CN219550943U - Air conditioning system - Google Patents
Air conditioning system Download PDFInfo
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- CN219550943U CN219550943U CN202320357151.7U CN202320357151U CN219550943U CN 219550943 U CN219550943 U CN 219550943U CN 202320357151 U CN202320357151 U CN 202320357151U CN 219550943 U CN219550943 U CN 219550943U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The utility model discloses an air conditioning system, comprising: a compressor; a condenser; an evaporator; a throttle device; a frequency converter module; a cooling device; the refrigerant circulates through the liquid outlet of the condenser, the cooling device and the air inlet of the condenser in sequence to form a refrigerant cooling loop; the inlet of the cooling device is connected with the liquid outlet of the condenser, and the outlet of the cooling device is connected with the exhaust pipe of the compressor. According to the air conditioning system, the refrigerant cooling loop is connected between the liquid outlet of the condenser and the exhaust pipe of the compressor, and when the frequency conversion equipment is required to be cooled, the refrigerant is separated from the liquid outlet of the condenser and enters the cooling device. The cooling circulation does not occupy the air suction amount of the compressor, so that the refrigerating energy efficiency of the compressor is not influenced, and the problem that the energy efficiency of the refrigerating air-conditioning system is influenced due to the fact that the refrigerating capacity provided by the compressor for the refrigerating system is reduced due to the fact that the temperature of the refrigerant is reduced is solved; and meanwhile, condensation is avoided in the cooling process.
Description
Technical Field
The utility model belongs to the technical field of air conditioners.
Background
In a variable frequency large refrigeration air conditioning system, the cooling of the frequency converter is of paramount importance. Because the power consumption of the frequency converter module is different in power, three common cooling modes of the frequency converter assembly exist at present: air-cooled, water-cooled, and refrigerant throttling-cooled.
The air-cooled type is only suitable for cooling frequency converters and components with smaller power, the effect is poor for high-power frequency converters, and the larger forced air exhaust system causes larger power consumption.
The water-cooled type has better cooling effect, but the defects are obvious: 1. if the cooling device is extremely easy to scale due to the adoption of non-softened circulating water cooling, the cooling effect is affected, and finally, the cooler needs to be replaced or the chemical cleaning is very troublesome. 2. In cold winter, when the unit is stopped, water of a cooling system is required to be emptied, or problems such as icing and bursting of a pipeline, a heat exchanger and the like are easy to occur, and water is required to be added again before starting up, so that time and labor are wasted; in summer, even the surface of the cooler can be exposed in the high-temperature and high-humidity machine room environment. 3. Vibration and noise of a water pump in a circulating water system can cause a series of leakage and complaint risks, and power consumption of the water pump during operation also can lower the overall energy efficiency of the system.
The cooling effect of the refrigerant throttling cooling type system is more ideal than the two types: the operation of the refrigerant does not cause scaling and power consumption caused by a driving motor, but the refrigerant for cooling enters the air suction end of the compressor after cooling the frequency converter assembly, so that the effective air suction amount of the compressor is occupied, the cold amount provided by the compressor for the refrigerating system is reduced, and the energy efficiency of the refrigerating and air conditioning system is influenced as a result; the temperature of the throttled two-phase mixed refrigerant is lower, and the condensation risk is higher than that of a water-cooled machine room in summer under high-temperature high-humidity environment.
Disclosure of Invention
The utility model provides an air conditioning system aiming at the problems existing in the prior art when the frequency conversion equipment is cooled, which can avoid various problems of air cooling and water cooling, and solve the problem that the energy efficiency of the refrigeration air conditioning system is affected as a result of the reduction of the cooling capacity provided by a compressor to the refrigeration system caused by cooling of a refrigerant.
