CN215337211U

CN215337211U - Efficient ice melting device of air energy heat pump

Info

Publication number: CN215337211U
Application number: CN202121443913.2U
Authority: CN
Inventors: 韦杰; 舒仁君
Original assignee: Cardiff Co Ltd
Current assignee: Cardiff Co Ltd
Priority date: 2021-06-28
Filing date: 2021-06-28
Publication date: 2021-12-28
Anticipated expiration: 2031-06-28

Abstract

The utility model provides an efficient ice melting device of an air energy heat pump, which comprises a chassis and a coil pipe fixedly arranged on the chassis through a pipe clamping plate, wherein the coil pipe is arranged at the lower side of an evaporator; the coiling direction of the coil pipe is consistent with the geometric shape of the cross section of the bottom of the evaporator; the coil pipe comprises a refrigerant inlet and a refrigerant outlet which are arranged at the same side; the refrigerant inlet is communicated with the outlet end of the condenser; the refrigerant outlet is communicated with the high-pressure end of the refrigerant throttling element; more than one first drainage hole is formed in the bottom of the base plate; the utility model utilizes the condensation waste heat source in the process of 'secondary supercooling' before throttling, and the released low-temperature heat is used for uninterruptedly melting ice and heating the evaporator chassis, thereby improving the energy efficiency of a heat pump, having stronger low-temperature adaptability, and having the characteristics of reliable ice melting of the chassis, safe and simple technical means, high efficiency and energy saving.

Description

Efficient ice melting device of air energy heat pump

Technical Field

The utility model relates to an efficient ice melting device of an air energy heat pump, and belongs to the technical field of air conditioner refrigeration and heating.

Background

When the air energy heat pump in the environment with low temperature, high humidity and the like is used for heating, the surface of the evaporator is easy to frost and appears periodically, and in severe cases, the air energy heat pump needs to be defrosted once every dozens of minutes, and the defrosting process is called as a primary defrosting process in the industry. A large amount of frost is melted into liquid water which flows down from the evaporator and is collected at the bottom of the evaporator and in the water pan. In order to meet the requirement of air flow organization circulation heat exchange, the chassis becomes a part of the air duct maintenance structure and is relatively closed. In the flowing process of the fluid, the fluid is influenced by the surface tension of the fluid and the movement viscosity force of the fluid, and a detention process exists on a contact surface. If the air-source heat pump cannot flow away in time, the evaporator chassis area is easy to freeze again, and the heating operation of the heat pump is seriously influenced by the vicious cycle, namely the water receiving chassis needs to be manually deiced when being seriously frozen, so that the air-source heat pump can normally heat and operate. The problem is most prominent in the field of small air energy heat pumps due to the structure. In order to overcome the problem of icing at the bottom of an evaporator and a chassis, the technical measures of a heating belt ice melting method, a hot gas bypass method and the like are commonly used in the industry.

The 'tracing band ice melting method' is that an electric tracing band is coiled on the edge of the chassis close to the lower part of an evaporator, the method adopts 'linear' heating in the accurate temperature control and heating mode, the starting and closing time is difficult to grasp, either the ice melting is incomplete or the energy consumption of the ice melting is large, and the reliability of the anti-icing is poor. Direct de-icing of the heat tracing band also presents a safety risk of electrical leakage.

The method of the hot gas bypass method is that a U-shaped steam heating coil is arranged along the part of a water receiving disc contacted with the lower end of an evaporator, a part of high-temperature steam which is shunted from a high-pressure section of a compressor passes through the U-shaped steam heating coil, and the high-temperature high-pressure refrigerant steam is used as a heat source for defrosting and deicing the chassis. This approach requires the addition of specialized hot gas bypass solenoid valves and system components, is costly, and also requires complex logic control programs. The heat source of the refrigerant with high temperature and high pressure is used for defrosting by sacrificing part of the available condensation heat at high temperature, so that the efficiency of the heat pump is reduced. The methods are usually limited by defrosting conditions, work in intervals, and are complex in system and logic control, so that the problems of partial icing or incomplete ice melting and the like frequently occur. In view of some limitations of the conventional technology at present, how to ensure reliable secondary defrosting, and also achieve the purposes of energy conservation, safety, high efficiency, simple technical means and the like is a problem to be researched and overcome in all air conditioning fields, particularly in the technical field of air energy heat pumps. The utility model can effectively overcome the series of defects (such as poor reliability, no energy conservation, complex control and realization process, high manufacturing cost and the like) of the secondary defrosting process of the existing evaporator.

