CN220321651U - Wide-temperature-range refrigerating system with double evaporators and double condensers - Google Patents
Wide-temperature-range refrigerating system with double evaporators and double condensers Download PDFInfo
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- 239000007788 liquid Substances 0.000 claims abstract description 37
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- 238000005057 refrigeration Methods 0.000 claims description 21
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- 238000006073 displacement reaction Methods 0.000 claims description 18
- 239000011521 glass Substances 0.000 claims description 15
- 238000001704 evaporation Methods 0.000 claims description 14
- 230000008020 evaporation Effects 0.000 claims description 8
- 238000004378 air conditioning Methods 0.000 claims description 5
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- 229910052802 copper Inorganic materials 0.000 claims description 4
- 239000010949 copper Substances 0.000 claims description 4
- 238000010438 heat treatment Methods 0.000 claims description 2
- 230000009977 dual effect Effects 0.000 claims 9
- 239000003921 oil Substances 0.000 description 12
- 239000003507 refrigerant Substances 0.000 description 12
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 6
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- 238000009833 condensation Methods 0.000 description 4
- 230000005494 condensation Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 239000000110 cooling liquid Substances 0.000 description 3
- 239000007921 spray Substances 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000003044 adaptive effect Effects 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
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- 238000005485 electric heating Methods 0.000 description 1
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- 238000000926 separation method Methods 0.000 description 1
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Abstract
The utility model discloses a wide temperature range refrigerating system with double evaporators and double condensers, which comprises a compressor, an evaporator A, B, a condenser A, B and a throttling element A, B, C, wherein the outlet of the compressor is provided with two paths, one path is connected with a first electromagnetic valve and a condenser A, the other path is connected with a second electromagnetic valve and a condenser B, the condenser A, B is connected with a liquid storage device, a drying filter and a viewing mirror after being combined and is divided into 3 paths, the 3 paths are respectively connected with the inlet of the throttling element A, B, C, the outlet of the throttling element C is connected with the inlets of a third electromagnetic valve, a fourth electromagnetic valve and a fifth electromagnetic valve in parallel, the outlet of the third electromagnetic valve is connected with the outlet of the throttling element A and then is connected with the inlet of the evaporator A, the outlet of the fourth electromagnetic valve is connected with the outlet of the throttling element B and then is connected with the inlet of the evaporator B, the outlet of the fifth electromagnetic valve is connected with the inlet of a gas-liquid separator after being combined with the outlet of the evaporator A, B, and the outlet of the gas-liquid separator is connected with the compressor. The utility model can realize the energy-saving operation of the product through a small pressure ratio working mode.
Description
Technical Field
The utility model relates to the field of refrigeration systems, in particular to a wide-temperature-range refrigeration system with double evaporators and double condensers.
Background
With the rapid development of electronic equipment and equipment, the requirements of people on the refrigeration of the traditional compressor are higher and higher, such as the operation mode of adapting to wider environment temperature, being safer and more reliable and saving electricity, so as to meet the iterative development of air-conditioning and cold liquid equipment. Currently, a single-way circulation vapor compression refrigeration system is very popular, and a stepless speed regulation fan and a direct current frequency conversion or stepping efficient compressor are added, so that the quick response, control and energy-saving operation of the refrigeration system reach a certain level, but under the condition of low rotation speed (low displacement) of the compressor, the oil return inside the system becomes a technical problem of no winding, for example, when the gaseous flow rate of the refrigerant in a pipe is low (< 5 m/s), the compressor oil is usually separated, the refrigerant cannot return to the compressor, and an oil shortage fault occurs, so that a plurality of measures such as an oil return bend (or an oil pressure lock), a double return pipe and the like are added. With the increase of the refrigerating capacity of the product, such as tens of kilowatts to several megawatts, when the air supply temperature or the liquid supply temperature is close to the set temperature or the load is reduced, the compressor is naturally switched to low-frequency or low-grade (such as the displacement is reduced to 25% -50% of the rated displacement) operation, and the condenser and the evaporator with larger relative volumes are operated, if the whole heat exchange is still adopted at the moment, the problems of oil shortage or oil return foaming and the like are greatly increased, so that the industry also has a working mode of accelerating oil return or avoiding a low-speed area simply by software control, but the large temperature fluctuation is brought.
