Coupling type refrigeration and cold supply decoupling system and design method

Abstract

The invention provides a coupled refrigeration and cold supply decoupling system and a design method, and the system comprises a first thermodynamic system which comprises a first condensation module and a first evaporation module; the second thermodynamic system comprises a first generation module and a second condensation module; the first generation module and the first condensation module are subjected to non-substance exchange energy coupling, the first condensation module drives the first generation module to generate vaporization through condensation heat release, and the second condensation module and the first evaporation module are subjected to non-substance exchange energy coupling; the first evaporation module drives the second condensation module to generate condensation through evaporation heat absorption. The coupling type refrigeration and cold supply decoupling system can effectively couple the compression type heat pump system and the absorption / adsorption type refrigeration system, high-grade heat released in the condensation process of the compression type system is used as a heat source of the absorption system, and energy gradient utilization between the compression type system and the absorption system is achieved; and the time relation between refrigeration and cold supply is effectively decoupled.

Description

Technical Field

[0001] The present invention belongs to the technical field of novel power systems, and in particular relates to a coupled refrigeration and cooling decoupling system and a design method. Background Art

[0002] With the development of industry and the improvement of people's living standards, the application of refrigeration and cooling systems is becoming more and more extensive. At present, refrigeration and cooling systems mainly use compression refrigeration and absorption / adsorption refrigeration.

[0003] The compression refrigeration system is the most common refrigeration method. Its working principle is to use a compressor to compress low-temperature and low-pressure refrigerant vapor into high-temperature and high-pressure superheated steam, and complete the refrigeration cycle through condensation, throttling, evaporation and other processes. This system has the advantages of high energy efficiency and compact structure, but it consumes high-grade electricity and has high operating costs.

[0004] Absorption / adsorption refrigeration system is a heat-driven refrigeration method that can utilize low-grade heat sources such as industrial waste heat and solar energy. Its working principle is to utilize the physical or chemical action between the refrigerant and the absorber / adsorbent to achieve refrigeration through the process of desorption-condensation-evaporation-absorption / adsorption. This system can utilize low-grade heat sources and has low operating costs, but it has disadvantages such as low energy efficiency and large system size.

[0005] There are the following major problems in the prior art:

[0006] 1. The two refrigeration methods are usually operated independently, failing to achieve effective energy coupling and cascade utilization. The high-quality heat generated by the compression refrigeration system during condensation is directly discharged into the environment, causing waste, while the absorption / adsorption refrigeration system requires an external heat source, and the overall energy utilization efficiency of the system is not high.

[0007] 2. Existing refrigeration systems often have difficulty in achieving time decoupling of refrigeration and cooling. The operation of refrigeration equipment and cooling demand must be carried out simultaneously, resulting in equipment selection based on maximum load configuration, resulting in investment waste and not conducive to peak load shaving and valley filling and rational use of energy.

[0008] 3. In terms of industrial waste heat recovery and utilization, since the quality and quantity of waste heat often fluctuate, a single refrigeration method is difficult to efficiently utilize these unstable heat sources, and it is necessary to develop a new type of coupled refrigeration system.

[0009] Therefore, there is an urgent need to develop a new type of coupled refrigeration and cooling system that can not only realize the efficient coupling of compression and absorption / adsorption refrigeration, but also achieve time decoupling of refrigeration and cooling through energy storage, thereby improving the energy utilization efficiency and operational flexibility of the system. Summary of the invention

[0010] In order to overcome the shortcomings of the prior art, the purpose of the present invention is to provide a coupled refrigeration and cooling decoupling system and design method to solve the problems of the existing compression and absorption / adsorption refrigeration systems that cannot be efficiently coupled, cannot achieve time decoupling, and have low energy utilization efficiency.

[0011] To solve the above problems, the technical solution adopted by the present invention is as follows:

[0012] In a first aspect, the present invention provides a coupled refrigeration and cooling decoupling system, comprising:

[0013] A first thermal system includes a first condensation module and a first evaporation module;

[0014] The second thermal system includes a first generating module and a second condensing module;

[0015] The first condensing module drives the first generating module to vaporize by releasing heat through condensation, thereby performing energy coupling of non-material exchange; the first evaporating module drives the second condensing module to condense by absorbing heat through evaporation, thereby performing energy coupling of non-material exchange.

[0016] In a second aspect, the present invention provides a design method for a coupled refrigeration and cooling decoupling system, comprising:

[0017] Set the first generating module pressure p g ;

[0018] Set the refrigerant dilute solution concentration c of the first generating module output o ;

[0019] According to p g , determine the refrigerant solution concentration c o The corresponding saturation temperature t s1 ;

[0020] Set the first generating module to drive the temperature difference ΔT g ;

[0021] Determine the first generation module drive temperature requirement T g ＝ t s +D T g ；

[0022] Select the working fluid of the heat pump system;

[0023] According to the physical properties of the working fluid in the heat pump system, the saturation temperature T is determined. g The corresponding pressure is the heat pump system compressor outlet pressure P c ;

[0024] According to the thermal properties of the refrigerant and the pressure p of the second condensing module c , determine the refrigerant saturation temperature t in the second condensing modulec ;

[0025] Set the driving temperature difference ΔT of the second condensation module c , determine the cooling drive temperature T of the second condensing module c =t c -ΔT c ;

[0026] According to T c Determine the pressure p of the heat pump working fluid after throttling v ;

[0027] Determine the heat pump compressor pressure ratio π=P c / p v .

