A cooling system and method with condensation control, hybrid feeding, redundancy, and dynamic phase management at low ambient temperatures.

TR202613154A2Pending Publication Date: 2026-08-21COOLAER İKLİMLENDİRME SİSTEMLERİ ANONİM ŞİRKETİ
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Patent Information

Application Number
TR202613154
Authority / Receiving Office
TR · TR
Patent Type
Applications
Current Assignee / Owner
Filing Date
2026-08-04
Publication Date
2026-08-21

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Abstract

The invention relates to a refrigeration system and method developed to eliminate technical problems arising from excessive condensation in the condenser and heat exchanger lines at low ambient temperatures, resulting in low-pressure blockage, instability in the evaporator supply, risks of interruption due to the non-redundant system structure, and the unnecessarily continuous high energy consumption of the compressor.
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Description

1 TARIFF HYBRID WITH CONDENSATION CONTROL AT LOW AMBIENT TEMPERATURES A cooling system with feed-in, redundant, and dynamic phase management. METHOD Technical Area 5 The invention describes a condensation-controlled, hybrid-fed, redundant system operating at low ambient temperatures. It relates to a dynamic phase-managed cooling system and method. State of the Art In the current state of the art, in conventional refrigeration cycles, the refrigerant is a Compressed by means of a compressor, it passes through a condenser unit at high pressure and temperature. It is sent here, where it is condensed and then passed through an expansion element. The water is passed through to the evaporator. In the evaporator, it absorbs the ambient heat and evaporates. The fluid completes the cycle by returning to the compressor suction line. This type in systems, especially during winter months or when low outdoor temperatures prevail In geographical regions, due to the increase in the heat transfer coefficient on the condenser surface, 15 the refrigerant transitioned to the liquid phase much faster and more intensely than expected, In other words, it is known that excessive condensation occurs. This excessive condensation takes place in the condenser. Condensation and cooling affect the critical pressure values ​​on the high-pressure side of the system. This causes levels to fall below these values, in other words, it leads to a low-pressure blockage. Reducing the pressure difference between the condenser and the evaporator requires the expansion element to be 20 preventing stable operation and ensuring sufficient and homogeneous fluid supply to the evaporator. This prevents the process from being completed. As a result, the system operates unstably. Entering the operating regime, the compressor is damaged due to frequent start-stop movements (hunting). This is observed, and the overall system efficiency decreases significantly. There are various solutions to this problem in the current state of the art. 25 These include reducing or completely stopping the speed of the condenser fans. stopping, using condenser pressure control valves and compressor pressure methods such as laying hot gas bypass lines from the pipeline to the condenser outlet These solutions can be considered. However, the solutions mentioned also come with a number of technical disadvantages. It brings. Primarily, 30 based on fan control or conventional bypass arrangements. The methods focus solely on equalizing the mechanical pressure entering the evaporator. 2 dynamic instantaneous liquid-vapor phase distribution of the fluid and feed flow rate It does not allow for management. Furthermore, it is problematic in critical industrial applications and for data. in their centers, run through a single compressor or a single condenser block. Any malfunction during operations could shut down the entire system and cause significant production disruption. or is known to lead to business losses; since existing systems have redundant 5 There is no structure that would allow for work. In addition, the outside temperature... The main driving element for the fluid to complete its cycle even when its level is very low. as a result, compressors that consume high energy continuously continue to be used, whereas a fluid that has completely passed into the liquid phase and does not require high pressure It has been observed that the use of compressors in transportation leads to a significant energy loss. 10 On the other hand, in current systems, the condenser capacity is determined by a single shell or block. Due to being managed through it, the condenser can operate at partial loads or in extremely cold conditions. The inability to effectively divide the surface area makes precise temperature and condensation control difficult. This prevents it from being done. In the current state of the art, the refrigerant also cools at low ambient temperatures. pump-assisted freewheeling, which conveys water to the evaporator with the help of a pump instead of a compressor. Some applications referred to as refrigeration cycles are also known. However, These systems are either in compressor mode only or pump mode only, open- It appears to operate with a sharp transition via shut-off or diverter valves. This situation causes sudden pressure fluctuations in the system during mode transitions, evaporator 20 This leads to interruptions in the power supply and instabilities in the expansion elements. In summary, under the current state of the technology, depending on the changing external environmental load, both the compressor-expansion line and the pump line flow simultaneously at different rates. a flexible hybrid structure that offers simultaneous and dynamic phase and flow rate management. This is not the case. This situation means that system stability is 25 at low ambient temperatures. in terms of protection, reduction of energy consumption and ensuring business continuity its existence as an unsolved technical problem in the known state of the art It continues. In conclusion, due to the negative aspects described above and the current solutions being the subject of discussion... Due to its shortcomings, an improvement in the relevant technical field is necessary. 