The common air conditioner generally has a compression ratio of 3-8, but applies a small pressure ratio (such as the compression ratio is less than or equal to 1.3) technology under the condition of low ambient temperature to replace heat pipe circulation or air-air heat exchange, namely, an original refrigerating system is adopted to convert the compressor into a small pressure ratio working mode, at the moment, the compressor only provides power required by the flowing of refrigerant gas, and the outdoor natural cold source is fully utilized to realize energy-saving operation, and the energy efficiency ratio is as high as 7.0-20. It is known that the lower the ambient temperature is, the more the heat exchange area of the original condenser is excessive, the speed regulation or gear shifting of the compressor is also carried out, and the oil return problem is also faced. In addition, providing a small pressure ratio means that the throttling element needs to provide more flow under the action of a small pressure differential, and the original throttling element generally cannot meet the flow requirement.
How to more effectively correspond the refrigeration cycle to the external environment change and the load change, and combine the modularization development direction to group control the condenser and the evaporator, and by adding a plurality of control valves, the reliable operation of the refrigeration system in a truly wide temperature range is realized, and the method is worthy of being tried.
Disclosure of Invention
The utility model provides a wide-temperature-range refrigerating system with double evaporators and double condensers, which aims to solve the problem that the wide-temperature-range reliable operation is difficult to realize under the small pressure ratio in the prior art.
In order to achieve the above purpose, the technical scheme adopted by the utility model is as follows:
the utility model provides a wide temperature range refrigerating system of two condensers of two evaporators, includes compressor, evaporimeter A, evaporimeter B, condenser A, condenser B, throttling element A, throttling element B, throttling element C, reservoir, drier-filter, sight glass, gas-liquid separation ware, wherein:
the condenser A and the condenser B are mutually independent, the condenser A is provided with a condensing fan A, and the condenser B is provided with a condensing fan B;
the evaporator A and the evaporator B are two different heat exchange channels in the same double-loop heat exchanger and are used for delivering cold liquid by cold liquid equipment; or the evaporator A and the evaporator B are mutually independent and share an evaporation fan and an air duct, and are used for air conditioning to deliver cold air;
the outlet of the compressor is connected with 2 pipelines in parallel, the 1 st pipeline of the outlet of the compressor is connected with the inlet of the condenser A through a first electromagnetic valve, the 2 nd pipeline of the outlet of the compressor is connected with the inlet of the condenser B through a second electromagnetic valve, and the outlets of the condenser A and the condenser B are combined and then sequentially connected with the inlet of the sight glass through a liquid storage device and a drying filter; the sight glass export parallel connection 3 way pipeline, sight glass export 1 st way pipeline connection throttling element A import, sight glass export 2 nd way connection throttling element B import, sight glass export 3 rd way connection throttling element C import, throttling element C export parallel connection third solenoid valve import, fourth solenoid valve import, fifth solenoid valve import, wherein third solenoid valve export and throttling element A export meet the back and connect evaporimeter A import again, fourth solenoid valve export and throttling element B export meet the back and connect evaporimeter B import again, fifth solenoid valve export and evaporimeter A export, evaporimeter B export meet the back and connect the gas-liquid separator import again, gas-liquid separator exit linkage the compressor import.
Further, the heat exchange area ratio of the evaporator A to the evaporator B is 2.5:7.5 to 1:1; the heat exchange area ratio of the condenser A to the condenser B is 2.5:7.5 to 1:1.
Further, when the evaporator is used for air-conditioning air supply, the evaporator A, the evaporator B, the condenser A and the condenser B are all copper tube fin type heat exchangers or micro-channel heat exchangers.
Further, the throttle element A, the throttle element B and the throttle element C are all electronic expansion valves, electronic control valves, electromagnetic valves or thermal expansion valves.
Further, the compressor is a variable displacement compressor.
Further, the condenser A and the condenser B are subdivided into a plurality of modules, and each module is provided with a condensing fan when the modules are divided into a plurality of modules.
Further, auxiliary electric heating is respectively arranged in the liquid storage device and the gas-liquid separator.
Furthermore, the gas-liquid separator adopts a double-return structure.
Further, the first electromagnetic valve and the second electromagnetic valve are normally open, and the third electromagnetic valve, the fourth electromagnetic valve and the fifth electromagnetic valve are normally closed.
