CN205641669U - Duplex condition is compressed - is drawn and penetrates heat pump air conditioning system - Google Patents
Duplex condition is compressed - is drawn and penetrates heat pump air conditioning system Download PDFInfo
- Publication number
- CN205641669U CN205641669U CN201620472008.2U CN201620472008U CN205641669U CN 205641669 U CN205641669 U CN 205641669U CN 201620472008 U CN201620472008 U CN 201620472008U CN 205641669 U CN205641669 U CN 205641669U
- Authority
- CN
- China
- Prior art keywords
- import
- heat exchanger
- outlet
- liquid separator
- way change
- 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.)
- Expired - Fee Related
Links
Abstract
The utility model relates to a compression of duplex condition draw and penetrate heat pump air conditioning system. Including ejector and two four -way reversing valve, outdoor heat exchanger's the import and the import of indoor heat exchanger are connected respectively through a four -way reversing valve to the gas vent of compressor, and the work nozzle inlet of ejector is connected respectively in outdoor heat exchanger's export through the 2nd four -way reversing valve imported with the suction chamber, the exit linkage vapour and liquid separator's of ejector import, the import of throttle valve is connected to the air inlet of vapour and liquid separator's gas outlet connection compressor, vapour and liquid separator's liquid outlet, and the work nozzle inlet and the suction chamber import of ejector are connected respectively through the import of the interior heat exchanger of four -way reversing valve difference junction chamber and outdoor heat exchanger's import, the export of indoor heat exchanger to the export of choke valve through the 2nd four -way reversing valve. It has improved refrigeration efficiency, has realized the refrigeration, has heated duplex condition function with two four -way reversing valve conversions to replace the expansion valve to retrieve the expansion work through the ejector.
Description
Technical field
This utility model relates to heat pump type air conditioning system, specifically a kind of Double-working-condition compression-injection heat pump type air conditioning system.
Background technology
Along with the growing tension of the energy, air-source heat pump air conditioning system is increasingly paid attention to by countries in the world.Air-source heat pump air conditioning system refers to obtain low grade heat energy from nature air and utilize electric energy to be translated into the new energy resources system of high-grade heat energy, and its existence effectively alleviates the problem that available energy is nervous.The operation principle of air-source heat pump air conditioning system is the same with vapour compression refrigeration system, is all inverse Carnot cycle principle, and parts all exist throttling arrangement.In current air source heat pump refrigeration system, throttling arrangement typically uses expansion valve, but uses expansion valve throttling that expansion work will be made to can not get effectively and reclaim, cause the waste of the energy.Using the injector can be with recovery section expansion work, but existing compression ejection circulation can only realize cooling in summer or the single operating mode heated winter.
Utility model content
In order to overcome above-mentioned the deficiencies in the prior art, this utility model provides a kind of Double-working-condition compression-injection heat pump type air conditioning system, effectively reclaims expansion work, and improves the operating mode scope of application of injector.
This utility model be the technical scheme is that
A kind of Double-working-condition compression-injection heat pump type air conditioning system, including compressor, outdoor heat exchanger, indoor heat exchanger, choke valve, gas-liquid separator, also include injector, the first four-way change-over valve, the second four-way change-over valve, the air vent of compressor passes through import and the import of indoor heat exchanger of the first four-way change-over valve junction chamber external heat exchanger respectively, the outlet of outdoor heat exchanger connects main jet import and the suction chamber import of injector respectively by the second four-way change-over valve, and the outlet of injector connects the import of gas-liquid separator by pipeline；The gas outlet of gas-liquid separator connects the air inlet of compressor by pipeline, the liquid outlet of gas-liquid separator connects the import of choke valve by pipeline, the outlet of choke valve connects import and the import of outdoor heat exchanger of indoor heat exchanger respectively by the first four-way change-over valve, and the outlet of indoor heat exchanger connects main jet import and the suction chamber import of injector respectively by the second four-way change-over valve.
