CN203286741U - Refrigerating device - Google Patents
Refrigerating device Download PDFInfo
- Publication number
- CN203286741U CN203286741U CN2013200394822U CN201320039482U CN203286741U CN 203286741 U CN203286741 U CN 203286741U CN 2013200394822 U CN2013200394822 U CN 2013200394822U CN 201320039482 U CN201320039482 U CN 201320039482U CN 203286741 U CN203286741 U CN 203286741U
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- Prior art keywords
- heat exchanger
- temperature
- compressor
- communicated
- refrigerant
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- 239000003507 refrigerant Substances 0.000 claims abstract description 55
- 238000004781 supercooling Methods 0.000 claims abstract description 28
- 238000010438 heat treatment Methods 0.000 claims abstract description 19
- 230000001502 supplementing effect Effects 0.000 claims abstract description 9
- 230000008676 import Effects 0.000 claims description 30
- 239000002826 coolant Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000007599 discharging Methods 0.000 description 3
- 230000009102 absorption Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000002146 bilateral effect Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000008016 vaporization Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000002277 temperature effect Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The utility model discloses a refrigerating device, which comprises a refrigerant loop formed by a compressor, an intermediate heat exchanger, a low-temperature heat exchanger, a high-temperature heat exchanger, a first throttling device, a second throttling device and a supercooling device, wherein the supercooling device comprises a refrigerant main path and an air supply branch path, and the intermediate heat exchanger comprises a high-temperature flow path and a low-temperature flow path; wherein, the high-temperature flow path inlet of the intermediate heat exchanger is communicated with the exhaust port of the compressor, and the outlet is communicated with the inlet of the high-temperature heat exchanger; the inlet of the low-temperature flow path of the intermediate heat exchanger is communicated with a refrigerant pipe between the outlet of the high-temperature heat exchanger and the second throttling device through a first throttling device, and the outlet of the low-temperature flow path is communicated with the inlet of the gas supplementing branch of the supercooling device; and an air supplementing branch outlet of the supercooling device is communicated with an air supplementing port of the compressor. Refrigerating plant can show the heating volume that improves heat pump cycle, reduce compressor exhaust temperature, reduce condenser volume and refrigerant charge volume.
Description
Technical field
The utility model belongs to field of Refrigeration and Air-conditioning, relates to a kind of refrigerating plant.
Background technology
The heating capacity of refrigerating plant heat pump cycle can descend decay rapidly and can't meet consumers' demand with outdoor environment temperature.In the middle of part producer adopts twin-stage or accurate two-stage compression at present, tonifying Qi increases the enthalpy technology, improves low-temperature heating capacity and COP, reduces compressor exhaust temperature.But the tonifying Qi of prior art increases the enthalpy DeGrain, and is also not obvious to improving heating capacity and reducing the compressor exhaust temperature effect.
The utility model content
The purpose of this utility model is to provide a kind of compressor tonifying Qi effective, effectively improves the refrigerating plant of heating capacity and coefficient of performance in heating.
The utility model is achieved through the following technical solutions:
Refrigerating plant, comprise compressor, cryogenic heat exchanger, high-temperature heat-exchanging, first throttle device, the second throttling arrangement and supercooling apparatus, and described supercooling apparatus comprises refrigerant main road and tonifying Qi branch road; Described compressor, high-temperature heat-exchanging, supercooling apparatus refrigerant main road, the second throttling arrangement and cryogenic heat exchanger are communicated with and form loop by refrigerant pipe; Also comprise:
Intermediate Heat Exchanger, comprise high temperature stream and low temperature stream;
The import of described high temperature stream is communicated with exhaust outlet of compressor, and described high-temperature stream way outlet is communicated with the high-temperature heat-exchanging import;
The import of described low temperature stream is communicated with the refrigerant pipe between described high-temperature heat-exchanging outlet and the second throttling arrangement by the first throttle device, and described cryogenic flow way outlet is communicated with the import of described tonifying Qi branch road; Described tonifying Qi is propped up way outlet and is communicated with described compressor gas supplementing opening.
Further, the high temperature stream of described Intermediate Heat Exchanger is connected on the first refrigerant pipeline between exhaust outlet of compressor and high-temperature heat-exchanging import.
Further, the high temperature stream of described Intermediate Heat Exchanger by branch circuit parallel connection on the first refrigerant pipeline between exhaust outlet of compressor and high-temperature heat-exchanging import.
