Ice energy source ice stab heat melting heat pump unit

Abstract

The application relates to the technical field of temperature regulation, and particularly discloses an ice-energy heat source ice-stab heat-melting heat pump unit. The ice-stab heat-melting heat pump unit comprises an ice-stab evaporator, a gravity liquid separator, a heat pump compressor, a gas storage separator and a flash expansion device. The ice-stab evaporator comprises an ice-water side shell pipe body and a working medium pipeline unit. The ice-stab evaporator is internally provided with a cavity. The side wall of the ice-stab evaporator is provided with a cold water inlet and an ice-water outlet. The working medium pipeline unit comprises an electrolytic layer ice-stab pipe. The outer wall of the electrolytic layer ice-stab pipe is fixedly provided with a plurality of protrusions. The gravity liquid separator is provided with a first air inlet, a first air outlet, a first liquid outlet and a first liquid inlet. The heat pump compressor is provided with an air suction port, an air exhaust port and a compression port. The cooling condenser is provided with a third air inlet, a second liquid outlet, a hot water return port and a hot water outlet. The gas storage separator is provided with a second air inlet, a second air outlet and an oil discharge port. The ice-stab heat-melting heat pump unit can improve the utilization rate of low-temperature energy.

Description

Technical Field

[0001] This invention relates to the field of temperature control technology, specifically to an ice energy heat source ice spike thermal fusion heat pump unit. Background Technology

[0002] As living standards continue to improve, people's demand for heating in winter and cooling in summer is constantly increasing. Taking heating as an example, traditional heating mainly relies on fossil fuels such as coal and natural gas. When coal and natural gas are burned, a large amount of black carbon and carbon dioxide are emitted. Carbon dioxide releases carbonate ions and hydrogen ions into water vapor, which are condensation nuclei. This leads to mild winter weather and excessive water vapor, affecting the diffusion of carbon particles into the atmosphere and forming smog. This results in a decrease in environmental quality and affects human health.

[0003] Later, as people's requirements for ecological environment and green and low-carbon development increased, heat pumps emerged. They adopt a low-carbon and environmentally friendly heating method that combines the absorption of low-temperature potential energy with a low-heat source heat pump. In winter, they efficiently absorb the water vapor energy of smog by using the phase change of cold water solution with a small temperature difference for heat transfer. In summer, they have high negative pressure evaporation, low water temperature cooling, and long-lasting cooling of waste heat from air conditioning. Therefore, in winter, there is no need to rely on fossil energy such as coal and natural gas, thereby reducing the emission of black carbon and carbon dioxide. In summer, the power consumption will also be reduced. Reduced energy consumption is also beneficial to environmental protection.

[0004] A heat pump includes an evaporator for heat exchange. Current evaporators contain pipes through which a working fluid (a low-temperature solution) flows. Another solution lies outside the pipes. Taking heating as an example, heat from the other solution is transferred to the working fluid, raising its temperature and thus utilizing the heat. However, during heat exchange, heat is first transferred to the sidewalls of the pipes and then from there to the other solution. While this achieves heat exchange between the two solutions, current pipe surfaces are smooth, limiting the contact area between the pipes and the other solution. Furthermore, since heat pumps primarily utilize low-temperature potential energy, the temperature difference between the working fluid and the other solution is small. Therefore, the limited contact area results in a limited heat transfer rate and relatively low utilization of the low-temperature potential energy of the other solution. Summary of the Invention

[0005] The present invention aims to provide an ice energy heat source ice spur heat pump unit to improve the utilization rate of low-temperature potential energy.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: an ice energy heat source ice spike thermal fusion heat pump unit, including an ice spike evaporator, a gravity liquid separator, a heat pump compressor, a gas storage separator, and a flash expansion device. The ice spike evaporator includes an ice water side shell tube and a working fluid pipeline unit. The ice water side shell tube is provided with a cavity, and the side wall of the ice water side shell tube is provided with a cold water inlet and an ice water outlet. The working fluid pipeline unit includes an electrolytic layer ice spike tube, which is located in the cavity. Several protrusions are fixed on the outer wall of the electrolytic layer ice spike tube.

[0007] The gravity liquid separator is provided with a first air inlet, a first air outlet, a first liquid outlet, and a first liquid inlet. The heat pump compressor is provided with an air intake, an air exhaust, and a pressure port. The electrolytic layer ice spike tube is connected to the first air inlet, the first air outlet is connected to the air intake, the first liquid outlet is connected to the end of the electrolytic layer ice spike tube away from the first air inlet, and the first liquid inlet is simultaneously connected to the end of the electrolytic layer ice spike tube away from the first air inlet and the flash expansion device.