Using this utility model of technique scheme, compared with prior art, it provides the benefit that:
Utilize injector to replace choke valve to reclaim major part expansion work, reduce the pressure ratio of compressor, be greatly improved refrigerant system efficiency, improve the utilization rate of the energy.Being changed by two four-way change-over valves, system can realize the function that cooling in summer heats winter, and freeze, heat injector under two kinds of operating modes and all can reclaim expansion work, makes the refrigerating efficiency of system be improved.
As preferably, this utility model further technical scheme is:
Described injector includes nozzle needle, main jet, suction chamber, mixing chamber and diffusion room, and nozzle needle is installed on inside main jet, and main jet is installed on the inside of suction chamber；Suction chamber, mixing chamber and diffusion room are in turn connected to form biphase working fluid and process chamber, and the outlet of main jet processes chamber with described biphase working fluid and connects.Moved axially by nozzle needle, change main jet throat opening area, change operative fluid flow rate, thus regulate injector running parameter and change with adaptation condition.
Accompanying drawing explanation
Fig. 1 is system structure schematic diagram of the present utility model；
Fig. 2 is ejector structure schematic diagram of the present utility model；
Fig. 3 is this utility model system structure schematic diagram when cooling condition；
Fig. 4 is this utility model system structure schematic diagram when heating condition；
In figure: 1-compressor；2-gas-liquid separator；3-choke valve；4-indoor heat exchanger；5-injector；6-the first four-way change-over valve；7-outdoor heat exchanger；8-the second four-way change-over valve；51-nozzle needle；52-main jet；53-suction chamber；54-mixing chamber；55-diffusion room.
Detailed description of the invention
The utility model is described in further detail for illustrated embodiment below in conjunction with the accompanying drawings, but embodiment does not constitutes any restriction to this utility model.
See Fig. 1, Fig. 2, Double-working-condition compression-injection heat pump type air conditioning system, it is made up of compressor 1, gas-liquid separator 2, choke valve 3, indoor heat exchanger 4, injector the 5, first four-way change-over valve 6, outdoor heat exchanger the 7, second four-way change-over valve 8, injector 5 has nozzle needle 51, main jet 52, suction chamber 53, mixing chamber 54, diffusion room 55, main jet 52 is installed on the inside of suction chamber 53, suction chamber 53, mixing chamber 54 and diffusion room 55 are sequentially connected with and form biphase working fluid and process chamber, and the outlet of main jet 52 processes chamber with this biphase working fluid and connects.
The air vent of compressor 1 passes through import and the import of indoor heat exchanger 4 of the first four-way change-over valve 6 junction chamber external heat exchanger 7 respectively, the outlet of outdoor heat exchanger 7 connects main jet 52 import and suction chamber 53 import of injector 5 respectively by the second four-way change-over valve 8, and the outlet of injector 5 connects the import of gas-liquid separator 2 by pipeline；The gas outlet of gas-liquid separator 2 connects the air inlet of compressor 1 by pipeline, the liquid outlet of gas-liquid separator 2 connects the import of choke valve 3 by pipeline, the outlet of choke valve 3 connects import and the import of outdoor heat exchanger 7 of indoor heat exchanger 4 respectively by the first four-way change-over valve 6, and the outlet of indoor heat exchanger 4 connects main jet 52 import and suction chamber 53 import of injector 5 respectively by the second four-way change-over valve 8.
As shown in Figure 3, during cooling condition, saturated refrigerant vapour in gas-liquid separator 2 enters compressor 1, high-temperature high-pressure refrigerant gas after compression enters outdoor heat exchanger 7(condenser through the first four-way change-over valve 6), subcooled liquid is become after condensation heat release, then in the second four-way change-over valve 8 enters the main jet 52 of injector 5, expand blood pressure lowering, low pressure is formed in main jet 52 exit, injection indoor heat exchanger 4(vaporizer simultaneously) steam that exports enters the suction chamber 53 of injector 5 through the second four-way change-over valve 8, two fluids enters deceleration supercharging in diffusion room 55 after mixing in mixing chamber 53, subsequently into gas-liquid separator 2.The saturated liquid separated through gas-liquid separator 2 enters indoor heat exchanger 4(vaporizer through the first four-way change-over valve 6 after choke valve 3) in evaporation endothermic, form steam by injection to injector 5, thus complete whole circulation.Cold air through indoor heat exchanger 4 refrigeration delivers to indoor, meets indoor cooling demand.