30 It has been made. 3 Purpose of the Invention The invention was created by drawing inspiration from existing situations and overcoming the aforementioned drawbacks. It aims to solve the problem. The invention describes a process described in the prior art and at low ambient temperatures. from excessive condensation occurring in the condenser and heat exchanger lines, and the resulting 5 from low-pressure blockage, instability in evaporator supply, system without redundancy from the risks of interruptions due to its structure and the unnecessary continuous operation of the compressor in order to eliminate technical problems arising from high energy consumption It has been developed. The aim of the invention is to eliminate the aforementioned drawbacks by reducing low environmental impact. even at high temperatures, a continuous, stable and energy-efficient cooling cycle 10 to provide. Another objective of the invention is to increase the flow rate of the fluid in the evaporator feed line and the liquid-vapor ratio. an intelligent control unit that manages the phase ratio based on real-time sensor data, and dynamically controlling it via a variable speed pump, and thus The goal is to stabilize the evaporator feed under all operating conditions. 15 Another purpose of the invention is to create a primary compressor and a secondary compressor connected in parallel. by using a compressor to provide redundancy in critical components and thus even in the event of a malfunction or maintenance on one of the compressors The goal is to ensure the system operates without interruption. Another objective of the invention is to combine the condenser or heat exchanger structure with a primary heat exchanger and 20 By dividing it to have a second heat exchanger, the condenser capacity is reduced externally. to enable flexible management even at ambient temperatures; thus allowing for extreme The aim is to prevent condensation and the resulting pressure drop. Another aim of the invention is to create a safe environment where the ambient temperature is very low and the fluid is completely saturated. In operating conditions where it transitions to the liquid phase, 25 instead of high energy consuming compressors. by engaging a variable speed pump that consumes relatively less energy, the fluid to complete the cycle, thereby reducing the compressor load and the system's total energy The goal is to reduce consumption and improve the performance coefficient. Another objective of the invention is to combine a dynamic bypass line with an auxiliary flow line. By integrating it, the pressure that may occur within the system is 30. to dampen fluctuations quickly and to transfer the fluid to the heat exchanger connection 4 by directing the system to the most suitable route via the main return line or the main return line. The goal is to improve its functioning. Another purpose of the invention is to analyze temperature from high and low pressure sensors. from sensors, superheat sensors, level sensors and flow sensors By processing the obtained data by the intelligent control unit, the bypass valve and 5 The mechanical components of the system, primarily solenoid valves, are fully automated. The goal is to ensure it operates flawlessly without requiring human intervention. The structural and characteristic features and all the advantages of the invention are given in the figures below. This becomes clearer thanks to the detailed explanation written with references to these figures. This will be understood, and therefore the evaluation should also take these forms and detailed explanations into account. 10 It needs to be done by taking precautions. Figures that will help understand the invention. Figure 1 shows the general structure of the cooling system that is the subject of the invention and the relationship between its components. It is a schematic view showing the structural relationship. Figure 2 shows the bidirectional flow of 15 through the evaporator expansion element line and the pump line. This is a detailed view showing the feeding (hybrid feeding) mechanism. Figure 3 shows the pump-assisted energy saving of the system under low ambient temperature conditions. This is the flowchart in (economy) mode. Figure 4 shows the system instrumentation structure and the intelligent control unit with sensors. This is a block diagram showing the signal / data connections on the actuators. 20 Figure 5 shows the dynamic bypass control that ensures intra-system pressure and phase balance. This is a decision tree flowchart for the algorithm. Explanation of Part References 1a First compressor unit 1b Second compressor unit 25 2a First heat exchanger 2b Second heat exchanger 4. Liquid storage and distribution center. Electronic expansion element 6 Evaporators 30 7 Pumps 12 Auxiliary flow lines 13 Smart control units 41 Common manifold 61 Main return line 100 Oil separator 5 102 Level sensor 103 First solenoid valve 104 Second solenoid valve 105 Check Valve 106 Bypass valve 10 107 High pressure sensor 108 Low pressure sensor 109 Condenser / heat exchanger temperature sensor 110 Evaporator temperature sensor 111 Superheat temperature sensor 15 112 Flow sensor Detailed Description of the Invention This detailed description explains that the invention involves controlled condensation at low ambient temperatures. The preferred cooling system is a hybrid-fed, redundant, and dynamically phase-managed cooling system. Their structures are explained solely for the purpose of better understanding the subject. 