Hybrid heat pump system

Abstract

The invention relates to the technical field of heat pumps, and particularly discloses a hybrid heat pump system which comprises a heat source input module, a heat pump circulation module, an energy storage regulation and control module, a flow control module and a central control module. The heat source input module comprises an air source heat exchanger, a ground source heat exchanger and a solar heat collector which are connected in parallel; each heat source outlet is communicated with an evaporator inlet of the heat pump circulation module through a capacity adjusting valve; the heat pump circulation module is a closed loop formed by sequentially connecting a compressor, a condenser, an expansion valve and an evaporator through a refrigerant pipeline; according to the method, the dynamic weight distribution algorithm is set, fuzzy logic and a reinforcement learning model are combined, and the heat source contribution proportion of an air source, a ground source and solar energy is optimized in real time, so that full application of high heat contribution intervals of various heat sources, maximization of system energy efficiency and accurate control of operation cost are realized; and through the arrangement of synchronous control over the rotating speed of the phase change energy storage unit and the rotating speed of the compressor, the economical efficiency of energy utilization is remarkably improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of heat pumps, and particularly relates to a hybrid heat pump system. Background Art

[0002] In the technical field of heat pumps, with the growth of global energy demand and the improvement of environmental awareness, improving the coefficient of performance (COP) and operating economy of heat pump systems has become a key development direction in the industry. In recent years, heat pump systems, with their characteristics of high efficiency, energy conservation, environmental protection and pollution-free, have been widely used in the fields of heating, cooling and hot water supply. Especially for hybrid heat pump systems, by integrating multiple heat sources (such as air source, ground source, solar energy and other waste heat), the diversified and efficient utilization of environmental heat energy has been realized, further improving the adaptability and energy efficiency of the system and increasing the operating stability of the system.

[0003] However, although hybrid heat pump systems have significant advantages in theory, they still face many challenges in practical applications. Among them, the most prominent problem is how to dynamically optimize the contribution ratio of each heat source under different environmental conditions to achieve continuous and stable operation of the system, maximization of energy efficiency and precise control of operating costs. Traditional hybrid heat pump systems mostly use fixed priority or simple proportional allocation methods to control the input of each heat source. Although this method is simple and easy to implement, it lacks adaptability to environmental changes and cannot dynamically adjust the weight allocation of each heat source according to factors such as real-time environmental temperature, heat source availability and electricity price fluctuations. This results in the system may not be able to fully utilize the advantageous heat source under certain working conditions, or operate under non-optimal working conditions, thus reducing the overall energy efficiency and increasing the operating costs. Therefore, technical improvement is needed. Summary of the Invention

[0004] The purpose of the present invention is to provide a hybrid heat pump system to solve the problems raised in the above background art.

[0005] To achieve the above purpose, the present invention provides the following technical solutions:

[0006] A hybrid heat pump system, comprising:

[0007] A heat source input module, a heat pump cycle module, an energy storage regulation module, a flow control module and a central control module;

[0008] The heat source input module includes an air source heat exchanger, a ground source heat exchanger and a solar collector connected in parallel, and the outlet of each heat source is communicated with the inlet of the evaporator of the heat pump cycle module through a capacity regulating valve;

[0009] The heat pump cycle module is composed of a compressor, a condenser, an expansion valve and an evaporator connected in sequence through a refrigerant pipeline to form a closed loop;

[0010] The energy storage regulation module includes a phase change material unit (PCM) integrated on the outer wall of the condenser, a temperature sensor and a melting rate calculation unit embedded inside the PCM, and its output terminal is connected to the central control module;

[0011] The flow control module includes a piezoelectric resonance cavity, an audio signal processor and a valve opening regulator provided at the expansion valve, which are used to detect the dryness of the refrigerant two-phase flow in real time and feedback to control the expansion valve;

[0012] The central control module is configured to perform the following operations:

[0013] Based on the fuzzy logic algorithm and the reinforcement learning model, dynamically calculate the weight distribution coefficients of each heat source, and control the switching valve opening;

[0014] According to the PCM melting rate and the electricity price period signal, adjust the compressor speed to synchronize the energy storage / discharge cycle;

[0015] Receive the dryness data from the audio signal processor, and generate an expansion valve opening command to avoid liquid hammer or flashing.