The utility model can select the adaptive working modes according to different working conditions of normal temperature, high temperature and low temperature, and comprises the following steps:
under normal temperature working conditions, when the load is large, 2 groups of evaporators and 2 groups of condensers work together, and when the load is small, 1 group of evaporators and 1 group of condensers work;
under the high-temperature working condition, using the 1 group of evaporators and the 2 groups of condensers as a high-temperature starting mode, working the 2 groups of evaporators and the 2 groups of condensers together when the load is large after starting, working the 1 group of evaporators and the 1 group of condensers when the load is small, and opening a throttling element C and a fifth electromagnetic valve to perform spray liquid cooling when the compressor is overheated and overloaded;
and under the low-temperature working condition, when the load is large, 2 groups of evaporators and 2 groups of condensers work together, and when the load is small, 1 group of evaporators and 1 group of condensers work, and simultaneously, the throttling element C and the corresponding third electromagnetic valve and/or fourth electromagnetic valve are opened, so that the working mode of the low-pressure ratio is entered.
In the utility model, the throttle element C and the third electromagnetic valve are opened and can be connected with the throttle element A in parallel or independently work to provide a small pressure ratio mode for the evaporator A; the throttle element C and the fourth electromagnetic valve are opened and can be connected with the throttle element B in parallel or independently work to provide a small pressure ratio mode for the evaporator B; the system compression ratio is the ratio of the condensation side P1 to the evaporation side P2, and the small pressure ratio is generally 1.05-1.8.
Compared with the prior art, the utility model has the advantages that:
1. the utility model utilizes 2 groups of evaporators, 2 groups of condensers, 3 groups of throttling elements and 5 groups of electromagnetic valves to realize different refrigeration operation modes under different loads under normal temperature, high temperature and low temperature working conditions, so that the evaporators, the condensers and the compressors are more matched, and the system performance is better.
2. Under the low-temperature working condition, the utility model realizes energy-saving operation through a small pressure ratio working mode.
3. According to the utility model, by adding the throttling element C, high-temperature spray cooling and larger flow at low temperature can be realized, and meanwhile, when one other throttling element fails, the throttling element can be used as a backup at any time.
4. The utility model is based on the modular design thought, has simple principle and is convenient to expand and realize.
Drawings
FIG. 1 is a schematic diagram of the structure of an embodiment of the present utility model when used in a chiller.
Fig. 2 is a schematic diagram of the structure of the present utility model when it is used for an air conditioner.
Fig. 3 is a schematic diagram of the structure of the condensation section according to the embodiment of the present utility model.
Detailed Description
The utility model will be further described with reference to the drawings and examples.
The embodiment discloses a double evaporator and double condenserAs shown in fig. 1 and 2, a wide temperature range refrigeration system is shownIndicating the air flow direction->Indicates the flow direction of the refrigerant under normal temperature condition>Indicates the flow direction of the flow increasing branch under the low-temperature working condition, < + >>Indicating the flow direction of the high-temperature working condition overheat control branch.
The embodiment comprises a compressor 1, an evaporator A10.1, an evaporator B10.2, a condenser A3.1, a condenser B3.2, a throttling element A8.1, a throttling element B8.2, a throttling element C8.3 and five groups of electromagnetic valves, a liquid storage device 5.1, a drying filter 6, a sight glass 7 and a gas-liquid separator 11.1.
In this embodiment, the condenser a3.1 and the condenser B3.2 are independent units, the condenser a3.1 is provided with the condensing fan a4.1, and the condenser B3.2 is provided with the condensing fan B4.2.
As shown in fig. 1, when the present embodiment is used for a cold liquid device to send cold liquid, a dual-loop heat exchanger 10 is used as the evaporator a10.1 and the evaporator B10.2. The dual-loop heat exchanger 10 comprises 3 heat exchange channels, wherein a middle-loop heat exchange channel is used as a cooling liquid channel for flowing through circulating cooling liquid, and two side heat exchange channels are respectively used as an evaporator A10.1 and an evaporator B10.2 and used for flowing through refrigerant of the evaporator A10.1 and the evaporator B10.2. In addition, when the evaporator is used for loosening liquid of cold liquid equipment, two heat exchangers can be integrated and combined to be used as the evaporator A10.1 and the evaporator B10.2 respectively.
As shown in fig. 2, when the air conditioner delivers cool air, the evaporators a10.1 and B10.2 are independent from each other, and the evaporators a10.1 and B10.2 share the evaporation fan 12 and the air duct.
