CN216814689U

CN216814689U - Refrigerating system

Info

Publication number: CN216814689U
Application number: CN202123262929.6U
Authority: CN
Inventors: 程姗; 李林达; 许海进; 董海凤; 郭凤杰
Original assignee: Nanjing Canatal Data Centre Environmental Tech Co Ltd
Current assignee: Nanjing Canatal Data Centre Environmental Tech Co Ltd
Priority date: 2021-12-23
Filing date: 2021-12-23
Publication date: 2022-06-24
Anticipated expiration: 2031-12-23

Abstract

The utility model discloses a refrigerating system, wherein an indoor tail end, a second ball valve, an intermediate heat exchanger, a first ball valve, a liquid storage device and a second refrigerant pump form a secondary side refrigerating cycle, the intermediate heat exchanger, a compressor, a single coil condenser, a first refrigerant pump and an electronic expansion valve form a primary side refrigerating cycle, the compressor is connected with a first bypass provided with a first one-way valve in parallel, and the first refrigerant pump is connected with a second bypass provided with a second one-way valve in parallel; the primary-side refrigeration cycle and the secondary-side refrigeration cycle exchange heat in the intermediate heat exchanger. The utility model separates the refrigerants on the primary side and the secondary side by the intermediate heat exchanger, solves the oil return problem of a refrigeration system under long pipelines and high altitude difference, and has strong applicability; meanwhile, the utility model has three operation modes, can partially or completely replace the compressor to work through the refrigerant pump, fully utilizes the natural cold source when the outdoor temperature is lower, and saves energy consumption.

Description

Refrigerating system

Technical Field

The utility model relates to air conditioning equipment, in particular to a refrigerating system.

Background

According to statistics, the power consumption of an air conditioning system in a communication machine room accounts for more than 40%, and along with the increasingly high requirements of low-carbon certification, carbon footprint and the like, how to reduce the power consumption of an air conditioner in the machine room, improve the energy efficiency of the air conditioner in the machine room and reduce the PUE value of an energy consumption index of the machine room becomes an increasingly concerned subject. For this reason, an indirect evaporative cooling system and a full inverter fluorine pump air conditioner have been developed successively in recent years. The indirect evaporation cooling system has higher requirements on the infrastructure of a machine room, a larger air supply air inlet is planned in the early stage, and the energy consumption of a compressor of a cooling compensation system is larger in high-temperature weather. The full-frequency conversion fluorine pump air conditioner adopts a frequency conversion compressor system and is distributed, but due to the characteristics of the compressor, the oil return problem and the cold quantity attenuation problem of the compressor cannot be avoided under the conditions of an overlong pipeline and a high altitude difference, particularly a high negative altitude difference. Data centers need to be refrigerated all the year round, machine rooms still need to be refrigerated in seasons with low temperature, and the existing refrigeration systems do not utilize sufficient outdoor natural cold sources, so that unnecessary waste of energy is caused.

Disclosure of Invention

The purpose of the utility model is as follows: the utility model aims to provide a refrigerating system which is high in applicability and energy-saving.

The technical scheme is as follows: the refrigerating system comprises an outdoor unit and an indoor tail end, wherein the outdoor unit comprises an intermediate heat exchanger, a compressor, a single coil condenser, a first refrigerant pump, an electronic expansion valve, a first ball valve, a second ball valve, a liquid storage device and a second refrigerant pump; the primary side refrigeration cycle and the secondary side refrigeration cycle exchange heat in the intermediate heat exchanger.

In the utility model, the intermediate heat exchanger is a condenser for the primary side refrigeration cycle and an evaporator for the secondary side refrigeration cycle, and the refrigerant on the primary side and the refrigerant on the secondary side are separated by the intermediate heat exchanger, so that the problem of oil return of a refrigeration system under a long pipeline and a high-altitude difference is solved, the applicability is strong, and a longer one-way pipe and a larger negative-altitude difference can be realized. The length of a single-pass pipe of the conventional air cooling system is 60m, and the length of the single-pass pipe can reach 150m or even longer. The negative height difference of the conventional air cooling system is 5m, and the negative height difference of the utility model can reach 50 m. There are three modes of operation on the primary side: a compressor cooling operation mode; a compressor and refrigerant pump mixed refrigeration operation mode; a refrigerant pump operating mode; when the outdoor temperature is low, the first refrigerant pump partially or completely replaces the compressor to work, a natural cold source is fully utilized, and the power of the compressor is generally more than 10kW, while the power of the refrigerant pump is less than 1kW, so that the power consumption of the unit can be saved. The three operation modes adopt the same single coil condenser, the wind side resistance is small, and the power consumption of a condensing fan is small. Compared with the conventional air cooling system, the annual energy efficiency ratio can be improved by more than 50%.