In order to achieve the aim of the utility model, the utility model is realized by adopting the following technical scheme:
an air conditioning system, comprising:
a compressor for compressing a refrigerant;
a condenser;
an evaporator;
a throttle device;
a frequency converter module for adjusting an operating frequency of the compressor;
the refrigerant circulates through the compressor, the condenser, the throttling device and the evaporator in sequence to form a main refrigerant loop;
the cooling device is arranged close to the frequency converter module;
the refrigerant circulates through the liquid outlet of the condenser, the cooling device and the air inlet of the condenser in sequence to form a refrigerant cooling loop;
the inlet of the cooling device is connected with the liquid outlet of the condenser, and the outlet of the cooling device is connected with the exhaust pipe of the compressor.
In some embodiments, the cooling muffler comprises: the refrigerant cooling circuit includes:
and the cooling return air pipe is used for connecting the outlet of the cooling device with the exhaust pipe of the compressor.
A pipe body connected to an outlet of the cooling device; and the pipeline main body is connected with the compressor exhaust pipe through the connecting section.
In some embodiments, the connection section is connected obliquely to the compressor discharge pipe, and the direction of inclination of the connection section is inclined from its connection to the compressor discharge pipe toward the upstream direction of the compressor discharge pipe; the upstream direction of the compressor discharge pipe is determined according to the flow direction of the refrigerant, the incoming direction of the refrigerant is upstream, and the outgoing direction of the refrigerant is downstream.
In some embodiments, the connection port of the connection section extends into the compressor discharge pipe, and the connection port is a split flat.
In some embodiments, the angle between the connecting section and the compressor discharge pipe is 45 ℃, and the depth of the connecting port of the connecting section penetrating into the compressor discharge pipe is 15mm.
In some embodiments, an access valve is provided in the cooling muffler.
In some embodiments, the inlet of the cooling device is lower than the outlet of the condenser.
In some embodiments, the cooling device has two inlets and two outlets, respectively.
In some embodiments, the refrigerant cooling circuit includes a first liquid-dividing pipe and a second liquid-dividing pipe, one end of each of which is communicated with the liquid outlet of the condenser; the other ends of the first liquid separating pipe and the second liquid separating pipe are respectively communicated with two inlets of the cooling device.
In some embodiments, the refrigerant cooling circuit includes two cooling return pipes, each in communication with two outlets of the cooling device.
Compared with the prior art, the utility model has the advantages and positive effects that:
the air conditioning system adopts the refrigerant to cool the variable frequency equipment, so that various problems of air cooling and water cooling can be avoided. This scheme is through setting up refrigerant cooling circuit, and this refrigerant cooling circuit connects between the liquid outlet of condenser and compressor blast pipe, when needs are the inverter device cooling down, the liquid outlet branch refrigerant entering cooling device of follow condenser. The liquid refrigerant of the cooling cycle comes from the condenser, and the heat absorbed by the supercooled refrigerant liquid after condensation in the cooling cycle without throttling is taken away by the condenser, so that the air suction amount of the compressor is not occupied, the refrigerating energy efficiency of the compressor is not influenced, condensation is not generated, the problem that the refrigerating energy provided by the compressor to the refrigerating system is reduced due to the cooling of the refrigerant is solved, and the energy efficiency of the refrigerating air-conditioning system is influenced as a result; meanwhile, the condensation risk in the cooling process is avoided by adopting a cooling mode that the refrigerant does not throttle phase change.
Other features and advantages of the present utility model will become apparent upon review of the detailed description of the utility model in conjunction with the drawings.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present utility model, the drawings that are needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present utility model, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a system schematic diagram of one embodiment of an air conditioning system in accordance with the present utility model;
FIG. 2 is a schematic view of a partial structure of the air conditioning system of FIG. 1;
fig. 3 is an enlarged view of a portion a in fig. 2;
FIG. 4 is a system schematic diagram of yet another embodiment of an air conditioning system in accordance with the present utility model;
FIG. 5 is a schematic view of a partial structure of the air conditioning system of FIG. 4;
FIG. 6 is a flow chart illustrating a configuration of a control module in an embodiment of an air conditioning system according to the present utility model;
FIG. 7 is a flow chart illustrating a configuration of a control module in yet another embodiment of an air conditioning system according to the present utility model;
FIG. 8 is a flow chart illustrating a configuration of a control module in yet another embodiment of an air conditioning system according to the present utility model;
FIG. 9 is a flow chart illustrating a configuration of a control module in yet another embodiment of an air conditioning system according to the present utility model;
fig. 10 is a flowchart illustrating a configuration of a control module in still another embodiment of an air conditioning system according to the present utility model.