20 The subject of the invention is a condensation-controlled, hybrid-fed, redundant system operating at low ambient temperatures. A dynamic phase-managed refrigeration system uses refrigerant as its basic structural component. compressing to reach high pressure and having redundant or capacity-sharing systems. a first compressor unit (1a) suitable for operation and a second compressor It houses the compressor unit (1b). The mentioned compressor units (1a, 1b) 25 On the discharge line, the oil circulating within the system is separated and transferred to the compressor crankcases. An oil separator (100) is positioned to enable its return. The system uses high-temperature and high-pressure gas coming from the compressor units (1a, 1b). Two components that can be connected in parallel or series to condense the fluid in its phase It has a segmented condenser / heat exchanger arrangement. The mentioned arrangement consists of a primary heat exchanger of 30°C. heat exchanger (2a) and a second heat exchanger (2b) and an evaporator (6) supporting them This occurs. Heat exchangers (2a, 2b) have a common connection among themselves. It is in fluid communication via the manifold (41). 6 The refrigerant that condenses into the liquid phase in the heat exchangers (2a, 2b) is transferred to a main return. by passing through the line (61) where the fluid is stored, phase separation is carried out and It is sent to a liquid storage and distribution center (4) where it is distributed to the system. Within the aforementioned liquid storage and distribution center (4), the liquid level inside is monitored instantly. There is a level sensor (102) that measures as 5 At the outlet of the liquid reservoir and distribution centre (4), the fluid feeds an evaporator (6) A hybrid supply structure is created by routing through two different functional lines for this purpose. It is formed by: The first line, or expansion line, reduces the pressure of the fluid. It contains an electronic expansion element (5) that conveys to the evaporator (6), this line It is opened by means of the first solenoid valve (103) and the second solenoid valve (104) 10 It can be shut off. The second line, the pump support line, carries the fluid in the liquid phase and at a high temperature. variable speed which can transmit directly to the evaporator (6) without needing mechanical pressure It includes a pump (7); the aforementioned pump (7) on the line prevents reverse flows. A check valve (105) is positioned for this purpose. The system also includes a direct transfer of hot gas from the compressor discharge line to the liquid tank and 15 by directing into the distribution centre (4) or into the auxiliary flow lines (12) within the system There is a dynamic bypass line that ensures pressure and temperature balance. This line flow control on it is via a bypass valve (106) which is proportional or on-off. This is being carried out. All mechanical and electronic components of the system are under high pressure. from sensor (107), low pressure sensor (108), condenser / heat exchanger temperature 20 from the sensor (109), evaporator temperature sensor (110), superheat temperature data from the sensor (111), level sensor (102) and flow sensor (112) by a smart control unit (13) that operates in real time and continuously It is managed. In a preferred configuration of the invention, the common manifold (41), electronic 25 common fluids coming from expansion element (5) line and pump (7) line directing through the junction manifold (41) to the evaporator (6) shell It is structured in a way that will provide this. In an alternative structure, the aforementioned lines, The evaporator (6) is directly connected to the evaporator (6) via separate inlets independent of each other. It can be arranged in such a way as to be connected. The system is designed so that the evaporator (6) outlet pressure is 30 If it falls below a predetermined threshold, it automatically switches to a low ambient temperature. switching to temperature-assisted operating mode, in other words, pump-assisted economy mode. It is structured in a way that will do so. 7 The cooling system described in this invention is designed to withstand varying ambient temperatures and load conditions. According to the smart control unit (13), it works with stable and high efficiency. This is achieved through a control algorithm. In the first step of this algorithm, a smart control unit (13), high pressure sensor (107), low pressure sensor (108), from superheat sensor (111), level sensor (102) and flow sensor (112) 5 It continuously scans and records the incoming data. In the next step, the first and second High pressure data from the heat exchanger (2a, 2b) outlet is sent to the intelligent control unit (13) This is compared against a predefined critical threshold value, for example, 12 bar. When the measured pressure exceeds the threshold value, the system switches to normal operating mode. it continues; when the measured pressure falls below the threshold value, the outside temperature is 10 It was determined that the ambient temperature was very low and excessive condensation had started, so the system was switched to a low-temperature environment. The temperature mode is being activated. In normal operating mode, the first compressor unit (1a) and / or the second The compressor unit (1b) is engaged as the main drive element and the heat exchangers (2a, 2b) All of these and their associated fans are operating effectively. The fluid is in the liquid tank 15 and after the outlet of the distribution centre (4) by the guidance of solenoid valves (103, 104) It is transmitted to the evaporator (6) by passing through the electronic expansion element (5) and The classic cooling cycle is carried out in this way. If the pressure remains below the threshold value, the intelligent control unit (13) sends a signal to the system. It