The outlet of the compressor 1 is connected with 2 pipelines in parallel, the 1 st pipeline is connected with the inlet of the condenser A3.1 through the first electromagnetic valve 2.1, the 2 nd pipeline is connected with the inlet of the condenser B3.2 through the second electromagnetic valve 2.2, and the outlets of the condenser A3.1 and the condenser B3.2 are combined and then sequentially connected with the liquid storage device 5.1 and the drying filter 6 and then connected with the inlet of the sight glass 7.
The outlet of the sight glass 7 is connected with 3 pipelines in parallel, the 1 st pipeline is connected with the inlet of the throttling element A8.1, the 2 nd pipeline is connected with the inlet of the throttling element B8.2, and the 3 rd pipeline is connected with the inlet of the throttling element C8.3. The outlet of the throttling element C8.3 is connected with the inlet of the third electromagnetic valve 9.1, the inlet of the fourth electromagnetic valve 9.2 and the inlet of the fifth electromagnetic valve 9.3 in parallel, wherein the outlet of the third electromagnetic valve 9.1 is connected with the outlet of the throttling element A8.1 and then connected with the inlet of the evaporator A10.1, the outlet of the fourth electromagnetic valve 9.2 is connected with the outlet of the throttling element B8.2 and then connected with the inlet of the evaporator B10.2, the outlet of the fifth electromagnetic valve 9.3 is connected with the outlet of the evaporator A10.1 and the outlet of the evaporator B10.2 and then connected with the inlet of the gas-liquid separator 11.1, and the outlet of the gas-liquid separator 11.1 is connected with the inlet of the compressor 1, thereby forming a refrigeration cycle system.
The working mode which can be adapted according to the working conditions of normal temperature, high temperature and low temperature is selected in the embodiment, and the method comprises the following steps:
under normal temperature working conditions, when the load is large, 2 groups of evaporators and 2 groups of condensers work together, and when the load is small, 1 group of evaporators and 1 group of condensers work;
under the high-temperature working condition, using the 1 group of evaporators and the 2 groups of condensers as a high-temperature starting mode, working together with the 2 groups of evaporators and the 2 groups of condensers when the load is large after starting, working with the 1 group of evaporators and the 1 group of condensers when the load is small, and opening a throttling element C8.3 and a fifth electromagnetic valve 9.3 for spray cooling when the compressor is overheated and overloaded;
under the low-temperature working condition, when the load is large, 2 groups of evaporators and 2 groups of condensers work together, and when the load is small, 1 group of evaporators and 1 group of condensers work, meanwhile, the throttling element C8.3 and the corresponding third electromagnetic valve 9.1 and/or fourth electromagnetic valve 9.2 are opened, and the working mode of the low-pressure ratio is entered.
In this embodiment, the heat exchange area ratio of the evaporators a10.1 and B10.2 is between 2.5:7.5 and 1:1, and the heat exchange area ratio of the same condensers a3.1 and B3.2 is between 2.5:7.5 and 1:1. When the evaporator is used for an air conditioner, the 2 groups of evaporators and the 2 groups of condensers are copper tube fin heat exchangers or micro-channel heat exchangers. When the evaporator is used for cold liquid equipment, the evaporator A10.1 and the evaporator B10.2 are double-loop heat exchangers 10.
In this embodiment, the throttle element a8.1, the throttle element B8.2 and the throttle element C8.3 are closed when not in operation, and specifically an electronic expansion valve or an electronic control valve is adopted, and in a similar principle, a solenoid valve and a thermal expansion valve can be used instead.
The throttle element C8.3 and the third electromagnetic valve 9.1 are opened and can be connected with the throttle element A8.1 in parallel or independently work to provide a small pressure ratio mode for the evaporator A10.1; the throttle element C8.3 and the fourth electromagnetic valve 9.2 are opened and can be connected with the throttle element B8.2 in parallel or independently work to provide a small pressure ratio mode for the evaporator B10.2; the system compression ratio is the ratio of the condensation side P1 to the evaporation side P2, and the small pressure ratio is generally 1.05-1.8.
In this embodiment, the compressor is a variable displacement compressor, and a variable displacement compressor, a variable frequency compressor, or the like may be used.
In this embodiment, the condensing fans a4.1 and B4.2 are adjustable speed fans, and the number and the wind amount of the adjustable speed fans are determined according to the condensing and heat-dissipating capacity of each fan.
In this embodiment, the liquid reservoir 5.1 and the gas-liquid separator 11.1 are respectively provided with auxiliary electric heaters 5.2 and 11.2 for low temperature working conditions.