Detailed Description
The following description of the embodiments of the present utility model will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.
In the description of the present utility model, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate describing the present utility model and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model.
The terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present utility model, unless otherwise indicated, the meaning of "a plurality" is two or more.
In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model will be understood in specific cases by those of ordinary skill in the art.
< basic operation principle of air conditioner >
The air conditioning system of the present utility model performs refrigerant circulation of the system by using a compressor, a condenser, a throttle device and an evaporator. The refrigerant cycle includes a series of processes involving compression, condensation, expansion and evaporation, and supplies a refrigerant to the air that has been conditioned and heat exchanged.
The compressor compresses refrigerant gas in a low-temperature and low-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.
The expansion device expands the liquid-phase refrigerant in a high-temperature and high-pressure state condensed in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the throttle device and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator may achieve a cooling effect by exchanging heat with a material to be cooled using latent heat of evaporation of a refrigerant. The air conditioner may adjust the temperature of the indoor space throughout the cycle.
The outdoor unit of the air conditioner refers to a portion of a refrigeration cycle including a compressor and an outdoor heat exchanger, the indoor unit of the air conditioner includes an indoor heat exchanger, and a throttle device may be provided in the indoor unit or the outdoor unit.
For the variable-frequency central air conditioning unit or the refrigerating system, in order to achieve the purposes of energy saving and low investment in operation, an externally-hung frequency converter is mostly adopted to realize the configuration scheme of variable-frequency energy adjustment. The frequency converter in a large-scale air conditioner or refrigeration system has larger power consumption, larger heat dissipation capacity of the frequency converter and additional cooling thereof is also indispensable. Because the power consumption of the inverter cooling itself does not provide more refrigeration capacity for the air conditioning and refrigeration system, the power consumption herein is due to idle work for the entire system, and it is desirable that the operating requirements of the inverter components be met without consuming power. The current common air-cooled, water-cooled and refrigerant throttling cooling type systems have the defects of high power consumption, heat exchanger scaling and internal condensation risks, or reduce the overall energy efficiency of the system, or have scaling or unstable risks.
In view of the present problem, this embodiment proposes an air conditioning system, as shown in fig. 1, including a compressor 11, a condenser 12, an evaporator 13, a throttling device 14, a frequency converter module (not shown in the figure), a cooling device 15, and a control module, wherein the compressor 11 is used for compressing a refrigerant, and the frequency converter module is used for adjusting an operating frequency of the compressor 11. The refrigerant circulates through the compressor 11, the condenser 12, the throttle device 14, and the evaporator 13 in this order to form a main refrigerant circuit.
The inlet of the cooling device 15 is connected with the liquid outlet 120 of the condenser, the outlet of the cooling device 15 is connected with the compressor discharge pipe 16, and the cooling device 15 is arranged close to the frequency converter module.
The refrigerant circulates in sequence through the outlet 120 of the condenser, the cooling device 15 and the inlet 121 of the condenser to form a refrigerant cooling circuit.
The air conditioning system further comprises a solenoid valve 17, which is arranged between the liquid outlet 120 of the condenser and the cooling device 15, and is used for controlling the on-off state of a refrigerant cooling circuit in which the solenoid valve 17 is positioned.
The control module is configured to control the on-off state of the solenoid valve 17, the refrigerant cooling circuit being on when the solenoid valve 17 is open, and the refrigerant cooling circuit being off when the solenoid valve 17 is closed.