is carrying out a two-stage intervention. In the first stage of this intervention, the second heat 20 By completely or partially disabling the changer (2b) and its associated fans, the total The condensation surface area is reduced, thus preventing excessive condensation and achieving high condensation levels. The pressure drop on the pressure side is being slowed down. In the second stage, dynamic bypass is used. By opening the bypass valve (106) on the line, the hot and high-pressure water coming out of the compressor is released. gas fluid, direct liquid storage and distribution via auxiliary flow lines (12) 25 The liquid is directed into the central (4) or to the condenser outlet; this allows the liquid to be directed into the reservoir. and instantaneous pressure and temperature of the liquid fluid inside the distribution centre (4) It is being balanced. The pressure difference between the first heat exchanger (2a) and the evaporator (6) is determined electronically. The expansion element (5) works stably on its own and the evaporator (6) 30 If the supply is insufficient, the intelligent control unit (13) will power the first and second Instead of completely shutting down the compressor unit (1a, 1b), it can be switched off according to the requirements of the external load. It can continue to operate at the minimum frequency. During this time, it operates at a variable speed. 8 The pump (7) is activated. The intelligent control unit (13) receives flow sensor (112) and According to the instantaneous data received from the superheat sensor (111), the fluid entering the evaporator (6) In order to improve the liquid / vapor phase ratio, electronic expansion with pump (7) line element (5) line at simultaneous and variable flow rates, i.e. in combined form It operates. The system depends on the external environmental conditions becoming completely stable. 5 by completely shutting down the compressor units (1a, 1b) and reducing the entire circulation load. It also has the flexibility to transfer to the pump (7). This simultaneous and incremental transfer structure, thermodynamic shocks and pressure drops that can occur during mode transitions It prevents blockages. When the pump (7) is running, the level sensor inside the liquid reservoir and distribution center (4) is 10 (102) When it detects that the liquid level has fallen below a critical value, the pump (7) In order to prevent cavitation from occurring by running without water, the pump (7) immediately is stopped and the system automatically restarts the electronic expansion element (5) line It is switched to safe mode so that it will feed power through. In addition, especially at low ambient temperatures and during transfers made with a pump (7), the flow is 15 Due to the decrease in speed, the compressor oil accumulated in the evaporator (6) returns In order to gain, the intelligent control unit (13) shortens the system at certain time periods. It switches to a high-flow oil sweeping mode for a short time. Through the oil separator (100) After the oil is returned to the compressors, the system returns to the data scanning step. It makes the loop continuous by rotating. 20 The system in question uses an evaporator (6) as both an expansion element (5) and a variable Thanks to its structure that can feed bi-directionally, i.e. in a hybrid manner, through the rotary pump (7), low pressure blockage experienced by conventional systems, especially in winter conditions It solves the problem. The mechanical compression work of the compressor units (1a, 1b) is completely solved. Instead of taking over, the kinetic energy of the liquefied fluid is transferred to a low-power pump (7) 25 Increasing the cycle to complete the process increases the total energy consumption across the system. It reduces and improves the system's performance coefficient. The application methods, parameters, and control steps given below constitute the subject of the invention. Examples have been provided to help to better understand the cooling system, This should not be interpreted as narrowing or restricting the scope of protection of the invention. 30 In a preferred configuration of the invention, the system described in the invention is fully operational. It dynamically executes its processes through the intelligent control unit (13). intelligent control unit (13); condenser / heat exchanger outlet pressure, evaporator pressure, 9 evaporator outlet temperature, superheat value of the fluid, liquid reservoir and distribution instantaneous fluid level of the fluid inside the center (4) and fluid on the main lines will use at least one of the flow rate parameters, or a combination of them, as input. It is structured in this way. The intelligent control unit (13) scans this input in real time. Depending on its parameters, the flow rate of the variable speed pump (7) is determined by the electronic expansion 5 proportional opening amount of element (5), first and second compressor unit (1a, 1b) operating / stopping or frequency conditions, the first and second heat exchangers (2a, 2b) in parallel, Serial or selective activation / deactivation states and dynamic bypass line It adjusts the opening rate of the bypass valve (106) on it in real time. Thus, the system has three basic characteristics depending on the external environment and internal load conditions. It has been developed to work in a way that minimizes compressor load and fluid low ambient temperature where transfer is mainly provided by variable speed pump (7) mode; used when the outside temperature is high or the cooling load is excessive. High load mode where compressor units (1a, 1b) are the main drive elements; and intermediate transition. With partial load conditions, both electronic expansion 15 determined by the intelligent control unit (13) of the element (5) and the pump (7) line Hybrid operating mode where variable speeds are