[0028] Compared with the prior art, the present invention has at least the following beneficial effects:

[0029] 1. Improve energy utilization efficiency: The coupled refrigeration and cooling decoupling system of the present invention can effectively couple the compression heat pump system and the absorption / adsorption refrigeration system, and use the high-grade heat released during the condensation process of the compression system as the heat source of the absorption system, thereby realizing the energy ladder utilization between the two. This innovative design not only improves the overall energy efficiency of the system, but also reduces energy waste, thereby achieving a more environmentally friendly and efficient refrigeration and cooling solution. The compression heat pump and absorption refrigeration adopt an energy coupling method of non-material exchange, which can facilitate the two cycles to select more suitable working fluids (pairs) according to different characteristic requirements, which is conducive to further improving the energy efficiency and comprehensive performance of the coupling system. Dividing the refrigeration process into two or more stages is based on the innovative concept of thermal cycle, and can also reduce the heat transfer of the refrigeration process. In addition, by utilizing the pressure difference between solution storage tanks at different height differences, the configuration of the solution pump can be effectively reduced, which can reduce power consumption, system costs, and simplify the system structure.

[0030] 2. Improve the stability of the intermediate storage system: By placing the refrigerant dilute solution intermediate storage device in the high-temperature section before the heat recovery system, the stability of the refrigerant dilute solution can be greatly improved, and the crystallization risk of working fluid solutions such as lithium bromide can be greatly reduced.

[0031] 3. Realize the time decoupling of refrigeration and cooling supply: By setting up a multi-stage energy storage system, including a refrigerant intermediate storage system, a refrigerant absorption intermediate storage system and a refrigerant desorption intermediate storage system, the present invention effectively decouples the time relationship between refrigeration and cooling supply. This feature enables the system to be flexibly adjusted and flexibly respond to load changes, which helps to maintain the operating efficiency of the system when the cooling demand is unstable, reduce the instantaneous load on the equipment during peak periods, and reduce operating costs.

[0032] 4. Reduce operating costs: Since the present invention can efficiently couple and utilize existing resources and achieve energy balance and allocation through intelligent energy management, it reduces the refrigeration system's dependence on high-quality electricity, further reducing the company's energy costs and operating costs. At the same time, the system's efficiency and flexibility also help companies optimize their energy consumption structure and achieve a win-win situation in terms of economic and environmental benefits.

[0033] The present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] The present invention is further described using the accompanying drawings, but the embodiments in the accompanying drawings do not constitute any limitation to the present invention. A person skilled in the art can obtain other drawings based on the following drawings without creative work.

[0035] Figure 1 It is a schematic diagram of the framework of a coupled refrigeration and cooling decoupling system under an implementation method in this embodiment 1.

[0036] Figure 2 It is a schematic diagram of the framework of a coupled refrigeration and cooling decoupling system under another implementation mode in this embodiment 1.

[0037] Figure 3 It is a schematic diagram of the framework of a coupled refrigeration and cooling decoupling system under an implementation method in Example 2.

[0038] Figure 4 It is a schematic framework diagram of a coupled refrigeration and cooling decoupling system under another implementation method in Example 2.

[0039] Figure 5 It is a schematic framework diagram of a coupled refrigeration and cooling decoupling system under an implementation method in Example 3.

[0040] Figure 6 It is a schematic framework diagram of a coupled refrigeration and cooling decoupling system under an implementation method in Example 3. DETAILED DESCRIPTION

[0041] The technical solution of the present invention will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0042] In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", and "third" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance.

[0043] In the description of the present invention, when it is described that a specific device is located between a first device and a second device, there may or may not be an intermediate device between the specific device and the first device or the second device. When it is described that a specific device is connected to other devices, the specific device may be directly connected to the other devices without an intermediate device, or may not be directly connected to the other devices but have an intermediate device.

[0044] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered as part of the specification.

[0045] Embodiment 1:

[0046] This embodiment provides a coupled refrigeration and cooling decoupling system, the core of which is to achieve energy coupling of two thermal systems and time decoupling of refrigeration and cooling. The specific implementation of the present invention is described in detail below with reference to the accompanying drawings. Figure 1 and Figure 2 ,include:

[0047] The first thermal system 100 includes a first condensing module 102 and a first evaporating module 104;

[0048] The second thermal system 200 includes a first generating module 201 and a second condensing module 202;

[0049] The first generating module 201 is coupled with the first condensing module 102 for energy exchange without material exchange, and the first condensing module 102 drives the first generating module 201 to vaporize by releasing heat through condensation. The second condensing module 202 is coupled with the first evaporating module 104 for energy exchange without material exchange, and the first evaporating module 104 drives the second condensing module 202 to condense by absorbing heat through evaporation.

[0050] Among them, from the perspective of material exchange, the first thermal system 100 and the second thermal system 200 are two independent systems, in which the running materials will not be exchanged, and the operation control time can also be independently controlled. However, there are two energy coupling scenarios, namely the first generation module 201 and the first condensation module 102, and the second condensation module 202 and the first evaporation module 104. It happens that one of them needs to release heat and the other needs to absorb heat. In addition, when energy coupling is performed, the liquid-gas phase change of the material is promoted to absorb or release latent heat.

[0051] Furthermore, to establish energy exchange, there needs to be a temperature difference between the two energy fields, that is, the quality of thermal energy must be high or low, in order to be effectively utilized. Specifically:

[0052] The first thermal system 100 is a compression heat pump system, which usually generates higher-grade heat energy because the energy consumption during the compression process of the compressor causes the heat energy to be concentrated at a higher temperature level. The compression heat pump system includes a compressor 101, a first condensing module 102, an expansion valve 103 and a first evaporation module 104.