Further, the low temperature stream import of described Intermediate Heat Exchanger is connected between described supercooling apparatus refrigerant main road import and high-temperature heat-exchanging outlet by the first throttle device.
Further, the low temperature stream import of described Intermediate Heat Exchanger is connected between described supercooling apparatus refrigerant main road outlet and the second throttling arrangement by the first throttle device.
Further, described first throttle device and the second throttling arrangement are electric expansion valve, heating power expansion valve, restriction sleeve, capillary or restricting orifice.
The beneficial effects of the utility model are as follows:
Refrigerating plant described in the utility model arranges Intermediate Heat Exchanger before the road of tonifying Qi, utilize compressor air-discharging to provide thermal source for tonifying Qi branch road refrigerant, thereby increases air compensation, can significantly improve heating capacity and the coefficient of performance in heating of heat pump cycle.
Description of drawings
Fig. 1 is the system flow chart during the refrigerating plant heating operation in one of them embodiment of the utility model;
Fig. 2 is the system flow chart during the refrigerating plant heating operation in second embodiment of the utility model;
Fig. 3 is the system flow chart during the refrigerating plant heating operation in the 3rd embodiment of the utility model.
Description of reference numerals: 1-compressor; The 2-cryogenic heat exchanger; The 3-high-temperature heat-exchanging; 41-first throttle device; 42-the second throttling arrangement; The 5-supercooling apparatus; The 6-Intermediate Heat Exchanger; 7-the first refrigerant pipeline; The 8-stop valve.
The specific embodiment
Below in conjunction with the drawings and specific embodiments, content of the present utility model is described in further details.
As shown in Figure 1, refrigerating plant in first embodiment of the utility model, comprise compressor 1, cryogenic heat exchanger 2, high-temperature heat-exchanging 3, first throttle device 41, the second throttling arrangement 42, supercooling apparatus 5 and Intermediate Heat Exchanger 6, supercooling apparatus 5 comprises refrigerant main road and tonifying Qi branch road, and Intermediate Heat Exchanger 6 comprises high temperature stream and low temperature stream.compressor 1 exhaust outlet is communicated with Intermediate Heat Exchanger 6 high temperature stream imports, Intermediate Heat Exchanger 6 high-temperature stream way outlets are communicated with high-temperature heat-exchanging 3 imports, Intermediate Heat Exchanger 6 high temperature streams are connected on the first refrigerant pipeline 7 of compressor 1 exhaust outlet and high-temperature heat-exchanging 3 imports, high-temperature heat-exchanging 3 outlets are communicated with the refrigerant main road import of supercooling apparatus 5, be provided with the first branch road between high-temperature heat-exchanging 3 outlets and supercooling apparatus 5 refrigerant main road imports, this first branch road is communicated with by the import of the low temperature stream of first throttle device 41 and Intermediate Heat Exchanger 6, the cryogenic flow way outlet of Intermediate Heat Exchanger 6 and the import of tonifying Qi branch road are communicated with.Described tonifying Qi is propped up way outlet and is communicated with the gas supplementing opening of compressor 1, and described refrigerant main road outlet is communicated with cryogenic heat exchanger 2 imports by the second throttling arrangement 42, and cryogenic heat exchanger 2 outlets are communicated with the compressor air suction mouth.
it is as follows that first embodiment heats the periodic duty principle: the HTHP cold media gas that exhaust outlet of compressor is discharged enter Intermediate Heat Exchanger 6 high temperature streams and with the heat exchange of cryogenic flow trackside refrigerant after enter high-temperature heat-exchanging 3, be condensed into liquid state in the further heat release of high-temperature heat-exchanging 3, minute two-way after liquid refrigerants flows out from high-temperature heat-exchanging 3, one tunnel enters the refrigerant main road of supercooling apparatus, realized cold with the refrigerant heat exchange in the tonifying Qi branch road, then enter cryogenic heat exchanger 2 after the second throttling arrangement 42 reducing pressure by regulating flows, flash to gaseous coolant in cryogenic heat exchanger 2 heat absorptions, then enter the compressor air suction mouth, another road enters the low temperature stream of Intermediate Heat Exchanger 6 after by first throttle device 41 reducing pressure by regulating flows, enter the tonifying Qi branch road of supercooling apparatus 5 after vaporizing with the refrigerant heat exchange in the high temperature stream, with the further heat exchange vaporization of the refrigerant in the refrigerant main road, finally, the gas supplementing opening of the compressed machine 1 of the gaseous coolant of tonifying Qi branch road enters compressor.Entered the gaseous coolant of compressor discharges from exhaust outlet of compressor with being entered by air entry after the gaseous coolant of compressor through being compressed to for the first time intermediate pressure mixes by gas supplementing opening again after being compressed to high pressure for the second time.The compressor air-discharging of introducing in Intermediate Heat Exchanger 6 high temperature streams provides high temperature heat source for being used for the refrigerant of tonifying Qi in the low temperature stream, thereby greatly increased air compensation, the system refrigerant circulation increases, thus the ratio merit that makes the suction temperature of compressing for the second time initial state in compressor 1 reduce to compress for the second time the delivery temperature of end of a period state and compress for the second time.Thereby significantly improve heating capacity and the coefficient of performance in heating of heat pump cycle.