operated simultaneously. The system's intermodal switching logic and dynamic bypass decision tree form the basis of the system's mechanics. It has been developed to maintain its stability. In normal operating mode, the evaporator (6) outlet 20 when the pressure is above a predefined safe threshold, preferably 12 bar. This mode is maintained; compressor units (1a, 1b) operate in capacity sharing, heat All exchangers (2a, 2b) are in operation and the evaporator (6) is supplied. It is carried out via an electronic expansion element (5). Low ambient temperature In this mode, the pressure value received from the high pressure sensor (107) is the threshold value. When the temperature drops below 25, and the phase of excessive condensation begins, the intelligent control unit (13) first detects 25 By closing the second heat exchanger (2b), the condensation surface is reduced. Simultaneously, By activating the dynamic bypass line and bypass valve (106), the hot air at the compressor outlet is reduced. The gas is pressed into the liquid storage and distribution center (4), so that the liquid temperature and liquid The internal pressure of the warehouse and distribution center is balanced. This is created by the compressors. When the pressure difference becomes insufficient for the evaporator feed, the pump (7) main flow 30 It is activated as a cavitation safety mode. In cavitation safety mode, the pump (7) to prevent mechanical damage to the pump due to cavitation while it is in operation In order to take into account the level sensor (102) inside the liquid reservoir and distribution center (4), it is instantaneous. It is monitored; as soon as the liquid level falls below the critical limit, the pump (7) is stopped and the flow is stopped. It is safely transferred to the fully electronic expansion element (5) line. Oil 35 In the sweeping algorithm, the coolant is used in pump-weighted or low flow rate modes. the compressor oil mixed into the fluid precipitates at the bottom of the evaporator (6) In order to prevent this, the smart control unit (13) temporarily disables the system at certain intervals. switching a compressor into a scavenging mode, in which the flow rate is rapidly increased, the oil, oil is recovered to the oil separator (100) and from there to the compressor crankcases 5 is provided. In a preferred configuration of the invention, the system subject to the invention is fluid management. It has a structure centered on liquid storage and distribution centre (4) in terms of; the liquid mentioned warehouse and distribution centre (4), functions as a liquid warehouse and flow distribution centre. It is seen. The first line branching off from the liquid reservoir and distribution centre (4) is electronic 10 The second line is connected to the first inlet of the evaporator (6) via the expansion element (5); then, via variable speed pump (7) to the second inlet of the evaporator (6) The compressor units (1a, 1b) outlets are routed after the oil separator (100). Passing through heat exchangers (2a, 2b) to the liquid reservoir and distribution centre (4) They are connected. Heat exchangers (2a, 2b), smart control unit (13) commands 15 in parallel, in series or independently selectively It has a valve infrastructure that can be operated. The dynamic bypass line, on the other hand, allows the system pressure to be controlled. For instantaneous balancing purposes, the liquid is directly connected to the condenser / heat exchanger outlet line. The warehouse and distribution centre (4) is located between the body or the inlet line. The system described in this invention makes significant contributions to the technology compared to conventional refrigeration cycles. Accordingly, the system provides evaporator (6) feed from the outside ambient temperature. It provides independent, uninterrupted flow stability and the liquid / vapor phase distribution of the fluid. It effectively controls the load according to the instantaneous condition. At low ambient temperatures. by reducing the compression ratios of the compressor units (1a, 1b) or by reducing the compressors By completely sealing them, they minimize mechanical load and wear. 25 Condenser / heat exchanger capacity of first heat exchanger (2a) and second heat exchanger (2b) By dividing it into two parts, it flexibly eliminates the risk of excessive condensation; critical in the components, namely the dual compressor, dual heat exchanger and dual supply line arrangement Thanks to the redundancy provided, system downtimes are prevented in case of failures. It offers uninterrupted operation. Furthermore, it provides high power even at low ambient temperatures. cycle of low power consuming variable speed pump (7) instead of consuming compressors Thanks to its completion, it reduces the system's total energy consumption and improves performance. It improves the coefficient. Finally, the dynamic bypass line and intelligent control unit (13) 11 Thanks to the algorithm run by [the company], the system pressure can be adjusted during sudden weather changes. It prevents low and high pressure blockages by maintaining stability within seconds. As shown in Figure 5, the dynamic bypass is performed by the intelligent control unit (13). control algorithm (600), real-time control of in-system pressure and phase balance It is operated within a cyclical decision tree structure to ensure this. The algorithm is a 5 The control loop starts with step (602), in which the intelligent control unit (13) monitors the parameters on the system continuously and in real time It is receiving. In the next step, a pressure sensing step (604) is performed, and in this step Data regarding system pressure (P_SYSTEM) and bypass line pressure (P_BYPASS) is available on the smart 10 system. The data obtained is read by the control unit (13). This data is displayed in a decision box. (606) between a predefined lower limit (P_MIN) and an upper limit (P_MAX) The generated range is compared with the desired range. The system pressure (P_SYSTEM) falls outside the desired range, i.e., the decision box... (606) If the "NO" branch is followed, the flow is a temperature sensing step (608a) 15 The system is being guided and an oil temperature (T_OIL) value is being read at this step. Then, a predetermined oil temperature (T_OIL) mentioned in a decision box (610a) whether it is within the desired range between the lower limit (T_MIN) and the upper limit (T_MAX) This is being questioned. If the oil temperature falls outside this range, a bypass ratio is required. By proceeding to adjustment step (612a), the flow rate directed to the bypass line is increased; 20 However, if the oil temperature is found to be within the desired range, then a By proceeding to the pump speed adjustment step (614a), the system pressure is restored. For this purpose, the speed of the pump (7) is adjusted. Determining that the system pressure (P_SYSTEM) is within the desired range, i.e., making a decision. If the "YES" branch of box (606) is followed, the flow is similarly a 25 is directed to the temperature sensing step (608b) and the oil temperature (T_OIL) is measured again. This value is read. This value is again the desired T_MIN–T_MAX in a decision box (610b). It is compared with a range. If the oil temperature falls outside this range, a By proceeding to the bypass ratio adjustment step (612b), the flow is now directed to the main line. In order to increase efficiency, the bypass ratio is reduced; the oil temperature is kept within the desired range of 30. If this is detected, then a pump speed adjustment step (614b) is taken, In order to increase the system efficiency, the speed of the pump (7) is improved. 12 Flows from four separate decision branches (612a, 614a, 612b, 614b) form a common decision. It is assembled in its box (616) and in this box there is no need for a change in the operating mode. It is being assessed whether it has been heard or not. It is determined that a change in approach is needed. If detected, the system will proceed to a mode change step (618), for example Normal operating mode, high load mode, or low ambient temperature (cooling) mode 5 It switches between them. It is determined that there is no need for a mode change. In this case, a step is taken in which the existing settings are preserved and monitoring continues (620) is operated. In both cases the flow reaches a cycle end step (622) and From the aforementioned step, the algorithm is rechecked for the next check cycle. By returning to the cycle initiation step (602), continuous and uninterrupted monitoring and intervention 10 It forms a cycle. The precise pressure of the bypass valve (106) located on the dynamic bypass line stabilization is performed within the intelligent control unit (13) by a PID control loop This is achieved through the condenser / heat exchanger in the aforementioned control loop. A target value for the outlet pressure, i.e., a reference pressure (P_set), is used for system operation. This is determined in advance according to the conditions. This reference pressure (P_set) is high pressure. Instantaneous condenser / heat exchanger outlet pressure (P_meas) measured via sensor (107) It is compared with the other and the difference is calculated as an error value (e). The resulting error value (e) is sent to a PID controller within the intelligent control unit (13). It is transmitted and the aforementioned PID controller consists of three separate computational branches. 20 The first of these is the product of the error value and a proportional gain coefficient (K_P). It is the proportional (P) branch that produces an output proportional to the instantaneous error. The second is the error value. by multiplying the integral over time by an integral gain factor (K_I), integral (I) that produces an output aimed at eliminating the persistent error that has become persistent It is a branch. The third is the derivative of the error value with respect to time, a derivative gain coefficient of 25. By multiplying by (K_D), it produces an output sensitive to the rate of change of the error, thus preventing sudden changes. It is the branch of derivatives (D) that dampens fluctuations in a predictive manner. The aforementioned proportional, By summing the outputs obtained from the integral and derivative branches, a control output (u) is obtained. is being done. The resulting control output (u) is transmitted to an actuator which drives the bypass valve (106). The aforementioned actuator reduces the opening ratio of the bypass valve (106) by percentage. The opening ratio of the bypass valve (106) adjusted in this way, It directly affects the condenser / cooling system and the system's output. 13 It changes the condenser pressure (P_meas). This changing pressure value is high. The pressure is re-measured by the pressure sensor (107) and fed back to the beginning of the cycle. And thus a closed-loop, continuously self-correcting control loop. is being created. In a preferred configuration of the invention, the aforementioned PID control loop, for example, 5 To maintain the condenser outlet pressure (P_meas) at a target value, the bypass valve (106) is structured to adjust in a continuous and proportional manner; thus, by the pressure and temperature-based decision tree structure described above (Figure 5) The defined bypass ratio targets are achieved through smooth and stable transitions via the PID controller. being carried out, avoiding sudden pressure spikes or excessive corrections 10 Mechanical and thermodynamic stresses that may arise are prevented. Thus, The combined use of proportional, integral, and derivative gains (K_P, K_I, K_D) in the system both quick response and consistently error-free operation with minimal oscillation. It provides these qualities simultaneously.