SUMMERY OF THE UTILITY MODEL

The utility model provides an efficient ice melting device of an air energy heat pump, which adopts a low-temperature heat source to heat and melt ice, utilizes a normal-temperature normal-pressure low-temperature refrigerant condensed by a condenser to continuously release heat and melt ice when flowing through a coil pipe at the bottom of an evaporator, actually carries out an uninterrupted 'secondary supercooling' process on the refrigerant, increases the heat absorption capacity of the evaporator, has reliable ice melting on a chassis, and has safe, simple and efficient technical means.

In order to solve the technical problems, the utility model adopts the technical scheme that:

the utility model provides a high-efficient ice-melt device of air-source heat pump, its includes the chassis and passes through the fixed coil pipe that sets up on the chassis of pipe strap, the coil pipe sets up in the evaporimeter downside.

The coiling direction of the coil pipe is consistent with the geometric shape of the cross section of the bottom of the evaporator;

the coil pipe comprises a refrigerant inlet and a refrigerant outlet which are arranged at the same side;

the refrigerant inlet is communicated with the outlet end of the condenser;

the coil pipe refrigerant outlet is communicated with the refrigerant throttling element high-pressure end;

more than one first drainage hole is formed in the bottom of the base plate;

the pipe clamping plate is provided with more than one second drain hole.

Furthermore, more than one side water drainage hole is arranged on the side edge of the chassis.

Further, the spacing between the side-by-side runs of the coil is slightly less than the width of the cross-section of the evaporator, and the working surface of the coil effectively covers the cross-section of the evaporator.

Furthermore, the coil pipe refrigerant inlet can be communicated with the outlet end of the liquid storage tank or the outlet end of the main loop of the air-supply enthalpy-increasing plate heat exchanger.

Furthermore, the pipe clamping plate is fixed on the chassis through self-tapping screws.

Adopt the produced beneficial effect of above-mentioned technical scheme to lie in:

the utility model utilizes the condensation heat of secondary supercooling to release heat to melt ice reliably, the bottom cross section of the evaporator is positioned right above the coil pipe, and the working surface effectively covers the bottom cross section of the evaporator, so that the ice melting is accurate, the ice melting is complete, and no dead angle exists. The cross section area at the bottom of the evaporator has the lowest temperature, the large risk of icing and the large amount of defrosted water. As long as the host machine is in a heating running state, the heat released by using the condensation heat through secondary supercooling can be continuously utilized, and the continuous low-temperature heat source always maintains the defrosting water level and the liquid water state of the evaporator chassis to be discharged without being influenced by the defrosting and deicing logic control condition.

The utility model has safe and simple technical means, does not need electric heating auxiliary equipment, does not need to bypass a high-temperature electromagnetic valve and the like and is specially provided with a set of 'secondary defrosting' system and an actuating mechanism. The utility model only utilizes the condensation waste heat for 'secondary supercooling' to release heat, utilizes the condensation waste heat as a normal-temperature low-temperature heat source as an evaporator chassis ice melting heat source, does not need a special electromechanical execution unit and a defrosting control unit, and only bypasses the medium-pressure normal-temperature liquid refrigerant before throttling to a low-temperature area of the cross section at the lower end of the evaporator. The main machine is in heating state, the temperature of the bottom plate of the evaporator at the cross section of the lower end of the evaporator can be maintained to be higher than 0 ℃ all the time, the liquid water in the low-temperature area can be ensured not to be frozen and can flow out, the process is summarized into the process of refrigerant natural property heating, and special electromagnetic valves and other execution elements and complex logic control processes are not needed.

The utility model adopts the low-temperature heat source for melting ice and the secondary supercooling of the refrigerant, and the system is efficient and energy-saving. After the heat of the high-temperature and high-pressure refrigerant gas is released in the condenser, a gas-liquid phase change process is carried out, the cooled refrigerant is in a medium-pressure normal-temperature liquid state, and the temperature of the liquid refrigerant is about 35-40 ℃ and far higher than the ice water phase change temperature by 0 ℃. But still belongs to a low-temperature heat source and can not be directly used for heating hot water per se. The defrosting heat source is derived from the condensed refrigerant liquid, so that the refrigerant is condensed again in the chassis defrosting process, and the refrigerant liquid subjected to secondary supercooling is subjected to secondary condensation after being subjected to pressure and temperature reduction again before being throttled. For the 'air-supply enthalpy-increasing system', the 'primary supercooling' process of the economizer is performed before the air-supply enthalpy-increasing system enters the coil pipe, the heat exchange temperature difference of the refrigerant in the evaporator is further improved after the coil pipe at the bottom of the evaporator is detoured to melt ice and release heat, the liquid refrigerant at normal temperature and medium pressure is cooled and decompressed by 'secondary supercooling', the enthalpy difference before the refrigerant is throttled is increased, the mass flow of the refrigerant in the evaporator is increased, and more refrigerant is evaporated in the evaporator. In other words, the thermal efficiency of the entire unit is actually improved. Under the low-temperature working condition, compared with a system without the secondary supercooling, the efficiency is obviously improved, and the two purposes are achieved. As long as the host machine runs in a heating state, the heating cycle process is a normal cycle process for stably releasing heat, does not need any control, is continuous and uninterrupted, does not need to increase any electromechanical execution equipment, is simple and reliable, and is efficient and energy-saving.