[0016] Preferably, the dynamic weight distribution coefficient calculation of the central control module includes: an input layer, a prediction layer and a decision layer. The input layer real-time collects the temperature, energy consumption cost coefficient and equipment fatigue data of each heat source. The prediction layer predicts the solar irradiance, air energy temperature attenuation rate and other auxiliary energy supply trends and ground source temperature fluctuations in the next 1 to 2 hours through the LSTM neural network. The decision layer takes the maximization of the system COP and the minimization of the operating cost as the objective function, and outputs the heat source switching strategy.

[0017] Preferably, the phase change material unit of the energy storage regulation module is a multi-layer composite structure, including: a paraffin-based main phase change material layer, a graphene heat conduction column array vertically penetrating the paraffin layer, the top of which is in contact with the outer wall of the condenser, an adiabatic shell covering the outer layer, and a melting rate sensor communicating with the central control module is provided at the opening of the shell.

[0018] Preferably, the piezoelectric resonance cavity of the flow control module includes:

[0019] A plurality of piezoelectric ceramic sheets arranged along the refrigerant flow direction, which are used to excite and receive acoustic signals of 10 - 50 kHz;

[0020] A signal processing unit extracts the audio frequency characteristic peak through the fast Fourier transform (FFT) and calculates the dryness of the two-phase flow;

[0021] The response delay time of the valve opening regulator ≤ 5 ms.

[0022] Preferably, it further includes a waste heat recovery interface module, which includes a waste heat input pipeline and a waste heat priority judgment unit. The waste heat input pipeline is connected to the secondary inlet of the evaporator after being pretreated by a zeolite molecular sieve adsorption bed. When the waste heat temperature ≥ 30°C and meets the current load demand of the heat pump, the central control module forcibly closes other heat source channels and preferentially closes the ground source part.

[0023] Preferably, the heat source input module can also be expanded to connect to the waste heat branch of the fuel cell. Its waste heat outlet is communicated with the evaporator inlet through a three-way valve, and the electrolytic cell of the fuel cell recovers the waste heat of the condenser through a heat pipe.

[0024] Compared with the prior art, the beneficial effects of the present invention are:

[0025] (1) Through the setting of multi-heat source parallel input and intelligent switching, the optimal heat source combination is automatically selected under extreme ambient temperatures, thus overcoming the technical problem of efficiency attenuation of traditional single cold-heat source heat pumps in low-temperature environments.

[0026] (2) Through the setting of the dynamic weight distribution algorithm, combining the fuzzy logic and the reinforcement learning model, the heat source contribution ratios of the air source, the ground source and the solar energy are optimized in real time, so as to realize the full application of the high-heat contribution intervals of various heat sources and the maximization of the system energy efficiency and the precise control of the operation cost.

[0027] (3) Through the setting of synchronous control of the phase change energy storage unit and the compressor speed, the charge / discharge cycle is dynamically adjusted according to the peak-valley periods of the electricity price, thus significantly improving the economy of energy utilization and reducing the dependence on the peak load of the power grid.

[0028] (4) Through the setting of piezoelectric resonator flow regulation, the refrigerant dryness is quickly identified by using the acoustic frequency characteristics and the expansion valve is feedback-controlled, thus avoiding the liquid hammer or flashing phenomenon and ensuring the stability and safety of the system operation.

[0029] (5) Through the setting of the graphene-enhanced phase change material structure, the heat conduction efficiency and response speed of the energy storage unit are significantly improved, thus realizing a more efficient heat storage and heat release cycle. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 is the system flow chart of the present invention;

[0031] Figure 2 is the schematic diagram of the hybrid heat pump system of the present invention;

[0032] Figure 3 is the original diagram of the ground source working condition of the present invention;

[0033] Figure 4 is the schematic diagram of the air source working condition operation of the present invention;

[0034] Figure 5 This is the schematic diagram of the solar energy operating condition of the present invention;