Claims

14 REQUESTS 1. Condensation-controlled, hybrid-fed, redundant, and dynamic system for low ambient temperatures. It is a phase-managed cooling system; its characteristic feature is:  redundant systems that compress the refrigerant to high pressure. a first compressor unit (1a) and a second compressor suitable for operation 5 unit (1b),  To condense the gaseous fluid coming from the compressor units (1a, 1b) a first heat exchanger (2a) and a second heat exchanger configured to (2b),  where the condensed fluid is stored in the first and second heat exchangers (2a, 2b) and 10 a liquid storage and distribution center where it is distributed (4),  an evaporator (6),  Connecting the liquid reservoir and distribution center (4) outlet to the evaporator (6), an electronic expansion that transmits the fluid to the evaporator (6) by reducing its pressure A primary supply line containing element (5), 15  Connecting the liquid reservoir and distribution center (4) outlet to the evaporator (6), a variable speed conveying fluid in liquid phase directly to the evaporator (6) A second supply line containing a pump (7),  Fluid from the discharge line of the compressor units (1a, 1b) to the liquid reservoir and a dynamic bypass line that can direct to the distribution centre (4) and dynamic 20 a bypass valve located on the bypass line (106),  at least one high pressure sensor (107) and one low pressure sensor measuring the system pressure pressure sensor (108),  obtained from the high pressure sensor (107) and the low pressure sensor (108) According to the data, the first and second compressor units (1a, 1b), first and second heating 25 changer (2a, 2b), electronic expansion element (5), pump (7) and an intelligent control unit (13) that controls the bypass valve (106), that measured pressure falls below a predetermined threshold value In this case, the second heat exchanger (2b) can be partially or completely deactivated. will release, open the bypass valve (106) and activate the pump (7) 30 intelligent control unit configured in this way (13) It includes.

2. A cooling system conforming to Claim 1, characterized by its compressor units (1a, 1b) The oil located in the discharge line and circulating within the system is separated and transferred to the compressor. an oil separator (100) to ensure that it is returned to its units (1a, 1b) It includes.

3. A cooling system conforming to claim 1 or 2, with the characteristic of being: 5 from the first supply line. and a common line that directs the fluids from the second feed line to the evaporator (6) It contains a coupling manifold (41).

4. A cooling system suitable for any of the previous requirements, and its feature is; first and a main connecting the second heat exchanger (2a, 2b) to the liquid reservoir and distribution centre (4) It includes a return line (61). 10 5. A cooling system suitable for any of the previous requirements, and its features include: The fluid coming from the discharge line of the compressor units (1a, 1b) is one or more through the auxiliary flow line (12) to the liquid storage and distribution centre (4) It includes a dynamic bypass line that is designed to redirect traffic.

6. A cooling system suitable for any of the previous requirements, and its feature is; first 15 a first solenoid valve (103) to enable the opening and closing of the supply line and It contains a second solenoid valve (104).

7. A cooling system suitable for any of the previous requirements, the feature of which is; second a check valve positioned on the supply line to prevent reverse flow (105) is included. 20 8. A cooling system suitable for any of the previous requirements, and its characteristic is; liquid a level that measures the level of fluid inside the reservoir and distribution centre (4) The liquid level taken from the sensor (102) and the level sensor (102) is at a critical value If it falls below this level, stop the pump (7) and supply the electronic expansion element. It includes an intelligent control unit (13) configured to transfer to line (5). 25 9. A cooling system suitable for any of the previous requirements, and its features include: To determine the liquid / vapor phase ratio of the fluid entering the evaporator (6), a superheat from the temperature sensor (111) and a flow sensor (112) and the superheat temperature sensor According to the data received from (111) and the flow sensor (112), the pump line (7) and the electronic 30 to operate the expansion element (5) line simultaneously and at variable rates It includes a structured intelligent control unit (13). 16 10. A cooling system suitable for any of the previous requirements, and its feature is; first and In addition to the second heat exchanger (2a, 2b), heat from the compressor units (1a, 1b) It contains an evaporator (6) that condenses the fluid in a supportive manner.