[0008] The cooling condenser is equipped with a third air inlet, a second liquid outlet, a hot water return inlet, and a hot water outlet. The gas separator is equipped with a second air inlet, a second air outlet, and an oil drain outlet. The exhaust port is connected to the second air inlet, and the pressure port is also connected to the flash expansion device. The second air outlet is simultaneously connected to the end of the electrolytic layer ice spike tube near the first air inlet and the third air inlet, and a throttling pipe is provided between the second air outlet and the electrolytic layer ice spike tube. The second liquid outlet is connected to the flash expansion device.

[0009] The beneficial effects of this plan are:

[0010] 1. Compared with the pipes in ordinary evaporation devices, the electrolytic layer ice spike tube in this scheme has protrusions on its surface. When cold water with a lower temperature enters the ice water side shell tube, it effectively increases the contact area with the cold water, so that the heat in the cold water can be quickly transferred into the working fluid through the electrolytic layer ice spike tube. During the test, it was found that the temperature and enthalpy of the cold water after passing through the electrolytic layer ice spike tube decreased, becoming subcooled water. This indicates that the heat utilization rate is much higher than that of existing heat pumps. That is, this scheme effectively improves the heat transfer speed and utilization rate.

[0011] 2. In this scheme, the working fluid in the electrolytic layer ice spike tube absorbs heat and evaporates into an unsaturated gas-liquid mixture. This mixture then enters a gravity-liquid separator for gas-liquid separation to remove the saturated working fluid gas. The gas is then boosted by a heat pump compressor to a relatively high-pressure working fluid vapor and transported into a gas storage separator. The second outlet of the gas storage separator is connected to the electrolytic layer ice spike tube. When the ambient temperature decreases or the ice spike evaporator is used for an extended period, resulting in a thick ice layer forming on the outside of the electrolytic layer ice spike tube, the high-pressure working fluid vapor from the gas storage separator can be introduced into the electrolytic layer ice spike tube. This raises the temperature of the sidewall of the electrolytic layer ice spike tube, causing the ice adhering to the outer wall to melt. Therefore, the ice layer on the outer wall of the electrolytic layer ice spike tube can detach from the tube, preventing the cold water entering the ice-water side shell from contacting the tube. This ensures that the low-temperature potential energy in the cold water can be transferred to the working fluid in the electrolytic layer ice spike tube more quickly and efficiently.

[0012] Furthermore, a gravity differential working fluid pump is provided between the first liquid outlet and the electrolytic layer ice spike tube, and the first liquid outlet is higher than the end of the electrolytic layer ice spike tube that is far away from the first air inlet.

[0013] The beneficial effects of this scheme are as follows: the gravity difference working fluid pump in this scheme can pressurize the working fluid, promote the flow of the working fluid into the electrolytic layer ice spike tube, and make the working fluid enter the electrolytic layer ice spike tube more uniformly and at a constant speed.

[0014] Furthermore, the flash expansion device is equipped with a secondary throttling valve, and the end of the electrolytic layer ice spike tube away from the first air inlet and the first liquid inlet are both connected to the secondary throttling valve.

[0015] The beneficial effects of this scheme are as follows: the high-pressure working fluid enters the flash expansion device from the cooling condenser and is throttled and flashed into a medium-pressure working fluid. Since the flash expansion device is connected to the electrolytic layer ice spike tube and the gravity liquid separator through a secondary throttling valve, the medium-pressure working fluid has two supply modes: one is to enter the electrolytic layer ice spike tube, which is the traditional direct expansion supply mode; the other is to enter the gravity liquid separator to form a high-efficiency heat transfer mode of gravity supply and gravity differential working fluid pump circulation turbulence.

[0016] In the other liquid supply mode, the medium-pressure working fluid enters the working fluid distribution pipe only under the action of gravity supply and gravity differential working fluid pump. Therefore, the working fluid has a faster flow rate and is more likely to form turbulence in the working fluid distribution pipe and the electrolysis layer ice spike pipe. This ensures that more working fluid can contact the side wall of the electrolysis layer ice spike pipe, thereby improving the efficiency of heat transfer into the working fluid, and at the same time improving the heat exchange rate and heat utilization rate.

