CN201666687U - Cascade refrigerating unit under working condition of full temperature - Google Patents
Cascade refrigerating unit under working condition of full temperature Download PDFInfo
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- CN201666687U CN201666687U CN2010201131873U CN201020113187U CN201666687U CN 201666687 U CN201666687 U CN 201666687U CN 2010201131873 U CN2010201131873 U CN 2010201131873U CN 201020113187 U CN201020113187 U CN 201020113187U CN 201666687 U CN201666687 U CN 201666687U
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Abstract
The utility model discloses a cascade refrigerating unit under the working condition of full temperature, wherein a high-temperature condenser, a first high-temperature expansion valve and an evaporative condenser are arranged from the outlet of a high-temperature compressor to the inlet of the compressor sequentially; and the evaporative condenser, a low-temperature expansion valve and a low-temperature evaporator are arranged from the outlet of a low-temperature compressor to the inlet of the compressor sequentially and are connected with a second high-temperature expansion tank in parallel. In addition, in order to meet the requirement of the working condition (at the moment, the cold supply temperature can be met by a single-stage cooling unit) of full temperature, the cascade refrigerating unit is also provided with a second high-temperature expansion valve and a high-temperature evaporator that are connected with the first high-temperature expansion valve and the evaporative condenser in parallel and can be switched over by an electromagnetic valve. In the utility model, only the high-temperature condenser works when in the cold supply under the working condition of high temperature; and the high-temperature condenser and the low-temperature condenser work simultaneously when in the cold supply under the working condition of low temperature, thereby achieving the aims of lowering the operating cost, saving the initial cost of equipment and improving the utilization ratio of the equipment at the same time.
Description
Technical field
The utility model relates to a kind of total temperature operating mode cascade refrigeration unit, particularly a kind of energy-conservation cascade refrigeration unit that adopts high temperature level double evaporators total temperature cooling operating mode.
Background technology
Common cascade refrigeration unit is to be made of parts such as high temperature stage compressor, high temperature level condenser, high temperature level expansion valve, evaporative condenser and low temperature stage compressor, low temperature level expansion valve, low temperature level evaporimeter and expansion vessels.The purpose that the medium that is cooled is cooled by low temperature level evaporimeter and low-temperature refrigerant generation heat exchange realization.But this total temperature cascade refrigeration unit high temperature stage compressor and low temperature stage compressor in reducing the process of medium temperature need to work simultaneously all the time, and energy consumption is big.
The utility model content
Technical problem to be solved in the utility model provides a kind of total temperature operating mode cascade refrigeration unit, to reach the reduction operating cost, saves the purpose of equipment investment and raising utilization rate of equipment and installations.
For achieving the above object, total temperature operating mode cascade refrigeration unit described in the utility model comprises high temperature stage compressor, high temperature level condenser, the first high temperature level expansion valve, evaporative condenser and low temperature stage compressor, low temperature level expansion valve, low temperature level evaporimeter and expansion vessel; Described high temperature stage compressor outlet enters the mouth through high temperature level condenser, the first high temperature level expansion valve, evaporative condenser to high temperature stage compressor successively; Low temperature stage compressor outlet successively through evaporative condenser, low temperature level expansion valve, low temperature level evaporimeter to the suction port of compressor and expansion vessel in parallel.It is characterized in that: further comprising the second high temperature level expansion valve, high temperature level evaporimeter, adopt parallel form to be connected between the described first high temperature level expansion valve, evaporative condenser and the second high temperature level expansion valve, the high temperature level evaporimeter, and realize switching by magnetic valve.
Above-mentioned evaporimeter is divided into high temperature level evaporimeter and low temperature level evaporimeter, and high temperature level evaporimeter and low temperature level evaporimeter are parallel with one another at the side medium that is cooled, and realizes switching by electrically operated valve.
Operation principle of the present utility model is: the total temperature operating mode is divided into worst hot case cooling and worst cold case cooling.
The worst hot case cooling: the high temperature and high pressure gas that the high temperature stage compressor is discharged enters high temperature level condenser, cooling and condensation become subcooled liquid, after the second high temperature level expansion valve throttling step-down, enter high temperature level evaporimeter again, absorption is flow through and is become superheated steam behind the heat of the medium that is cooled of high temperature level evaporimeter and be inhaled in the compressor, thereby finishes the once circulation of refrigerant system.Cooling reaches the temperature that needs to the medium that is cooled through evaporimeter.
