 20 minutes, also can carry out with the capable action of sending circulating path back to of liquid refrigerant in the accumulator 17.
And, in case when the action of sending the liquid refrigerants in the accumulator 17 back to circulating path surpassed 10 minutes, then controller 95 can finish this action forcibly.
And, relevant described embodiment, in case accumulator 17 inner product liquid storage cryogens in the freezing running of first heating installation (first drive manner) of carrying out 100% recuperation of heat, then controller 95 can be set at second state with first four-way change-over valve 12 as switching mechanism and change operating condition.At this moment, expansion valve 22 in the close chamber.During this situation, the condition that first four-way change-over valve 12 is converted to second state is that the condition when carrying out sending the liquid refrigerant in the accumulator 17 action of circulating path back to described cold-producing medium loopback mechanism 5 is identical.In case first four-way change-over valve 12 is set to second state, similarly will become second drive manner that cold-producing medium circulates with described freezing running.But different with freezing running is that outdoor fan 16 is halted state.Thus, the high-pressure gas refrigerant from compressing mechanism 11D ejection flows into accumulator 17 by outdoor heat converter 15.Thus, the interior pressure of accumulator 17 will rise, and the liquid refrigerant in the accumulator 17 will be discharged forcibly from set liquid pipe 53 is sent back to refrigeration unit 30 and freezing unit 40.
And, also can magnetic valve be set at the liquid branch pipe 66 of described embodiment and replace pressure-reducing valve 107.
And, in described embodiment, though the example that illustrates is the outdoor unit 10 with respect to, two indoor units 20, eight refrigeration units 30 and a freezing unit 40 are set, but so long as can carry out suitably to change the platform number that each utilizes side unit 20,30,40 under the situation of 100% recuperation of heat running.
And, at described embodiment although understand with three compressor 11A, 11B, 11C and constitute the example of compressing mechanism 11D, 11E, but also can suitably change the platform number of compressor.
And, be desirable in essence example at the foregoing description, be not to be used for limiting the present invention, suitable thing of the present invention or the scope of purposes of the present invention.
The possibility of utilizing on the industry
As above-mentioned explanation, for having utilizing the side heat exchanger and can respectively utilizing the refrigerating plant that carries out 100% recuperation of heat running between the side heat exchanger of multisystem, the present invention is extremely useful.

Claims (7)