[0035] Figure 6 This is the schematic diagram of the operation condition of the surplus waste heat of the present invention. Specific embodiments

[0036] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0037] Embodiment 1:

[0038] Please refer to Figure 1 As shown, a hybrid heat pump system includes:

[0039] A heat source input module, a heat pump cycle module, an energy storage control module, a flow control module, and a central control module;

[0040] The heat source input module includes an air source heat exchanger, a ground source heat exchanger, and a solar collector connected in parallel, and the outlets of each heat source are connected to the inlet of the evaporator of the heat pump cycle module through a capacity adjustment valve;

[0041] The heat pump cycle module is composed of a compressor, a condenser, an expansion valve, and an evaporator connected in sequence through a refrigerant pipeline to form a closed loop;

[0042] The energy storage control module includes a phase change material unit (PCM) integrated on the outer wall of the condenser, a temperature sensor and a melting rate calculation unit embedded inside the PCM, and its output end is connected to the central control module;

[0043] The flow control module includes a piezoelectric resonance cavity, an audio signal processor, and a valve opening regulator provided at the expansion valve, which is used to detect the dryness of the refrigerant two-phase flow in real time and feedback to control the expansion valve;

[0044] The central control module is configured to perform the following operations:

[0045] Based on the fuzzy logic algorithm and the reinforcement learning model, dynamically calculate the weight distribution coefficients of each heat source, and control the opening degree of the switching valve;

[0046] According to the PCM melting rate and the electricity price period signal, adjust the compressor speed to synchronize the energy storage / discharge cycle;

[0047] Receive the dryness data of the audio signal processor, and generate an expansion valve opening instruction to avoid liquid hammer or flashing.

[0048] The dynamic weight allocation coefficient calculation of the central control module includes: input layer, prediction layer and decision layer. The input layer collects the temperature, energy consumption cost coefficient and equipment fatigue data of each heat source in real time. The prediction layer predicts the solar radiation attenuation rate and ground source temperature fluctuations in the next 1 to 2 hours through the LSTM neural network. The decision layer takes maximizing the system COP and minimizing the operating cost as the objective function and outputs the heat source switching strategy.

[0049] The phase change material unit of the energy storage and control module is a multi-layer composite structure, including: a paraffin-based main phase change material layer, a graphene thermal conductive column array vertically penetrating the paraffin layer, the top of which is in contact with the outer wall of the condenser and is covered by an outer insulating shell. A melting rate sensor that communicates with the central control module is provided at the opening of the shell.

[0050] The piezoelectric resonant cavity of the flow control module includes:

[0051] Multiple piezoelectric ceramic plates arranged along the refrigerant flow direction are used to excite and receive 10-50kHz acoustic signals;

[0052] The signal processing unit extracts the audio characteristic peaks through fast Fourier transform (FFT) and calculates the dryness of the two-phase flow;

[0053] The response delay time of the valve opening regulator is ≤5ms.

[0054] It also includes a waste heat recovery interface module, which includes: a waste heat input pipeline and a waste heat priority judgment unit. The waste heat input pipeline is connected to the secondary inlet of the evaporator after pre-treatment of the zeolite molecular sieve adsorption bed. When the waste heat temperature is ≥30°C and meets the current load demand of the heat pump, the central control module forces the closure of other heat source channels and gives priority to closing the ground source part.

[0055] The central control module is further configured as follows:

[0056] During the off-peak period of electricity prices and when the terminal load is small, the compressor speed is increased to 120% of the rated power to completely melt the PCM;

[0057] During peak electricity price periods and when the terminal load is high, the compressor speed is limited to 70%, giving priority to releasing the PCM stored heat.

[0058] The heat source input module also includes a fuel cell waste heat branch, whose waste heat outlet is connected to the evaporator inlet through a three-way valve, and the electrolyzer of the fuel cell recovers the condenser waste heat through a heat pipe.

[0059] Heat source input module: air source heat exchanger (fin tube type, heat exchange area 10m 2 ), ground source heat exchanger (U-shaped buried pipe, depth 100m), solar collector (vacuum tube type, heat collection area 5m 2) Each heat source outlet and the reserved auxiliary heat source interface are connected to the evaporator inlet through an electric three-way valve group.