[0017] Furthermore, a baffle plate is fixed inside the chilled water side shell tube, which divides the inner cavity of the chilled water side shell tube into a cold water inlet shell and a chilled water outlet shell, which are connected. The cold water inlet and the chilled water outlet are connected to the cold water inlet shell and the chilled water outlet shell, respectively. The working fluid return pipe and the working fluid distribution pipe are located inside the cold water inlet shell and the chilled water outlet shell, respectively, and the electrolytic layer ice spike pipe penetrates the baffle plate.

[0018] The beneficial effects of this scheme are as follows: the flow plate can block the cold water in the chilled water side shell tube, thereby enabling the cold water entering the cold water inlet shell to form turbulence, which promotes the contact between the chilled water away from the electrolysis layer ice spike tube and the electrolysis layer ice spike tube; similarly, the chilled water entering the chilled water outlet shell from the cold water inlet shell can also form turbulence, which can also promote the contact between the chilled water and the electrolysis layer ice spike tube, thereby enabling more efficient utilization of the heat in the cold water and further improving the heat utilization rate.

[0019] Furthermore, a thermal resistance defroster is installed inside the ice water side shell tube.

[0020] The beneficial effects of this solution are as follows: When the evaporator needs to be shut down after use, if the ambient temperature is too low, the liquid inside the ice-water side shell and tube will freeze. The thermal resistance defroster in this solution can heat the solution inside the ice-water side shell and tube, melting the ice and allowing the evaporator to start up and operate normally.

[0021] Furthermore, an ultrasonic transducer is installed inside the cold water inlet tank.

[0022] The beneficial effects of this scheme are as follows: In this scheme, cold water forms subcooled water after passing through the electrolytic layer ice spike tube. Under the action of the ultrasonic transducer, the subcooled water generates ice nuclei and continues to freeze, causing the enthalpy value to decrease and the temperature change to slow down. The ice nuclei crystals grow, releasing solidification heat and forming vertical ice spikes on the outer wall of the electrolytic layer ice spike tube. Because some of the subcooled water undergoes direct turbulent flow on the outer wall of the electrolytic layer ice spike tube, the growing ice spikes break off and detach from the electrolytic layer ice spike tube, forming an ice-water solution with the subcooled water. Unlike ordinary cold water, the ice-water solution can further absorb heat from the air to melt and form cold water. This cold water can then be used as a low-temperature potential energy heat source and re-entered into the ice-water side shell tube. Through heat exchange with the working fluid in the electrolytic layer ice spike tube, the heat can be utilized. In other words, the evaporator in this scheme can utilize heat from the air by forming an ice-water solution, instead of being limited to using heat from the external water.

[0023] Secondly, ice water needs to absorb more heat from the air before the ice in it melts and it completely turns into cold water. Therefore, compared to cold water, the same amount of ice water can absorb more heat, further improving the speed and efficiency of heat utilization. Finally, because ice water can maintain a lower temperature for a longer period of time, the temperature difference between ice water and the air is greater than that of cold water, allowing heat to be transferred to the ice water more quickly, thus further improving the speed of heat utilization.

[0024] Furthermore, the cross-sectional area of ​​the end of the protrusion furthest from the electrolytic layer ice spike tube is smaller than the cross-sectional area of ​​the section closest to the electrolytic layer ice spike tube.

[0025] The beneficial effects of this solution are as follows: the protrusions in this solution form gaps that allow cold and ice water to flow through, thereby increasing the contact area with cold and ice water while also preventing the formation of dead corners between the protrusions that would trap and prevent the flow of cold and ice water.

[0026] Furthermore, all the protrusions are divided into several groups of ice spikes distributed sequentially along the axial direction of the ice spike tube in the electrolysis layer, with the protrusions of adjacent groups of ice spikes being staggered.

[0027] The beneficial effects of this solution are as follows: This solution further enables gaps to be formed between adjacent protrusions for the flow of cold water and ice water, allowing the cold water and ice water to come into more full contact with the outer wall of the electrolytic layer ice spike tube, thereby improving the heat utilization efficiency.

[0028] Furthermore, a return steam control valve is installed between the first air inlet and the electrolytic layer ice spike pipe.