Drawings

FIG. 1 is a schematic top view of the present invention;

FIG. 2 is a schematic sectional view of the structure of the present invention A-A;

FIG. 3 is a pressure-enthalpy diagram of a coil condensation heat chassis ice melting plus economizer "secondary subcooling" refrigerant system of the present invention;

the cooling system comprises a base plate 1, a base plate 101, side drain holes 102, a first drain hole 201, a second drain hole 2, a pipe clamping plate 3, a coil pipe 301, a refrigerant inlet 302, a refrigerant outlet 4, an evaporator 5 and self-tapping screws.

Detailed Description

The utility model is further described below with reference to the accompanying drawings.

As shown in the attached drawings 1-3, the embodiment provides a high-efficiency ice melting device for an air-source heat pump, which comprises a chassis 1 and a coil pipe 3 fixedly arranged on the chassis 1 through a pipe clamping plate 2, wherein the coil pipe 3 is arranged at the lower side of an evaporator 4, and the pipe clamping plate 2 is fixed on the chassis 1 through self-tapping screws; the coiling direction of the coil 3 is consistent with the geometric shape of the cross section of the bottom of the evaporator 4; the coil pipe 3 comprises a refrigerant inlet 301 and a refrigerant outlet 302 which are arranged at the same side; the refrigerant inlet 301 is communicated with the outlet end of the condenser, the refrigerant inlet 301 of the coil 3 can also be communicated with the outlet end of the liquid storage tank or the outlet end of the main loop of the air-supply enthalpy-increasing plate heat exchanger, and the refrigerant outlet 302 of the coil 3 is communicated with the high-pressure end of the refrigerant throttling element; more than one first drainage hole 102 is arranged at the bottom of the chassis 1; the pipe clamping plate 2 is provided with more than one second drain hole 201, and the side of the chassis 1 is provided with more than one side drain hole 101.

The spacing between the side-by-side tubes of the coil 3 is slightly less than the width δ of the cross-section of the evaporator 4, and the working surface of the coil 3 effectively covers the cross-section of the evaporator 4, ensuring that the bottom cross-section of the evaporator 4 completely covers the coil 3 and effectively transfers heat. According to the utility model, the condensation waste heat is supercooled for the second time to release heat for melting ice, the cross section of the bottom of the evaporator 4 is positioned right above the coil pipe 3, and the working surface effectively covers the cross section of the bottom of the evaporator 4, so that the ice melting is accurate, the ice melting is complete, and no dead angle exists. The cross-sectional area at the bottom of the evaporator 4 has the lowest temperature, the risk of icing is high, and the amount of defrosted water is large. As long as the main machine is in a heating running state, the condensation waste heat can be used for releasing heat through secondary supercooling, and the condensation waste heat low-temperature level heat source is used for maintaining the defrosting water level and liquid water state discharge of the chassis area of the evaporator 4 without being influenced by defrosting and deicing logic control conditions.

The specific working process and principle are as follows:

the utility model relates to a method for using condensation waste heat for secondary supercooling to release heat during heating of a heat pump, and using a low-temperature heat source of the condensed refrigerant waste heat as a heat source for melting ice on a chassis of an evaporator 4, wherein the temperature of the low-temperature heat source is far higher than the phase change temperature of ice water by 0 ℃ although the temperature is at normal temperature, and the low-temperature heat source still belongs to the low-temperature heat source. At a medium-pressure normal-temperature outlet end (including a liquid storage tank outlet end or an outlet end of a main loop of the air-supply enthalpy-increasing plate heat exchanger) of the condenser 4, a liquid refrigerant enters the coil 3 from the refrigerant inlet 301 to make a circle of detour, is cooled and decompressed for the second time for secondary supercooling, and then flows out of a refrigerant outlet 302 of the coil 3 to a high-pressure end of the throttling element. The normal temperature refrigerant waste heat in the coil pipe 3 and the easy icing area of the chassis of the evaporator 4 all participate in the heat exchange process through several heat exchange modes of heat conduction, convection and radiation, so that the water in the easy icing area at the bottom of the evaporator 4 exists in a liquid state all the time, and is finally discharged through the side water discharge holes 101 arranged on the upper side of the chassis 1 and the first water discharge holes 102 on the bottom surface of the chassis. The refrigerant is cooled for the second time in the coil 3 and then enters the high-pressure end of the throttling element through the refrigerant outlet 302 of the coil 3. In the circulation heating process of the low-temperature refrigerant heat source, the refrigerant is naturally subcooled for the second time in the coil pipe 3, and the pressure and the temperature of the refrigerant are further reduced before the refrigerant is throttled, for example, the temperature of the refrigerant is reduced before heat exchange. For the 'air-supply enthalpy-increasing system', the 'primary supercooling' process of the economizer is performed before the refrigerant enters the coil 3 assembly, the refrigerant bypasses the evaporator 4 to melt ice and release heat, the heat exchange temperature difference of the refrigerant in the evaporator 4 is further improved, the normal-temperature medium-pressure liquid refrigerant is cooled and decompressed by 'secondary supercooling', the enthalpy difference before throttling of the refrigerant is increased, the mass flow of the refrigerant in the evaporator is increased, and more refrigerant is evaporated in the evaporator. In other words, the thermal efficiency of the entire unit is actually improved. Under low temperature conditions, the efficiency improvement is significant over systems that do not experience such "secondary subcooling".

The utility model releases heat by using ' condensation waste heat ' secondary supercooling ', uses the low-temperature heat released by using the condensed refrigerant waste heat for the deicing and heating of the evaporator chassis, is actually a ' secondary supercooling ' process of the refrigerant before throttling, improves the energy efficiency of the heat pump, and has stronger low-temperature adaptability. If the air energy heat pump system is provided with the air-supply enthalpy-increasing air energy, before entering the bypassing coil pipe 3, the refrigerant is subjected to a primary supercooling process by the economizer, and after bypassing the coil pipe 3 to release heat, the liquid refrigerant is subjected to pressure reduction and temperature reduction again to be regarded as secondary supercooling, so that the temperature and the pressure before the refrigerant is throttled are reduced, the mass flow of the refrigerant entering the evaporator for evaporation is increased, and the fact that more heat is absorbed from the air and enters the compressor for compression is meant; the secondary supercooling of the refrigerant increases the heating capacity of the heat pump system and improves the energy efficiency of the heat pump. The increased heating gauge pressure-enthalpy is shown in fig. 3: from the pressure-enthalpy diagram, it can be seen that the traditional vapor-filling enthalpy-increasing method is that the liquid refrigerant is subcooled for the first time in the condensation process from 4 points to 5 points; after the bypassing U-shaped copper pipe assembly 3 releases partial condensation heat at the bottom of the evaporator, the refrigerant is secondarily subcooled from 5 points to 6 points. The enthalpy value at 6/point is: h6/= [ (Ga-Gb) × (h1-h5) ]/Gb; ga is the mass flow of the refrigerant after secondary supercooling; gb secondary pre-subcooling refrigerant mass flow; increased heating capacity of the system: q = (Ga-Gb) (-h 6/-h5 /).

The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the utility model. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. The efficient ice melting device for the air energy heat pump is characterized by comprising a chassis (1) and a coil (3) fixedly arranged on the chassis (1) through a pipe clamping plate (2), wherein the coil (3) is arranged on the lower side of an evaporator (4);

the coiling direction of the coil (3) is consistent with the geometric shape of the cross section of the bottom of the evaporator (4);

the coil pipe (3) comprises a refrigerant inlet (301) and a refrigerant outlet (302) which are arranged on the same side;

the refrigerant inlet (301) is communicated with the outlet end of the condenser;

the refrigerant outlet (302) is communicated with a high-pressure end of the refrigerant throttling element;

more than one first drainage hole (102) is formed in the bottom of the chassis (1);

the pipe clamping plate (2) is provided with more than one second drain hole (201).

2. The efficient ice melting device of the air-energy heat pump according to claim 1, characterized in that more than one side drain hole (101) is arranged on the side of the chassis (1).

3. The efficient deicing device for the air-energy heat pump according to claim 1, characterized in that the spacing between the side-by-side pipelines of the coil (3) is slightly smaller than the width of the cross section of the evaporator (4), and the working surface of the coil (3) effectively covers the cross section of the evaporator (4).

4. The efficient ice melting device of the air-source heat pump as claimed in claim 1, wherein the refrigerant inlet (301) is further communicated with an outlet end of the liquid storage tank or an outlet end of the main loop of the air-supplying enthalpy-increasing plate heat exchanger.

5. The efficient ice melting device for the air-source heat pump according to claim 1, wherein the pipe clamping plate (2) is fixed on the chassis (1) through self-tapping screws (5).