The increase of air compensation can reduce compressor exhaust temperature, and Intermediate Heat Exchanger 6 has reduced the high-temperature heat-exchanging 3 entrance refrigerant degrees of superheat simultaneously, thereby has improved the medium side average heat transfer coefficient and reduced condensation load.The super cooling effect of 5 pairs of main road refrigerants of supercooling apparatus makes the second throttling arrangement 42 entrance refrigerant specific enthalpies reduce, thereby increased the ratio enthalpy difference of cryogenic heat exchanger 2 import and export refrigerants, and reduced the refrigerant flow resistance, thereby reduced the ratio merit of compression for the first time, improve effective heat transfer temperature difference of cryogenic heat exchanger 2 bilateral media, helped further to improve heating capacity and efficiency.
As shown in Figure 2, the refrigerating plant in second embodiment of the utility model, with the difference of embodiment one only be Intermediate Heat Exchanger 6 high temperature streams by branch circuit parallel connection on the first refrigerant pipeline 7 of compressor 1 exhaust outlet and high-temperature heat-exchanging 3 imports.Compressor air-discharging is divided into two-way, and a road directly enters high-temperature heat-exchanging 3, and another road enters high-temperature heat-exchanging 3 after stop valve 8 enters refrigerant heat exchange in Intermediate Heat Exchanger 6 high temperature streams and low temperature stream.Be provided with two stop valves 8 on the pipeline at Intermediate Heat Exchanger 6 two ends, can be according to using needs, be communicated with or block this Intermediate Heat Exchanger 6 branch roads by switch stop valve 8.
As shown in Figure 3, refrigerating plant in the 3rd embodiment of the utility model, and the difference of embodiment one is to establish the first branch road between the outlet of supercooling apparatus refrigerant main road and the second throttling arrangement 42, and this first branch road is communicated with the import of tonifying Qi branch road by the low temperature stream of first throttle device 41 and Intermediate Heat Exchanger 6.Refrigerant all enter after high-temperature heat-exchanging 3 condensations supercooling apparatus 5 the refrigerant main road and and the tonifying Qi branch road in the refrigerant heat exchange realized cold, the refrigerant of crossing after cold is divided into two-way in the outlet of refrigerant main road, one tunnel, to the cryogenic heat exchanger evaporation, enters the compressor air suction mouth finally after the second throttling arrangement 42 throttlings; Another road enters Intermediate Heat Exchanger 6 after the first branch road enters 41 throttlings of first throttle device low temperature stream carries out heat exchange, and the refrigerant after heat absorption enters after the tonifying Qi branch road of supercooling apparatus 5 and the further heat exchange of refrigerant in the refrigerant main road gas supplementing opening that enters compressor 1 and carries out tonifying Qi.Excessively cold owing to having carried out before the coolant throttle in the first branch road, the low temperature stream import that has increased Intermediate Heat Exchanger 6 is compared enthalpy difference with the refrigerant that way outlet is propped up in the tonifying Qi of supercooling apparatus 5, and reduced the refrigerant flow resistance, thereby reduced the refrigerant that fills into compressor in the ratio merit of compression for the second time, improve effective heat transfer temperature difference of Intermediate Heat Exchanger and supercooling apparatus bilateral medium, helped further to improve heating capacity and efficiency.
Above-listed detailed description is for the illustrating of the utility model possible embodiments, and this embodiment is not in order to limit the scope of the claims of the present utility model, does not allly break away from the equivalence that the utility model does and implements or change, all should be contained in the scope of the claims of this case.