[0053] The second thermal system 200 is an absorption refrigeration system or an adsorption refrigeration system, which is usually able to utilize lower-grade thermal energy, such as low-temperature industrial waste heat or environmental thermal energy; the absorption or adsorption refrigeration system includes a first generating module 201, a second condensing module 202, a throttle valve 203 and a second evaporation module 204; further, it also includes a refrigerant intermediate storage system 205, a refrigerant absorption intermediate storage system 206 and a refrigerant desorption intermediate storage system 207.

[0054] It should be noted that the compressor 101 compresses the low-temperature and low-pressure refrigerant vapor into high-temperature and high-pressure superheated steam, which enters the first condensing module 102. In the first condensing module 102, the high-temperature and high-pressure steam condenses and releases heat. The condensed high-pressure liquid refrigerant is depressurized by the expansion valve 103 and enters the first evaporation module 104. In the first evaporation module 104, the low-pressure liquid refrigerant absorbs heat and vaporizes to form low-temperature and low-pressure steam, which enters the compressor 101 again to complete a cycle.

[0055] The first generating module 201 receives heat from the first condensing module 102, and desorbs the refrigerant from the solution (or adsorbent). The desorbed high-temperature and high-pressure refrigerant vapor enters the second condensing module 202, where it is condensed into liquid. The liquid refrigerant is depressurized by the throttle valve 203 and then enters the second evaporation module 204. In the second evaporation module 204, the refrigerant absorbs heat and vaporizes, producing a cooling effect.

[0056] There are two coupling and decoupling actions in the working process:

[0057] 1. Energy coupling between two thermal systems: Energy coupling of non-material exchange is performed between the first condensation module 102 and the first generation module 201. The heat released by the first condensation module 102 during the condensation process is used to drive the refrigerant desorption process in the first generation module 201; Energy coupling of non-material exchange is also performed between the first evaporation module 104 and the second condensation module 202. The heat absorbed by the first evaporation module 104 during the evaporation process is used to drive the refrigerant condensation process in the second condensation module 202;

[0058] 2. Time decoupling of refrigeration and cooling:

[0059] The refrigerant intermediate storage system 205 is connected to the outlet of the second condensing module 202 through a pipeline, and is used to store liquid refrigerant coming out of the second condensing module 202; the refrigerant intermediate storage system 205 is connected to the second evaporation module 204 through the throttle valve 203, and can supply refrigerant to the second evaporation module 204 according to demand; the capacity of the refrigerant absorption intermediate storage system 206 and the refrigerant desorption intermediate storage system 207 matches the refrigerant intermediate storage system 205, and is used to store refrigerant solutions of different concentrations (or adsorbents in different adsorption states).

[0060] Through the above design, the present invention realizes efficient energy coupling between the compression heat pump system and the absorption / adsorption refrigeration system. The condensation temperature of the compression heat pump system is higher than the generation temperature of the absorption / adsorption refrigeration system, so that heat energy can flow from the first thermal system 100 to the second thermal system 200. In the absorption cycle, the waste heat of the heat pump is directly used to regenerate the refrigerant, and the temperature gradient and the energy level between the systems are matched to ensure efficiency.

[0061] At the same time, multiple storage systems are used to achieve time decoupling of refrigeration and cooling, which greatly improves the energy efficiency and operational flexibility of the system. Specifically, it includes at least the following three time decoupling strategies:

[0062] 1. Peak and valley electricity price utilization strategy:

[0063] 1) During the low electricity price period (usually at night):

[0064] a) Make full use of the compression heat pump system (the first thermal system 100) to convert electrical energy into heat energy and cold energy.

[0065] b) Storing excess cold energy in the refrigerant storage system 205.

[0066] c) The thermal energy is used to drive the absorption / adsorption system (the second thermal system 200), and the generated cold energy is also stored.

[0067] 2) During peak electricity price periods (usually during daytime):

[0068] a) Reduce the operation of compression heat pump systems and rely mainly on stored cold and absorption / adsorption systems to provide cooling.

[0069] b) Use the stored thermal energy to continue driving the absorption / adsorption system.

[0070] This strategy can significantly reduce electricity costs while alleviating load pressure on the power grid during peak periods.

[0071] 2. Load matching strategy:

[0072] 1) During low load periods (such as nighttime or weekends):

[0073] a) Operate the compression heat pump system and store the excess energy in various intermediate storage systems.

[0074] b) Preheat the generator of the absorption / adsorption system to improve its startup efficiency.

[0075] 2) During high-load periods (such as daytime on weekdays):

[0076] a) Combine compression system and absorption / adsorption system to operate simultaneously to meet peak load requirements.

[0077] b) Use stored cooling and heat to supplement system output and smooth out load fluctuations.

[0078] This strategy can improve the system's load adaptability and ensure stable operation under various working conditions.

[0079] 3. Intelligent predictive control strategy:

[0080] 1) Using weather forecasts and historical energy consumption data:

[0081] a) Forecast future cooling demand and available energy in advance.

[0082] b) According to the prediction results, adjust the storage capacity of each storage system in advance.

[0083] 2) Real-time load monitoring:

[0084] a) Dynamically adjust the operating ratio of the two thermal systems.

[0085] b) Optimize the timing of energy storage and release.

[0086] This strategy can further improve the operating efficiency and economy of the system.

[0087] Combination Figure 2 In some possible embodiments, the refrigerant intermediate storage system 205 is connected to the outlet of the second condensing module 202 of the second thermal system 200 through a pipeline, and is used to store the refrigerant at the outlet of the second condensing module 202;

[0088] The refrigerant intermediate storage system 205 is connected to the second evaporation module 204 in the second thermal system 200 through a throttle valve 203 .