[0060] Heat pump cycle module: variable-frequency compressor (rated power 5kW), plate condenser (stainless steel material), electronic expansion valve (the original valve body is replaced with an acoustic resonance flow regulating valve), copper tube evaporator.

[0061] Energy storage control module: A phase change material unit (PCM) is integrated on the outer wall of the condenser. It is composed of paraffin (phase change temperature 55°C) and 5wt% graphene nanosheets, and a PT100 temperature sensor is buried inside. The melting rate is calculated by the differential temperature integration method.

[0062] Flow control module: A piezoelectric resonance cavity (including 3 pieces of PZT-5H piezoelectric ceramics, resonance frequency 20kHz) is installed at the expansion valve. The dryness value is output to the controller after the audio signal is analyzed by FFT.

[0063] Central control module: Developed based on Raspberry Pi 4B, running a fuzzy PID controller and DQN reinforcement learning algorithm.

[0064] Workflow

[0065] Scenario: Winter heating mode, outdoor temperature -5°C, off-peak electricity price period (22:00 - 6:00).

[0066] S1. The central control module starts dynamic weight calculation:

[0067] Real-time data: Solar irradiance 0W / m 2 (at night), ground source temperature 8°C, air temperature -5°C;

[0068] Predicted data: The LSTM model predicts that the air temperature will drop to -7°C in the next 2 hours;

[0069] Decision output: Ground source weight coefficient 0.7, air source 0.3 (to avoid low-temperature efficiency decay), close the solar path.

[0070] S2. Phase change energy storage synchronous control:

[0071] Detect that the current melting rate of the PCM is 30% (mainly solid state), the compressor speed is increased to 60Hz (120% of the rated value), and the condensation temperature is increased to 60°C to accelerate heat storage;

[0072] After 3 hours, the PCM is completely melted, and the speed is reduced to 40Hz to maintain heating.

[0073] S3. Acoustic valve flow regulation:

[0074] The piezoelectric resonator detects that the refrigerant dryness is 0.4 (lower than the safety threshold of 0.5), and the controller increases the valve opening by 15%. The superheat at the evaporator outlet stabilizes at 5K.

[0075] Data:

[0076] Dynamic weight control effect: Compared with the fixed-priority switching, the system COP is increased by 22% (measured 3.8 vs 3.1);

[0077] Phase change energy storage economy: The heat storage ratio during off-peak electricity hours reaches 78%, and the operating cost is reduced by 35%;

[0078] Acoustic valve response speed: The adjustment delay is 8ms during sudden change of dryness, and no liquid hammer phenomenon occurs.

[0079] The multi-source dynamic weight distribution function is:

[0080]

[0081] Parameters:

[0082] α i (t) (dynamic weight) is the contribution coefficient of the i-th heat source at time t, with the value range [0,1], and ∑α i = 1;

[0083] λ i (τ) (instantaneous efficiency) is the COP of the heat source i at time τ, collected by real-time sensors;

[0084] N(τ) (normalized electricity price factor) is with the value range [0.2,1.5];

[0085] ψ i (τ) (fatigue decay function) is where β i is the material constant, and Top,i is the cumulative operation time;

[0086] n (total number of heat sources) is the number of heat sources connected in parallel in the system (such as air source, ground source, solar energy).

[0087] Value range:

[0088] α i (t) = 1 indicates that the heat source is currently optimal and completely dominant;

[0089] α i (t) = 0 indicates that the heat source efficiency is too low or the cost is too high and is suppressed.

[0090] Phase change energy storage - compressor speed synchronous control equation:

[0091]

[0092] Parameter:

[0093] ω(t) (compressor speed) is a real-time adjusted value, with the unit of Hz;

[0094] Φ(t) (PCM melting rate) has a value range of [0, 1];

[0095] erf(x) (Gaussian error function) is used for smooth transition;

[0096] σ (standard deviation) is the tolerance for melting rate fluctuation, experimentally calibrated (typical value 0.1);

[0097] ω max , ω min are the upper and lower limits of the compressor's allowable speed.