In this embodiment, by providing a refrigerant cooling circuit, the refrigerant cooling circuit is connected between the liquid outlet 120 of the condenser and the compressor discharge pipe 16, and when the frequency conversion device needs to be cooled, the control module controls the electromagnetic valve 17 to open, so that the refrigerant is separated from the liquid outlet 120 of the condenser and enters the cooling device 15. The liquid refrigerant of the cooling cycle comes from the condenser 12, so that the heat absorbed in the cooling cycle is taken away by the condenser 12, and the air suction amount of the compressor 11 is not occupied, so that the refrigerating energy efficiency of the compressor 11 is not influenced, and the problem that the refrigerating energy provided by the compressor to the refrigerating system is reduced due to the cooling of the refrigerant, and the energy efficiency of the refrigerating and air conditioning system is influenced as a result is solved.
The low-temperature refrigerant entering the cooling device 15 is cooled by the variable-frequency equipment, the liquid refrigerant is evaporated into a gaseous state and then returns to the compressor exhaust pipe 16, the evaporated gas is carried into the condenser 12 by the high-speed air flow of the compressor exhaust, and the smaller part of the condensed refrigerant liquid enters the cooling device 15 again, so that stable circulation is formed.
The refrigerant is cooled by the cooling device 15 in an unthrottled phase change mode, so that condensation possibly generated by cooling by adopting a throttling mode can be avoided, and a series of risks caused by the condensation can be further avoided.
In the scheme, a mode of cooling by a refrigerant is adopted for cooling the variable frequency equipment, so that various problems existing in air cooling and water cooling can be correspondingly avoided.
In addition, the supercooled liquid from the condenser is about 35 ℃ under the standard working condition, the temperature is over 25 ℃ due to slightly lower condensing temperature during winter operation, and the cooling principle is that the liquid refrigerant is utilized to evaporate into heat absorbed in the process of saturated or slightly overheated refrigerant steam when meeting heat, so that the cooling of the frequency conversion equipment is realized.
The temperature of the supercooled refrigerant liquid taken from the condenser is above the ambient temperature and below the cooling temperature required by the condenser assembly, so that the cooling requirement of the frequency converter equipment is met, and the condensation risk which can occur in a similar water cooling and refrigerant throttling cooling mode is avoided; the refrigerant undergoes a phase change in the cooling device 15, which also eliminates the risk of scaling inside the heat exchanger.
In some embodiments, the refrigerant cooling circuit includes a cooling return line for connecting the outlet of the cooling device 15 with the compressor discharge line 16. The refrigerant vapor from the cooling device 15 returns to the condenser 12 through the compressor discharge pipe 16 along with the gaseous refrigerant discharged from the compressor 11, and continues to circulate in order of heat release and temperature reduction.
In some embodiments, the cooling muffler includes a pipe body 181 and a connecting section 182, the pipe body 181 and the connecting section 182 being in communication. And the pipe body 181 is connected to the outlet of the cooling device 15, and the refrigerant exiting from the cooling device 15 first enters the pipe body 181.
The pipe body 181 is connected to the compressor discharge pipe 16 through a connection section 182.
In some embodiments, the conduit body 181 and the connecting segment 182 are of an integrally formed structure.
In some embodiments, the connection segment 182 is connected obliquely to the compressor discharge line 16, i.e., the connection segment 182 forms an angle with the compressor discharge line 16, and the direction of inclination of the connection segment 182 is inclined from its connection with the compressor discharge line 16 toward the upstream direction of the compressor discharge line 16, the refrigerant flowing in the compressor discharge line 16 forms a siphon effect to the connection segment 182, drawing the refrigerant in the cooling muffler into the compressor discharge line 16, and continuing to condense as the compressor 11 discharge line returns to the condenser 12.
The upstream direction of the compressor discharge pipe 16 is determined according to the flow direction of the refrigerant, the compressor 11 compresses the refrigerant into the compressor discharge pipe 16, the incoming direction of the refrigerant is upstream, and the outgoing direction of the refrigerant is downstream.