The worst cold case cooling: the high temperature and high pressure gas that the high temperature stage compressor is discharged enters high temperature level condenser, cooling and condensation become subcooled liquid, after the first high temperature level expansion valve throttling step-down, enter evaporative condenser again, absorption is flow through and is become superheated steam behind the heat of the high temperature and high pressure gas that the low temperature stage compressor of evaporative condenser discharges and be inhaled in the compressor, the high temperature and high pressure gas that the low temperature stage compressor is discharged enters evaporative condenser, cooling and condensation become subcooled liquid, after low temperature level expansion valve throttling step-down, enter low temperature level evaporimeter again, absorption is flow through and is become superheated steam behind the heat of the medium that is cooled of low temperature level evaporimeter and be inhaled in the compressor, thereby finishes the once circulation of refrigerant system.Cooling reaches the temperature that needs to the medium that is cooled through low temperature level evaporimeter.
The utility model compared with prior art, it is made of high temperature stage compressor, high temperature level condenser, the first high temperature level expansion valve, evaporative condenser and low temperature stage compressor, low temperature level expansion valve, low temperature level evaporimeter and expansion vessel etc. equally, but has increased by the second high temperature level expansion valve, high temperature level evaporimeter.The other first high temperature level expansion valve, evaporative condenser adopt parallel form to be connected with the second high temperature level expansion valve, high temperature level evaporimeter, switch by magnetic valve; High temperature level evaporimeter adopts parallel form to be connected with low temperature level evaporimeter at the side medium that is cooled, and switches high temperature level evaporimeter and low temperature level evaporimeter by electrically operated valve.Temperature according to the medium that is cooled is selected required cooling operating mode, both can adopt the cooling of high temperature level, can adopt the cooling of low temperature level again, solved cascade refrigeration unit high temperature stage compressor and low temperature stage compressor in the process that the reduces medium temperature big problem of energy consumption of need working simultaneously all the time, reach the reduction operating cost, save investment of equipment, improve the purpose of utilization rate of equipment and installations.
Description of drawings
Fig. 1 is the utility model structural principle schematic diagram
Wherein: 1-high temperature stage compressor, 2-high temperature level condenser, 3-high temperature level fluid hand valve, 4-high temperature level device for drying and filtering, 5-high temperature level magnetic valve one, the 6-first high temperature level expansion valve, the 7-evaporative condenser, the 8-second high temperature level magnetic valve, the 9-second high temperature level expansion valve, 10-high temperature level evaporimeter, 11-low temperature stage compressor, 12-low temperature level fluid hand valve, 13-low temperature level device for drying and filtering, 14-low temperature level device for drying and filtering hand valve, 15-low temperature level expansion valve, 16-low temperature level evaporimeter, 17-expansion vessel, the 18-side medium high temperature level electrically operated valve that is cooled, the 19-side medium low temperature level electrically operated valve that is cooled.
The specific embodiment
As shown in Figure 1, be example with FDCWD32 total temperature operating mode cascade refrigeration unit, it is mainly by high temperature stage compressor 1 (HANBELL semi-hermetic screw compressor); High temperature level condenser 2 (JM155CZ1 water-cooled condenser); High temperature level Φ 22 fluid hand valves 3, high temperature level device for drying and filtering 4 (U.S. ALCO device for drying and filtering); The first high temperature level magnetic valve 5 (Italian Castel magnetic valve); The first high temperature level expansion valve 6 (U.S. ALCO expansion valve); Evaporative condenser 7 (German GEA evaporative condenser); The second high temperature level magnetic valve 8 (Italian Castel magnetic valve); The second high temperature level expansion valve 9 (U.S. ALCO expansion valve); High temperature level evaporimeter 10 (German GEA evaporimeter); Low temperature stage compressor 11 (HANBELL semi-hermetic screw compressor); Low temperature level Φ 22 fluid hand valves 12; Low temperature level device for drying and filtering 13 (U.S. ALCO device for drying and filtering); Low temperature level Φ 22 device for drying and filtering hand valves 14; Low temperature level expansion valve 15 (U.S. ALCO expansion valve); Low temperature level evaporimeter 16 (German GEA evaporimeter); 300 liters of expansion vessels 17; The side medium high temperature level that is cooled electrically operated valve 18; The side medium low temperature level that is cooled electrically operated valve 19 is formed, and has realized the function of total temperature operating mode cooling.