[0029] The beneficial effects of this solution are: the return steam electronic control valve can better control the flow of the working fluid between the electrolytic layer ice spike tube and the gravity liquid separator. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the structure of an embodiment of the present invention;

[0031] Figure 2 for Figure 1 A three-dimensional view of the ice spike tube in the middle electrolysis layer. Detailed Implementation

[0032] The following detailed description illustrates the specific implementation method:

[0033] The reference numerals in the accompanying drawings include: ice spike evaporator LZ, cold water inlet tank Z1, ice water outlet tank Z2, working fluid inlet Z3, working fluid return gas outlet Z4, working fluid separator ZA, working fluid return gas pipe ZB, ice water side shell ZG, electrolytic layer ice spike tube ZK, thermal resistance defroster ZR, ultrasonic transducer ZV, baffle plate ZW, gravity differential working fluid pump LG, suction port G1, discharge port G2, gravity liquid separator LC, first air inlet C1, first air outlet C2, first liquid outlet C3, first liquid inlet... Port C4, Heat pump compressor LQ, Suction port Q1, Exhaust port Q2, Pressure port Q3, Gas separator LY, Second air inlet Y1, Second air outlet Y2, Oil outlet Y3, First throttling pipe YY, Cooling condenser LR, Third air inlet R1, Second liquid outlet R2, Hot water return port R3, Hot water outlet R4, Flash expansion device LS, Medium pressure outlet SZ, Return steam control valve CW, Hot melt control valve YW, Secondary throttling valve SP, Second throttling pipe SJ, Gravity control valve SW, Direct expansion control valve SR.

[0034] Example

[0035] Ice energy heat source ice spike thermal fusion heat pump unit, such as Figure 1 and Figure 2 As shown, the device includes an ice spike evaporator LZ, a gravity liquid separator LC, a heat pump compressor LQ, a gas storage separator LY, a flash expansion device LS, and a gravity differential working fluid pump LG. The ice spike evaporator LZ includes an ice water side shell tube zg and several working fluid pipeline units. The ice water side shell tube zg has a cavity, and a baffle plate zw is vertically installed in the cavity. The baffle plate zw divides the cavity into a cold water inlet shell Z1 on the left and an ice water outlet shell Z2 on the right. A gap is formed between the baffle plate zw and the inner wall of the ice water side shell tube zg to allow liquid to flow from the cold water inlet shell Z1 into the ice water outlet shell Z2. The left end of the chilled water side shell tube Zg is provided with a chilled water inlet connected to the chilled water inlet shell Z1, and the right end of the chilled water side shell tube Zg is provided with a chilled water outlet connected to the chilled water outlet shell Z2. In actual implementation, both the chilled water inlet and the chilled water outlet are connected to pipes, which are used to introduce chilled water into the chilled water inlet shell Z1 and to discharge chilled water out of the chilled water outlet shell Z2, respectively.

[0036] A thermal resistance defroster zr is installed inside the cavity. The thermal resistance defroster zr passes laterally through the baffle plate zw and is used to defrost the liquid in the cold water inlet tank Z1 and the ice water outlet tank Z2 on the right side after they have completely frozen. An ultrasonic transducer zv is installed on the top of the cold water inlet tank Z1. Specifically, in this embodiment, both the thermal resistance defroster zr and the ultrasonic transducer zv are existing devices, and their structure and installation method are the same as those in the prior art. They will not be described again in this embodiment.

[0037] Several working fluid piping units are distributed sequentially from front to back. Taking one working fluid unit as an example, the working fluid unit includes a working fluid return pipe zb, a working fluid distribution pipe za, and multiple electrolytic layer ice spike pipes zk. The working fluid return pipe zb and the working fluid distribution pipe za are located in the cold water inlet shell Z1 and the ice water outlet shell Z2, respectively. The multiple electrolytic layer ice spike pipes zk are distributed sequentially from top to bottom, with the left end of each of the multiple electrolytic layer ice spike pipes zk connected to the working fluid return pipe zb, and the right end passing through the baffle plate zw and connecting to the working fluid distribution pipe za. All the working fluid return pipes zb are connected, and the upper end of one of the working fluid return pipes zb passes through the top of the cold water inlet shell Z1 to form a working fluid return port; all the working fluid distribution pipes za are connected, and the lower end of one of the working fluid distribution pipes za passes through the bottom of the ice water outlet shell Z2 to form a working fluid inlet.