In order to facilitate the introduction of the refrigerant in the cooling muffler into the compressor discharge pipe 16, the cooling muffler has design angle requirements when it is tapped into the compressor discharge pipe 16. In some embodiments, as shown, the connection port 180 of the connection segment 182 extends into the compressor discharge tube 16, and the connection port 180 is a split flat. So that the exhaust and drainage are smooth, the siphon effect is formed, and the smooth refrigeration cycle is achieved.
In some embodiments, the angle between the connection segment 182 and the compressor discharge pipe 16 is 45 ℃, and the depth to which the connection port 180 of the connection segment 182 protrudes into the compressor discharge pipe 16 is 15mm.
In some embodiments, the inlet of the cooling device is lower than the outlet of the condenser to ensure that the subcooled refrigerant liquid in the condenser 12 enters the cooling device 15 smoothly.
In some embodiments, the inlet of the cooling device is about 500mm below the outlet of the condenser.
In some embodiments, since the liquid refrigerant in the cooling cycle comes from the condenser 12, the heat absorbed in the cooling cycle is taken away by the condenser 12 without occupying the suction amount of the compressor 11, so the refrigeration energy efficiency of the compressor 11 is not affected, only the heat load required by cooling the inverter device is added when the condenser 12 is designed, and the inverter cooling scheme is reliable and energy-saving compared with the conventional inverter cooling scheme.
In some embodiments, to further increase the stability of the operation of the present cooling device, ensure the cooling effect and accurate control, and reasonably control the on-off state of the refrigerant cooling circuit, the air conditioning system further includes a temperature detecting element (not shown in the figure) for detecting the temperature of the cooling device 15. The detected value of the temperature detecting element may be used as a basis for controlling the on-off state of the refrigerant cooling circuit.
In some embodiments, as shown in fig. 1, an inspection valve 21 is further provided in the cooling muffler, and when the cooling muffler needs to be inspected, the inspection valve 21 can be manually closed for inspection.
In some embodiments, the service valve 21 is disposed in the pipe body 181, which is convenient to connect.
In some embodiments, service valve 21 may be implemented using a manual ball valve.
In some embodiments, as shown in fig. 6, the control module further comprises a logic configured to:
the detection value of the temperature detecting element is obtained, the solenoid valve 17 is opened when the detection value rises to the upper temperature limit value, and the solenoid valve 17 is closed when the detection value falls to the lower temperature limit value, the upper temperature limit value being larger than the lower temperature limit value.
In some embodiments, the refrigerant cooling circuit further comprises a tap 19 and an electrically operated valve 20, the tap 19 being connected between the outlet 120 of the condenser and the inlet of the cooling device 15.
An electric valve 20 is connected to the liquid separation pipe 19.
As shown in fig. 7, the control module further includes a controller configured to:
during the opening of the electromagnetic valve 17, the opening of the electric valve 20 is adjusted according to the temperature of the cooling device 15, and the opening of the electric valve 20 is positively correlated with the temperature of the cooling device 15. That is, the higher the temperature of the cooling device 15, the larger the opening degree of the electric valve 20 is, so that more refrigerant enters the cooling device 15, so that the cooling device 15 is conveniently cooled as soon as possible, and the failure caused by high temperature is prevented.
In some embodiments, as shown in fig. 8, the control module further comprises a logic configured to:
the electrically operated valve 20 is linked to the solenoid valve 17, and when the solenoid valve is closed, the electrically operated valve is closed at the same time.
By linking the electrically operated valve 20 with the solenoid valve 17, the safety of the system can be improved.
In some embodiments, the pressure loss on the refrigerant side of the cooling device on the frequency conversion device needs to be controlled reasonably, and the theoretical pressure loss under the working condition must not be higher than 50KP, so as to avoid the risk of affecting the reasonable circulation of the refrigerant, thereby bringing about the problems of poor cooling and the like.