In this embodiment, the gas-liquid separator 11.1 should meet the requirement of normal oil return under small displacement, and specifically, a dual-return structure may be adopted.
In this embodiment, the first solenoid valve 2.1, the second solenoid valve 2.2 are normally open, and the third solenoid valve 9.1, the fourth solenoid valve 9.2 and the fifth solenoid valve 9.2 are normally closed.
This example is further illustrated as follows:
for example, an air conditioner with a cooling capacity of 25kW, a refrigerant R134a and an indoor side fan air quantity Q Internal wind =4400 m 3 Wind pressure P Internal wind =300 Pa, outdoor side fan volume Q External wind =2´7500 m 3 Wind pressure P External wind =80 Pa, a heat exchange area of 2 sets of evaporators and 2 sets of condensers versus a 1:1 design, i.e. the same heat exchange design, was used.
Under the working condition of normal temperature,taking the evaporating temperature of 7 ℃, the superheat degree of 5 ℃, the condensing temperature of 54 ℃ and the supercooling degree of 3 ℃, obtaining a corresponding thermodynamic cycle chart through corresponding refrigerant pressure enthalpy diagrams, and finding out that the enthalpy values of the inlet evaporator, the inlet compressor and the outlet compressor are 273.0kj/kg, 406.3kj/kg and 434.3 kj/kg respectively, and the specific volume of the inlet compressor is V= 0.0561m 3 Taking the compressor gas transmission coefficient l=0.85, the efficiency h=0.68, then:
unit refrigeration capacity q= 406.3-273.0 =133.3 kJ/kg
Unit theoretical compression work al=434.3-406.3 =28 kJ/kg
Refrigerant circulation amount g=q/q=25″3600/133.3≡675 kg/h
Theoretical displacement v=g×v/l=675″ 0.0561/0.85≡44.55 m of the compressor 3 /h
Compressor power n=g ∙ AL/h=675″ 28/0.68= 27794 kJ/h≡7721W
If the evaporator adopts a copper tube with F9.52' of 0.35mm, an aluminum sheet with df=0.15 mm thick is sleeved outside, the fin distance is 2.0mm, the fin shape is corrugated, the tube distance is 25.4mm, the row distance is 22mm, the total tube length of the evaporator is about 180m, the shunt n=20, each path is 9m, and the theoretical displacement of the compression compressor is 44.55 m 3 And (3) calculating the flow rate in the pipe at the displacement of 100 percent by the method:
V=100%V/(π∙r 2 ) /n=44.55/3600/(3.14´0.004412)/20≈10 m/s
at 25% displacement, the flow rate in the tube is:
V=25%V/(π∙r 2 ) /n=0.25´44.55/3600/(3.14´0.004412)/20≈2.5 m/s
the low-discharge compressor has the advantages that when the discharge capacity of the compressor is low, the flow rate of the refrigerant is correspondingly low, and oil return and the like are easy to cause.
Under the low-temperature working condition, the evaporating temperature is 7 ℃, the superheat degree is 5 ℃, the condensing temperature is 12 ℃, the supercooling degree is 3 ℃, the corresponding thermodynamic cycle diagram is obtained through the corresponding refrigerant pressure enthalpy diagram, and the enthalpy values of the inlet evaporator, the inlet compressor and the outlet compressor are respectively 211.8kj/kg, 406.3kj/kg and 409.7kj/kg, and the specific volume of the inlet compressor is V= 0.0561m 3 Taking the compressor gas transmission coefficient l=0.85, the efficiency h=0.68, then:
unit refrigeration capacity q= 406.3-211.8=194.5 kJ/kg
Unit theoretical compression work al=409.7-406.3 =3.4 kJ/kg
Refrigerant circulation amount g=q/q=25″3600/194.5≡ kg/h
Theoretical displacement v=g×v/l=463' -0.0561/0.85≡ 30.56 m of the compressor 3 /h
Compressor power n=g ∙ AL/h=463' -3.4/0.68=2315 kJ/h≡643W
Theoretical displacement 30.56 m of compressor 3 And (3) calculating the flow rate in the pipe by the following steps:
V=100%V/(π∙r 2 ) /n=30.56/3600/(3.14´0.004412)/20≈7 m/s
under the low-temperature working condition, the displacement of the compressor is 30.56/44.55 approximately 69% of the normal-temperature rated displacement, 2 groups of evaporators are all put into the device at the moment, the gaseous flow rate of the refrigerant is 7 m/s, and the problems of difficult oil return and the like are avoided. When the load is small, the displacement of the compressor is the lowest 25% of the normal temperature rated displacement, and the gaseous flow rate of the refrigerant in the pipe can be maintained at 5.1 m/s by using 1 group of evaporators, so that the problems of difficult oil return and the like are avoided.