1. refrigerating plant, this refrigerating plant has possessed the heat source side unit (10) of have compressing mechanism (11D, 11E), heat source side heat exchanger (15) and accumulator (17), having first utilizes first of side heat exchanger (31,41) to utilize side unit (30,40), have second and utilize second of side heat exchanger (21) to utilize side unit (20), and connect gas side communication pipe arrangement (51,52) and the hydraulic fluid side communication pipe arrangement (53,54,55) that each unit (10,20,30,40) constitutes refrigerant loop (50); Described gas side communication pipe arrangement (51,52) has first gas side communication pipe arrangement (51) and second gas side communication pipe arrangement (52), this first gas side communication pipe arrangement (51) connects described heat source side unit (10) and described first and utilizes side unit (30,40), and this second gas side communication pipe arrangement (52) connects described heat source side unit (10) and described second and utilizes side unit (20); Described hydraulic fluid side communication pipe arrangement (53,54,55) has the set liquid pipe (53) that connects described heat source side unit (10), divides inconsistent and connect described first from this set liquid pipe (53) and utilize the first difference liquid pipe (54) of side unit (30,40) and inconsistent and connect the described second second difference liquid pipe (55) that utilizes side unit (20) from this set liquid pipe (53) branch; Described refrigerant loop (50) can form following cold-producing medium circulating path, and just: the cold-producing medium of sending from described compressing mechanism (11D, 11E) does not utilize side unit (20) to flow through by described accumulator (17) from described second first to utilize side unit (30,40) to get back to this compressing mechanism (11D, 11E); It is characterized in that:
This refrigerating plant is provided with cold-producing medium loopback mechanism (5), this cold-producing medium loopback mechanism (5) is formed with under the operating condition of described circulating path in described refrigerant loop (50), pressurize in by import high-pressure refrigerant to described accumulator (17), send the liquid refrigerant in the described accumulator (17) back to described circulating path by described set liquid pipe (53) described accumulator (17).
2. refrigerating plant according to claim 1 is characterized in that:
Described cold-producing medium loopback mechanism (5) has ingress pipe (71), this ingress pipe (71) is used for and will imports to described accumulator (17) from the high-pressure refrigerant of described compressing mechanism (11D, 11E) ejection, by from this ingress pipe (71) described high-pressure refrigerant being imported to described accumulator (17) and pressurization makes the liquid refrigerant in this accumulator (17) get back to described circulating path via described set liquid pipe (53) to this accumulator (17).
3. refrigerating plant according to claim 1 is characterized in that:
Be provided with thermal source fan (16) in described heat source side unit (10), this thermal source fan (16) is used for carrying air to described heat source side heat exchanger (15),
Described cold-producing medium loopback mechanism (5) has means of communication (13), this means of communication (13) is to be used for making described accumulator (17) be communicated with described compressing mechanism (11D by described heat source side heat exchanger (15), ejection side 11E) makes this accumulator (17) be communicated with described compressing mechanism (11D by this means of communication (13) under the state that described thermal source fan (16) is stopped, ejection side 11E) also makes this compressing mechanism (11D, 11E) high-pressure refrigerant that is sprayed flows into described accumulator (17) and makes the liquid refrigerant in this accumulator (17) get back to described circulating path by described set liquid pipe (53).
4. according to the described refrigerating plant of each claim in the claim 1 to 3, it is characterized in that:
This refrigerating plant comprises:
Sucking degree of superheat detector (79,81), is to be used for detecting utilizing side heat exchanger (31,41) to flow to the degree of superheat of the cold-producing medium of described compressing mechanism (11D, 11E) suction side from described first; And
Controller (95) is to be used for controlling described cold-producing medium loopback mechanism (5), so that send the cold-producing medium in the described accumulator (17) back to described circulating path when the detected value of described suction degree of superheat detector (79,81) becomes setting when above.
5. according to the described refrigerating plant of each claim in the claim 1 to 3, it is characterized in that:
This refrigerating plant comprises:
Ejection degree of superheat detector (75,76) is the degree of superheat that is used for detecting the cold-producing medium that described compressing mechanism (11D, 11E) sprayed; And
Controller (95) is to be used for controlling described cold-producing medium loopback mechanism (5), so that send the cold-producing medium in the described accumulator (17) back to described circulating path when the detected value of described ejection degree of superheat detector (75,76) becomes setting when above.
6. according to the described refrigerating plant of each claim in the claim 1 to 3, it is characterized in that:
This refrigerating plant comprises:
Ejection refrigerant temperature detector (76) is to be used for detecting the refrigerant temperature that described compressing mechanism (11D, 11E) is sprayed; And
Controller (95) is to be used for controlling described cold-producing medium loopback mechanism (5), so that then send the cold-producing medium in the described accumulator (17) back to described circulating path when the detected value of described ejection refrigerant temperature detector (76) becomes setting when above.
7. refrigerating plant, this refrigerating plant has possessed the heat source side unit (10) of have compressing mechanism (11D, 11E), heat source side heat exchanger (15) and accumulator (17), having first utilizes first of side heat exchanger (31,41) to utilize side unit (30,40), have second and utilize second of side heat exchanger (21) to utilize side unit (20), and connect gas side communication pipe arrangement (51,52) and the hydraulic fluid side communication pipe arrangement (53,54,55) that each unit (10,20,30,40) constitutes refrigerant loop (50); Be provided with thermal source fan (16) in described heat source side unit (10), this thermal source fan (16) is used for carrying air to described heat source side heat exchanger (15); Described gas side communication pipe arrangement (51,52) has first gas side communication pipe arrangement (51) and second gas side communication pipe arrangement (52), this first gas side communication pipe arrangement (51) connects described heat source side unit (10) and described first and utilizes side unit (30,40), and this second gas side communication pipe arrangement (52) connects described heat source side unit (10) and described second and utilizes side unit (20); Described hydraulic fluid side communication pipe arrangement (53,54,55) has the set liquid pipe (53) that connects described heat source side unit (10), divides inconsistent and connect described first from this set liquid pipe (53) and utilize the first difference liquid pipe (54) of side unit (30,40) and inconsistent and connect the described second second difference liquid pipe (55) that utilizes side unit (20) from this set liquid pipe (53) branch; Be provided with the switching mechanism (12) of conversion first drive manner and second drive manner at described refrigerant loop (50), this first drive manner is described compressing mechanism (11D, the cold-producing medium of 11E) sending utilizes side unit (20) to flow through from described second and first utilizes side unit (30,40) get back to this compressing mechanism (11D, 11E), this second drive manner is described compressing mechanism (11D, the cold-producing medium of 11E) sending flows into accumulator (17) from described heat source side heat exchanger (15) and flows through afterwards and first utilize side unit (30,40) get back to this compressing mechanism (11D, 11E); It is characterized in that:
Under the state that described thermal source fan (16) is stopped, being converted to second drive manner from first drive manner, will in this first drive manner, accumulating in liquid refrigerant in the accumulator (17) and send described first back to by described set liquid pipe (53) and utilize side unit (30,40) by described switching mechanism (12).
CN2006800298921A 2005-08-15 2006-08-11 Refrigerating apparatus Expired - Fee Related CN101243294B (en)