The operating heat dissipation capacity of the frequency converter is related to the actual execution frequency: the higher the execution frequency of the frequency converter with the same rated power is, the larger the heat dissipation capacity is. Because the same compressor has higher running frequency, namely the exhaust gas quantity is larger, the size of the exhaust gas quantity determines the flow rate of the refrigerant gas in the exhaust pipe, when the flow rate is high, the circulation quantity of the refrigerant in the frequency converter assembly is large, and when the flow rate is low, the circulation quantity of the refrigerant in the frequency converter assembly is small, and the stability of the cooling temperature can be ensured due to the isotropy of the two factors.
In some embodiments, as shown in fig. 9 and 10, the method for configuring the pipe diameter of the refrigerant cooling circuit includes:
the method comprises the steps of obtaining heat dissipation power Ps of a frequency converter module when the frequency converter module runs under full load of a unit;
calculating the volume flow qm of the liquid refrigerant under the heat radiation power Ps;
the pipe diameter of the refrigerant cooling loop is determined according to the volume flow qm of the refrigerant.
Specifically, the frequency converter is installed in a relatively airtight box, the temperature rise value is related to the total power loss of equipment in the cabinet and the heat dissipation area of the cabinet body, when the frequency converter works at full load, the total loss (converted into heat) is about 3% -5% of the rated power of the system, and for balance calculation, the intermediate value is taken, and the total loss can be estimated as follows:
1、Ps＝Pc*4％。
in the above formula:
ps—inverter heat dissipation power (kW);
pc—converter rated power (kW).
2. Calculating the volume flow of the liquid refrigerant under the cooling of the heat radiation:
qm＝Ps/(h1-h2)
in the above formula:
qm—refrigerant mass flow (kg/s);
h 1-enthalpy (kJ/kg) of saturated gas at the refrigerant outlet;
h 2-enthalpy of saturated gas at the refrigerant inlet (kJ/kg);
qv＝qm*v′。
in the above formula:
qv-refrigerant volume flow (m 3 /s)；
v' —specific volume of liquid of supercooled refrigerant at refrigerant inlet (m 3 /kg)。
3. The pipe diameter D of the refrigerant cooling loop is determined according to the volume flow of the refrigerant, and the flow rate in the pipe is 1m/s.
D＝(4qv/π)1/2。
The pipe diameter D of the refrigerant cooling circuit can be used as the pipe diameter of the liquid separating pipe and/or the refrigerant cooling circuit.
Example two
The inverter device comprises an inverter module and a cooling inverter cabinet, whereby in some embodiments the refrigerant cooling circuit has two cooling circuits for cooling the inverter module and the cooling inverter cabinet, respectively.
In some embodiments, as shown in fig. 4, the refrigerant cooling circuit of the inverter device includes two liquid separation pipes, namely a first liquid separation pipe 191 and a second liquid separation pipe 192, two paths of refrigerant can be separated from the liquid outlet 120 of the condenser, one path of refrigerant enters the first liquid separation pipe 191 and enters the cooling device 15 to cool the inverter cabinet, and the other path of refrigerant enters the second liquid separation pipe 192 and enters the cooling device 15 to cool the inverter module.
The refrigerant cooling loop of the frequency converter device correspondingly comprises two cooling air return pipes which are respectively used for returning the refrigerant for cooling the frequency converter cabinet body and returning the refrigerant for cooling the frequency converter module.
In some embodiments, the cooling device 15 has two inlets and two outlets corresponding to the two refrigerant cooling circuits, respectively. The two inlets are respectively connected with a first liquid separating pipe 191 and a second liquid separating pipe 192, and the two outlets are respectively connected with two cooling air return pipes.
Accordingly, there should be two temperature detecting elements, a first temperature detecting element and a second temperature detecting element, for detecting the temperature of the cooling inverter cabinet and the inverter module, respectively.
The first liquid separating pipe 191 is provided with a first electromagnetic valve 171, the second liquid separating pipe 192 is provided with a second electromagnetic valve 172, and the two electromagnetic valves are respectively used for controlling the on-off state of the corresponding liquid separating pipes.
The on-off states of the first liquid dividing pipe 191 and the second liquid dividing pipe 192 are respectively and independently controlled, and the temperature values detected by the two temperature detecting elements are respectively used for controlling the on-off states of the refrigerant circuits where the two temperature detecting elements are respectively located.