Adopt the worst hot case cooling when medium temperature that is cooled is higher than-30 ℃: the high temperature and high pressure gas that high temperature stage compressor 1 is discharged enters high temperature level condenser 2, cooling and condensation become subcooled liquid, after the 9 throttling step-downs of the second high temperature level expansion valve, enter high temperature level evaporimeter 10 again, absorption is flow through and is become superheated steam behind the heat of the medium that is cooled of high temperature level evaporimeter 10 and be inhaled in the compressor, thereby finish the once circulation of refrigerant system, the medium that is cooled is through high-temperature evaporator 10 coolings, and low temperature stage compressor 11 is not worked.
Adopt the worst cold case cooling when medium temperature that is cooled is lower than-30 ℃: the high temperature and high pressure gas that high temperature stage compressor 1 is discharged enters high temperature level condenser 2, cooling and condensation become subcooled liquid, after the 6 throttling step-downs of the first high temperature level expansion valve, enter evaporative condenser 7 again, absorption is flow through and is become superheated steam behind the heat of the high temperature and high pressure gas that the low temperature stage compressor 11 of evaporative condenser discharges and be inhaled in the compressor, the high temperature and high pressure gas that low temperature stage compressor 11 is discharged enters evaporative condenser 7, cooling and condensation become subcooled liquid, after low temperature level expansion valve throttling 15 step-downs, enter low temperature level evaporimeter 16 again, absorption is flow through and is become superheated steam behind the heat of the medium that is cooled of low temperature level evaporimeter 16 and be inhaled in the compressor, thereby finish the once circulation of refrigerant system, 16 coolings reach the temperature that needs to the medium that is cooled through low temperature level evaporimeter.
Switch the medium that is cooled by the side medium high temperature level electrically operated valve 18 that is cooled, the side medium low temperature level that is cooled electrically operated valve 19 and enter high temperature level evaporimeter 10, low temperature level evaporimeter 16 respectively.
Claims (2)
1. total temperature operating mode cascade refrigeration unit, comprise high temperature stage compressor (1), high temperature level condenser (2), the first high temperature level expansion valve (6), evaporative condenser (7) and low temperature stage compressor (11), low temperature level expansion valve (15), low temperature level evaporimeter (16) and expansion vessel (17), described high temperature stage compressor (1) outlet enters the mouth through high temperature level condenser (2), the first high temperature level expansion valve (6), evaporative condenser (7) to high temperature stage compressor (1) successively; Low temperature stage compressor (11) outlet enters the mouth and expansion vessel in parallel (17) through evaporative condenser (7), low temperature level expansion valve (15), low temperature level evaporimeter (16) to low temperature stage compressor (11) successively; It is characterized in that: further comprising the second high temperature level expansion valve (9), high temperature level evaporimeter (10), adopt parallel form to be connected between the described first high temperature level expansion valve (6), evaporative condenser (7) and the second high temperature level expansion valve (9), the high temperature level evaporimeter (10), and realize switching by magnetic valve.
2. total temperature operating mode cascade refrigeration unit according to claim 1 is characterized in that: described high temperature level evaporimeter (10) and low temperature level evaporimeter (16), and parallel with one another with high temperature level evaporimeter (10) and low temperature level evaporimeter (16) at the side medium that is cooled.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201131873U CN201666687U (en) | 2010-02-10 | 2010-02-10 | Cascade refrigerating unit under working condition of full temperature |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201131873U CN201666687U (en) | 2010-02-10 | 2010-02-10 | Cascade refrigerating unit under working condition of full temperature |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201666687U true CN201666687U (en) | 2010-12-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010201131873U Expired - Lifetime CN201666687U (en) | 2010-02-10 | 2010-02-10 | Cascade refrigerating unit under working condition of full temperature |
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| Country | Link |
|---|---|
| CN (1) | CN201666687U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105972849A (en) * | 2016-03-25 | 2016-09-28 | 合肥天鹅制冷科技有限公司 | Wide temperature range cooling liquid supply system |
| WO2019058360A1 (en) | 2017-09-24 | 2019-03-28 | N. A. M. Technology Ltd. | Combined-type cascade refrigerating apparatus |
-
2010
- 2010-02-10 CN CN2010201131873U patent/CN201666687U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105972849A (en) * | 2016-03-25 | 2016-09-28 | 合肥天鹅制冷科技有限公司 | Wide temperature range cooling liquid supply system |
| WO2019058360A1 (en) | 2017-09-24 | 2019-03-28 | N. A. M. Technology Ltd. | Combined-type cascade refrigerating apparatus |
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| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20101208 |
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| CX01 | Expiry of patent term |