[0089] Combination Figure 2 In some possible embodiments, the refrigerant absorption storage system 206 includes a pressure reducing valve 208, an absorber 209 and a refrigerant concentrated solution storage device 210;

[0090] The absorber 209 is connected to the pipeline after the pressure reducing valve 208 through a pipeline, and the refrigerant concentrated solution storage device 210 is connected to the pipeline from the downstream of the absorber 209 to the first generating module 201 through a pipeline. Its capacity can accommodate the refrigerant concentrated solution generated after all the refrigerants in the refrigerant storage system 205 are completely absorbed by the refrigerant dilute solution after throttling expansion and evaporation and heat absorption.

[0091] Preferably, the refrigerant concentrated solution storage device 210 is disposed at the lower portion of the absorber 209 to collect the refrigerant concentrated solution generated by the absorber 209 absorbing the refrigerant vapor by gravity.

[0092] Combination Figure 2 In some possible embodiments, the refrigerant desorption storage system 207 includes a solution pump 211 and a refrigerant dilute solution storage device 212;

[0093] The solution pump 211 is arranged on the pipeline between the refrigerant concentrated solution storage device 210 and the first generating module 201;

[0094] The refrigerant dilute solution intermediate storage device 212 is connected to the pipeline from the downstream of the first generating module 201 to the pressure reducing valve 208 through a pipeline, and its capacity can accommodate the refrigerant dilute solution generated after desorption of all the refrigerant concentrated solutions in the refrigerant absorption intermediate storage system 206.

[0095] Preferably, the refrigerant dilute solution storage device 212 is disposed at the lower part of the first generating module 201, and collects the refrigerant dilute solution generated by desorbing the refrigerant through the first generating module 201 by gravity.

[0096] It should be noted that the refrigerant intermediate storage system 205 is connected between the outlet of the second condensing module 202 and the second evaporation module 204; the refrigerant absorption intermediate storage system 206 includes a pressure reducing valve 208, an absorber 209 and a concentrated solution intermediate storage device, which is used to store the concentrated solution that absorbs the refrigerant; the refrigerant desorption intermediate storage system 207 includes a solution pump 211 and a dilute solution intermediate storage device, which is used to store the dilute solution after desorption. The above technical means ensure that the refrigerant and the solution can be effectively stored and recycled at all stages. Through reasonable storage and circulation, energy loss is reduced, system efficiency is improved, and the flow of the refrigerant and the solution can be flexibly adjusted according to the load demand, thereby enhancing the system regulation capability. Even in the case of large load fluctuations, the system can maintain stable operation and achieve continuous operation.

[0097] In some possible embodiments, the compressor 101 in the compression heat pump system is also combined with a load control module 105 based on grid demand. Based on different grid demands, the load control module 105 sends corresponding control instructions to the compressor 101 to achieve more efficient operation.

[0098] Embodiment 2:

[0099] Combination Figure 3 and Figure 4 Based on the above embodiments, this embodiment further includes a regenerative heat exchanger 300, the regenerative heat exchanger 300 includes at least one heat source and one cold source, and the heat source and the cold source perform heat exchange in the regenerative heat exchanger 300;

[0100] The heat source is a high-temperature medium drawn from the outlet of the first generating module 201 and / or the second condensing module 202;

[0101] The cold source is the low-temperature medium before the entrance of the first generating module 201 .

[0102] The heat exchanger 300 utilizes the high-temperature medium in the system (lead out from the outlet of the first generating module 201 and / or the second condensing module 202) to preheat the low-temperature medium (the solution entering the first generating module 201), further improving the energy utilization efficiency of the system and reducing heat waste. By recovering the heat of the high-temperature medium in the second thermal system 200, the demand for external heat sources is reduced and the energy utilization efficiency is improved. By internally recycling heat, energy consumption is reduced and operating costs are reduced. In addition, preheating the solution entering the first generating module 201 can improve the efficiency of the first generating module 201 and improve system performance.

[0103] Optionally, the heat source inlet end of at least one heat source is connected to the refrigerant storage system 205 through a pipeline, and the heat source outlet end is connected to the throttle valve 203 through a pipeline;

[0104] The cold source inlet end of the cold source is connected to the solution pump 211 through a pipeline, and the cold source outlet end is connected to the first generating module 201 through a pipeline;

[0105] The heat recovery heat exchanger 300 is used to recover the heat contained in the high-temperature refrigerant in the refrigerant intermediate storage system 205 to heat the low-temperature solution in the refrigerant absorption intermediate storage system 206 .

[0106] Optionally, the heat source inlet end of at least one heat source is connected to the refrigerant desorption storage system 207 through a pipeline, and the heat source outlet end is connected to the pressure reducing valve 208 through a pipeline;

[0107] The cold source inlet end of the cold source is connected to the solution pump 211 through a pipeline, and the cold source outlet end is connected to the first generating module 201 through a pipeline;

[0108] The heat recovery heat exchanger 300 is used to recover the heat contained in the high-temperature solution in the refrigerant analysis intermediate storage system to heat the low-temperature solution in the refrigerant absorption intermediate storage system 206.

[0109] Reference Figure 3 As an implementation mode, the regenerative heat exchanger 300 includes two heat sources and one cold source, the heat sources include a first heat source 310 and a second heat source 320, and the cold source includes a first cold source 330;

[0110] The heat source inlet end of the first heat source 310 is connected to the refrigerant storage system 205 through a pipeline, and the heat source outlet end is connected to the throttle valve 203 through a pipeline;

[0111] The heat source inlet end of the second heat source 320 is connected to the refrigerant desorption storage system 207 through a pipeline, and the heat source outlet end is connected to the pressure reducing valve 208 through a pipeline;

[0112] The cold source inlet end of the first cold source 330 is connected to the solution pump 211 through a pipeline, and the cold source outlet end is connected to the first generating module 201 through a pipeline;

[0113] The heat recovery heat exchanger 300 is used to recover the high-temperature refrigerant in the refrigerant intermediate storage system 205 and the heat contained in the high-temperature solution in the refrigerant absorption intermediate storage system to heat the low-temperature solution in the refrigerant absorption intermediate storage system 206.