[0098] Value range:

[0099] When Φ(t) = 1, ω(t) = ω min (fully melted, frequency reduction for heat storage);

[0100] When Φ(t) = 0, ω(t) = ω max (solid state, full power heating).

[0101] Example 2:

[0102] Heat source input module:

[0103] Retain the air source heat exchanger (fin-tube type) and the solar collector (vacuum tube type);

[0104] Add a waste heat recovery branch: The waste heat source is the factory cooling water (temperature 45 - 60°C), which is pre-treated by a zeolite molecular sieve adsorption bed (model Zeolite13X) and then connected to the secondary inlet of the evaporator through an electric valve;

[0105] Add a fuel cell waste heat co-generation branch: A 5kW PEM fuel cell stack, and its coolant outlet (temperature 65°C) is connected in parallel with the evaporator inlet through a plate heat exchanger.

[0106] Heat pump cycle module:

[0107] The compressor adopts a two-stage compression structure (high-low pressure cylinder volume ratio 1:3) to adapt to heat source input in a wide temperature range;

[0108] A heat pipe type waste heat recovery device is added to the condenser to introduce part of the condensation waste heat (40 - 50°C) into the preheating end of the electrolytic cell of the fuel cell.

[0109] Control module upgrade:

[0110] The central controller adds a waste heat priority judgment algorithm: when the waste heat temperature ≥ 30°C and the current load demand of the heat pump is met, the solar collector path is forcibly closed;

[0111] Integrate the fuel cell management system (BMS) to coordinate the power generation and heat supply demands in real time.

[0112] Workflow

[0113] Scenario: Summer refrigeration + process hot water supply in a food processing factory, ambient temperature 32°C, continuous waste heat supply.

[0114] S1. Activation of waste heat recovery:

[0115] The industrial cooling water temperature is detected to be 52°C, and the zeolite adsorption bed upgrades its temperature to 65°C. The central controller closes the solar collector and preferentially enables the waste heat branch;

[0116] The inlet temperature of the evaporator is increased from the original -5°C (pure air source mode) to 15°C, and the compressor power consumption is reduced by 18%.

[0117] S2. Regulation of fuel cell combined heat and power supply:

[0118] During the peak electricity consumption period of the factory, the fuel cell operates at full load, and its 65°C waste heat is input into the evaporator through a heat exchanger, replacing 50% of the waste heat branch load;

[0119] The 45°C waste heat recovered by the condenser preheats the electrolytic cell through a heat pipe, increasing the electrolysis efficiency by 12% (the measured voltage requirement drops from 1.8V to 1.6V).

[0120] S3. Dynamic mode switching:

[0121] When the waste heat temperature fluctuates to 38°C (below the threshold), the controller automatically switches to the air source + solar hybrid mode, and the weight coefficient is dynamically allocated according to the real-time irradiance intensity.

[0122] Data: Energy efficiency improvement:

[0123] The comprehensive COP reaches 4.3 (waste heat mode) vs 3.1 (traditional air source mode);

[0124] The waste heat utilization rate of the fuel cell is 92%, and the primary energy efficiency of the system is increased to 85%.

[0125] Economy: Waste heat replaces 60% of the traditional energy consumption, and the annual operating cost is reduced by about 120,000 (calculated based on 8,000 hours / year);

[0126] The electrolytic cell preheating saves electricity consumption of 15 kWh / day.

[0127] Example 3:

[0128] Designed for extremely cold environments below -25°C, the main improvements include:

[0129] Anti-frost evaporator assembly: Adopts a three-stage composite structure evaporator:

[0130] Outer layer: Superhydrophobic photothermal coating (graphene / TiO2 composite material, contact angle 162°);

[0131] Middle layer: Interleaved microchannel heat exchange tubes (pipe diameter gradient from 2 mm to 1 mm);

[0132] Inner layer: Magnetothermal compensation unit (Gd5Si2Ge2 alloy thin sheet, thickness 200 μm).

[0133] New defrosting subsystem: Pulse reverse defrosting device:

[0134] Four-way reversing valve (response time < 50 ms), hot gas bypass pipe (equipped with PTC ceramic heater), surface acoustic wave frost sensor (center frequency 125 MHz).