[0038] Specifically, in this embodiment, the surface of the electrolytic layer ice spike tube zk is integrally formed with several protrusions. All protrusions are divided into several protrusion groups, which are sequentially distributed along the axial direction of the electrolytic layer ice spike tube zk, with adjacent protrusion groups staggered. The cross-section of each protrusion is rhomboid, and the cross-sectional area of ​​the end of the protrusion furthest from the electrolytic layer ice spike tube zk is smaller than the cross-sectional area of ​​the end closest to the electrolytic layer ice spike tube zk, creating gaps between adjacent protrusions for the flow of cold water and ice water. The inner wall of the electrolytic layer ice spike tube zk is provided with several circumferential ridges. In this embodiment, these ridges are spiral-shaped. In actual implementation, the ridges can also extend along the axial direction of the electrolytic layer ice spike tube zk. The ridges can obstruct the flow of the working fluid, thereby promoting turbulence during the flow of the working fluid. This further promotes contact between different working fluids and the sidewall of the electrolytic layer ice spike tube zk, allowing direct heat exchange and increasing the heat exchange rate.

[0039] The structures of the gravity liquid separator LC, heat pump compressor LQ, gas separator LY, cooling condenser LR, flash expansion device LS, and gravity differential working fluid pump LG in this embodiment are the same as those in the prior art, and will not be described again in this embodiment. The gravity liquid separator LC is provided with a first air inlet C1, a first air outlet C2, a first liquid outlet C3, and a first liquid inlet C4. The first air inlet C1 is connected to the working fluid return air port, and a return steam control valve CW is provided between the first air inlet C1 and the working fluid return air port. The first liquid outlet C3 is connected to the working fluid distribution port. The gravity differential working fluid pump LG is located between the first liquid outlet C3 and the working fluid distribution port. Specifically, the gravity differential working fluid pump LG includes an inlet G1 and an outlet G2. The first liquid outlet C3 is connected to the inlet G1, and the working fluid distribution port is connected to the outlet G2.

[0040] The heat pump compressor LQ is equipped with an intake port Q1, an exhaust port Q2, and a pressure port Q3. The first exhaust port C2 is connected to the intake port Q1. The gas separator LY is equipped with a second intake port Y1, a second exhaust port Y2, and an oil drain port Y3. The exhaust port Q2 is connected to the second intake port Y1, and the oil drain port Y3 is connected to the intake port Q1. A first throttling pipe YY is provided between the oil drain port Y3 and the intake port Q1. The cooling condenser LR is equipped with a third intake port R1, a second liquid outlet R2, a hot water return port R3, and a hot water outlet R4. The hot water return port R3 is used to introduce hot water into the cooling condenser LR, and the hot water outlet R4 is used to discharge the heated hot water. The working fluid return port and the third intake port R1 are connected to the second exhaust port Y2 through a three-way pipe. A thermoelectric control valve YW is also provided between the working fluid return port and the second exhaust port Y2.

[0041] The second liquid outlet R2 is connected to the flash expansion device LS. Specifically, a second throttling pipe SJ is provided between the second liquid outlet R2 and the flash expansion device LS, connecting the second liquid outlet R2 and the flash expansion device LS through the second throttling pipe SJ. In this embodiment, both throttling pipes are corrugated. The flash expansion device LS is connected to a secondary throttling valve SP. The end of the secondary throttling valve SP away from the flash expansion device LS is connected to the first liquid inlet C4 and the working fluid inlet through a three-way pipe. A gravity-controlled electric valve SW is provided between the secondary throttling valve SP and the first liquid inlet C4, and a direct expansion electric valve SR is provided between the secondary throttling valve SP and the working fluid inlet. The flash expansion device LS is provided with a medium-pressure gas outlet SZ, which is connected to the pressure port Q3.

[0042] The specific implementation process is as follows:

[0043] The working fluid is located in the working fluid distribution pipe za, the electrolysis layer ice spike pipe zk, and the working fluid return pipe zb. In this embodiment, when the ice energy heat source ice spike thermal fusion heat pump unit is working, cold water enters the cold water inlet tank Z1 from the cold water inlet, forming turbulence in the cold water inlet tank Z1, and then enters the ice water outlet tank Z2 from the cold water inlet tank Z1, forming turbulence in the ice water outlet tank Z2, and finally being discharged from the ice water outlet.