The power consumption of this embodiment is further described as follows:
in order to illustrate the energy-saving operation of the small pressure ratio mode under the low-temperature working condition, the power consumption of the product is analyzed by simplifying theoretical calculation, and the power consumption of the product comprises a compressor, a condensing fan A, a condensing fan B and an evaporating fan. Wherein, fan power utilization N Wind power =k∙Q Wind power ∙P Wind power And (3) calculating a formula of/h, wherein h is the product of the internal efficiency and the mechanical efficiency of the fan, uniformly taking 0.75, uniformly taking 1.2 as a safety coefficient k, and then uniformly taking the power of the indoor side fan:
N internal wind =k∙(Q Internal wind /3600)∙P Internal wind /h=1.2´(4400/3600)´300/0.75≈587 W
Single outdoor side fan power:
N external wind =k∙(Q Internal wind /3600)∙P Internal wind /h=1.2´(7500/3600)´80/0.75≈267 W
The normal temperature theoretical power consumption is about: 7721+587+2' -267=8842W, energy efficiency ratio eer=25000/8842≡2.83.
The theoretical power consumption at low temperature is about: 643+587+267=1497W, energy efficiency ratio eer=25000/1497≡16.70.
The above can be known that the low pressure ratio mode is adopted at low temperature, the natural cold source is fully utilized to realize energy-saving operation, and the EER efficiency is improved from 2.83 at normal temperature to 16.70 at low temperature. Particularly, when the outdoor environment temperature is lower than the indoor temperature by more than 20 ℃, the larger and more obvious energy efficiency ratio is even more than 20.0.
Further explaining the system pressure ratio, assuming that the evaporation temperature is unchanged, taking the saturated evaporation pressure (absolute) corresponding to 7 ℃ to be 3.75bar
Under the high-temperature working condition, the condensing temperature of 70 ℃ corresponds to the saturated evaporating pressure (absolute pressure) of 21.17 bar, and the system pressure ratio=21.17/3.75=5.65;
under normal temperature working conditions, the corresponding saturated evaporation pressure (absolute pressure) of the condensing temperature of 50 ℃ is 13.19 bar, and the system pressure ratio=13.19/3.75=3.52;
under the low-temperature working condition, the condensing temperature is 12 ℃ and the corresponding saturated evaporating pressure (absolute pressure) is 4.43 bar, and then the system pressure ratio=4.43/3.75=1.18.
When the low pressure ratio mode is enabled, the condensing temperature is typically above 3 ℃ above the evaporating temperature to maintain normal thermodynamic cycle, so it is necessary to employ adjustable speed condensing fans and condenser groupings.
In addition, if the air conditioner has a heating (heat pump) function, a four-way reversing valve and the like can be additionally arranged, so that the reverse heat pump cycle of the system is satisfied, and the description is omitted here.
As shown in fig. 3, when the cooling liquid device or the air conditioner is used in a large-scale refrigeration device, for example, the condensation heat exchange amount corresponding to a compressor is 400 kW, and the condenser adopting forced air heat exchange adopts 2 groups of designs, the size can be large, which is unfavorable for the modularized design, and the condenser can be divided into multiple modules. As shown in fig. 3, in this embodiment, the condenser a3.1 and the condenser B3.2 may be respectively subdivided into 2 modules according to specific requirements, and each module is respectively configured with a condensing fan, so as to obtain 4 condenser modules, and the heat exchange capacity of each condenser module is 100kW, and then the 2 condenser modules are connected in parallel, and are respectively controlled by the first electromagnetic valve 2.1 and the second electromagnetic valve 2.2 at the inlet end, and the first electromagnetic valve 2.1 and the second electromagnetic valve 2.2 may be replaced by electromagnetic valves, so that the basic control method thereof does not conflict with the present patent.
Each group of condensers or each condenser module is specifically designed according to specific situations, such as specific internal flow channels and flow designs, fin sheets and sheet distances and the like. For large or ultra-large cold liquid equipment or air conditioners, such as the cooling capacity of 200 kW-10 MW, a plurality of sets of systems with the same principle can be adopted.