[0135] Intelligent control unit: Extremely cold mode control algorithm:

[0136] Frost formation prediction model (based on LSTM + meteorological API), magnetothermal compensation strategy (magnetic field intensity adjustable from 0 to 1.5 T).

[0137] Workflow (-25°C working condition)

[0138] S1. Anti-frost stage

[0139] Daytime working condition: The photothermal coating absorbs solar radiation (efficiency 92%), and the surface temperature is maintained at 5 - 8°C; the magnetothermal unit is not activated.

[0140] Nighttime working condition: When the surface acoustic wave sensor detects that the frost layer thickness > 0.3 mm: Start a 0.8 T magnetic field to instantaneously increase the temperature of the evaporator surface by 3°C; at the same time, the refrigerant flow rate in the microchannel is increased by 20%.

[0141] S2. High-efficiency defrosting stage

[0142] When the predicted frost layer thickness will reach 1 mm: The four-way valve switches (time-consuming 45 ms), the PTC heater starts (outputs 80°C hot gas within 3 s), and the entire defrosting process takes < 90 s, and the energy consumption is only 17% of that of traditional electric heating.

[0143] S3. Energy compensation mechanism

[0144] During defrosting: The ground source heat exchanger temporarily undertakes 70% of the load; the phase change energy storage unit releases the stored heat; the system COP remains ≥ 2.1 (the COP of the conventional system is ≤ 1.3 at this time).

[0145] Data: Anti-frost performance: Frost formation cycle extended to 48 hours (8 - 12 hours for conventional systems); Frost layer growth rate reduced by 76%.

[0146] Energy efficiency index: Magnetocaloric compensation energy consumption: 0.15 kWh / time;

[0147] Annual average defrosting energy consumption reduced by 83%; System COP stable at 2.3 ± 0.2 under the condition of -30°C.

[0148] Magnetocaloric unit life > 150,000 cycles; Abrasion resistance of superhydrophobic coating > 5000 cleaning cycles.

[0149] Example 4:

[0150] Efficient summer refrigeration and multi-heat source collaborative control: Optimize the system configuration for the refrigeration mode and strengthen the functions of ground source heat dissipation and waste heat recovery.

[0151] Heat pump cycle module: Add a four-way reversing valve. Under the refrigeration mode, the refrigerant flow direction is switched to:

[0152] Compressor to evaporator (indoor heat absorption for refrigeration) to expansion valve to condenser (ground source / waste heat dissipation).

[0153] The condenser is connected in parallel with the ground source heat dissipation branch and the waste heat recovery branch, and is switched through an electric three-way valve.

[0154] Energy storage regulation module: Add a low-temperature phase change material layer (hydrated salt base, phase change temperature 5°C) to store the remaining cold energy during off-peak electricity hours.

[0155] The PCM unit structure is upgraded to a two-temperature zone:

[0156] High-temperature layer (55°C paraffin): Store waste heat from heating;

[0157] Low-temperature layer (5°C hydrated salt): Store cold energy for refrigeration.

[0158] Heat source input module: The ground source heat exchanger is preferentially used as the heat dissipation end of the condenser (the underground temperature is stably lower than the ambient temperature in summer); The solar collector is switched to the night radiation cooling mode (enhance infrared heat dissipation through a selective coating).

[0159] Control strategy: When the ambient temperature > 35°C, automatically close the air source heat dissipation path to avoid efficiency decay caused by high temperature; When the waste heat temperature ≥ 40°C, the heat of the condenser is preferentially recovered to the fuel cell electrolyzer through a heat pipe.

[0160] Workflow

[0161] Scenario: Refrigeration of commercial buildings in summer, ambient temperature 38°C, peak electricity price period (14:00 - 16:00).

[0162] S1. Mode Initialization:

[0163] The four-way reversing valve is switched to the refrigeration mode, and the central controller starts dynamic weight calculation:

[0164] Real-time data: The ground source temperature is 18°C (heat dissipation advantage), the surface temperature of the solar collector is 42°C (closed), and the waste heat temperature is 45°C;

[0165] Decision output: The ground source heat dissipation weight coefficient is 0.8, and the waste heat recovery weight is 0.2.

