CN1188880A - Coolant distributing system in multi-type air conditioner - Google Patents
Coolant distributing system in multi-type air conditioner Download PDFInfo
- Publication number
- CN1188880A CN1188880A CN97122646A CN97122646A CN1188880A CN 1188880 A CN1188880 A CN 1188880A CN 97122646 A CN97122646 A CN 97122646A CN 97122646 A CN97122646 A CN 97122646A CN 1188880 A CN1188880 A CN 1188880A
- Authority
- CN
- China
- Prior art keywords
- independently
- conduit
- pipeline
- independent
- pipelines
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 31
- 239000002131 composite material Substances 0.000 claims abstract description 10
- 238000001816 cooling Methods 0.000 claims description 15
- 230000008676 import Effects 0.000 claims description 11
- 238000007664 blowing Methods 0.000 claims description 2
- 238000009423 ventilation Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 3
- 150000001875 compounds Chemical class 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000006386 neutralization reaction Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
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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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
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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
- 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
- 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
- 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
- F25B2400/06—Several compression cycles arranged in parallel
Abstract
The invention provides a coolant distribution system for a composite air conditioner, which comprises three groups of inlets and outlets. The inlets and the outlets are arranged in the three sections of a first conduit and a second conduit. The first conduit and the second conduit are divided into a first section, a second section, a third section, a fourth section, a fifth section and a sixth section independently. The sections are arranged between the inlets and the outlets on the two opposite sides. Opening distributors are arranged among the independent first conduit, the independent second conduit, the independent third conduit, the independent fourth conduit, and a first compressor and a second compressor so that the two compressors are connected with the inlets. The invention also comprises a mixing duct connecting the outlets of the independent first conduit and the independent second conduit with the outlets of the independent third conduit and the independent fourth conduit; and a joint connected with the inlets of the fifth independent conduit and the sixth independent conduit and the mixing duct.
Description
What the present invention relates to is coolant distribution system, and what relate in particular to is the coolant distribution system that multiple compressors share compound (multi-type) air-conditioner of a condenser.
The air-cooling apparatus that resembles air-conditioner or refrigerator one class carries out work according to the cool cycles of closed-loop path usually.Therefore, cooling agent flows through the coolant circuit that is made of compressor-condenser-expansion valve-evaporimeter.
As mentioned above, air-conditioner is divided into two classes: i.e. combined type (integral type) and split type (separatetype).Combined type for example is the integral window formula, it mainly comprises a compressor that is contained in the main frame, a condenser, a capillary (capillary tube) and an evaporimeter, and be split type by separately, thereby reduce installing space and reduce noise the indoor unit that comprises evaporimeter and the outdoor unit that comprises condenser and compressor.Specifically, use composite air conditioner cool room effectively, reduce the installing space of air-conditioner by some indoor units are linked to each other with an outdoor unit.
As shown in Figure 2, composite air conditioner comprises an outdoor unit (O) and two indoor units (I and I '), outdoor unit comprises first and second compressors (50 and 51), condenser (54) that is connected with this two compressor (50 and 51) by first and second pipelines (52 and 53) and first and second capillaries (55 and 56) that are connected with these two pipelines (52 and 53), indoor unit comprises first and second evaporimeters (57 and 58) that are contained in the unit separately, and these two evaporimeters are connected with first and second capillaries.Though ventilation (Ventilating) equipment is not shown among the figure, must has ventilation equipment to force to finish the heat exchange in condenser (54) and two evaporimeters (57 and 58).
Therefore, owing to link to each other with evaporimeter (57 and 58) with compressor (50 and 51) with a shared condenser (54), and utilized in the condenser (54) some independently refrigerant tubings, so the heat exchange that a condenser (54) is finished is enough to provide effectively some evaporimeters needed so much energy.
As mentioned above, when ventilation equipment move, the first and second independent pipelines are installed in a condenser, can be made the ducted heat exchanger effectiveness difference of two opposite sides, so just cause the different problem of cooling effectiveness in the some evaporimeters that link to each other with these pipelines.So, descend owing to poor heat exchanger effectiveness makes its cooling effectiveness away from the evaporimeter that links to each other with a pipeline of ventilation equipment.
The present invention is intended to solve the aforementioned problems in the prior, the object of the present invention is to provide the coolant distribution system of a kind of compound (multi-type) air-conditioner, this distribution system makes each independent tubes that links to each other with a condenser have identical heat exchanger effectiveness.In order to finish purpose of the present invention, the coolant distribution system of a kind of composite air conditioner that is provided, comprise the mixing apparatus that is arranged on the condenser, wherein alternately change the position and utilize blowing device (flowing means) by the condenser and first and second pipelines that link to each other with each evaporimeter, to deliver to first and second pipelines with identical quantity from the air of cooling fan thus, to realize uniform heat exchange.
In order to fully understand feature of the present invention and purpose, describe the present invention in detail below in conjunction with accompanying drawing, wherein:
Fig. 1 is the schematic diagram of the coolant distribution system of composite air conditioner of the present invention;
Fig. 2 is the schematic diagram of the coolant distribution system of conventional composite type air-conditioner.