As shown in Figure 4, during heating condition, saturated refrigerant vapour in gas-liquid separator 2 enters compressor 1, high-temperature high-pressure refrigerant gas after compression enters indoor heat exchanger 4(condenser through the first four-way change-over valve 6), subcooled liquid is become after condensation heat release, subsequently into expanding blood pressure lowering in the main jet 52 of injector 5, low pressure is formed in main jet 52 exit, injecting chamber external heat exchanger 7(vaporizer simultaneously) steam that exports enters the suction chamber 53 of injector 5 through the second four-way change-over valve 8, two fluids enters deceleration supercharging in diffusion room 55 after mixing in mixing chamber 54, subsequently into gas-liquid separator 2.The saturated liquid separated through gas-liquid separator 2 enters outdoor heat exchanger 7(vaporizer through the first four-way change-over valve 6 after choke valve 3) in evaporation endothermic, form steam by injection to injector 5, thus complete whole circulation.Hot-air through indoor heat exchanger 4 delivers to indoor, meets indoor heating demands.
Double-working-condition compression-injection the heat pump type air conditioning system provided by the present embodiment, has the following characteristics that
Being applicable to refrigeration and heat two aspects, by the changeable function of double four-way change-over valves, and injector can be effectively utilized；Replace expansion valve to reclaim most expansion work with injector, make refrigerating efficiency be improved.
The foregoing is only the embodiment that this utility model is the most feasible, not thereby limit to interest field of the present utility model, the equivalent structure change that all utilization this utility model description and accompanying drawing content are made, within being both contained in interest field of the present utility model.
Claims (2)
1. a Double-working-condition compression-injection heat pump type air conditioning system, including compressor, outdoor heat exchanger, indoor heat exchanger, choke valve, gas-liquid separator, it is characterized in that: also include injector, the first four-way change-over valve, the second four-way change-over valve, the air vent of compressor passes through import and the import of indoor heat exchanger of the first four-way change-over valve junction chamber external heat exchanger respectively, the outlet of outdoor heat exchanger connects main jet import and the suction chamber import of injector respectively by the second four-way change-over valve, and the outlet of injector connects the import of gas-liquid separator by pipeline；The gas outlet of gas-liquid separator connects the air inlet of compressor by pipeline, the liquid outlet of gas-liquid separator connects the import of choke valve by pipeline, the outlet of choke valve connects import and the import of outdoor heat exchanger of indoor heat exchanger respectively by the first four-way change-over valve, and the outlet of indoor heat exchanger connects main jet import and the suction chamber import of injector respectively by the second four-way change-over valve.