[0044] Throughout the flow of cold water, it comes into contact with the electrolytic layer ice spike tube zk. The heat in the cold water is transferred to the working fluid in the electrolytic layer ice spike tube zk, causing the working fluid to evaporate into an unsaturated gas-liquid mixture, which eventually flows out from the working fluid return port. The cold water temperature decreases, forming subcooled water. Simultaneously with the introduction of cold water, the ultrasonic transducer zv is activated. Under the action of the ultrasonic transducer zv, ice nuclei form in the subcooled water at the tip of the protrusion furthest from the electrolytic layer ice spike tube zk. As time progresses, the ice nuclei crystals grow on the outer wall of the electrolytic layer ice spike tube zk, forming vertical ice spikes. As the length of the ice spikes increases, they break under the action of turbulence and flow with the subcooled water, eventually forming an ice-water solution.

[0045] Under the action of gravity differential working fluid pump LG and heat pump compressor LQ, the unsaturated gas-liquid mixture working fluid is discharged from the working fluid return port, passes through the return steam control valve CW, and enters the gravity liquid separator LC from the first air inlet C1 for gas-liquid separation to form a working fluid saturated with gas and liquid. Under the action of gravity differential working fluid pump LG, the working fluid enters the working fluid separator za from the working fluid inlet, and finally enters the electrolysis layer ice spike tube zk for heat exchange. The saturated working fluid gas enters the heat pump compressor LQ through the first outlet C2 and the intake Q1. Inside the heat pump compressor LQ, it performs work and is upgraded into high-pressure working fluid vapor. Then, it enters the gas separator LY through the second intake Y1 from the exhaust port Q2 of the heat pump compressor LQ to separate oil droplets from the high-pressure working fluid vapor. After the oil droplets are separated, the high-pressure working fluid vapor enters the pipe inside the cooling condenser LR through the second outlet Y2 and the third intake R1 to release high-temperature potential energy. In actual implementation, the water or gas that needs to be heated enters through the hot water return port R3, is heated by the high-pressure working fluid vapor, and is discharged from the hot water outlet R4 to achieve heating.

[0046] After releasing high-temperature potential energy, the high-pressure working fluid vapor condenses into a high-pressure working fluid liquid. This liquid exits through the second outlet R2 and enters the flash expansion device LS via the second throttling pipe SJ between R2 and SJ. As the high-pressure working fluid passes through SJ, it undergoes a throttling flash evaporation, forming a medium-pressure working fluid liquid and flash vapor. The flash vapor then enters the flash expansion device LS and exits through the medium-pressure outlet SZ. Finally, it enters the heat pump compressor LQ via the pressure port Q3, moving along with the saturated working fluid gas separated by the gravity liquid separator LC.

[0047] This embodiment includes two liquid supply modes: In the first mode, the medium-pressure working fluid enters the electrolytic layer ice spike tube zk through the working fluid inlet via the direct expansion solenoid valve SR, where it exchanges heat with cold water to utilize the low-temperature potential energy from the outside. In the second mode, the medium-pressure working fluid enters the gravity liquid separator LC through the first inlet C4 via the gravity solenoid valve SW, and then enters the working fluid distribution tube za under the action of gravity supply and gravity differential working fluid pump LG. Compared with the first mode, the second mode has a faster working fluid flow rate because the medium-pressure working fluid only enters the working fluid distribution tube za under the action of gravity supply and gravity differential working fluid pump LG. This makes it easier to form turbulence in the working fluid distribution tube za and the electrolytic layer ice spike tube zk, thus ensuring that more working fluid can contact the sidewall of the electrolytic layer ice spike tube zk, thereby improving the efficiency of heat transfer into the working fluid, and simultaneously improving the heat exchange rate and heat utilization rate. Furthermore, if any of the pumps, valves, or pipes in any of the above modes fail during actual implementation, rendering that mode unusable, another mode can be used to supply liquid to the point-level ice spike pipes to ensure the normal operation of the heat pump unit.

[0048] When the outside temperature is too low, causing the cold water in the ice-water side shell tube zg to freeze completely, or when the evaporator is shut down and the cold water in the ice-water side shell tube zg is completely frozen, the thermal resistance defroster zr is started first to heat the ice in the ice-water side shell tube zg, causing the ice to melt, thereby ensuring that the evaporator can be restarted and work normally.