Fig. 1 is the schematic diagram of the coolant distribution system of composite air conditioner of the present invention; This system comprises, the mixing apparatus in condenser (54), and it can make the location swap of first and second pipelines to ventilation equipment, so that obtain the air of same amount from cooling fan.
This mixing apparatus comprises three groups of imports and outlet, and these are imported and exported respectively in three sections that first and second pipelines are divided into, and promptly is divided into independently first, second, the the three, the four, the 5th, the 6th pipeline section (3,4,5,6,7 and 8), they are positioned between the import (1) and outlet (2) of two opposite sides; At the opening distributor (9) between the first, the second, third and fourth pipeline (3,4,5 and 6) and first and second compressors (50 and 51) independently, be used to make these two compressors to link to each other with import (1); One will be independently the mixing duct (10) that links to each other with the outlet (2) of third and fourth pipeline (5 and 6) independently of the outlet (2) of first and second pipelines (3 and 4); And one with the 5th joint that links to each other with the import (1) and the mixing duct (10) of the 6th pipeline (7 and 8) independently.Certainly, first and second evaporimeters (57 and 58) with independently the 5th link to each other with the outlet of the 6th pipeline.
Be incorporated into respectively independently the first and the 3rd pipeline (3) and (5) neutralization independently the cooling agent in the second and the 4th pipeline (4 and 6) in each pipeline, rotate also mixed and in mixing duct, rotates, make their position turn to ventilation equipment simultaneously like this, thereby make cooling agent obtain identical heat exchange.
Although first and second pipelines (52 and 53) make them by condenser (54) time position alternately towards mixing apparatus obtaining similar effects, the heat exchanger effectiveness that causes low than the time with mixing apparatus.Effect of the present invention is that the operation of air-conditioner makes the cooling agent that compressed enter the independently import of first and second pipelines (3 and 4) by distributor (9) in first and second compressors (50 and 51), and enters the independently import of third and fourth pipeline (5 and 6).
When entering independently first, second, when the third and fourth ducted cooling agent forces heat exchange by ventilation equipment, ventilation equipment just can be sent more air and independently first contact with the 3rd pipeline (3 and 5), or with the second and the 4th tube contacts independently, like this, in the independently pipeline of a side, very high heat exchanger effectiveness is just arranged.So, by each pipeline is carried out heat exchange in short distance in turn, cooling agent is come back in the mixing duct (10).
In other words, even both sides independently first with the 3rd pipeline or independently second different with the heat exchanger effectiveness of the 4th ducted cooling agent, flow through independently first, second, third and fourth pipeline (3,4,5,6) cooling agent also with mixing duct that each pipe outlet (2) links to each other in mixed.
When the cooling agent that passes through heat exchange in varying degrees mixes in mixing duct (10), then cooling agent becomes the cooling agent that carried out heat exchange equally, and cooling agent flows in the import (1) of the 5th and the 6th pipeline (7 and 8) independently by joint (11) then.Enter into independently that the cooling agent of the 5th and the 6th pipeline (7 and 8) obtains heat exchange, and in pipeline, be rotated the back as cryogen discharge with identical heat exchanger effectiveness to outlet (2).
When flowing into independently in first and second evaporimeters (57,58) through the cooling agent of even heat exchange, the room that cooling agent just will have indoor unit equably cools down.As shown in table 1, evenly the cooling agent of heat exchange make each independently evaporimeter (57 and 58) have identical cooling effectiveness, and improved whole efficiency of air conditioner.
Table 1: the cooling effectiveness in each room
| The cooling of first room | The cooling of second room | |||||
| ????A | ????B | ????A | ?????B | |||
| The cooling in each room | Before the change | ?Btu/h | ???8,615 | ???8,787 | ???8,066 | ????8,239 |
| ??(％) | ???95,7％ | ???97,6％ | ???89,6％ | ????91,5％ | ||
| After the change | ?Btu/h | ???9,073 | ???9,295 | ???8,691 | ????8,596 | |
| ??(％) | ???100,8％ | ???103,3％ | ???96,6％ | ????95,5％ | ||
In addition, also avoided in the conventional air conditioner (54) problem because of the cooling capacity variation that difference caused of the heat exchanger effectiveness of first and second pipelines (52 and 53).Certainly, under the situation of heat-pump-type (heat pump type) air-conditioner, that is to say that its cooling and heating efficiency can keep steady state, even under the situation that can be improved, can make cooling agent carry out recycled back by a commutation (reversing) valve (not shown).
The invention has the advantages that by making the first and second ducted cooling agents turn to ventilation equipment, and by cooling agent is flowed into each evaporimeter under admixture, make the cooling capacity in each evaporimeter all identical, and improve cooling and the heating efficiency of whole composite air conditioner.
Claims (2)
1. the coolant distribution system of a composite air conditioner, this distribution system comprises, be arranged on the mixing apparatus on the condenser, wherein alternately change the position and utilize blowing device by the condenser and first and second pipelines that link to each other with each evaporimeter, to deliver to first and second pipelines with identical quantity from the air of cooling fan thus, to obtain uniform heat exchanger effectiveness.