Further, the second refrigerant pump is connected with a third refrigerant pump in parallel, and two ends of the second refrigerant pump and two ends of the third refrigerant pump are respectively connected with the inlet ball valve and the outlet ball valve in series. The second refrigerant pump and the third refrigerant pump are used and backup with each other, and the stability and the reliability of the system can be improved.

Further, the intermediate heat exchanger is a plate heat exchanger or a sleeve heat exchanger.

Further, the compressor adopts an inverter compressor.

Furthermore, the compressor is a single compressor or two compressors connected in parallel, and is determined according to different cold quantities.

Further, the indoor end is in the form of a heat pipe back plate, a heat pipe column, a ceiling-mounted heat pipe or a room-level heat pipe.

Further, the number of the indoor ends is one or more, and the indoor ends are connected in parallel.

Has the advantages that: compared with the prior art, the utility model has the following advantages: (1) the utility model separates the refrigerants on the primary side and the secondary side by the intermediate heat exchanger, solves the oil return problem of a refrigeration system under a long pipeline and a high altitude difference, has strong applicability, and can realize longer one-way pipe length and larger negative altitude difference; (2) the utility model has three operation modes, can partially or completely replace the compressor to work through the refrigerant pump, fully utilizes the natural cold source when the outdoor temperature is lower, and saves the energy consumption.

Drawings

FIG. 1 is a system schematic of the present invention.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings.

As shown in fig. 1, a refrigeration system includes an outdoor unit and an indoor end 16, the outdoor unit includes an intermediate heat exchanger 1, a compressor 3, a single coil condenser 4, a first refrigerant pump 6, an electronic expansion valve 8, a first ball valve 11, a second ball valve 12, a reservoir 13, and a second refrigerant pump 14, the indoor end 16, the second ball valve 12, the intermediate heat exchanger 1, the first ball valve 11, the reservoir 13, and the second refrigerant pump 14 constitute a secondary side refrigeration cycle, the intermediate heat exchanger 1, the compressor 3, the single coil condenser 4, the first refrigerant pump 6, and the electronic expansion valve 8 constitute a primary side refrigeration cycle, the compressor 3 is connected in parallel with a first bypass provided with a first check valve 2, and the first refrigerant pump 6 is connected in parallel with a second bypass provided with a second check valve 7. The primary-side refrigeration cycle and the secondary-side refrigeration cycle exchange heat in the intermediate heat exchanger 1. And a condensing fan 5 is arranged on the single-coil condenser 4. In addition, the second refrigerant pump 14 is connected in parallel with a third refrigerant pump 15, the inlet ball valve 22 and the outlet ball valve 21 are connected in series at both ends of the second refrigerant pump 14, and the inlet ball valve 24 and the outlet ball valve 23 are connected in series at both ends of the third refrigerant pump 15. The second refrigerant pump 14 and the third refrigerant pump 15 are used as backup for each other. The system automatically judges and preferentially starts the refrigerant pump with less running time.

In this embodiment, the intermediate heat exchanger 1 is a plate heat exchanger, and the compressor 3 is a variable frequency compressor. The indoor end 16 is in the form of a heat pipe back plate, a heat pipe column, a ceiling mounted heat pipe, or a room level heat pipe. The number of the indoor ends 16 is plural and they are connected in parallel, and the indoor ends 16 are respectively provided with an electronic expansion valve and are respectively controlled independently.

The high-temperature refrigerant gas on the secondary side from the intermediate heat exchanger 1 sequentially passes through the first ball valve 11, the liquid storage tank 13 and the inlet ball valve, then enters the second refrigerant pump 14 or the third refrigerant pump 15, then passes through the outlet ball valve, and enters the indoor tail end 16. The refrigerant gas returning from the chamber passes through the second ball valve 12 and enters the intermediate heat exchanger 1.