[0114] Optionally, the heat source inlet end of at least one heat source is connected to the second condensing module 202 through a pipeline, and the heat source outlet end is connected to the refrigerant storage system 205 through a pipeline;

[0115] The cold source inlet end of the cold source is connected to the solution pump 211 through a pipeline, and the cold source outlet end is connected to the refrigerant concentrated solution storage device 210 through a pipeline;

[0116] The heat recovery heat exchanger 300 is used to recover the heat contained in the high-temperature refrigerant at the outlet of the second condensing module 202 to heat the low-temperature solution in the refrigerant absorption storage system 206 .

[0117] Optionally, the heat source inlet end of at least one heat source is connected to the first generating module 201 through a pipeline, and the heat source outlet end is connected to the refrigerant analysis and storage system through a pipeline;

[0118] The cold source inlet end of the cold source is connected to the solution pump 211 through a pipeline, and the cold source outlet end is connected to the refrigerant concentrated solution storage device 210 through a pipeline;

[0119] The heat recovery heat exchanger 300 is used to recover the heat contained in the high-temperature solution at the outlet of the first generating module 201 to heat the low-temperature solution in the refrigerant absorption storage system 206 .

[0120] Reference Figure 4 As an implementation mode, the regenerative heat exchanger 300 includes two heat sources and one cold source, the heat sources include a third heat source 340 and a fourth heat source 350, and the cold source includes a second cold source 360;

[0121] The heat source inlet end of the third heat source 340 is connected to the second condensing module 202 through a pipeline, and the heat source outlet end is connected to the refrigerant intermediate storage system 205 through a pipeline;

[0122] The heat source inlet end of the fourth heat source 350 is connected to the first generating module 201 through a pipeline, and the heat source outlet end is connected to the refrigerant analysis and storage system through a pipeline;

[0123] The cold source inlet end of the second cold source 360 ​​is connected to the solution pump 211 through a pipeline, and the cold source outlet end is connected to the refrigerant concentrated solution storage device 210 through a pipeline;

[0124] The heat recovery heat exchanger 300 is used to recover the heat contained in the high-temperature refrigerant at the outlet of the second condensing module 202 and the high-temperature solution at the outlet of the first generating module 201 to heat the low-temperature solution in the refrigerant absorption storage system 206.

[0125] In some possible embodiments, PCM microcapsules or PCM plates are embedded in the wall or pipe of the regenerative heat exchanger 300, in which phase change materials are integrated and stored, and the latent heat storage capacity of the phase change materials is utilized to increase the heat capacity of the regenerative heat exchanger 300, smooth temperature fluctuations, and improve system stability.

[0126] Embodiment 3:

[0127] In this embodiment, the total capacity of the second evaporation module 204 matches the sum of the converted refrigeration capacity of the refrigerant storage system 205 and the converted refrigeration capacity of the first generation module 201 of the second thermal system 200 at full load operation.

[0128] The second evaporation module 204 serves as a buffer zone to adjust the energy difference between the refrigerant storage system 205 and the second thermal system 200, avoid system overload or energy shortage, ensure stable operation of the system under different working conditions, and optimize energy conversion efficiency.

[0129] Reference Figure 5 and 6 In some possible embodiments, the second evaporation module 204 includes at least two stages of evaporation units, and each stage of the evaporation unit is connected to the refrigerant intermediate storage system 205 through a throttle valve 203;

[0130] The refrigerant absorption storage system 206 includes a multi-stage absorber 209 having the same number as the evaporation unit, and each stage of the absorber 209 is connected to the corresponding evaporation unit through a pipeline;

[0131] The second evaporation module 204 is used to cool down the cooled medium, and the cooled medium passes through each stage of evaporation units in sequence.

[0132] The cascade design of multi-stage evaporation units and corresponding number of absorbers 209 is adopted, and the throttle valve 203 is precisely connected to the refrigerant storage system 205, and the cooling medium flows in sequence between the evaporation units at each level, so as to realize the cascade energy utilization and refined control of the refrigeration process. This design can not only improve the heat exchange efficiency of the system and reduce irreversible losses, but also realize more accurate temperature control and more flexible load adjustment. At the same time, it improves the system reliability through multi-stage backup, which is especially suitable for large-scale refrigeration needs under complex working conditions, fully reflects the technical characteristics of energy saving and high efficiency, and provides an advanced cooling method for the industrial refrigeration field.

[0133] As an implementation method, the multi-stage evaporation units are arranged in descending order according to the temperature, and the cooled medium passes through the evaporation units of each stage in descending order according to the temperature. This technical solution fully reflects the basic principle of thermodynamic energy cascade utilization, optimizes the heat transfer process and improves the overall heat exchange efficiency of the system by maintaining a large temperature difference driving force and reducing irreversible losses. This top-down temperature cascade method can not only maximize the heat exchange potential of each stage of the evaporation unit, but also effectively reduce the energy consumption of the system and enhance the accuracy and stability of temperature control.