The preferred embodiments of the present utility model have been described in detail above with reference to the accompanying drawings, and the examples described herein are merely illustrative of the preferred embodiments of the present utility model and are not intended to limit the spirit and scope of the present utility model. The individual technical features described in the above-described embodiments may be combined in any suitable manner without contradiction, and such combination should also be regarded as the disclosure of the present disclosure as long as it does not deviate from the idea of the present utility model. The various possible combinations of the utility model are not described in detail in order to avoid unnecessary repetition.
The present utility model is not limited to the specific details of the above embodiments, and various modifications and improvements made by those skilled in the art to the technical solution of the present utility model should fall within the protection scope of the present utility model without departing from the scope of the technical concept of the present utility model, and the technical content of the present utility model is fully described in the claims.
Claims (9)
1. The utility model provides a wide temperature range refrigerating system of two condensers of two evaporators, its characterized in that includes compressor, evaporimeter A, evaporimeter B, condenser A, condenser B, throttling element A, throttling element B, throttling element C, reservoir, drier-filter, sight glass, gas-liquid separator, wherein:
the condenser A and the condenser B are mutually independent, the condenser A is provided with a condensing fan A, and the condenser B is provided with a condensing fan B;
the evaporator A and the evaporator B are two different heat exchange channels in the same double-loop heat exchanger and are used for delivering cold liquid by cold liquid equipment; or the evaporator A and the evaporator B are mutually independent and share an evaporation fan and an air duct, and are used for air conditioning to deliver cold air;
the outlet of the compressor is connected with 2 pipelines in parallel, the 1 st pipeline of the outlet of the compressor is connected with the inlet of the condenser A through a first electromagnetic valve, the 2 nd pipeline of the outlet of the compressor is connected with the inlet of the condenser B through a second electromagnetic valve, and the outlets of the condenser A and the condenser B are combined and then sequentially connected with the inlet of the sight glass through a liquid storage device and a drying filter; the sight glass export parallel connection 3 way pipeline, sight glass export 1 st way pipeline connection throttling element A import, sight glass export 2 nd way connection throttling element B import, sight glass export 3 rd way connection throttling element C import, throttling element C export parallel connection third solenoid valve import, fourth solenoid valve import, fifth solenoid valve import, wherein third solenoid valve export and throttling element A export meet the back and connect evaporimeter A import again, fourth solenoid valve export and throttling element B export meet the back and connect evaporimeter B import again, fifth solenoid valve export and evaporimeter A export, evaporimeter B export meet the back and connect the gas-liquid separator import again, gas-liquid separator exit linkage the compressor import.
2. A dual evaporator dual condenser wide temperature range refrigeration system as set forth in claim 1 wherein the heat exchange area ratio of evaporator a to evaporator B is between 2.5:7.5 and 1:1; the heat exchange area ratio of the condenser A to the condenser B is 2.5:7.5 to 1:1.
3. The wide temperature range refrigeration system of claim 1, wherein the evaporator a, the evaporator B, the condenser a, and the condenser B are all copper tube fin heat exchangers or microchannel heat exchangers when used for air-conditioning.
4. A dual evaporator dual condenser wide temperature range refrigeration system as set forth in claim 1 wherein the throttling element a, the throttling element B and the throttling element C are each electronic expansion valves, or electronic control valves, or solenoid valves, or thermal expansion valves.
5. A dual evaporator dual condenser wide temperature range refrigeration system as set forth in claim 1 wherein said compressor is a variable displacement compressor.
6. The wide temperature range refrigeration system as set forth in claim 1, wherein said condenser a, said condenser B are subdivided into a plurality of modules, each of said modules being configured with a condensing fan when divided into a plurality of modules.
7. A dual evaporator dual condenser wide temperature range refrigeration system as set forth in claim 1 wherein said accumulator and gas-liquid separator are each provided with auxiliary electrical heating.
8. The wide temperature range refrigeration system of claim 1, wherein said gas-liquid separator is of a dual return air configuration.
9. The wide temperature range refrigeration system of claim 1, wherein the first solenoid valve, the second solenoid valve are normally open, and the third solenoid valve, the fourth solenoid valve and the fifth solenoid valve are normally closed.
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| CN202321759050.9U CN220321651U (en) | 2023-07-05 | 2023-07-05 | Wide-temperature-range refrigerating system with double evaporators and double condensers |
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