Double-working-condition compression-injection heat pump type air conditioning system the most according to claim 1, it is characterized in that: described injector includes nozzle needle, main jet, suction chamber, mixing chamber and diffusion room, nozzle needle is installed on inside main jet, and main jet is installed on the inside of suction chamber；Suction chamber, mixing chamber and diffusion room are in turn connected to form biphase working fluid and process chamber, and the outlet of main jet processes chamber with described biphase working fluid and connects.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620472008.2U CN205641669U (en) | 2016-05-23 | 2016-05-23 | Duplex condition is compressed - is drawn and penetrates heat pump air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620472008.2U CN205641669U (en) | 2016-05-23 | 2016-05-23 | Duplex condition is compressed - is drawn and penetrates heat pump air conditioning system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205641669U true CN205641669U (en) | 2016-10-12 |
Family
ID=57055502
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620472008.2U Expired - Fee Related CN205641669U (en) | 2016-05-23 | 2016-05-23 | Duplex condition is compressed - is drawn and penetrates heat pump air conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205641669U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105805981A (en) * | 2016-05-23 | 2016-07-27 | 华北理工大学 | Dual-operation compression-ejection heat pump air conditioner system |
| CN107906786A (en) * | 2017-12-25 | 2018-04-13 | 华北理工大学 | The coupled system of medically low temperature environment is produced based on double stage heat pump and autocascade cycle |
| CN114459179A (en) * | 2021-12-27 | 2022-05-10 | 华北理工大学 | Carbon dioxide direct evaporation type ice making system for artificial ice rink and using method thereof |
-
2016
- 2016-05-23 CN CN201620472008.2U patent/CN205641669U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105805981A (en) * | 2016-05-23 | 2016-07-27 | 华北理工大学 | Dual-operation compression-ejection heat pump air conditioner system |
| CN107906786A (en) * | 2017-12-25 | 2018-04-13 | 华北理工大学 | The coupled system of medically low temperature environment is produced based on double stage heat pump and autocascade cycle |
| CN107906786B (en) * | 2017-12-25 | 2023-06-30 | 华北理工大学 | Coupling system for preparing medical low-temperature environment based on two-stage heat pump and cascade circulation |
| CN114459179A (en) * | 2021-12-27 | 2022-05-10 | 华北理工大学 | Carbon dioxide direct evaporation type ice making system for artificial ice rink and using method thereof |
| CN114459179B (en) * | 2021-12-27 | 2023-05-12 | 华北理工大学 | Artificial ice rink carbon dioxide direct evaporation type ice making system and application method thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105805981A (en) | Dual-operation compression-ejection heat pump air conditioner system | |
| CN100552323C (en) | The solar energy-air source energy-saving type solution heat pump device | |
| CN104089424A (en) | Ejection refrigerating cycle device | |
| CN108007006B (en) | A kind of the self-cascade heat pump system and operational mode of multi-mode injection synergy | |
| CN103148629A (en) | Gas-liquid phase ejector synergy refrigeration system for double temperature direct cooling-type refrigerator | |
| CN101949611A (en) | Low-grade heat energy auxiliary-drive composite low-temperature refrigerating system | |
| CN103776189A (en) | Gas-supplying enthalpy-increasing type heat pump circulating system with ejector for heat pump device | |
| CN105042931A (en) | Combined heat pump system adopting trans-critical circulation and absorption heat pump co-production | |
| CN205641669U (en) | Duplex condition is compressed - is drawn and penetrates heat pump air conditioning system | |
| CN103759449B (en) | The two-stage steam compression type circulatory system of dual jet synergy | |
| CN107990580B (en) | A kind of the self-cascade heat pump system and operational mode of separating for several times injection synergy | |
| CN201355133Y (en) | Hot water device combining solar hot water system and heat pump | |
| CN103808101B (en) | A kind of two injection for two temperature refrigerator and the double back heat integration synergism refrigerating circulatory system | |
| CN201615649U (en) | Oil gas recycling device utilizing steam-ejection refrigeration | |
| CN105004095B (en) | A kind of trans critical cycle and the combined heat-pump system of two-stage absorption heat pump coproduction | |
| CN108007009B (en) | A kind of the solar-energy jet-type waring and cooling air conditioning system and operational mode of waste heat auxiliary | |
| CN107975896B (en) | A kind of absorption waring and cooling air conditioning system and operational mode of gas-liquid separation injection synergy | |
| CN105698431B (en) | A kind of double heat source high-efficiency compression injection combined heat-pump system and application | |
| CN103175333B (en) | Central air-conditioning combined solar injection refrigerating system | |
| CN207763287U (en) | Energy-efficient two-stage air source high-temperature heat pump system | |
| CN203672022U (en) | Double-injection and double-heat-regeneration combined synergistic refrigerating cycle system for dual-temperature refrigerator | |
| CN202915556U (en) | Device for improving thermal efficiency of gas water heater | |
| CN110307673A (en) | A kind of solar energy synergy heat pump system | |
| CN110307669A (en) | A kind of solar energy synergy multi-mode heating combined equipment based on compressing hot pump circulation | |
| CN201844611U (en) | Energy-saving deep refrigeration device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20161012 Termination date: 20180523 |