In some embodiments, the electric valve 20 should have two electric valves, namely a first electric valve 201 and a second electric valve 202, respectively disposed in the first liquid-dividing pipe 191 and the second liquid-dividing pipe 192, and the two electric valves are controlled in linkage with the electromagnetic valves in the same pipeline.
The refrigerants circulating in the two refrigerant cooling loops are used for cooling the frequency converter cabinet body and the frequency converter module respectively.
As shown in fig. 5, the two refrigerant cooling circuits are connected to the compressor discharge pipe 16 through respective connection sections, and the connection sections of the two refrigerant cooling circuits are kept in the same inclination direction.
In this embodiment, two refrigerant cooling circuits are provided to ensure that each refrigerant cooling circuit is independent and smooth.
In some embodiments, the defined control parameter setting variables are as follows:
tg—real-time temperature in the inverter cabinet;
tb—real-time temperature of the frequency converter module;
ton1, the upper limit value of the temperature of the cabinet body of the frequency converter;
ton 2-upper limit of the converter module temperature;
toff 1-lower limit of the temperature of the frequency converter cabinet;
toff 2-lower limit of the converter module temperature;
k1-opening degree of an electric ball valve in a cooling loop corresponding to the frequency converter cabinet body;
and K2, opening degree of the electric ball valve in the cooling circuit corresponding to the frequency converter module.
Wherein to tg and tb real time monitoring, when detecting that converter cabinet internal temperature tg is greater than or equal to ton1, its solenoid valve that corresponds opens, and the aperture of motorised valve carries out real time control according to the temperature in the cabinet: the opening of the electric valve is increased when the temperature in the cabinet is increased, and is decreased when the temperature in the cabinet is decreased. When ton1 is more than tg and more than toff1, the electromagnetic valve is kept in an open or closed state, and the control logic of the electric valve is consistent with that of tg which is more than or equal to ton1 in the open state; when the temperature tg in the frequency converter cabinet body is less than or equal to toff1, the electromagnetic valve is closed. When the electromagnetic valve is closed, the electric valve is closed in a linkage way.
The motor-driven valve is provided with a driving module, and the motor-driven valve is driven to act after the monitoring variable is transmitted to the driving module in actual execution.
The control logic of the frequency converter module is the same as that of the frequency converter cabinet. Wherein ton1, ton2, toff1 and toff2 can be set according to different requirements. In the scheme, the Kv value of the electromagnetic valve should meet the cold quantity required by calculation during type selection.
In general, the control temperature requirements of the frequency converter module and the frequency converter cabinet are slightly different, and the flow of the refrigerant can be adjusted by adjusting the pipe diameter of each module so as to realize the deviation of the temperature after cooling through different superheat degrees.
In some embodiments, one cooling device 15 may be respectively provided for two refrigerant cooling circuits, or one cooling device 15 may be provided, and two heat exchange cavities for cooling the frequency converter module and the frequency converter cabinet are respectively provided inside the two cooling devices.
In designing the cooling device 15 corresponding to the two refrigerant cooling circuits, the working conditions of the refrigeration cycle should be considered:
1) The saturation temperature of the refrigerant liquid at the inlet of the cooling device is 36 ℃;
2) The cooling device outlet refrigerant gas temperature was 36 ℃.
During actual calculation, the maximum heat dissipation power (Pg) of the frequency converter cabinet body is 0.1 of the heat dissipation power (Ps) of the frequency converter module, and during actual use, the opening degree of the electric valve is controlled according to the actual temperature association in the frequency converter cabinet body to adjust the liquid supply amount.
The condition of the condition cooling device is calculated by selecting, the refrigerant at the inlet of the cooling device has supercooling of 2-3 ℃ in actual operation, and the outlet of the cooling device also has overheating of 2-3 ℃, which can be used as a design margin to further ensure the cooling effect of the system.