[0166] S2. Ground Source Heat Dissipation and Cold Storage:

[0167] The heat of the condenser is dissipated through the buried pipe (the efficiency is 40% higher than that of air cooling);

[0168] During the valley electricity period (22:00 - 6:00), the compressor operates overclocked (110% speed), and the excess cold is stored in the low-temperature PCM layer.

[0169] S3. Waste Heat Recovery Collaboration:

[0170] When the waste heat temperature is detected to be 48°C, the controller conducts 20% of the condensation heat into the electrolytic cell through the heat pipe, and the preheating efficiency is increased by 15%;

[0171] The dryness at the evaporator outlet is 0.6, and the piezoelectric resonance cavity dynamically adjusts the opening of the expansion valve (response delay 4ms).

[0172] S4. High Temperature Emergency Strategy:

[0173] When the ambient temperature suddenly rises to 40°C, the air source heat dissipation is turned off, and the ground source heat dissipation weight rises to 1.0;

[0174] The low-temperature PCM is activated to release cold to maintain the stability of the indoor temperature (fluctuation ±0.3°C).

[0175] Performance Data:

[0176]

[0177]

[0178] Effect: Through the collaborative control of the four-way reversing valve and the dual-temperature zone PCM, the COP in the refrigeration mode is increased by more than 50%, and the ground source heat dissipation energy consumption is reduced by 35%; the combination of night radiation cooling and valley electricity cold storage reduces the peak electricity load by 40%.

[0179] Comparative Example:

[0180] Technical solution of traditional air source heat pump system: only air source heat exchanger is adopted, without integration of multiple heat sources such as ground source / solar energy, etc.; the compressor starts and stops according to preset temperature thresholds, without dynamic weight distribution; the condenser directly releases heat to the environment, unable to utilize the peak-valley difference of electricity price; the response speed > 50ms, unable to match the change of two-phase flow in real time.

[0181] Comparison test data (-5°C heating condition):

[0182] Index Prior art Example 1 Improvement range COP 2.8 3.8 +35.7％ Defrosting frequency Once every 4 hours No need for active defrosting 100％ Utilization rate of valley electricity 0％ 78％ - Fluctuation of evaporator superheat ±3K ±0.5K +83.3％

[0183] COP decays sharply in low temperature environment (COP < 2.0 at -10°C); frequent defrosting leads to increased energy consumption (accounting for 15%-20% of annual energy consumption); unable to participate in power grid demand response, with poor economy.

[0184] Technical solution of conventional waste heat recovery heat pump: industrial cooling water is directly introduced into the evaporator, without grade improvement (efficiency drops sharply when the temperature < 50°C); there is no coordination between fuel cell and heat pump, and waste heat is directly discharged; heat source is switched manually, unable to respond to the temperature fluctuation of waste heat in real time.

[0185] Comparison test data (32°C refrigeration condition in summer):

[0186] Index Prior art Example 2 Improvement range Comprehensive COP 2.9 4.3 +48.3％ Utilization rate of waste heat 45％ 92％ +104.4％ Preheating energy consumption of electrolyzer 1.8V 1.6V -11.1％ Annual operating cost (10,000 yuan) 28 16 -42.9％

[0187] Low-grade waste heat (30 - 50°C) cannot be effectively utilized; the energy coupling efficiency is low, and the primary energy efficiency of the system < 60%; manual intervention leads to response delay (> 30 minutes).

[0188] Technical solution of ordinary ultra-cold heat pump: resistance wires are embedded in the fins of the evaporator, and the defrosting power > 3kW; the switching period of the four-way valve > 5 minutes, and the hot gas bypass temperature is insufficient (< 60°C); the frost formation prediction depends on fixed time intervals, not intelligent judgment.