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Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008016664A1 (en) * 2008-04-01 2009-10-29 Efficient Energy Gmbh Vertical heat pump and method of manufacturing the vertically arranged heat pump
JP2010054194A (en) * 2008-07-31 2010-03-11 Daikin Ind Ltd Refrigerating device
WO2011112495A2 (en) * 2010-03-08 2011-09-15 Carrier Corporation Refrigerant distribution apparatus and methods for transport refrigeration system
JP4888583B2 (en) 2010-05-31 2012-02-29 ダイキン工業株式会社 Refrigeration equipment
JP2012077983A (en) * 2010-09-30 2012-04-19 Daikin Industries Ltd Refrigerating circuit
US9816739B2 (en) 2011-09-02 2017-11-14 Carrier Corporation Refrigeration system and refrigeration method providing heat recovery
EP2778567B1 (en) * 2011-11-07 2021-01-20 Mitsubishi Electric Corporation Air-conditioning apparatus
CN104390384B (en) * 2014-10-15 2017-03-29 珠海格力电器股份有限公司 Air conditioning system
CN106642780B (en) * 2016-12-30 2019-09-27 中原工学院 It is a kind of to refrigerate and freeze synchronous Two-way Cycle composite system
JP6849036B1 (en) * 2019-09-30 2021-03-24 ダイキン工業株式会社 Heat source unit and refrigeration equipment
CN111964208A (en) * 2020-07-14 2020-11-20 宁波奥克斯电气股份有限公司 Heating indoor unit high-temperature-resistant control method and device, air conditioner and storage medium
JP6958692B1 (en) * 2020-08-28 2021-11-02 ダイキン工業株式会社 Heat source unit and refrigeration equipment

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002228297A (en) * 2001-02-02 2002-08-14 Daikin Ind Ltd Refrigerating device
CN1149373C (en) * 2000-12-12 2004-05-12 东芝株式会社 Refrigerator
US20040182101A1 (en) * 2003-03-17 2004-09-23 Daikin Industries, Ltd. Heat pump apparatus
CN1606681A (en) * 2002-07-12 2005-04-13 大金工业株式会社 Refrigeration equipment
WO2005033593A1 (en) * 2003-10-06 2005-04-14 Daikin Industries, Ltd. Freezer

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07305903A (en) * 1994-05-10 1995-11-21 Hitachi Ltd Controller for freezer
WO2002046663A1 (en) * 2000-12-08 2002-06-13 Daikin Industries, Ltd. Refrigerator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1149373C (en) * 2000-12-12 2004-05-12 东芝株式会社 Refrigerator
JP2002228297A (en) * 2001-02-02 2002-08-14 Daikin Ind Ltd Refrigerating device
CN1606681A (en) * 2002-07-12 2005-04-13 大金工业株式会社 Refrigeration equipment
US20040182101A1 (en) * 2003-03-17 2004-09-23 Daikin Industries, Ltd. Heat pump apparatus
WO2005033593A1 (en) * 2003-10-06 2005-04-14 Daikin Industries, Ltd. Freezer
JP2005134103A (en) * 2003-10-06 2005-05-26 Daikin Ind Ltd Refrigeration device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
同上.

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WO2007020885A1 (en) 2007-02-22
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US20090077985A1 (en) 2009-03-26
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