There are three modes of operation on the primary side: a compressor cooling operation mode; a compressor and refrigerant pump mixed refrigeration operation mode; refrigerant pump operating mode. In particular, the amount of the solvent to be used,

(1) when the outdoor temperature is higher than the mixed mode starting temperature (default 20 ℃), the unit operates in the compressor refrigeration mode, at this time, the compressor 3 is operated, and the first refrigerant pump 6 is not operated: refrigerant vapor from the intermediate heat exchanger 1 enters the compressor 3 to be pressurized to become high-temperature and high-pressure refrigerant vapor, and then enters the single-coil condenser 4 to be condensed. The condensed refrigerant is subcooled, passes through a second one-way valve 7, is throttled and depressurized through an electronic expansion valve 8, and then enters the intermediate heat exchanger 1, so that the whole cycle is formed.

(2) When the temperature is lower than the mixed mode starting temperature (default 20 ℃) and higher than the fluorine pump starting temperature (default 10 ℃), the unit operates in a compressor and refrigerant pump mixed refrigeration mode, the compressor 3 works at the moment, and the first refrigerant pump 6 also works: refrigerant vapor from the intermediate heat exchanger 1 enters the compressor 3 to be pressurized to become high-temperature and high-pressure refrigerant vapor, and then enters the single-coil condenser 4 to be condensed. The condensed refrigerant is subcooled, is pressurized by the first refrigerant pump 6, is throttled and depressurized by the electronic expansion valve 8, and then enters the intermediate heat exchanger 1, so that the whole cycle is formed.

(3) When the temperature is lower than the fluorine pump starting temperature (default 10 ℃), the unit operates in a refrigerant pump refrigeration mode, the compressor 3 does not work, and the first refrigerant pump 6 works: refrigerant vapor from the intermediate heat exchanger 1 passes through the first check valve 2 and enters the single-coil condenser 4 for condensation. The condensed refrigerant is subcooled, is pressurized by the first refrigerant pump 6, is throttled and depressurized by the electronic expansion valve 8, and then enters the intermediate heat exchanger 1, so that the whole cycle is formed.

Claims

1. A refrigeration system comprising an outdoor unit and an indoor terminal (16), characterized by: the outdoor unit comprises an intermediate heat exchanger (1), a compressor (3), a single coil condenser (4), a first refrigerant pump (6), an electronic expansion valve (8), a first ball valve (11), a second ball valve (12), a liquid storage device (13) and a second refrigerant pump (14), wherein an indoor tail end (16), the second ball valve (12), the intermediate heat exchanger (1), the first ball valve (11), the liquid storage device (13) and the second refrigerant pump (14) form a secondary side refrigeration cycle, the intermediate heat exchanger (1), the compressor (3), the single coil condenser (4), the first refrigerant pump (6) and the electronic expansion valve (8) form a primary side refrigeration cycle, the compressor (3) is connected with a first bypass provided with a first one-way valve (2) in parallel, and the first refrigerant pump (6) is connected with a second bypass provided with a second one-way valve (7) in parallel; the primary-side refrigeration cycle and the secondary-side refrigeration cycle exchange heat in the intermediate heat exchanger (1).

2. The refrigeration system of claim 1, wherein: the second refrigerant pump (14) is connected with a third refrigerant pump (15) in parallel, and two ends of the second refrigerant pump (14) and two ends of the third refrigerant pump (15) are respectively connected with an inlet ball valve and an outlet ball valve in series.

3. The refrigeration system of claim 1, wherein: the intermediate heat exchanger (1) adopts a plate heat exchanger or a sleeve heat exchanger.

4. The refrigeration system of claim 1, wherein: the compressor (3) adopts a variable frequency compressor.

5. The refrigeration system of claim 1, wherein: the compressor (3) is a single compressor or two compressors connected in parallel.

6. The refrigeration system of claim 1, wherein: the indoor end (16) is in the form of a heat pipe back plate, a heat pipe column, a ceiling-mounted heat pipe or a room-level heat pipe.

7. The refrigeration system of claim 1, wherein: the number of the indoor terminals (16) is one or more, and a plurality of indoor terminals (16) are connected in parallel with each other.