[0189] Comparison test data (-25°C condition):

[0190] Index Prior art Example 3 Improvement range Annual average defrosting energy consumption (kWh) 1,850 315 -83％ COP at 30℃ 1.2 2.3 +91.7％ Defrosting time 8 minutes 90 seconds -81.3％ Lifetime of magnetothermal unit None > 150,000 times -

[0191] The electric auxiliary heating energy consumption accounts for 25%-30% of the total system energy consumption; the heating is interrupted during defrosting (room temperature fluctuation > 3°C); the compressor frequently shuts down due to low pressure protection at extremely low temperature (< -20°C).

[0192] Although the embodiments of the present invention have been shown and described, for those of ordinary skill in the art, it can be understood that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A hybrid heat pump system, characterized in that, Including: A heat source input module, a heat pump cycle module, an energy storage regulation module, a flow control module, and a central control module; The heat source input module includes an air source heat exchanger, a ground source heat exchanger, and a solar collector connected in parallel, and the outlets of each heat source are connected to the inlet of the evaporator of the heat pump cycle module through a capacity adjustment valve; The heat pump cycle module is composed of a compressor, a condenser, an expansion valve, and an evaporator connected in sequence through a refrigerant pipeline to form a closed loop; The energy storage regulation module includes a phase change material unit (PCM) integrated on the outer wall of the condenser, a temperature sensor embedded inside the PCM, and a melting rate calculation unit, and its output end is connected to the central control module; The flow control module includes a piezoelectric resonance cavity, an audio signal processor, and a valve opening regulator arranged at the expansion valve, which is used to detect the dryness of the refrigerant two-phase flow in real time and feedback to control the expansion valve; The central control module is configured to perform the following operations: Based on the fuzzy logic algorithm and the reinforcement learning model, dynamically calculate the weight distribution coefficient of each heat source, and control the opening of the switching valve; According to the PCM melting rate and the electricity price period signal, adjust the compressor speed to synchronize the charging / discharging cycle; Receive the dryness data of the audio signal processor, and generate an expansion valve opening command to avoid liquid hammer or flashing.

2. The hybrid heat pump system according to claim 1, characterized in that: The dynamic weight distribution coefficient calculation of the central control module includes an input layer, a prediction layer, and a decision layer. The input layer real-time collects the temperature, energy consumption cost coefficient, and equipment fatigue degree data of each heat source. The prediction layer predicts the solar irradiance, the air energy temperature attenuation rate, and the energy supply trends of other auxiliary energy sources and the ground source temperature fluctuation in the next 1 to 2 hours through an LSTM neural network. The decision layer takes the maximization of the system COP and the minimization of the operating cost as the objective function, and outputs a heat source switching strategy.

3. A hybrid heat pump system according to claim 1, characterized in that: The phase change material unit of the energy storage regulation module is a multi-layer composite structure, including: a paraffin-based main phase change material layer, a graphene heat conduction column array vertically penetrating the paraffin layer, the top of which is in contact with the outer wall of the condenser, an adiabatic shell covering the outer layer, and a melting rate sensor communicating with the central control module is provided at the opening of the shell.

4. A hybrid heat pump system according to claim 1, characterized in that: The piezoelectric resonance cavity of the flow control module includes: A plurality of piezoelectric ceramic sheets arranged along the refrigerant flow direction, which are used to excite and receive acoustic signals of 10 - 50 kHz; A signal processing unit extracts the acoustic frequency characteristic peak through fast Fourier transform (FFT) and calculates the dryness of the two-phase flow; The response delay time of the valve opening regulator ≤ 5 ms.

5. A hybrid heat pump system according to claim 1, characterized in that: It also includes a waste heat recovery interface module, which includes: a waste heat input pipeline and a waste heat priority judgment unit. The waste heat input pipeline is connected to the secondary inlet of the evaporator after being pretreated by a zeolite molecular sieve adsorption bed. When the waste heat temperature ≥ 30 °C and meets the current load demand of the heat pump, the central control module forcibly closes other heat source channels, and preferentially closes the ground source part.

6. A hybrid heat pump system according to claim 1, characterized in that: The heat source input module can also be extended to connect to the fuel cell waste heat branch. The waste heat outlet is connected to the evaporator inlet through a three-way valve, and the electrolytic cell of the fuel cell recovers the waste heat of the condenser through a heat pipe.

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