CN212431381U - Double-cold-source refrigerant liquid separating device - Google Patents
Double-cold-source refrigerant liquid separating device Download PDFInfo
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- CN212431381U CN212431381U CN202021851413.8U CN202021851413U CN212431381U CN 212431381 U CN212431381 U CN 212431381U CN 202021851413 U CN202021851413 U CN 202021851413U CN 212431381 U CN212431381 U CN 212431381U
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Abstract
The embodiment of the application provides a two cold sources refrigerant divide liquid device relates to air conditioning equipment technical field. The double-cold-source refrigerant liquid separating device comprises a compressor, a regulating valve, an air-cooled heat exchanger, an evaporative cooling heat exchanger and a heat exchanger; the compressor is used for compressing refrigerant gas; the regulating valve comprises a first interface, a second interface and a third interface, the first interface of the regulating valve is connected with the compressor, and the regulating valve is used for regulating the drift diameter of the refrigerant according to the ambient temperature and the running power consumption; the air-cooled heat exchanger is connected with a second interface of the regulating valve; the evaporative cooling heat exchanger is connected with a third interface of the regulating valve; the heat exchanger is respectively connected with the compressor, the air-cooled heat exchanger and the evaporation-cooled heat exchanger to form a circulation loop of the refrigerant. The double-cold-source refrigerant liquid separating device can reduce the overall power consumption of the unit, improve the performance coefficient and reliability, and realize the technical effects of energy conservation and efficiency improvement.
Description
Technical Field
The application relates to the technical field of air conditioning equipment, in particular to a double-cold-source refrigerant liquid separating device.
Background
At present, the cooling efficiency of evaporation cooling is much higher than that of air cooling, and the COP (coefficient of performance) value (unit W/W) of an evaporation cooling water chilling unit is higher than that of an air cooling water chilling unit. However, in the aspect of heating, the evaporation cold-hot pump hot water unit is limited by the freezing factor of low-temperature water, and the service environment is limited; and the air-cooled heat pump hot water unit can run at the temperature below zero in winter, so that the requirement of heating in winter is met.
In the prior art, double cold source heat pump units are available on the market. The double cold source consists of an air-cooled fin heat exchanger and an evaporative cooling heat exchanger. If two groups of heat exchangers are connected in series, the heat exchange capacity of one heat exchanger cannot be exerted. The parallel connection can meet the liquid separation problem, and the liquid separation can not lead to the fact that two heat exchanges can not reach the best performance according to the specific conditions, so that the energy consumption of the unit is high, and the energy-saving effect can not be achieved.
SUMMERY OF THE UTILITY MODEL
An object of the embodiment of the application is to provide a two cold source refrigerant divide liquid device, can reduce the whole consumption of unit, improve coefficient of performance and reliability, realize energy-conserving synergistic technological effect.
The embodiment of the application provides a double-cold-source refrigerant liquid separating device, which comprises a compressor, a regulating valve, an air-cooled heat exchanger, an evaporative-cooled heat exchanger and a heat exchanger;
the compressor is used for compressing refrigerant gas;
the regulating valve comprises a first interface, a second interface and a third interface, the first interface of the regulating valve is connected with the compressor, and the regulating valve is used for regulating the drift diameter of the refrigerant according to the ambient temperature and the running power consumption;
the air-cooled heat exchanger is connected with a second interface of the regulating valve;
the evaporative cooling heat exchanger is connected with a third interface of the regulating valve;
the heat exchanger is respectively connected with the compressor, the air-cooled heat exchanger and the evaporation-cooled heat exchanger to form a circulation loop of the refrigerant.
In the implementation process, the double-cold-source refrigerant liquid separating device can be converted into a refrigeration mode or a heating mode by converting the flow direction of the refrigerant among the compressor, the air-cooled heat exchanger, the evaporative cooling heat exchanger and the heat exchanger, and the heat exchanger provides cold or heat; the regulating valves are arranged among the compressor, the air-cooled heat exchanger and the evaporation-cooling heat exchanger, the drift diameter of the refrigerant is regulated according to the ambient temperature and the running power consumption, so that the flow of the refrigerant entering the air-cooled heat exchanger and the evaporation-cooling heat exchanger is regulated through the regulating valves, the air-cooled heat exchanger and the evaporation-cooling heat exchanger are always in the best heat exchange performance, the overall power consumption of a unit can be reduced, the performance coefficient and the reliability are improved, and the technical effects of energy conservation and efficiency improvement are realized.