[0049] When the ice layer outside the electrolytic layer ice spike tube zk is too thick, preventing the cold water from contacting the outer wall of the electrolytic layer ice spike tube zk, the return steam control valve CW is closed. The high-pressure working fluid steam is then introduced from the working fluid return port into the working fluid return pipe zb via the heat fusion control valve YW, and enters the electrolytic layer ice spike tube zk. This heats the side wall of the electrolytic layer ice spike tube zk, melting the part of the ice layer in contact with the electrolytic layer ice spike tube zk. This allows the ice layer to detach from the outer wall of the electrolytic layer ice spike tube zk and be carried away by the cold water, ensuring that the cold water can contact the outer wall of the electrolytic layer ice spike tube zk, thereby improving the speed and efficiency of heat utilization.

[0050] The above descriptions are merely embodiments of the present invention, and common knowledge such as specific technical solutions and / or characteristics are not described in detail here. It should be noted that those skilled in the art can make various modifications and improvements without departing from the technical solutions of the present invention, and these should also be considered within the scope of protection of the present invention. These modifications and improvements will not affect the effectiveness of the implementation of the present invention or the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

Claims

1. Ice energy source ice spike heat melting heat pump unit, characterized in that: The ice-stick evaporator comprises an ice-water side shell pipe body and a working medium pipeline unit, the ice-water side shell pipe body is internally provided with a cavity, the side wall of the ice-water side shell pipe body is provided with a cold water inlet and an ice-water outlet, and the working medium pipeline unit comprises an electrolytic layer ice-stick pipe. The gravity liquid separator is provided with a first gas inlet, a first gas outlet, a first liquid outlet and a first liquid inlet, the heat pump compressor is provided with a suction port, an exhaust port and a compression port, the electrolytic layer ice-stick pipe is communicated with the first gas inlet, the first gas outlet is communicated with the suction port, the first liquid outlet is communicated with one end of the electrolytic layer ice-stick pipe away from the first gas inlet, and the first liquid inlet is simultaneously communicated with the one end of the electrolytic layer ice-stick pipe away from the first gas inlet and the flash expansion device. The ice-stick heat melting heat pump unit further comprises a cooling condenser, the cooling condenser is provided with a third gas inlet, a second liquid outlet, a hot water return port and a hot water outlet, the hot water return port is used for guiding hot water into the cooling condenser, the hot water outlet is used for guiding the heated hot water out, the storage gas separator is provided with a second gas inlet, a second gas outlet and an oil discharge port, the exhaust port is communicated with the second gas inlet, and the compression port is also communicated with the flash expansion device. The ice-water side shell pipe body is fixedly provided with a baffle, the baffle divides the inner cavity of the ice-water side shell pipe body into a cold water inlet shell box and an ice-water outlet shell box, the cold water inlet shell box is communicated with the ice-water outlet shell box, and the cold water inlet shell box is provided with an ultrasonic vibrator.

2. The ice thermal source ice-spike thermal melting heat pump unit according to claim 1, characterized in that: The cross-sectional area of the protrusion away from the electrolytic layer ice-stick pipe is smaller than the cross-sectional area of the protrusion close to the electrolytic layer ice-stick pipe.

3. The ice thermal source ice-spike thermal melting heat pump unit according to claim 2, characterized in that: The first liquid outlet is provided with a gravity difference working medium pump, and the first liquid outlet is higher than the one end of the electrolytic layer ice-stick pipe away from the first gas inlet.

4. The ice thermal source ice-spike thermal melting heat pump unit according to claim 1, characterized in that: The flash expansion device is provided with a secondary throttling valve, and the one end of the electrolytic layer ice-stick pipe away from the first gas inlet and the first liquid inlet are both communicated with the secondary throttling valve.

5. The ice thermal source ice-spike thermal melting heat pump unit according to claim 4, characterized in that: The cold water inlet and the ice-water outlet are respectively communicated with the cold water inlet shell box and the ice-water outlet shell box, the working medium return gas pipe and the working medium distribution pipe are respectively located in the cold water inlet shell box and the ice-water outlet shell box, and the electrolytic layer ice-stick pipe penetrates through the baffle.

6. The ice thermal source ice-spike thermal melt heat pump chiller unit of claim 1, wherein: The ice-water side shell pipe body is provided with a thermal resistance thawing device.

7. The ice thermal source ice-spike thermal melt heat pump chiller unit of claim 1, wherein: All the protrusions are divided into a plurality of ice-stick groups which are sequentially distributed along the axial direction of the electrolytic layer ice-stick pipe, and the protrusions of adjacent ice-stick groups are distributed in a staggered manner. A steam return electric control valve is arranged between the first gas inlet and the electrolytic layer ice-stick pipe.

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