The above embodiments are only for illustrating the technical solution of the present utility model, and are not limiting; although the utility model has been described in detail with reference to the foregoing embodiments, it will be apparent to one skilled in the art that modifications may be made to the technical solutions described in the foregoing embodiments, or equivalents may be substituted for some of the technical features thereof; such modifications and substitutions do not depart from the spirit and scope of the corresponding technical solutions.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present utility model, and not for limiting the same; although the utility model has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the utility model.
The foregoing description, for purposes of explanation, has been presented in conjunction with specific embodiments. However, the illustrative discussions above are not intended to be exhaustive or to limit the embodiments to the precise forms disclosed above. Many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles and the practical application, to thereby enable others skilled in the art to best utilize the embodiments and various embodiments with various modifications as are suited to the particular use contemplated.
Claims (10)
1. An air conditioning system, comprising:
a compressor for compressing a refrigerant;
a condenser;
an evaporator;
a throttle device;
a frequency converter module for adjusting an operating frequency of the compressor;
the refrigerant circulates through the compressor, the condenser, the throttling device and the evaporator in sequence to form a main refrigerant loop;
the cooling device is arranged close to the frequency converter module;
the refrigerant circulates through the liquid outlet of the condenser, the cooling device and the air inlet of the condenser in sequence to form a refrigerant cooling loop;
and the inlet of the cooling device is connected with the liquid outlet of the condenser, and the outlet of the cooling device is connected with the exhaust pipe of the compressor.
2. The air conditioning system of claim 1, wherein the refrigerant cooling circuit comprises:
a cooling muffler for connecting an outlet of the cooling device with the compressor discharge pipe;
the cooling muffler includes:
a pipe body connected to an outlet of the cooling device;
and the pipeline main body is connected with the compressor exhaust pipe through the connecting section.
3. The air conditioning system according to claim 2, wherein the connection section is connected to the compressor discharge pipe in an inclined manner, and an inclined direction of the connection section is inclined from a connection portion thereof to the compressor discharge pipe toward an upstream direction of the compressor discharge pipe;
the upstream direction of the compressor discharge pipe is determined according to the flow direction of the refrigerant, the incoming direction of the refrigerant is upstream, and the outgoing direction of the refrigerant is downstream.
4. An air conditioning system according to claim 3 wherein the connection port of the connection section extends into the compressor discharge duct and the connection port is a split flat.
5. The air conditioning system according to claim 4, wherein an included angle between the connection section and the compressor discharge pipe is 45 ℃, and a depth of the connection port of the connection section penetrating into the compressor discharge pipe is 15mm.
6. An air conditioning system according to claim 2, wherein a service valve is provided in the cooling muffler.
7. The air conditioning system of claim 1, wherein the inlet of the cooling device is lower than the outlet of the condenser.
8. An air conditioning system according to claim 2, wherein the cooling device has two inlets and two outlets, respectively.
9. The air conditioning system of claim 8, wherein the refrigerant cooling circuit includes a first liquid-dividing pipe and a second liquid-dividing pipe, one end of each of which is in communication with a liquid outlet of the condenser; the other ends of the first liquid separating pipe and the second liquid separating pipe are respectively communicated with two inlets of the cooling device.
10. An air conditioning system according to claim 9, wherein the refrigerant cooling circuit includes two of the cooling return air pipes, the two cooling return air pipes being in communication with the two outlets of the cooling device, respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320357151.7U CN219550943U (en) | 2023-03-01 | 2023-03-01 | Air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320357151.7U CN219550943U (en) | 2023-03-01 | 2023-03-01 | Air conditioning system |
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| Publication Number | Publication Date |
|---|---|
| CN219550943U true CN219550943U (en) | 2023-08-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202320357151.7U Active CN219550943U (en) | 2023-03-01 | 2023-03-01 | Air conditioning system |
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| Country | Link |
|---|---|
| CN (1) | CN219550943U (en) |
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2023
- 2023-03-01 CN CN202320357151.7U patent/CN219550943U/en active Active
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