Furthermore, the device also comprises a reversing valve, wherein the reversing valve is provided with four interfaces which are respectively connected with the inlet of the compressor, the outlet of the compressor, the first interface of the regulating valve and the heat exchanger, and the reversing valve is used for regulating the flow direction of the refrigerant.
In the implementation process, the reversing valve is provided with four interfaces, the four interfaces can mutually switch the channels, the reversing of the flow direction of the refrigerant is realized, and therefore the double-cold-source refrigerant liquid separating device is switched between the refrigerating mode and the heating mode. Illustratively, in the refrigeration mode of the double-cold-source refrigerant liquid separation device, the refrigerant flow direction cycle is as follows: compressor → governing valve → air-cooled heat exchanger and evaporative-cooled heat exchanger → compressor; under the heating mode of the double-cold-source refrigerant liquid separating device, the refrigerant flow direction circulation is as follows: compressor → heat exchanger → air-cooled heat exchanger and evaporative cooling heat exchanger → regulating valve → compressor.
Further, the device also comprises a gas-liquid separator, and the gas-liquid separator is respectively connected with the reversing valve and the inlet of the compressor.
In the implementation process, the gas-liquid separator can be arranged at the inlet of the gas compressor and used for gas-liquid separation, processing the refrigerant containing a small amount of condensate and realizing the recovery of the refrigerant.
Furthermore, the device also comprises a liquid storage device, wherein the air-cooled heat exchanger and the evaporative cooling heat exchanger are provided with confluence ports, and the liquid storage device is respectively connected with the confluence ports and the heat exchangers.
In the implementation process, the liquid accumulator can temporarily store the refrigerant and plays a role in transferring the refrigerant.
Further, the device also comprises a throttling mechanism, and the throttling mechanism is respectively connected with the liquid storage device, the confluence port and the heat exchanger.
In the implementation process, the refrigerant flows from the liquid accumulator to the throttling mechanism, and the refrigerant passes through the throttling mechanism to be throttled and decompressed to become the gas-liquid two-phase refrigerant.
Further, the device comprises at least one-way valve, and the one-way valve is arranged on a connecting pipeline of the liquid reservoir.
In the implementation process, the one-way valve is arranged on the connecting pipeline of the liquid accumulator, and the one-way valve has the characteristic of one-way liquid passing, so that the flow direction of the refrigerant of the double-cold-source refrigerant liquid separating device is always kept to be the liquid accumulator → the throttling mechanism no matter in the heating mode or the cooling mode.
Furthermore, the device comprises a first one-way valve and a second one-way valve, wherein the first one-way valve is arranged on a connecting pipeline of the confluence port and the liquid accumulator, and the second one-way valve is arranged on a connecting pipeline of the throttling mechanism and the heat exchanger, so that the refrigerant sequentially flows through the confluence port, the liquid accumulator, the throttling mechanism and the heat exchanger.
In the implementation process, the first check valve and the second check valve can enable the double-cold-source refrigerant liquid separating device to have the following flow directions in the refrigeration mode: converging port → reservoir → throttling mechanism → heat exchanger.
Furthermore, the device comprises a third one-way valve and a fourth one-way valve, wherein the third one-way valve is arranged on a connecting pipeline of the heat exchanger and the liquid accumulator, and the fourth one-way valve is arranged on a connecting pipeline of the throttling mechanism and the converging port, so that the refrigerant sequentially flows through the heat exchanger, the liquid accumulator, the throttling mechanism and the converging port.
In the implementation process, the third check valve and the fourth check valve can enable the double-cold-source refrigerant liquid separating device to have the following flow directions in the heating mode: heat exchanger → reservoir → throttling mechanism → junction.
Furthermore, the air-cooled heat exchanger comprises a fan and a fin heat exchange mechanism, the fin heat exchange mechanism is respectively connected with the second interface of the regulating valve and the heat exchanger, and the fan is arranged above the fin heat exchange mechanism.
Further, the evaporation cold heat exchanger includes spraying mechanism, board pipe heat transfer mechanism, water pump, water tank and exhaust fan, stacks gradually from last to bottom spraying mechanism board pipe heat transfer mechanism with the water tank, the water pump is connected respectively spray mechanism and water tank, the exhaust fan set up in the top that sprays the mechanism.
Additional features and advantages of the disclosure will be set forth in the description which follows, or in part may be learned by the practice of the above-described techniques of the disclosure, or may be learned by practice of the disclosure.
In order to make the aforementioned objects, features and advantages of the present application more comprehensible, preferred embodiments accompanied with figures are described in detail below.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments of the present application will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and that those skilled in the art can also obtain other related drawings based on the drawings without inventive efforts.
Fig. 1 is a schematic structural diagram of a dual cold source refrigerant liquid separating device according to an embodiment of the present disclosure;
fig. 2 is a schematic structural diagram of another dual-cold-source refrigerant liquid separation device provided in an embodiment of the present application;
fig. 3 is a schematic structural diagram of an air-cooled heat exchanger according to an embodiment of the present disclosure;
fig. 4 is a schematic structural diagram of an evaporative cooling heat exchanger according to an embodiment of the present application.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. The components of the embodiments of the present application, generally described and illustrated in the figures herein, can be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of the embodiments of the present application, presented in the accompanying drawings, is not intended to limit the scope of the claimed application, but is merely representative of selected embodiments of the application. All other embodiments, which can be derived by a person skilled in the art from the embodiments of the present application without making any creative effort, shall fall within the protection scope of the present application.
In this application, the terms "upper", "lower", "left", "right", "front", "rear", "top", "bottom", "inner", "outer", "middle", "vertical", "horizontal", "lateral", "longitudinal", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the present application and its embodiments, and are not used to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation.
Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meaning of these terms in this application will be understood by those of ordinary skill in the art as appropriate.
Furthermore, the terms "mounted," "disposed," "provided," "connected," and "connected" are to be construed broadly. For example, it may be a fixed connection, a removable connection, or a unitary construction; can be a mechanical connection, or a point connection; either directly or indirectly through intervening media, or may be an internal communication between two devices, elements or components. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.
Furthermore, the terms "first," "second," and the like, are used primarily to distinguish one device, element, or component from another (the specific nature and configuration may be the same or different), and are not used to indicate or imply the relative importance or number of the indicated devices, elements, or components. "plurality" means two or more unless otherwise specified.
The embodiment of the application provides a double-cold-source refrigerant liquid separating device which can be applied to the field of air conditioners for refrigerating or heating; the double-cold-source refrigerant liquid separating device can be converted into a refrigeration mode or a heating mode by converting the flow direction of the refrigerant among the compressor, the air-cooled heat exchanger, the evaporative cooling heat exchanger and the heat exchanger, and the heat exchanger provides cold or heat; the regulating valves are arranged among the compressor, the air-cooled heat exchanger and the evaporation-cooling heat exchanger, the drift diameter of the refrigerant is regulated according to the ambient temperature and the running power consumption, so that the flow of the refrigerant entering the air-cooled heat exchanger and the evaporation-cooling heat exchanger is regulated through the regulating valves, the air-cooled heat exchanger and the evaporation-cooling heat exchanger are always in the best heat exchange performance, the overall power consumption of a unit can be reduced, the performance coefficient and the reliability are improved, and the technical effects of energy conservation and efficiency improvement are realized.
Referring to fig. 1, fig. 1 is a schematic structural diagram of a double-cold-source refrigerant liquid separating device provided in an embodiment of the present application, where the double-cold-source refrigerant liquid separating device includes a compressor 10, an adjusting valve 20, an air-cooled heat exchanger 30, an evaporative-cooled heat exchanger 40, and a heat exchanger 50;
illustratively, the compressor 10 is used to compress a refrigerant gas.
Illustratively, the compressor 10(compressor), which is a driven fluid machine that raises low-pressure gas to high-pressure gas, is the heart of a refrigeration system. The refrigerating cycle is powered by sucking low-temperature and low-pressure refrigerant gas from the air suction pipe, driving the piston to compress the refrigerant gas through the operation of the motor, and discharging high-temperature and high-pressure refrigerant gas to the exhaust pipe. Thereby realizing a refrigeration cycle of compression → condensation (heat release) → expansion → evaporation (heat absorption).
The control valve 20 comprises a first connection 21, a second connection 22 and a third connection 23, the first connection 21 of the control valve being connected to the compressor 10, the control valve 20 being used to control the refrigerant path as a function of the ambient temperature and the operating power consumption.
In some embodiments, the ambient temperature comprises an ambient dry bulb temperature and an ambient wet bulb temperature; the operation power consumption and the whole operation power consumption of the double-cold-source refrigerant liquid separating device are achieved.
Illustratively, the ambient bulb temperature (dry bulb temperature) is a value read from a dry bulb temperature chart that is exposed to air without direct exposure to the sun.
Illustratively, ambient wet bulb temperature (wet bulb temperature) refers to the condition of adiabatic conditions where a large amount of water is in contact with the limited humid air, and the latent heat required for water evaporation comes entirely from the sensible heat given off by the decrease in the temperature of the humid air, and the temperature of the system when the air in the system is saturated and the system is in thermal equilibrium.
In some embodiments, the dual cold source refrigerant liquid separation device further comprises an ambient dry bulb temperature sensor and an ambient wet bulb temperature sensor for detecting the ambient dry bulb temperature and the ambient wet bulb temperature, respectively.
In some embodiments, the regulator valve 20 is an electric three-way regulator valve.
Illustratively, the air-cooled heat exchanger 30 is connected to the second port 22 of the damper 20.
Illustratively, the air-cooled heat exchanger 30 serves the purpose of exchanging heat with the refrigerant by accelerating the flow of air.
The evaporator-cold heat exchanger 40 is connected, for example, to the third connection 23 of the control valve 20.
The evaporative cooling heat exchanger 40 is illustratively a shower type heat exchanger in which heat exchange tubes are fixed in rows on a steel frame, hot fluid flows through the tubes, and cooling water is sprayed from above. The exterior of the spray heat exchanger is a layer of liquid film with higher turbulence degree. In addition, the heat exchanger can be placed at the position where air circulates, and the evaporation of cooling water also takes away a part of heat, so that the functions of reducing the temperature of the cooling water and increasing the heat transfer thrust can be achieved.
Illustratively, the heat exchanger 50 is connected to the compressor 10, the air-cooled heat exchanger 30 and the evaporative cooling heat exchanger 40, respectively, to constitute a refrigerant circulation circuit.
Illustratively, the heat exchanger 50 may be a shell and tube heat exchanger or a fin heat exchanger. It should be understood that the heat exchanger 50 is merely exemplary and not limiting, and that the heat exchanger 50 may take other forms as desired.
In some implementations, the regulating valve 20 is an electric three-way regulating valve having three ports, namely, a first port 21, a second port 22, and a third port 23; in the cooling mode, after the refrigerant gas is compressed by the compressor 10, the refrigerant enters the first port 21, and then the regulating valve 20 controls and regulates the drift diameters between the first port 21 and the second port 22, and between the first port 21 and the third port 23 according to the ambient dry bulb temperature, the ambient wet bulb temperature, and the operating power consumption, so as to change the flow rates of the refrigerant flowing to the air-cooled heat exchanger 30 and the evaporative cold heat exchanger 40.
In some implementations scenarios, the ambient dry-bulb temperature is denoted TD and the ambient wet-bulb temperature is denoted TW; the flow rates of the refrigerants entering the air-cooled heat exchanger 30 and the evaporative cooling heat exchanger 40 are adjusted through the calculation adjusting valve 20 according to different changes of the environment dry bulb temperature TD and the environment wet bulb temperature TW, so that the air-cooled heat exchanger 30 and the evaporative cooling heat exchanger 40 are always in the best heat exchange performance, the overall power consumption of the unit is reduced, the performance coefficient and the reliability are improved, and the technical effects of energy conservation and efficiency improvement are achieved.
In some embodiments, the double cold source refrigerant separating device further comprises a reversing valve 60, wherein the reversing valve is provided with four interfaces, namely a first reversing interface 61, a second reversing interface 62, a third reversing interface 63 and a fourth reversing interface 64, which are respectively connected with the inlet of the compressor, the outlet of the compressor, the first interface of the regulating valve and the heat exchanger, and the reversing valve is used for regulating the flow direction of the refrigerant.
Illustratively, the reversing valve is provided with four interfaces, the four interfaces can mutually switch the paths, so that the reversing of the refrigerant flow direction is realized, and the switching of the double-cold-source refrigerant liquid separating device between the refrigerating mode and the heating mode is realized. Illustratively, in the refrigeration mode of the double-cold-source refrigerant liquid separation device, the refrigerant flow direction cycle is as follows: compressor 10 → governor valve 20 → air-cooled heat exchanger 30 and evaporative cold heat exchanger 40 → heat exchanger 50 → compressor 10; under the heating mode of the double-cold-source refrigerant liquid separating device, the refrigerant flow direction circulation is as follows: compressor 10 → heat exchanger 50 → air-cooled heat exchanger 30 and evaporative cooling heat exchanger 40 → regulator valve 20 → compressor 10.
Referring to fig. 2, fig. 2 is a schematic structural diagram of another dual cold source refrigerant liquid separating device provided in an embodiment of the present application, where the dual cold source refrigerant liquid separating device includes a compressor 10, an adjusting valve 20, an air-cooled heat exchanger 30, an evaporative cold heat exchanger 40, a heat exchanger 50, a reversing valve 60, a gas-liquid separator 70, an accumulator 80, a throttling mechanism 90, and at least one check valve 100.
Illustratively, the gas-liquid separator 70 is connected to the reversing valve 60 and the inlet of the compressor 10, respectively; optionally, a gas-liquid separator 70 is connected to the second reversing port 62 of the reversing valve 60 and to the inlet of the compressor 10, respectively.
Illustratively, the gas-liquid separator 70 may be installed at an inlet of the gas compressor for gas-liquid separation, processing the refrigerant containing a small amount of condensate, and recovering the refrigerant.
Illustratively, the air-cooled heat exchanger 30 and the evaporative cooled heat exchanger 40 are provided with the confluence port 34, and the reservoir 80 is connected to the confluence port 34 and the heat exchanger 50, respectively.
For example, the accumulator may temporarily store the refrigerant, serving to relay the refrigerant.
Illustratively, the throttle mechanism 90 is connected to the accumulator 80, the junction 34, and the heat exchanger 50, respectively.
Illustratively, the refrigerant flows from the accumulator 80 to the throttle mechanism 90, passes through the throttle mechanism 90, is throttled and depressurized, and becomes a gas-liquid two-phase refrigerant.
Illustratively, the check valve 100 is disposed on a connecting conduit of the reservoir 80.
For example, the check valve 100 is provided in the connection pipe of the accumulator 80, and the check valve 100 has a characteristic of one-way passage of liquid, so that the flow direction of the refrigerant in the double-cold-source refrigerant distribution device can be always maintained between the accumulator 80 → the throttling mechanism 90 in both the heating mode and the cooling mode.
In some embodiments, the dual cold source refrigerant distribution device includes a first check valve 101 and a second check valve 102, the first check valve 101 is disposed on a connecting pipeline of the junction 34 and the accumulator 80, and the second check valve 102 is disposed on a connecting pipeline of the throttling mechanism 90 and the heat exchanger 50, so that the refrigerant flows through the junction 34, the accumulator 80, the throttling mechanism 90 and the heat exchanger 50 in sequence.
For example, the first check valve 101 and the second check valve 102 may enable the dual cold source refrigerant separating device to be in the cooling mode, and the flow direction of the refrigerant is as follows: the confluence port 34 → the accumulator 80 → the throttling mechanism 90 → the heat exchanger 50.
In some embodiments, the dual cold source refrigerant distribution device includes a third check valve 103 and a fourth check valve 104, the third check valve 103 is disposed on a connecting pipeline of the heat exchanger 50 and the accumulator 80, and the fourth check valve 104 is disposed on a connecting pipeline of the throttling mechanism 90 and the confluence port 34, so that the refrigerant flows through the heat exchanger 50, the accumulator 80, the throttling mechanism 90 and the confluence port 34 in sequence.
In the implementation process, the third check valve 103 and the fourth check valve 104 enable the dual cold source refrigerant separating device to be in the heating mode, and the flow direction of the refrigerant is as follows: heat exchanger 50 → accumulator 80 → throttling mechanism 90 → sink 34.
In some embodiments, the air-cooled heat exchanger 30 includes a fan 31 and a fin heat exchanging mechanism 32, the fin heat exchanging mechanism 32 is respectively connected to the second port 22 of the regulating valve 20 and the heat exchanger 50, and the fan 31 is disposed above the fin heat exchanging mechanism 32.
Referring to fig. 3, fig. 3 is a schematic structural diagram of an air-cooled heat exchanger according to an embodiment of the present disclosure.
Illustratively, the fin heat exchange mechanism 32 may be composed of three rows of parallel spiral fin tube bundles between air flow directions, the fin heat exchange mechanism 32 may employ mechanical winding fins, the contact surface between the heat dissipation fins and the heat dissipation tube is large and tight, the heat transfer performance is good and stable, the air passing resistance is small, the refrigerant flows through the steel tube, the heat is transferred to the air passing through the fins by the fins tightly wound on the steel tube, and the air heating and cooling effects are achieved.
In some embodiments, the evaporative cooling heat exchanger 40 includes a spraying mechanism 41, a plate-tube heat exchange mechanism 42, a water pump 43, a water tank 44, and an exhaust fan 45, the spraying mechanism 41, the plate-tube heat exchange mechanism 42, and the water tank 44 are stacked in sequence from top to bottom, the water pump 43 is connected to the spraying mechanism 41 and the water tank 44, respectively, and the exhaust fan 45 is disposed above the spraying mechanism 41.
Referring to fig. 4, fig. 4 is a schematic structural diagram of an evaporative cooling heat exchanger according to an embodiment of the present disclosure.
Illustratively, the evaporative cooling heat exchanger 40 implements water circulation by the spraying mechanism 41, the plate-and-tube heat exchanging mechanism 42, and the water tank 44, and removes condensation heat by using moisture evaporation and forced air circulation to cool the high-temperature and high-pressure refrigerant discharged from the compressor 10 to condense it into liquid.
In some implementation scenarios, the dual cold source refrigerant liquid separation device operates in a cooling mode, and the work flow is as follows:
the compressor 10 compresses a low-temperature and low-pressure refrigerant gas into a high-temperature and high-pressure refrigerant gas; the refrigerant gas passes through the first direction port 61 to the third direction port 63 of the direction valve 60 to the first port 21 of the regulator valve 20. The regulating valve 20 obtains the drift diameters of the second interface 22 and the third interface 23 in the regulating valve 20 through calculation by a corresponding thermodynamic formula according to different environment dry bulb temperatures TD and environment wet bulb temperatures TW. Wherein the refrigerant flows to the air-cooled heat exchanger 30 for condensation through the second interface 22 and flows to the evaporative cold heat exchanger 40 for condensation through the third interface 23. The condensed high-temperature and high-pressure two refrigerant liquids flow through the first check valve 101 and the reservoir 80 after being converged, are throttled and depressurized by the throttling mechanism 90 to become a gas-liquid two-phase refrigerant, then flow to the heat exchanger 50 for evaporation and refrigeration to become a low-temperature and low-pressure refrigerant gas, then flow through the fourth reversing connector 64 of the reversing valve 60 to the second reversing connector 62 and the gas-liquid separator 70, and then flow back to the inlet of the compressor 10; and (5) performing reciprocating circulation on the process, namely the refrigeration cycle of the double-cold-source refrigerant liquid separating device.
In the condensing process of the air-cooled heat exchanger 30, the air is forced to flow through the fin heat exchange mechanism 32 by the fan 31 by using the ambient dry bulb temperature TD, so that the heat of the refrigerant is taken away by the air. In the condensation process of the evaporative cooling heat exchanger 40, the temperature of the circulating water is reduced by utilizing the environmental wet bulb temperature TW; the cooled circulating water is sent to the spraying mechanism 41 by a water pump 43 from a water tank 44 and then is uniformly distributed on the surface of the plate-tube heat exchange mechanism 42; the heat is conducted to the water film, which evaporates and is exhausted by the exhaust fan 45. The heat exchanger 50 may be a shell and tube heat exchanger, a fin heat exchanger, or the like, and may provide cooling energy to a user.
In some implementation scenarios, the dual cold source refrigerant liquid separation device operates in a heating mode, and the workflow is as follows:
the compressor 10 compresses a low-temperature and low-pressure refrigerant gas into a high-temperature and high-pressure refrigerant gas. The refrigerant gas passes through the first reversing connector 61 to the fourth reversing connector 64 of the reversing valve 60, and then is condensed in the heat exchanger 50, so that the refrigerant gas is changed into high-temperature and high-pressure refrigerant liquid. Then the refrigerant passes through the third one-way valve 103 and the reservoir 80, reaches the throttling mechanism 90 for throttling and pressure reduction, is changed into a gas-liquid two-phase refrigerant, and then is divided into two streams of refrigerants, wherein one stream of refrigerant is evaporated by the air-cooled heat exchanger 30 and flows to the second interface 22 of the regulating valve 20, and the other stream of refrigerant is condensed by the evaporative cooling heat exchanger 40 and flows to the third interface 23 of the regulating valve 20; the two flows of refrigerant are collected to the first port 21 of the regulating valve, then pass through the third direction-changing port 63 of the direction-changing valve 60 to the second direction-changing port 62 and the gas-liquid separator 70, and return to the inlet of the compressor 10. And (5) performing reciprocating circulation on the processes, namely performing heating circulation of the double-cold-source refrigerant liquid separating device.
In the condensation process of the air-cooled heat exchanger 30, the air is forced to flow through the fin heat exchange mechanism 32 by the fan 31 by using the ambient dry bulb temperature TD, so that the cold energy of the refrigerant is carried away by the air. In the condensation process of the evaporative cooling heat exchanger 40, the temperature of the circulating water is reduced by utilizing the environmental wet bulb temperature TW; the cooled circulating water is sent to the spraying mechanism 41 by the water pump 43 from the water tank 44 and then is uniformly arranged on the surface of the plate-tube heat exchange mechanism 42. The cold energy is conducted to the water film, which evaporates and is discharged by the exhaust fan 45. The heat exchanger 50 may be a shell and tube heat exchanger, a fin heat exchanger, or the like, which may provide heat to a user.
In some embodiments, the air-cooled heat exchanger 30 is provided with a pressure sensor, which can detect the real-time pressure P1 of the air-cooled heat exchanger 30, and calculate through a thermodynamic formula, the corresponding saturation temperature T1 can be obtained; the evaporative cooling heat exchanger 40 is provided with a pressure sensor, which can detect the real-time pressure P2 of the evaporative cooling heat exchanger 40, and the corresponding saturation temperature T2 can be obtained through calculation of a thermodynamic formula. The heat exchanger 50 is provided with a pressure sensor which can detect the real-time pressure P3 of the heat exchanger 50, and the corresponding saturation temperature T3 can be obtained through calculation of a thermodynamic formula.
For example, the corresponding power consumption, cooling capacity and mass flow of the dual cold source refrigerant separating device can be calculated through preset coefficients (C0-C9) of the compressor 10 and the following formula:
Y＝C0+C1*Te+C2*Tc+C3*Te^2+C4*Te*Tc+C5*Tc^2+C6*Te^3+C7*Tc*Te^2+C8*Te*Tc^2+C9*Tc^3；
when the double-cold-source refrigerant separating device is used for refrigerating, Y1 corresponds to Te which is T3, Tc which is T1, Y2 corresponds to Te which is T3, and Tc which is T2; when the double-cold-source refrigerant separating device heats, Y1 corresponds to Te-T1, Tc-T3, Y2 corresponds to Te-T2, and Tc-T3.
The preset coefficients C0-C9 are specific parameter values determined according to different types of compressors 10 and different power consumption, refrigerating capacity and mass flow.
In some implementations, when the dual cold source refrigerant separation device is refrigerating, the adjustment of the adjustment valve 20 is as follows: after the double-cold-source refrigerant separating device is started, the second interface 22 and the third interface 23 of the regulating valve 20 equally distribute the flow of the refrigerant. Then, according to the changes of the environment dry bulb temperature TD and the environment wet bulb temperature TW, the flow distribution of the refrigerant is adjusted, and the refrigerant is preferentially supplied to the evaporative cooling heat exchanger 40; calculating the whole power consumption of the double-cold-source refrigerant liquid separating device, and if the power consumption calculated by the current period detection is larger than the previous period, adjusting to perform the action opposite to the previous period; and if the power consumption calculated by the current period detection is less than the last period, continuing the action of the last week. Wherein a fluctuation range is set as a stable interval. Alternatively, the amplitude of the motion may be the same or different for each cycle.
In some implementations, when the dual cold source refrigerant separator device is heating, the adjustment of the adjustment valve 20 is as follows: after the double-cold-source refrigerant liquid separating device is started, detecting the environment dry-bulb temperature TD and the environment wet-bulb temperature TW. When the dry bulb temperature TD is lower than 0 ℃, the passage of the regulating valve 20 is directly regulated to be a first port 21 to a second port 22, and the rest is closed. When the wet bulb temperature TW is lower than 8 ℃ or a certain set value, and the dry bulb temperature TD is higher than 0 ℃, the adjusting valve 20 is adjusted to give priority to the passage from the first port 21 to the second port 22, and the opening degrees of the first port 21 to the third port 22 are appropriately adjusted. When the wet bulb temperature TW is higher than 8 ℃ or a certain set value, calculating the whole power consumption of the double-cold-source refrigerant liquid separating device, and if the power consumption calculated by the current period detection is higher than the last period, adjusting to perform the action opposite to the action of the last period; and if the current cycle detection calculation power consumption is less than the last cycle, continuing the action of the last week. Wherein a fluctuation range is set as a stable interval. Alternatively, the amplitude of the motion may be the same or different for each cycle.
In all embodiments of the present application, the terms "large" and "small" are relatively speaking, and the terms "upper" and "lower" are relatively speaking, so that descriptions of these relative terms are not repeated herein.
It should be appreciated that reference throughout this specification to "in this embodiment," "in an embodiment of the present application," or "as an alternative implementation" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the present application. Thus, the appearances of the phrases "in this embodiment," "in the examples of the present application," or "as an alternative embodiment" in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments. Those skilled in the art should also appreciate that the embodiments described in this specification are all alternative embodiments and that the acts and modules involved are not necessarily required for this application.
In various embodiments of the present application, it should be understood that the size of the serial number of each process described above does not mean that the execution sequence is necessarily sequential, and the execution sequence of each process should be determined by its function and inherent logic, and should not constitute any limitation on the implementation process of the embodiments of the present application.
The above description is only for the specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present application, and shall be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.
Claims (10)
1. A double-cold-source refrigerant liquid separating device is characterized by comprising a compressor, a regulating valve, an air-cooled heat exchanger, an evaporative-cooled heat exchanger and a heat exchanger;
the compressor is used for compressing refrigerant gas;
the regulating valve comprises a first interface, a second interface and a third interface, the first interface of the regulating valve is connected with the compressor, and the regulating valve is used for regulating the drift diameter of the refrigerant according to the ambient temperature and the running power consumption;
the air-cooled heat exchanger is connected with a second interface of the regulating valve;
the evaporative cooling heat exchanger is connected with a third interface of the regulating valve;
the heat exchanger is respectively connected with the compressor, the air-cooled heat exchanger and the evaporation-cooled heat exchanger to form a circulation loop of the refrigerant.
2. The dual cold source refrigerant liquid separation device according to claim 1, further comprising a reversing valve, wherein said reversing valve is provided with four ports respectively connected to an inlet of said compressor, an outlet of said compressor, a first port of said regulating valve and said heat exchanger, and said reversing valve is used for regulating a refrigerant flow direction.
3. The dual cold source refrigerant liquid separation device according to claim 2, further comprising a gas-liquid separator connected to the reversing valve and an inlet of the compressor, respectively.
4. The double cold source refrigerant liquid separating device according to claim 1, further comprising a liquid reservoir, wherein the air-cooled heat exchanger and the evaporative cold heat exchanger are provided with a confluence port, and the liquid reservoir is respectively connected with the confluence port and the heat exchanger.
5. The dual cold source refrigerant liquid separation device according to claim 4, further comprising a throttling mechanism, wherein the throttling mechanism is respectively connected with the reservoir, the confluence port and the heat exchanger.
6. The dual cold source refrigerant liquid separation device according to claim 5, wherein said device comprises at least one-way valve, said one-way valve being disposed on a connection pipe of said accumulator.
7. The dual cold source refrigerant liquid separating device according to claim 6, wherein the device comprises a first one-way valve and a second one-way valve, the first one-way valve is arranged on a connecting pipeline of the confluence port and the accumulator, and the second one-way valve is arranged on a connecting pipeline of the throttling mechanism and the heat exchanger, so that the refrigerant flows through the confluence port, the accumulator, the throttling mechanism and the heat exchanger in sequence.
8. The double cold source refrigerant liquid separating device according to claim 6, wherein the device comprises a third one-way valve and a fourth one-way valve, the third one-way valve is arranged on a connecting pipeline of the heat exchanger and the accumulator, and the fourth one-way valve is arranged on a connecting pipeline of the throttling mechanism and the confluence port, so that the refrigerant flows through the heat exchanger, the accumulator, the throttling mechanism and the confluence port in sequence.
9. The double-cold-source refrigerant liquid separating device according to claim 1, wherein the air-cooled heat exchanger comprises a fan and a fin heat exchange mechanism, the fin heat exchange mechanism is respectively connected with the second interface of the regulating valve and the heat exchanger, and the fan is arranged above the fin heat exchange mechanism.
10. The dual cold source refrigerant liquid separating device according to claim 1, wherein the evaporative cooling heat exchanger comprises a spraying mechanism, a plate-tube heat exchange mechanism, a water pump, a water tank and an exhaust fan, the spraying mechanism, the plate-tube heat exchange mechanism and the water tank are sequentially stacked from top to bottom, the water pump is respectively connected with the spraying mechanism and the water tank, and the exhaust fan is arranged above the spraying mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021851413.8U CN212431381U (en) | 2020-08-28 | 2020-08-28 | Double-cold-source refrigerant liquid separating device |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202021851413.8U CN212431381U (en) | 2020-08-28 | 2020-08-28 | Double-cold-source refrigerant liquid separating device |
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| CN212431381U true CN212431381U (en) | 2021-01-29 |
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| CN202021851413.8U Active CN212431381U (en) | 2020-08-28 | 2020-08-28 | Double-cold-source refrigerant liquid separating device |
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