[0134] As an implementation method, the multi-stage absorbers 209 are arranged in order from low to high pressure, and the absorbers 209 at each stage are connected in series through the absorption solution pump 470 or pipeline, wherein the absorber 209 at the lowest pressure level is connected to the refrigerant analysis storage system through the pressure reducing valve 208, and the absorber 209 at the highest pressure level is connected to the refrigerant concentrated solution storage device 210 of the refrigerant absorption storage system 206, which fully considers the rational use of the pressure gradient in the thermodynamic system and realizes the orderly transmission and step-by-step regulation of the internal pressure of the system. This pressure cascade method can not only optimize the absorption and analysis process of the refrigerant under different pressure environments, but also improve the overall mass transfer efficiency of the system, reduce energy loss, and enhance the stability and reliability of the system operation.

[0135] Reference Figure 5 and 6 Optionally, the second evaporation module 204 includes a low-temperature evaporation unit 410 and a high-temperature evaporation unit 420, the low-temperature evaporation unit 410 is connected to the refrigerant intermediate storage system 205 through a low-temperature throttle valve 430, and the high-temperature evaporation unit 420 is connected to the refrigerant intermediate storage system 205 through a high-temperature throttle valve 440;

[0136] The refrigerant absorption storage system 206 includes a low-pressure absorber 450 and a high-pressure absorber 460;

[0137] The low-pressure absorber 450 is connected to the low-temperature evaporation unit 410 through a pipeline, and is connected to the refrigerant analysis and storage system through the pressure reducing valve 208;

[0138] The high-pressure absorber 460 is connected to the high-temperature evaporation unit 420 through a pipeline, is connected to the low-pressure absorber 450 through a pipeline, and is connected to the refrigerant concentrated solution storage device 210 through a pipeline.

[0139] Reference Figure 5 As an implementation mode, the low-pressure absorber 450 is arranged above the high-pressure absorber 460 to maintain the pressure difference by the height difference.

[0140] Reference Figure 6 As another embodiment, the high-pressure absorber 460 is connected to the low-pressure absorber 450 via an absorption solution pump 470 .

[0141] Embodiment 4:

[0142] This embodiment provides a design method for a coupled refrigeration and cooling decoupling system, including:

[0143] Set the pressure p of the first generating module 201 g ;

[0144] Set the first generating module 201 to output the refrigerant dilute solution concentration c o ;

[0145] According to p g , determine the refrigerant solution concentration c o The corresponding saturation temperature t s1 ;

[0146] Set the first generating module 201 to drive the temperature difference ΔT g ;

[0147] Determine the first generating module 201 driving temperature requirement T g =t s +ΔT g ;

[0148] Select the working fluid of the heat pump system;

[0149] According to the physical properties of the working fluid in the heat pump system, the saturation temperature T is determined. g The corresponding pressure is the outlet pressure P of the heat pump system compressor 101 c ;

[0150] According to the thermophysical properties of the refrigerant and the pressure p of the second condensing module 202 c , determine the refrigerant saturation temperature t in the second condensing module 202 c ;

[0151] Set the driving temperature difference ΔT of the second condensing module 202 c , determine the cooling driving temperature T of the second condensing module 202 c =t c -ΔT c ;

[0152] According to T c Determine the pressure p of the heat pump working fluid after throttling v ;

[0153] Determine the pressure ratio of the heat pump compressor 101 π=P c / p v .

[0154] In this embodiment, a step-by-step derivation and optimization process of system parameters is adopted, starting from the initial pressure and concentration setting of the first generating module 201, and gradually determining various key parameters of the system through thermodynamic relationships, including saturation temperature, driving temperature difference, compressor 101 pressure and pressure ratio, etc. This top-down parameter design method not only ensures the thermodynamic matching and coordination between the various components of the system, but also can achieve the optimal configuration of system performance. At the same time, by reasonably setting the driving temperature difference and pressure parameters, the energy efficiency and economy of the system are effectively balanced.

[0155] In summary, compared with the prior art, the above embodiments have at least the following technical advantages:

[0156] 1. Multi-system energy coupling and time decoupling: Through the innovative coupling of compression heat pump system and absorption / adsorption refrigeration system, the non-material exchange energy coupling of the two thermal systems is realized. Compared with the traditional single refrigeration system, this technology introduces multiple intermediate storage systems, realizes the time decoupling of refrigeration and cooling, and can be intelligently adjusted according to peak and valley electricity prices, load demand, etc., significantly improving the system's energy utilization efficiency and operational flexibility;

[0157] 2. Stepped heat energy utilization and precise temperature control: The cascade design of multi-stage evaporation units and absorber 209 is adopted, and the cooled medium passes through each level of units in order according to the temperature from high to low. This design is different from the traditional uniform temperature refrigeration system, which fully reflects the principle of step-by-step utilization of thermodynamic energy, optimizes the heat transfer process by maintaining a large temperature difference driving force, and improves the overall heat exchange efficiency and temperature control accuracy of the system;

[0158] 3. Intelligent matching of system parameters: Innovatively proposed a system design method that gradually derives from the initial parameters of the generating module, and accurately determines key parameters such as saturation temperature, driving temperature difference, and compressor 101 pressure through thermodynamic relationships. This top-down parameter design method, different from traditional empirical design, can ensure the thermodynamic matching between system components, achieve the optimal configuration of system performance, and effectively balance the energy efficiency and economy of the system.

[0159] The above-mentioned embodiments are only preferred embodiments of the present invention and cannot be used to limit the scope of protection of the present invention. Any non-substantial changes and substitutions made by technicians in this field on the basis of the present invention shall fall within the scope of protection required by the present invention.