11. A cooling system suitable for any of the previous requirements, and its feature is; specific During time periods, the system is briefly switched to a high-flow oil sweeping mode. 5 by taking the oil back to the compressor units (1a, 1b) via the oil separator (100). Intelligent control unit structured to enable the acquisition of (13) It includes.

12. A cooling system suitable for any of the previous requirements, and its feature is; intelligent. The control unit (13) uses a proportional, 10-bit control algorithm via a PID control algorithm. It includes a bypass valve (106) controlled by integral and derivative calculations.

13. A cooling system in accordance with claim 12, the feature of which is to drive the bypass valve (106). It includes a bypass valve actuator (114) and the condenser / heat exchanger outlet pressure a reference pressure value and the measured value taken from the high pressure sensor (107) The difference between the pressure values ​​is calculated as an error value, and error 15 By processing the value with proportional, integral and derivative gains (K_P, K_I, K_D) and bypassing it. PID control based on obtaining a control output transmitted to the valve actuator (114) It includes an algorithm.

14. A cooling system suitable for any of the previous requirements, and its characteristic is; an oil Oil temperature taken from the temperature sensor (113) and oil temperature sensor (113) 20 the desired range between a predetermined lower and upper limit of its value If it stays outside, it will adjust the opening ratio of the bypass valve (106), oil If the temperature value is within the desired range, the speed of the pump (7) It includes an intelligent control unit (13) configured to adjust.

15. A cooling system suitable for any of the previous requirements, and its feature is; system 25 the pressure between a predetermined lower limit value and an upper limit value It will compare the measured pressure to a range that has been established, and if the measured pressure falls outside the range... According to the data received from the oil temperature sensor (113), the bypass valve (106) intelligently configured to adjust the opening ratio or the speed of the pump (7) It includes a control unit (13). 30 17 16. Condensation-controlled, hybrid-fed, and dynamic phase at low ambient temperatures. It is a method for operating a controlled cooling system, and its characteristic feature is;  via a smart control unit (13) from a high pressure sensor (107) and pressure data from a low pressure sensor (108) continuously scanning, 5  Comparing the pressure data with a predetermined threshold value,  If the measured pressure is above the aforementioned threshold value, a first compressor unit (1a) and / or a second compressor unit (1b) main drive will be kept in the circuit as an element and the supply of an evaporator (6) A normal 10 will be carried out via the electronic expansion element (5). maintaining the operating mode,  If the measured pressure falls below the aforementioned threshold value, a primary heat loss occurs. a second heat exchanger (2b) that condenses the fluid together with the heat exchanger (2a) total condensation by partially or completely disabling it reducing the surface area, 15  a bypass valve located on a dynamic bypass line (106) by opening, the discharge line from the compressor units (1a, 1b) directing the fluid to a liquid reservoir and distribution centre (4),  pressure between a primary heat exchanger (2a) and the evaporator (6) in question 20 difference is insufficient for stable operation of the electronic expansion element (5). If this remains, a variable speed pump (7) can be put into operation, the fluid is sent from the liquid reservoir and distribution centre (4) to the evaporator (6) to be done It includes the steps of the process.

17. The method according to claim 16 is characterized by the oil taken from an oil temperature sensor (113) 25 the desired temperature value between a predetermined lower and upper limit. Comparison with the range; the mentioned oil temperature value is outside the desired range. increasing the opening ratio of the bypass valve (106) if it remains; and the oil mentioned If the temperature value is within the desired range, the speed of the pump (7) is The adjustment process includes the following steps. 30 18. Method according to claim 16 or 17; its characteristic is that the pressure data is predetermined. The step of comparing the measured pressure with a threshold value is a predetermined step. 18 Comparison using a range created between a lower limit value and an upper limit value. This is accomplished in this way.

19. The method according to any of claims 16 to 18 is characterized by having a reference pressure. between the value and the measured pressure value received from the high pressure sensor (107) Calculating the difference as an error value; the mentioned error value is proportional, 5 A control output is obtained by processing integral and derivative gains (K_P, K_I, K_D). to be done; and the mentioned control output is a bypass that drives the bypass valve (106). This includes the process step of transmitting the signal to the valve actuator (114).

20. Method according to any of claims 16 to 19, characterized by: liquid storage and distribution. The liquid level value taken from a level sensor (102) inside the centre (4) is critical 10 If the value falls below a certain value, the pump (7) is stopped and the flow is electronically controlled. The process involves transferring the expansion element (5) to the line.