2. chilled distribution according to claim 1 system, wherein, this mixing apparatus comprises three groups of imports and outlet, and these are imported and exported in three sections that first and second pipelines are divided into, and promptly is divided into independently the first, second, third, fourth, the 5th, the 6th pipeline section (3,4,5,6,7 and 8), they are positioned between the import (1) and outlet (2) of two opposite sides; At the opening distributor (9) between the first, second, third and the 4th pipeline (3,4,5 and 6) and first and second compressors (50 and 51) independently, so that these two compressors link to each other with import (1); One will be independently the mixing duct (10) that links to each other with the outlet of third and fourth pipeline (2) independently of the outlet (2) of first and second pipelines (3 and 4); And one with the 5th joint that links to each other with the import (1) and the mixing duct (10) of the 6th pipeline (7 and 8) independently.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1019970001522A KR100225628B1 (en) | 1997-01-20 | 1997-01-20 | Refrigerant distribution structure of multi type airconditioner |
| KR1522/97 | 1997-01-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1188880A true CN1188880A (en) | 1998-07-29 |
| CN1091508C CN1091508C (en) | 2002-09-25 |
Family
ID=19495125
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97122646A Expired - Fee Related CN1091508C (en) | 1997-01-20 | 1997-11-26 | Coolant distributing system in multi-type air conditioner |
Country Status (4)
| Country | Link |
|---|---|
| KR (1) | KR100225628B1 (en) |
| CN (1) | CN1091508C (en) |
| FR (1) | FR2758615B1 (en) |
| IT (1) | IT1297083B1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106918167A (en) * | 2015-12-24 | 2017-07-04 | 杭州三花微通道换热器有限公司 | Heat-exchanger rig and the refrigerant vapor compression system with the heat-exchanger rig |
| CN107131670A (en) * | 2017-06-09 | 2017-09-05 | 杨玄星 | A kind of double-compressor refrigeration system of shared condensation fan |
| CN108679881A (en) * | 2018-05-10 | 2018-10-19 | 王梅军 | Odevity is alternatively arranged long rectangle reciprocating cold medium heater and its snow melt de-icing method |
| CN108692494A (en) * | 2017-04-05 | 2018-10-23 | 雷诺士工业公司 | The integrated row that interweaves divides the method and apparatus that the sub-load of condenser pipe optimizes refrigeration system |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102168630B1 (en) | 2013-11-05 | 2020-10-21 | 엘지전자 주식회사 | Refrigeration cycle of refrigerator |
| CN113375376A (en) * | 2020-03-10 | 2021-09-10 | 开利公司 | Integrated heat pump system and control method thereof |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3984224A (en) * | 1973-12-10 | 1976-10-05 | Dawkins Claude W | Air conditioning system for a motor home vehicle or the like |
| US4201065A (en) * | 1978-12-18 | 1980-05-06 | Carrier Corporation | Variable capacity vapor compression refrigeration system |
| DE3938842A1 (en) * | 1989-06-06 | 1991-05-29 | Thermal Waerme Kaelte Klima | CONDENSER FOR A VEHICLE AIR CONDITIONING REFRIGERANT |
| US5205130A (en) * | 1991-07-02 | 1993-04-27 | Pannell Bobby L | Dual stage AC system for recreational vehicle |
-
1997
- 1997-01-20 KR KR1019970001522A patent/KR100225628B1/en not_active IP Right Cessation
- 1997-11-26 IT IT97RM000734A patent/IT1297083B1/en active IP Right Grant
- 1997-11-26 CN CN97122646A patent/CN1091508C/en not_active Expired - Fee Related
- 1997-11-28 FR FR9714998A patent/FR2758615B1/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106918167A (en) * | 2015-12-24 | 2017-07-04 | 杭州三花微通道换热器有限公司 | Heat-exchanger rig and the refrigerant vapor compression system with the heat-exchanger rig |
| CN108692494A (en) * | 2017-04-05 | 2018-10-23 | 雷诺士工业公司 | The integrated row that interweaves divides the method and apparatus that the sub-load of condenser pipe optimizes refrigeration system |
| CN107131670A (en) * | 2017-06-09 | 2017-09-05 | 杨玄星 | A kind of double-compressor refrigeration system of shared condensation fan |
| CN108679881A (en) * | 2018-05-10 | 2018-10-19 | 王梅军 | Odevity is alternatively arranged long rectangle reciprocating cold medium heater and its snow melt de-icing method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1091508C (en) | 2002-09-25 |
| KR100225628B1 (en) | 1999-10-15 |
| ITRM970734A0 (en) | 1997-11-26 |
| KR19980066167A (en) | 1998-10-15 |
| FR2758615B1 (en) | 2000-01-14 |
| FR2758615A1 (en) | 1998-07-24 |
| IT1297083B1 (en) | 1999-08-03 |
| ITRM970734A1 (en) | 1999-05-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20020925 Termination date: 20091228 |