Claims

1. A coupled refrigeration and cooling decoupling system, characterized in that: include: A first thermal system includes a first condensation module and a first evaporation module; The second thermal system includes a first generating module and a second condensing module; The first condensing module drives the first generating module to vaporize by releasing heat through condensation, thereby performing energy coupling of non-material exchange; the first evaporating module drives the second condensing module to condense by absorbing heat through evaporation, thereby performing energy coupling of non-material exchange.

2. A coupled refrigeration and cooling decoupling system as claimed in claim 1, characterized in that: The first thermal system is a compression heat pump system; The second thermal system is an absorption refrigeration system or an adsorption refrigeration system.

3. A coupled refrigeration and cooling decoupling system as claimed in claim 2, characterized in that: The second thermal system also includes: Refrigerant central storage system; Refrigerant absorption intermediate storage system, the capacity matches the refrigerant intermediate storage system; The refrigerant desorption intermediate storage system has a capacity matching that of the refrigerant intermediate storage system.

4. A coupled refrigeration and cooling decoupling system as claimed in claim 3, characterized in that: The refrigerant intermediate storage system is connected to the outlet of the second condensing module of the second thermal system through a pipeline, and is used to store the refrigerant at the outlet of the second condensing module; The refrigerant intermediate storage system is connected to the second evaporation module pipeline in the second thermal system through a throttle valve.

5. A coupled refrigeration and cooling decoupling system as claimed in claim 3, characterized in that: The refrigerant absorption intermediate storage system comprises a pressure reducing valve, an absorber and a refrigerant concentrated solution intermediate storage device; The absorber is connected to the pipeline after the pressure reducing valve through a pipeline, and the refrigerant concentrated solution storage device is connected to the pipeline between the downstream of the absorber and the first generating module through a pipeline. Its capacity can accommodate the refrigerant concentrated solution generated after all the refrigerants in the refrigerant storage system are completely absorbed by the refrigerant dilute solution after throttling expansion and evaporation and heat absorption.

6. A coupled refrigeration and cooling decoupling system as claimed in claim 5, characterized in that: The refrigerant concentrated solution storage device is arranged at the lower part of the absorber, and collects the refrigerant concentrated solution generated by the absorber absorbing the refrigerant vapor by gravity.

7. A coupled refrigeration and cooling decoupling system as claimed in claim 5, characterized in that: The refrigerant desorption storage system comprises a solution pump and a refrigerant dilute solution storage device; The solution pump is arranged on the pipeline between the refrigerant concentrated solution storage device and the first generating module; The refrigerant dilute solution intermediate storage device is connected to the pipeline from the downstream of the first generating module to the pressure reducing valve through a pipeline, and its capacity can accommodate the refrigerant dilute solution generated after desorption of all refrigerant concentrated solutions in the refrigerant absorption intermediate storage system.

8. A coupled refrigeration and cooling decoupling system as claimed in claim 7, characterized in that: The refrigerant dilute solution storage device is arranged at the lower part of the first generating module, and collects the refrigerant dilute solution generated by desorbing the refrigerant through the first generating module by gravity.

9. A coupled refrigeration and cooling decoupling system according to any one of claims 1 to 8, characterized in that: It also includes a regenerative heat exchanger, wherein the regenerative heat exchanger includes at least one heat source and one cold source, and the heat source and the cold source perform heat exchange in the regenerative heat exchanger; The heat source is a high-temperature medium drawn from the outlet of the first generation module and / or the second condensation module; The cold source is the low-temperature medium before the inlet of the first generating module.

10. A coupled refrigeration and cooling decoupling system as claimed in claim 9, characterized in that: The heat source inlet end of at least one heat source is connected to the refrigerant storage system through a pipeline, and the heat source outlet end is connected to the throttle valve through a pipeline; The cold source inlet end of the cold source is connected to the solution pump through a pipeline, and the cold source outlet end is connected to the first generating module through a pipeline; The heat recovery heat exchanger is used to recover the heat contained in the high-temperature refrigerant in the refrigerant intermediate storage system to heat the low-temperature solution in the refrigerant absorption intermediate storage system.

11. A coupled refrigeration and cooling decoupling system as claimed in claim 9, characterized in that: The heat source inlet end of at least one heat source is connected to the refrigerant desorption storage system through a pipeline, and the heat source outlet end is connected to the pressure reducing valve through a pipeline; The cold source inlet end of the cold source is connected to the solution pump through a pipeline, and the cold source outlet end is connected to the first generating module through a pipeline; The heat recovery heat exchanger is used to recover the heat contained in the high-temperature solution in the refrigerant analysis storage system to heat the low-temperature solution in the refrigerant absorption storage system.

12. A coupled refrigeration and cooling decoupling system as claimed in claim 9, characterized in that: The regenerative heat exchanger comprises two heat sources and one cold source, and the heat sources comprise a first heat source and a second heat source; The heat source inlet end of the first heat source is connected to the refrigerant storage system through a pipeline, and the heat source outlet end is connected to the throttle valve through a pipeline; The heat source inlet end of the second heat source is connected to the refrigerant desorption storage system through a pipeline, and the heat source outlet end is connected to the pressure reducing valve through a pipeline; The cold source inlet end of the cold source is connected to the solution pump through a pipeline, and the cold source outlet end is connected to the first generating module through a pipeline; The heat recovery heat exchanger is used to recover the heat contained in the high-temperature refrigerant in the refrigerant intermediate storage system and the high-temperature solution in the refrigerant absorption intermediate storage system, so as to heat the low-temperature solution in the refrigerant absorption intermediate storage system.

13. The coupled refrigeration and cooling decoupling system according to claim 9, characterized in that: The heat source inlet end of at least one heat source is connected to the second condensing module through a pipeline, and the heat source outlet end is connected to the refrigerant storage system through a pipeline; The cold source inlet end of the cold source is connected to the solution pump through a pipeline, and the cold source outlet end is connected to the refrigerant concentrated solution storage device through a pipeline; The heat recovery heat exchanger is used to recover the heat contained in the high-temperature refrigerant at the outlet of the second condensing module to heat the low-temperature solution in the refrigerant absorption storage system.

14. The coupled refrigeration and cooling decoupling system according to claim 9, characterized in that: The heat source inlet end of at least one heat source is connected to the first generating module through a pipeline, and the heat source outlet end is connected to the refrigerant analysis and storage system through a pipeline; The cold source inlet end of the cold source is connected to the solution pump through a pipeline, and the cold source outlet end is connected to the refrigerant concentrated solution storage device through a pipeline; The heat recovery heat exchanger is used to recover the heat contained in the high-temperature solution at the outlet of the first generating module to heat the low-temperature solution in the refrigerant absorption storage system.

15. The coupled refrigeration and cooling decoupling system according to claim 9, characterized in that: The regenerative heat exchanger comprises two heat sources and one cold source, and the heat sources comprise a third heat source and a fourth heat source; The heat source inlet end of the third heat source is connected to the second condensing module through a pipeline, and the heat source outlet end is connected to the refrigerant storage system through a pipeline; The heat source inlet end of the fourth heat source is connected to the first generating module through a pipeline, and the heat source outlet end is connected to the refrigerant analysis and storage system through a pipeline; The cold source inlet end of the cold source is connected to the solution pump through a pipeline, and the cold source outlet end is connected to the refrigerant concentrated solution storage device through a pipeline; The heat recovery heat exchanger is used to recover the heat contained in the high-temperature refrigerant at the outlet of the second condensing module and the high-temperature solution at the outlet of the first generating module to heat the low-temperature solution in the refrigerant absorption storage system.

16. A coupled refrigeration and cooling decoupling system according to any one of claims 3 to 8 and 10 to 15, characterized in that: The total capacity of the second evaporation module matches the sum of the converted refrigeration capacity of the refrigerant storage system and the converted refrigeration capacity of the first generating module of the second thermal system at full load operation.

17. A coupled refrigeration and cooling decoupling system as claimed in claim 16, characterized in that: The second evaporation module comprises at least two stages of evaporation units, and each stage of the evaporation unit is connected to the refrigerant intermediate storage system through a throttle valve; The refrigerant absorption and storage system comprises a plurality of absorbers of the same number as the evaporation units, and each absorber of each stage is connected to a corresponding evaporation unit through a pipeline; The second evaporation module is used to cool down the cooled medium, and the cooled medium passes through each stage of evaporation units in sequence.

18. A coupled refrigeration and cooling decoupling system as claimed in claim 17, characterized in that: The multi-stage evaporation units are arranged in order from high to low temperature, and the cooled medium passes through the evaporation units of each stage in order from high to low temperature.

19. A coupled refrigeration and cooling decoupling system as claimed in claim 17, characterized in that: The multiple levels of absorbers are arranged in order from low to high pressure, and the absorbers at each level are connected in series through an absorption solution pump or pipeline, wherein the absorber at the lowest pressure level is connected to the refrigerant analysis intermediate storage system through a pressure reducing valve, and the absorber at the highest pressure level is connected to the refrigerant concentrated solution intermediate storage device of the refrigerant absorption intermediate storage system.

20. The coupled refrigeration and cooling decoupling system according to claim 16, characterized in that: The second evaporation module includes a low-temperature evaporation unit and a high-temperature evaporation unit, the low-temperature evaporation unit is connected to the refrigerant intermediate storage system through a low-temperature throttle valve, and the high-temperature evaporation unit is connected to the refrigerant intermediate storage system through a high-temperature throttle valve; The refrigerant absorption storage system comprises a low-pressure absorber and a high-pressure absorber; The low-pressure absorber is connected to the low-temperature evaporation unit through a pipeline, and is connected to the refrigerant analysis and storage system through a pressure reducing valve; The high-pressure absorber is connected to the high-temperature evaporation unit through a pipeline, connected to the low-pressure absorber through a pipeline, and connected to the refrigerant concentrated solution storage device through a pipeline.

21. A coupled refrigeration and cooling decoupling system as claimed in claim 20, characterized in that: The low-pressure absorber is arranged above the high-pressure absorber, and the pressure difference is maintained by the height difference.

22. A coupled refrigeration and cooling decoupling system as claimed in claim 20, characterized in that: The high-pressure absorber is connected to the low-pressure absorber via an absorption solution pump.

23. A design method for a coupled refrigeration and cooling decoupling system according to any one of claims 2 to 22, characterized in that: include: Set the first generating module pressure p g ; Set the refrigerant dilute solution concentration c of the first generating module output o ; According to p g , determine the refrigerant solution concentration c o The corresponding saturation temperature t s1 ; Set the first generating module to drive the temperature difference ΔT g ; Determine the first generation module driving temperature requirement T g =t s +ΔT g ; Select the working fluid of the heat pump system; According to the physical properties of the working fluid in the heat pump system, the saturation temperature T is determined. g The corresponding pressure is the heat pump system compressor outlet pressure P c ; According to the thermal properties of the refrigerant and the pressure p of the second condensing module c , determine the refrigerant saturation temperature t in the second condensing module c ; Set the driving temperature difference ΔT of the second condensation module c , determine the cooling drive temperature T of the second condensing module c =t c -ΔT c ; According to T c Determine the pressure p of the heat pump working fluid after throttling v ; Determine the heat pump compressor pressure ratio π=P c / p v .

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