Claims (8)
1. refrigerating plant, comprise compressor (1), cryogenic heat exchanger (2), high-temperature heat-exchanging (3), first throttle device (41), the second throttling arrangement (42) and supercooling apparatus (5), described supercooling apparatus (5) comprises refrigerant main road and tonifying Qi branch road; Described compressor (1), high-temperature heat-exchanging (3), supercooling apparatus (5) refrigerant main road, the second throttling arrangement (42) and cryogenic heat exchanger (2) are communicated with and form loop by refrigerant pipe; It is characterized in that, also comprise:
Intermediate Heat Exchanger (6), comprise high temperature stream and low temperature stream;
The import of described high temperature stream is communicated with compressor (1) exhaust outlet, and described high-temperature stream way outlet is communicated with high-temperature heat-exchanging (3) import;
The import of described low temperature stream is communicated with the refrigerant pipe between described high-temperature heat-exchanging (3) outlet and the second throttling arrangement (42) by first throttle device (41), and described cryogenic flow way outlet is communicated with the import of described tonifying Qi branch road; Described tonifying Qi is propped up way outlet and is communicated with described compressor (1) gas supplementing opening.
2. refrigerating plant according to claim 1, is characterized in that, the high temperature stream of described Intermediate Heat Exchanger (6) is connected on the first refrigerant pipeline between compressor (1) exhaust outlet and high-temperature heat-exchanging (3) import.
3. refrigerating plant according to claim 1, is characterized in that, the high temperature stream of described Intermediate Heat Exchanger (6) by branch circuit parallel connection on the first refrigerant pipeline between compressor (1) exhaust outlet and high-temperature heat-exchanging (3) import.
4. the described refrigerating plant of according to claim 1 to 3 any one, it is characterized in that, the low temperature stream import of described Intermediate Heat Exchanger (6) is connected between described supercooling apparatus (5) refrigerant main road import and high-temperature heat-exchanging (3) outlet by first throttle device (41).
5. the described refrigerating plant of according to claim 1 to 3 any one, it is characterized in that, the low temperature stream import of described Intermediate Heat Exchanger (6) is connected between the outlet of described supercooling apparatus (5) refrigerant main road and the second throttling arrangement (42) by first throttle device (41).
6. the described refrigerating plant of according to claim 1 to 3 any one, is characterized in that, described first throttle device (41) and/or the second throttling arrangement (42) are electric expansion valve, heating power expansion valve, restriction sleeve, capillary or restricting orifice.
7. refrigerating plant according to claim 4, is characterized in that, described first throttle device (41) and/or the second throttling arrangement (42) are electric expansion valve, heating power expansion valve, restriction sleeve, capillary or restricting orifice.
8. refrigerating plant according to claim 5, is characterized in that, described first throttle device (41) and/or the second throttling arrangement (42) are electric expansion valve, heating power expansion valve, restriction sleeve, capillary or restricting orifice.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013200394822U CN203286741U (en) | 2013-01-21 | 2013-01-21 | Refrigerating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013200394822U CN203286741U (en) | 2013-01-21 | 2013-01-21 | Refrigerating device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203286741U true CN203286741U (en) | 2013-11-13 |
Family
ID=49543102
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013200394822U Expired - Lifetime CN203286741U (en) | 2013-01-21 | 2013-01-21 | Refrigerating device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203286741U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103940135A (en) * | 2013-01-21 | 2014-07-23 | 珠海格力电器股份有限公司 | Refrigerating device |
| CN110953699A (en) * | 2018-09-26 | 2020-04-03 | 杭州三花研究院有限公司 | Air conditioning system and control method thereof |
| US11828507B2 (en) | 2018-09-25 | 2023-11-28 | Hangzhou Sanhua Research Institute Co., Ltd. | Air conditioning system and control method therefor |
-
2013
- 2013-01-21 CN CN2013200394822U patent/CN203286741U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103940135A (en) * | 2013-01-21 | 2014-07-23 | 珠海格力电器股份有限公司 | Refrigerating device |
| CN103940135B (en) * | 2013-01-21 | 2016-06-08 | 珠海格力电器股份有限公司 | Refrigerating device |
| US11828507B2 (en) | 2018-09-25 | 2023-11-28 | Hangzhou Sanhua Research Institute Co., Ltd. | Air conditioning system and control method therefor |
| CN110953699A (en) * | 2018-09-26 | 2020-04-03 | 杭州三花研究院有限公司 | Air conditioning system and control method thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20131113 Effective date of abandoning: 20160608 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |