CN217844344U - Indirect evaporation air source heat pump device - Google Patents

Abstract

The embodiment of the application provides an indirect evaporation air source heat pump device, and relates to the technical field of heat pumps. The air source heat pump device comprises a compressor, a four-way valve, a fin heat exchanger, a first expansion valve, an economizer, an electromagnetic valve, a shell and tube heat exchanger and an atomization mechanism; the compressor, the finned heat exchanger, the first expansion valve, the economizer and the shell and tube heat exchanger are sequentially connected, wherein the compressor is connected with the finned heat exchanger through the four-way valve, the compressor is connected with the shell and tube heat exchanger through the four-way valve, the economizer is connected with the compressor, and the electromagnetic valve is respectively connected with the economizer and the shell and tube heat exchanger; the atomization mechanism is arranged on the front side of the air inlet direction of the fin heat exchanger and used for atomizing and spraying water to the front side area of the air inlet direction of the fin heat exchanger. The air source heat pump device can achieve the technical effect of improving the heat exchange efficiency.

Description

Indirect evaporation air source heat pump device

Technical Field

The application relates to the technical field of heat pumps, in particular to an indirect evaporation air source heat pump device.

Background

At present, when an existing air-cooled heat pump unit is used for refrigerating in summer, ambient air is used for heat exchange, along with the rising of the temperature of outdoor dry balls, the heat exchange efficiency of an air-cooled condenser is low, the refrigerating capacity of the unit is reduced, the power consumption is increased, and the refrigerating performance coefficient is reduced. However, the existing air-cooled heat pump unit has high power consumption and low energy consumption when in high-ambient-temperature refrigeration operation in summer; when the low-loop temperature heating operation is carried out in winter, the exhaust temperature is high, the operation is unstable, and the heat exchange efficiency is low.

SUMMERY OF THE UTILITY MODEL

The embodiment of the application aims to provide an indirect evaporation air source heat pump device and a control method, and the technical effect of improving the heat exchange efficiency can be achieved.

In a first aspect, an embodiment of the present application provides an indirect evaporation air source heat pump device, including a compressor, a four-way valve, a fin heat exchanger, a first expansion valve, an economizer, a solenoid valve, a shell and tube heat exchanger, and an atomization mechanism;

the compressor, the finned heat exchanger, the first expansion valve, the economizer and the shell and tube heat exchanger are sequentially connected, wherein the compressor is connected with the finned heat exchanger through the four-way valve, the compressor is connected with the shell and tube heat exchanger through the four-way valve, the economizer is connected with the compressor, and the electromagnetic valve is respectively connected with the economizer and the shell and tube heat exchanger;

the atomization mechanism is arranged on the front side of the air inlet direction of the fin heat exchanger and used for atomizing and spraying water to the front side area of the air inlet direction of the fin heat exchanger.

In the implementation process, the atomization mechanism is additionally arranged on the air inlet side of the fin heat exchanger, the atomization mechanism is used for atomizing water into a large number of high-speed liquid drop particles in a micron level, the air dry bulb temperature is reduced through the evaporation heat absorption effect of liquid, and the heat exchange temperature difference between the fin heat exchanger and the air is improved, so that the power consumption of the air source heat pump device is reduced, the unit performance is improved, in addition, the economizer is arranged to reduce the exhaust temperature, the supercooling degree is improved during heating, the length of a gas phase heat exchange area of the air source heat pump device is reduced, the two-phase heat exchange area is increased, the heat exchange efficiency of the air source heat pump device is improved, the compression process is divided into two sections by the air supply process, the two-stage compression process is changed into a quasi-two-stage compression process, the work of a compressor is reduced, and the outlet temperature of the compressor is reduced; therefore, the air source heat pump device can achieve the technical effect of improving the heat exchange efficiency.

Further, the four-way valve comprises a first interface, a second interface, a third interface and a fourth interface, wherein the outlet end of the compressor is connected with the first interface, the inlet end of the compressor is connected with the fourth interface, the second interface is connected with the fin heat exchanger, and the third interface is connected with the shell and tube heat exchanger.

In the implementation process, the first interface and the second interface of the four-way valve can be communicated, the third interface and the fourth interface can be communicated, and at the moment, the refrigerant flows to the outlet of the compressor and the fin heat exchanger 8230, the shell and tube heat exchanger and then returns to the inlet of the compressor; the first interface and the third interface of the four-way valve can be communicated, the second interface and the fourth interface can be communicated, and at the moment, the refrigerant flows to an outlet of the compressor and a shell and tube heat exchanger (8230) \ 8230, a fin heat exchanger and then returns to an inlet of the compressor; therefore, the communication direction of the four-way valve is adjusted, so that the circulation direction of the refrigerant is adjusted, and the conversion between a heating mode and a cooling mode is realized.

Further, the atomization mechanism comprises a water retaining filler, an atomization nozzle and a water pump;

the water retaining filler is arranged on the front side of the air inlet direction of the fin heat exchanger and can be opened or closed along the preset direction;

the water pump is connected with the atomizing nozzle, the water pump delivers water to the atomizing nozzle when the water pump is in an open state, and the atomizing nozzle sprays atomized water to the front side area in the air inlet direction of the fin heat exchanger.

In the implementation process, the water retaining filler is arranged on the front side of the air inlet direction of the fin heat exchanger and is kept a certain distance away from the fin heat exchanger so as to be convenient for air equalization; the water retaining filler can be opened or closed along a preset direction, so that the water retaining filler can be opened when spraying is not needed, and the wind resistance of the heat exchanger in the air inlet direction is reduced; the water retaining filler can prevent unevaporated liquid drops from entering the surface of the fin heat exchanger for evaporation, avoid causing fin scaling and improve the heat exchange efficiency.

Further, the water retaining filler is a high polymer material water retaining filler or a wet curtain paper water retaining filler.

In the implementation process, the water retaining filler can be made of high polymer materials or wet curtain paper, so that unevaporated liquid drops are prevented from entering the surface of the fin heat exchanger to be evaporated, and scaling of fins is avoided.

Furthermore, the air source heat pump device further comprises a transmission mechanism, the transmission mechanism is connected with the water retaining filler, and the transmission mechanism is used for driving the water retaining filler to rotate along a preset direction.

In the implementation process, the water retaining filler is provided with the transmission mechanism, so that the water retaining filler can be rotated at multiple angles according to requirements, the water retaining filler is convenient to open when spraying is not needed, and the wind resistance is reduced.

Furthermore, the atomizing mechanism also comprises a water softening processor which is connected with the water pump.

In the implementation process, the softened water treatment device is arranged, so that the concentration of calcium and magnesium ions in water is reduced, and the scaling problem of the fin heat exchanger and the dirty and blocked problem of the atomizing nozzle are further reduced.

Further, the air source heat pump device further comprises a second expansion valve, and the economizer, the second expansion valve, the electromagnetic valve and the shell and tube heat exchanger are sequentially connected.

In the implementation process, the economizer and the shell and tube heat exchanger are provided with two passages, wherein one passage is connected with the second expansion valve and the electromagnetic valve, and the on-off of the passage is controlled by the electromagnetic valve.

Further, the air source heat pump device further comprises a fan.

In the implementation process, the fan is used for blowing air to the fin heat exchanger, and the air can be discharged from the side surface or the top surface, so that the air inlet efficiency of the fin heat exchanger is improved.

Further, the air source heat pump device further comprises a one-way valve assembly, and the one-way valve assembly is arranged in a communication pipeline between the fin heat exchanger and the economizer.

In the above implementation, the cryogenic assembly is provided by a one-way valve assembly.

Further, the one-way valve assembly includes a first one-way valve and a second one-way valve;

the communication pipeline between the fin heat exchanger and the economizer comprises a first communication pipeline and a second communication pipeline, the first one-way valve is arranged on the first communication pipeline, the second one-way valve is arranged on the second communication pipeline, and the second communication pipeline is arranged at the bottom of the fin heat exchanger.

In the implementation process, during heating, the refrigerant enters the bottom of the fin heat exchanger through the second one-way valve, and the high-temperature liquid refrigerant is introduced, so that the bottom of the fin heat exchanger is prevented from frosting while the supercooling degree is improved; during refrigeration, the refrigerant completes a cycle through the first check valve.

In a second aspect, an embodiment of the present application provides an indirect evaporation air-source heat pump control method, which is applied to the indirect evaporation air-source heat pump device described in any one of the first aspects, and the control method includes:

acquiring environmental temperature information and condensation temperature information;

controlling the air source heat pump device to operate in a refrigeration mode, wherein the compressor is started, and the atomization mechanism is stopped;

after the air source heat pump device runs for a first preset time, the air source heat pump device enters an atomization mechanism adjustable control mode, and the air source heat pump device executes the following processing under the atomization mechanism adjustable control mode:

in a monitoring period of second preset time, comparing the environmental temperature information and the condensation temperature information with a target temperature value, and if the environmental temperature information is greater than or equal to the first target temperature value or the condensation temperature information is greater than or equal to the second temperature value and lasts for third preset time, starting the atomizing mechanism;

after the atomization mechanism is started, in the next monitoring period of the second preset time, if the environment temperature information is smaller than a third target temperature value or the condensation temperature information is smaller than a fourth temperature value and lasts for a third preset time, the atomization mechanism is stopped.

In a third aspect, an embodiment of the present application provides an indirect evaporation air-source heat pump control method, which is applied to the indirect evaporation air-source heat pump device described in any one of the first aspect, and the control method includes:

acquiring environmental temperature information and exhaust temperature information;

controlling the air source heat pump device to operate in a heating mode, wherein the compressor is opened, the atomizing mechanism is stopped, and the electromagnetic valve is opened;

after the air source heat pump device operates for a first preset time, entering an economizer adjustable control mode, and executing the following processing by the air source heat pump device in the economizer adjustable control mode:

in a monitoring period of second preset time, comparing the environment temperature information and the exhaust temperature information with a target temperature value, and if the environment temperature information is greater than or equal to a fifth target temperature value or the exhaust temperature information is less than a sixth temperature value for third preset time, closing the electromagnetic valve;

after the electromagnetic valve is closed, in the next monitoring period of the second preset time, if the environment temperature information is smaller than a seventh target temperature value or the exhaust temperature information is greater than or equal to an eighth temperature value and lasts for a third preset time, the electromagnetic valve is opened.

Additional features and advantages of the disclosure will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by the practice of the above-described techniques.

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 an indirect evaporation air-source heat pump device provided in an embodiment of the present application;

fig. 2 is a schematic structural diagram of an atomization mechanism provided in the embodiment of the present application when stopping;

fig. 3 is a schematic structural diagram of an atomizing mechanism provided in the embodiment of the present application when the atomizing mechanism is opened;

FIG. 4 is a schematic diagram of a refrigerant cycle of an air source heat pump device in a cooling mode according to an embodiment of the present application;

FIG. 5 is a schematic diagram of a refrigerant cycle of an air source heat pump device in a heating mode according to an embodiment of the present application;

fig. 6 is a schematic flow chart of a control method of an indirect evaporation air source heat pump in a cooling mode according to an embodiment of the present application;

fig. 7 is a schematic flowchart of a control method of an air-source heat pump for indirect evaporation in a heating mode according to an embodiment of the present application.

An icon: a compressor 100; a four-way valve 200; a finned heat exchanger 300; a fan 310; a first expansion valve 400; a second expansion valve 410; an economizer 500; a solenoid valve 600; a shell and tube heat exchanger 700; an atomization mechanism 800; a water blocking filler 810; an atomizing nozzle 820; a water pump 830; a water softener 840; a one-way valve assembly 900; a first one-way valve 910; a second one-way valve 920.

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 in other meanings besides orientation or positional relationship, for example, the term "upper" may also be used in some cases to indicate a certain attaching or connecting relationship. 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 an indirect evaporation air source heat pump device and a control method, which can be applied to the refrigeration or heating process of a heat pump; according to the indirect evaporation air source heat pump device, the atomization mechanism is additionally arranged on the air inlet side of the fin heat exchanger, the atomization mechanism is used for atomizing water into a large number of high-speed liquid drop particles in a micron level, the air dry bulb temperature is reduced through the evaporation heat absorption effect of liquid, the heat exchange temperature difference between the fin heat exchanger and air is improved, the power consumption of the air source heat pump device is reduced, the unit performance is improved, in addition, the exhaust temperature can be reduced through the arrangement of the economizer, the supercooling degree is improved during heating, the length of a gas phase heat exchange area of the air source heat pump device is reduced, the two-phase heat exchange area is increased, the heat exchange efficiency of the air source heat pump device is improved, the compression process is divided into two sections through the air supply process, the quasi-second-stage compression process is changed, the work of a compressor is reduced, and the outlet temperature of the compressor is reduced; therefore, the air source heat pump device can achieve the technical effect of improving the heat exchange efficiency.

Referring to fig. 1, fig. 1 is a schematic structural diagram of an indirect evaporation air source heat pump device according to an embodiment of the present disclosure, where the indirect evaporation air source heat pump device includes a compressor 100, a four-way valve 200, a finned heat exchanger 300, a first expansion valve 400, an economizer 500, a solenoid valve 600, a shell-and-tube heat exchanger 700, and an atomization mechanism 800.

Illustratively, the compressor 100, the finned heat exchanger 300, the first expansion valve 400, the economizer 500, and the shell-and-tube heat exchanger 700 are connected in sequence, wherein the compressor 100 is connected to the finned heat exchanger 300 via the four-way valve 200, the compressor 100 is connected to the shell-and-tube heat exchanger 700 via the four-way valve 200, the economizer 500 is connected to the compressor 100, and the solenoid valve 600 is connected to the economizer 500 and the shell-and-tube heat exchanger 700, respectively.

Illustratively, the four-way valve 200 has four interfaces, and the compressor 100, the finned heat exchanger 300 and the shell and tube heat exchanger 700 are respectively connected with different interfaces of the four-way valve 200, so that the circulation direction of the refrigerant can be changed, and the switching control of the cooling mode and the heating mode of the air source heat pump device is realized.

Illustratively, the economizer 500 is one type of heat exchanger that absorbs heat by throttling evaporation of the refrigerant itself, thereby subcooling another portion of the refrigerant. In the indirect evaporation air source heat pump device provided by the embodiment of the application, because the pressure ratio of the compressor 100 is relatively large, the exhaust temperature is very high at this time, and the normal operation of the air source heat pump device is influenced; by providing the economizer 500, the exhaust temperature can be lowered and the supercooling degree can be increased.

Illustratively, the atomizing mechanism 800 is arranged at the front side of the air inlet direction of the fin heat exchanger 300, and the atomizing mechanism 800 is used for atomizing and spraying water to the front side area of the air inlet direction of the fin heat exchanger 300; wherein, the atomization mechanism 800 does not directly spray the water mist to the finned heat exchanger 300 (direct spraying is easy to cause fin scaling), so that the water mist is completely evaporated in the air, thereby reducing the temperature of the dry bulb.

Illustratively, by adding the atomizing mechanism 800, the atomizing mechanism 800 is utilized to atomize water into a large number of high-speed liquid drop particles in a micron level, the temperature of an air dry bulb is reduced through the evaporation heat absorption effect of liquid, and the heat exchange temperature difference between the fin heat exchanger 300 and the air is improved, so that the power consumption of a unit is reduced, and the performance of the air source heat pump device is improved.

In some embodiments, the indirect evaporation air source heat pump device increases the atomization mechanism 800 on the air inlet side of the fin heat exchanger 300, atomizes water into a large number of micron-level high-speed liquid drop particles by using the atomization mechanism 800, reduces the air dry bulb temperature by the evaporation heat absorption effect of liquid, and improves the heat exchange temperature difference between the fin heat exchanger 300 and air, thereby reducing the power consumption of the air source heat pump device, and improving the unit performance; therefore, the air source heat pump device can achieve the technical effect of improving the heat exchange efficiency.

Illustratively, the four-way valve 200 includes a first port, a second port, a third port and a fourth port, the outlet end of the compressor 100 is connected to the first port, the inlet end of the compressor 100 is connected to the fourth port, the second port is connected to the fin heat exchanger 300, and the third port is connected to the shell-and-tube heat exchanger 700.

Illustratively, the first port and the second port of four-way valve 200 may be connected, and the third port and the fourth port may be connected, and the refrigerant flows to the outlet of compressor 100, to finned heat exchanger 300 8230, to shell and tube heat exchanger 700, and then to the inlet of compressor 100; the first interface and the third interface of the four-way valve 200 can be communicated, the second interface and the fourth interface can be communicated, and at the moment, the refrigerant flows to the outlet of the compressor 100, the shell and tube heat exchanger 700 \8230, the shell and tube heat exchanger 8230, the fin heat exchanger 300 and then returns to the inlet of the compressor 100; accordingly, the switching between the heating mode and the cooling mode is realized by adjusting the circulation direction of the refrigerant by adjusting the communication direction of the four-way valve 200.

Referring to fig. 2 and fig. 3, fig. 2 is a schematic structural view of the atomizing mechanism provided in the embodiment of the present application when the atomizing mechanism is stopped, and fig. 3 is a schematic structural view of the atomizing mechanism provided in the embodiment of the present application when the atomizing mechanism is started.

Illustratively, the atomizing mechanism 800 includes a water blocking packing 810, an atomizing nozzle 820, and a water pump 830; the water blocking filler 810 is arranged on the front side of the air inlet direction of the fin heat exchanger 300, and the water blocking filler 810 can be opened or closed along the preset direction; the water pump 830 is connected with the atomizing nozzle 820, and the water pump 830 delivers water to the atomizing nozzle 820 when the on-state, and the atomizing nozzle 820 sprays the water atomized back to the front side region of the air inlet direction of the fin heat exchanger 300, avoids directly spraying the fin heat exchanger 300 through the water blocking filler 810, thereby avoiding causing fin scaling.

Exemplarily, the water blocking filler 810 is arranged on the front side of the air inlet direction of the fin heat exchanger 300 and is spaced from the fin heat exchanger 300 by a certain distance so as to equalize the air; the water retaining filler 810 can be opened or closed along a preset direction, so that the water retaining filler can be opened when spraying is not needed, and the wind resistance of the fin heat exchanger 300 in the air inlet direction is reduced; due to the arrangement of the water retaining filler, the liquid drops which are not evaporated can be prevented from entering the surface of the finned heat exchanger 300 for evaporation, the fins are prevented from scaling, and the effect of improving the heat exchange efficiency is realized.

For example, as shown in fig. 2, when the atomizing mechanism 800 is in a stop state, the water pump 830 is turned off, the water blocking filler 810 is in an open state (an open state in which the water blocking filler 810 is parallel to the horizontal plane), and the side of the fin heat exchanger 300 has smooth air intake, so that the wind resistance is reduced; as shown in fig. 3, when the atomizing mechanism 800 is in a stopped state, the water-blocking filler 810 is in a closed state (the closed state where the water-blocking filler 810 is perpendicular to the horizontal plane), at this time, the water pump 830 of the atomizing mechanism 800 is turned on, the atomizing nozzle 820 generates a large amount of high-speed liquid droplet particles, the temperature of the air dry bulb is reduced by the evaporation and heat absorption effect of the liquid, and the heat exchange temperature difference between the fin heat exchanger 300 and the air is increased.

Exemplarily, the water blocking filler 810 is a polymer material water blocking filler or a wet curtain paper water blocking filler.

Illustratively, the material of the water blocking filler 810 may be a polymer material or wet curtain paper, so as to prevent the non-evaporated liquid drops from entering the surface of the fin heat exchanger 300 to evaporate, and avoid causing fin scaling.

Exemplarily, the air source heat pump device further comprises a transmission mechanism, the transmission mechanism is connected with the water blocking filler 810, and the transmission mechanism is used for driving the water blocking filler 810 to rotate along a preset direction.

Exemplarily, the water blocking filler 810 is provided with a transmission mechanism, so that the water blocking filler 810 can be rotated at multiple angles according to requirements, the water blocking filler 810 can be conveniently opened when spraying is not needed, and the wind resistance is reduced.

Illustratively, the atomization mechanism 800 further includes a water softener 840, and the water softener 840 is connected to the water pump 830.

Illustratively, the softened water treatment device 840 is arranged to reduce the concentration of calcium and magnesium ions in water, and further reduce the problems of scaling of the fin heat exchanger 300 and fouling of the atomizing nozzle 820.

In some embodiments, the atomizing nozzle 820 is disposed at the front side of the water blocking filler 810 in the air inlet direction, and is spaced apart from the water blocking filler 810 by a certain distance (preferably 100cm-150 cm), so that the water mist sprayed by the atomizing nozzle 820 has a sufficient flight distance, thereby increasing the evaporation time and sufficiently reducing the temperature of the inlet air dry bulb, the atomizing nozzle 820 atomizes the water into a large number of high-speed droplet particles in the micron level, and the average particle diameter of the droplets is optimally 20 μm-50 μm through testing and accounting for the optimal evaporation effect and water saving effect.

Referring to fig. 4 and fig. 5, fig. 4 is a schematic refrigerant cycle diagram of an air source heat pump device in a cooling mode according to an embodiment of the present application, and fig. 5 is a schematic refrigerant cycle diagram of an air source heat pump device in a heating mode according to an embodiment of the present application.

The air-source heat pump apparatus further illustratively includes a second expansion valve 410, and the economizer 500, the second expansion valve 410, the solenoid valve 600, and the shell-and-tube heat exchanger 700 are connected in this order.

Illustratively, the economizer 500 and the shell and tube heat exchanger 700 have two paths, one of which is connected by the second expansion valve 410 and the solenoid valve 600, and the on/off is controlled by the solenoid valve 600. In the heating mode, the refrigerant is depressurized by the solenoid valve 600 and the second expansion valve 410, becomes two phases, enters the economizer 500, and exchanges heat with a main refrigerant flow flowing out of the shell-and-tube heat exchanger 700 inside the economizer; after heat exchange, the small refrigerant is gasified, then returns to the compressor 100 to be mixed with the refrigerant in the compressor 100 after the first-stage compression is completed, and then is compressed in the next stage, so that the heat exchange efficiency is improved.

In some embodiments, the connection order of the second expansion valve 410 and the solenoid valve 600 may be changed, which is not limited herein.

Illustratively, the air-source heat pump apparatus further includes a fan 310; optionally, the fan 310 is disposed above the fin heat exchanger 300.

Illustratively, the blower 310 is used for blowing air to the fin heat exchanger 300, and the air can be discharged from the side or from the top, so as to increase the air inlet efficiency of the fin heat exchanger 300.

Illustratively, the air source heat pump apparatus further comprises a check valve assembly 900, the check valve assembly 900 being disposed in the communication conduit between the finned heat exchanger 300 and the economizer 500.

Illustratively, the cryogenic assembly is provided by a one-way valve assembly 900; because the bottom air volume of the fin heat exchanger 300 is small under the general condition, the frost formation and even the icing are most easily caused by the gathering of condensed water during the heating process to influence the heat exchange efficiency, and the high-temperature liquid refrigerant is introduced through the check valve assembly 900 during the heating process, so that the frost formation at the bottom of the fin heat exchanger 300 is avoided while the supercooling degree is improved.

Illustratively, the one-way valve assembly 900 includes a first one-way valve 910 and a second one-way valve 920; the communication pipeline between the fin heat exchanger 300 and the economizer 500 comprises a first communication pipeline and a second communication pipeline, the first check valve 910 is arranged on the first communication pipeline, the second check valve 920 is arranged on the second communication pipeline, and the second communication pipeline is arranged at the bottom of the fin heat exchanger.

Illustratively, during heating, the refrigerant enters the bottom of the finned heat exchanger 300 through the second check valve 920, and high-temperature liquid refrigerant is introduced, so that the bottom of the finned heat exchanger 300 is prevented from frosting while the supercooling degree is improved; during cooling, the refrigerant completes the cycle through the first check valve 910.

For example, in low-temperature heating, because the pressure ratio of the compressor 100 is relatively large, the exhaust temperature is high at this time, which affects normal operation of the air source heat pump device; by arranging the economizer 500, the exhaust temperature can be reduced, the supercooling degree is improved, the length of a gas phase heat exchange area of the air source heat pump device is reduced, the two-phase heat exchange area is increased, the heat exchange efficiency of the air source heat pump device is improved, the compression process is divided into two sections by the air supplementing process and becomes a quasi-two-stage compression process, the work of the compressor 100 is reduced, and the outlet temperature of the compressor 100 is reduced.

In some embodiments, the operation modes of the air source heat pump device provided in the examples of the present application include a heating mode and a cooling mode, and specific examples are as follows:

(1) Heating mode: the electromagnetic valve 600 is opened and the atomizing mechanism 800 is closed;

as shown in fig. 5, the refrigerant is compressed by the compressor 100 to perform work, enters the shell-and-tube heat exchanger 700 through the four-way valve 200, is condensed into refrigerant liquid, a small portion of the refrigerant is decompressed by the solenoid valve 600 and the second expansion valve 410, becomes two-phase and enters the economizer 500, exchanges heat with the main refrigerant flow flowing out of the shell-and-tube heat exchanger 700 inside the economizer 500, is gasified after exchanging heat, and then returns to the compressor 100 to be mixed with the refrigerant in the compressor 100 after the first-stage compression, and then performs the next-stage compression together. The main refrigerant passes through the economizer 500 to obtain a lower temperature and a higher supercooling degree, then enters the bottom of the finned heat exchanger 300 through the second one-way valve 920, is depressurized through the first expansion valve 400, enters the finned heat exchanger 300 to exchange heat with ambient air, then passes through the four-way valve 200, and finally returns to the compressor 100 to continue to circulate.

(2) The refrigeration mode comprises a refrigeration operation mode with high ring temperature or high condensation temperature and a refrigeration operation mode with low ring temperature or low condensation temperature:

(2.1) a high-ring-temperature or high-condensation-temperature refrigeration operation mode: the electromagnetic valve 600 is closed, and the atomizing mechanism 800 is opened;

as shown in fig. 4, the refrigerant is compressed by the compressor 100 to do work, enters the fin heat exchanger 300 through the four-way valve 200 to exchange heat with ambient air, is condensed into refrigerant liquid, then is depressurized by the first expansion valve 400, enters the shell and tube heat exchanger 700 through the first one-way valve 910 and the economizer 500 to evaporate and absorb heat, then passes through the four-way valve 200, and finally returns to the compressor 100 to continue to circulate;

optionally, municipal water enters a water softening device 840 to filter impurities and calcium and magnesium ion concentration, the water is pressurized by a water pump 830 and enters an atomizing nozzle 820 to atomize the water into a large number of high-speed droplet particles in the micron level, in order to achieve the optimal evaporation effect and water saving effect, the average particle diameter of the droplets is optimally 20-50 μm through testing and calculation, the droplets absorb heat through evaporation to reduce the temperature of the inlet air dry bulb, and the droplets which are not evaporated are adsorbed on a water blocking filler 810 (made of a high polymer material or wet curtain paper) to further absorb heat through evaporation to reduce the temperature of the dry bulb;

(2.2) a low-ring-temperature or low-condensation-temperature refrigeration operation mode: the electromagnetic valve 600 is closed, and the atomizing mechanism 800 is closed;

the refrigerant is compressed by the compressor 100 to do work, enters the fin heat exchanger 300 through the four-way valve 200 to exchange heat with ambient air, is condensed into refrigerant liquid, is depressurized by the first expansion valve 400, enters the shell and tube heat exchanger 700 through the first one-way valve 910 and the economizer 500 to evaporate and absorb heat, then passes through the four-way valve 200 and finally returns to the compressor 100 to continue to circulate.

Referring to fig. 6, fig. 6 is a schematic flow chart of a control method of an indirect evaporation air-source heat pump in a cooling mode according to an embodiment of the present application, where the control method of an indirect evaporation air-source heat pump includes the following steps:

s110: acquiring ambient temperature information and condensation temperature information;

s120: controlling the air source heat pump device to operate in a refrigeration mode, and starting a compressor and stopping an atomizing mechanism;

s130: after the air source heat pump device operates for a first preset time, entering an atomization mechanism adjustable control mode, and executing the following processing by the air source heat pump device in the atomization mechanism adjustable control mode:

s140: in a monitoring period of second preset time, comparing the environmental temperature information and the condensing temperature information with a target temperature value, and if the environmental temperature information is greater than or equal to the first target temperature value or the condensing temperature information is greater than or equal to the second temperature value and lasts for third preset time, starting an atomizing mechanism; after the atomization mechanism is started, in the next monitoring period of second preset time, if the environment temperature information is smaller than a third target temperature value or the condensing temperature information is smaller than a fourth temperature value and lasts for third preset time, the atomization mechanism is stopped.

Referring to fig. 7, fig. 7 is a schematic flow chart of a control method of an indirect evaporation air-source heat pump in a heating mode according to an embodiment of the present application, where the control method of an indirect evaporation air-source heat pump includes the following steps:

s210: acquiring environmental temperature information and exhaust temperature information;

s220: controlling the air source heat pump device to operate in a heating mode, and opening a compressor, stopping an atomizing mechanism and opening an electromagnetic valve;

s230: after the air source heat pump device operates for a first preset time, the air source heat pump device enters an economizer adjustable control mode, and the air source heat pump device executes the following processing under the economizer adjustable control mode:

s240: in a monitoring period of second preset time, comparing the environment temperature information and the exhaust temperature information with a target temperature value, and if the environment temperature information is greater than or equal to a fifth target temperature value or the exhaust temperature information is less than a sixth temperature value for third preset time, closing the electromagnetic valve; after the electromagnetic valve is closed, in the next monitoring period of second preset time, if the environment temperature information is less than a seventh target temperature value or the exhaust temperature information is greater than or equal to an eighth temperature value and lasts for third preset time, the electromagnetic valve is opened.

In some embodiments, with reference to fig. 1 to 7, an example of a general control manner of the indirect evaporation air source heat pump device provided by the embodiment of the present application is as follows:

(1) In the cooling mode (corresponding to fig. 4 and 6), the solenoid valve 600 is always kept closed, and the control steps are as follows:

step 1.1: monitoring the ambient temperature Th and the condensing temperature Tc in real time;

step 1.2: when a starting command is received, the fan 310 is started, the atomizing mechanism 800 is closed, the electromagnetic valve 600 is closed, the compressor 100 is opened, and the air source heat pump device operates normally;

step 1.3: after the operation is carried out for t1 time, entering an adjustable control mode of an atomizing mechanism;

step 1.4: during a monitoring period of time t2, the ambient temperature Th, the condensing temperature Tc are compared with a target temperature value:

step 1.5: when the ambient temperature Th is more than or equal to Thh (for example, 38 ℃) or the condensation temperature Tc is more than or equal to Tch (for example, 48 ℃) and lasts for t3 time, the atomization mechanism 800 is started, otherwise, the atomization mechanism 800 keeps the current state;

step 1.6: after the atomization mechanism 800 is started, in the next monitoring period of time t2, when the ambient temperature Th is less than Thh (for example, 32 ℃) and the condensation temperature Tc is less than Tch (for example, 44 ℃) and lasts for time t3, the atomization mechanism 800 is closed, otherwise, the atomization mechanism 800 keeps the current state.

(2) In heating mode (corresponding to fig. 5 and 7):

step 2.1: monitoring the ambient temperature Th and the exhaust temperature Tp in real time;

step 2.2: when a starting command is received, the fan 310 is started, the atomizing mechanism 800 is closed, the electromagnetic valve is started, the compressor 100 is opened, and the air source heat pump device operates normally;

step 2.3: after the operation is carried out for t1 time, entering an economizer energy-adjusting control mode;

step 2.4: during a monitoring period of time t2, the ambient temperature Th, the exhaust temperature Tp are compared with target temperature values:

step 2.5: when the ambient temperature Th is more than or equal to Thr (for example: 5 ℃) or the Tp exhaust temperature is less than T1 and the electromagnetic exhaust temperature is turned off for T3 time, the electromagnetic valve 600 is closed, otherwise, the electromagnetic valve 600 keeps the current state;

step 2.6: after the solenoid valve 600 is closed, in the next monitoring period of time t2, when the ambient temperature Th is less than Thr-2 ℃ (for example: 3 ℃) and the Tp exhaust temperature is greater than or equal to the on-electromagnetic exhaust temperature (for example: 85 ℃), and the time lasts for t3, the solenoid valve 600 is opened, otherwise, the solenoid valve 600 keeps the current state.

Wherein, th: ambient temperature; tc: the condensation temperature; and (Thh): the refrigerating environment temperature is high; and (Thl): the refrigeration environment temperature is low; thr: opening the loop temperature of the electromagnetic valve; tp: the temperature of the exhaust gas; t1: turning off the electromagnetic temperature discharge; t2: switching on the electromagnet for temperature discharge; and (4) Tch: high value of condensation temperature; tcl: the condensation temperature is low; t1: a first preset time, i.e. a delay monitoring time, for example, 5min; t2: a second preset time, i.e. a monitoring period, e.g. 3min; t3: a third preset time, i.e. duration, for example 3s.

Exemplarily, in the air source heat pump device and the control method for indirect evaporation provided by the embodiment of the present application, the atomizing mechanism 800 is added on the air inlet side of the fin heat exchanger 300, the atomizing mechanism 800 is utilized to atomize water into a large number of high-speed liquid droplet particles in micron level, the air dry bulb temperature is reduced through the evaporation heat absorption effect of liquid, the heat exchange temperature difference between the fin heat exchanger 300 and the air is increased, the power consumption of the air source heat pump device is reduced, the unit performance is improved, and the water blocking filler 810 is added between the fin heat exchanger 300 and the atomizing mechanism 800 to prevent unevaporated liquid droplets from entering the fin surface to evaporate, so that the fin scaling is prevented to reduce the heat exchange efficiency; in addition, when heating in winter, the economizer 500 is arranged to reduce the exhaust temperature, improve the supercooling degree, reduce the length of a gas phase heat exchange area of the condenser, increase the two-phase heat exchange area and improve the heat exchange efficiency of the condenser, the compression process is divided into two sections by the air supplementing process and is changed into a quasi-two-stage compression process, the work of the compressor 100 is reduced, and the outlet temperature of the compressor 100 is reduced. Therefore, through the mode, the technical effect of improving the heat exchange efficiency is achieved.

In all embodiments of the present application, the terms "large" and "small" are relative terms, and the terms "more" and "less" are relative terms, and the terms "upper" and "lower" are relative terms, and the description of these relative terms is 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 exemplary embodiments in nature, and that acts and modules are not necessarily required to practice the invention.

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. An indirect evaporation air source heat pump device is characterized by comprising a compressor, a four-way valve, a fin heat exchanger, a first expansion valve, an economizer, an electromagnetic valve, a shell and tube heat exchanger and an atomization mechanism;

the compressor, the finned heat exchanger, the first expansion valve, the economizer and the shell and tube heat exchanger are sequentially connected, wherein the compressor is connected with the finned heat exchanger through the four-way valve, the compressor is connected with the shell and tube heat exchanger through the four-way valve, the economizer is connected with the compressor, and the electromagnetic valve is respectively connected with the economizer and the shell and tube heat exchanger;

the atomization mechanism is arranged on the front side of the air inlet direction of the fin heat exchanger and used for atomizing and spraying water to the front side area of the air inlet direction of the fin heat exchanger.

2. The indirect evaporative air-source heat pump apparatus of claim 1, wherein the four-way valve comprises a first port, a second port, a third port and a fourth port, the outlet port of the compressor is connected to the first port, the inlet port of the compressor is connected to the fourth port, the second port is connected to the finned heat exchanger, and the third port is connected to the shell and tube heat exchanger.

3. The indirect evaporative air-source heat pump apparatus of claim 1, wherein the atomizing mechanism comprises a water baffle packing, an atomizing nozzle, and a water pump;

the water retaining filler is arranged on the front side of the air inlet direction of the fin heat exchanger and can be opened or closed along a preset direction;

the water pump is connected with the atomizing nozzle, the water pump delivers water to the atomizing nozzle when the water pump is in an open state, and the atomizing nozzle sprays atomized water to the front side area in the air inlet direction of the fin heat exchanger.

4. The indirect evaporative air-source heat pump apparatus of claim 3, wherein the water-retaining filler is a polymeric material water-retaining filler or a wet-curtain paper water-retaining filler.

5. The indirect evaporative air-source heat pump apparatus of claim 3, further comprising a transmission mechanism, wherein the transmission mechanism is connected to the water-blocking filler, and the transmission mechanism is used for driving the water-blocking filler to rotate along a preset direction.

6. The indirect-evaporation air-source heat pump device of claim 3, wherein the atomization mechanism further comprises a water softening treatment device connected to the water pump.

7. The indirect evaporative air-source heat pump apparatus of claim 6, further comprising a second expansion valve, wherein the economizer, the second expansion valve, the solenoid valve, and the shell-and-tube heat exchanger are connected in sequence.

8. The indirect evaporative air-source heat pump apparatus of claim 1, further comprising a fan.

9. The indirect evaporative air-source heat pump apparatus of claim 1, further comprising a one-way valve assembly disposed in the communication conduit between the finned heat exchanger and the economizer.

10. The indirect evaporative air-source heat pump apparatus of claim 9, wherein the one-way valve assembly comprises a first one-way valve and a second one-way valve;

the communication pipeline between the fin heat exchanger and the economizer comprises a first communication pipeline and a second communication pipeline, the first check valve is arranged on the first communication pipeline, the second check valve is arranged on the second communication pipeline, and the second communication pipeline is arranged at the bottom of the fin heat exchanger.

Images