Rotary supercharger ejector refrigeration system

Abstract

This invention relates to a refrigeration system designed as Rotary Supercharger Ejector Refrigeration System to improve the coefficient of performance and to reduce mechanical complexity. The design ensures that the working fluid performs expansion work as it passes through the generator. On the other hand, it eliminates the need for subcooling the liquid entering the pump. The design allows conversion of the high-speed kinetic energy from the ejector's outlet stream into recoverable potential energy. Consequently, the cycle closely approaches the ideal cycle. The rotation of coils increases convective heat transfer between coils and the atmosphere and eliminates the need for a blower as well as a complex mechanical pump. In addition to coil-air heat exchange, the system can be thermally coupled with hot rotating bodies to absorb waste heat and generate effective cooling.

Description

DescriptionTitle of Invention

[0001] Rotary Supercharger Ejector Refrigeration SystemTechnical Field

[0002] The present invention relates to the fields of mechanical and thermodynamic engineering, and more specifically to rotary ejector-cycle refrigeration technologies. Background Art

[0003] Ejector-based refrigeration systems have been studied for over a century and offer notable advantages, including the ability to utilize low-grade heat sources such as industrial waste heat, geothermal energy, and solar thermal energy for cooling purposes. One of the fundamental strengths of these systems is the absence of a mechanical compressor, which reduces system complexity, maintenance costs, vibration, and electrical consumption.

[0004] These advantages have driven extensive research into various ejector technologies such as thermal pumping ejectors, gravitational configurations, and rotary ejector mechanisms.

[0005] Many studies have focused on eliminating mechanical pumping components, even though the majority of energy consumption in ejector-based systems typically occurs within the generator component and the pump consumes relatively minimal power.

[0006] Significant efforts have been made to optimize ejector geometry, working fluid selection, operating pressures and temperatures (evaporator, condenser, generator), fluid flow rates, and internal Mach number.

[0007] For example:• in 2010, Jacek Kaperski introduced a system named Rotational Type of a Gravitational Ejector Refrigerator: A System Balance of the Refrigerant Analysis, published in the International Journal of Refrigeration, Volume 33, Issue 1 [1], wherein centrifugal acceleration replaces gravitational forces. However, in that system, the ejector positioned coaxial with the axis of rotation, unlike in the present invention.• Additionally, a technical report from NTNll titled “Simultaneous Implementation of Rotary Pressure Exchanger and Ejectors for CO2Refrigeration Systems” GL2022 - Proceedings - Trondheim, Norway, June 13-15th 2022 [2],

[0008] Recent advancements in rotary ejector technology have demonstrated substantial efficiency gains through rotational dynamics and Coriolis force utilization. Key studies and patents encompassing, without limitation, this technical foundation includes:

[0009] Academic Research• Zhang et al. (2018) in the Journal of Fluids Engineering analyzed supersonic rotary ejectors, revealing enhanced momentum transfer efficiency with rotational operation, though noting Coriolis-induced instabilities at extreme velocities [3],• Lee & Kim's (2020) International Journal of Heat and Fluid Flow study employed CFD to document Coriolis-driven secondary flows and pressure redistribution in rotating ejector systems [4],• Experimental work by Chen et al. (2019) in Applied ThermalEngineering demonstrated a 15% efficiency improvement in refrigeration cycles using rotary ejectors [5],• Muller et al. (2021 ) in Aerospace Science and Technology emphasized Coriolis force compensation requirements to maintain flow stability in rotational designs [6],

[0010] Patent Literature• The US 9,068,743 system (2015) pioneered vacuum generation via centrifugal ejector rotation [7],• EP 3,025,421 (2016) introduced a rotating fluid ejector with optimized mixing through controlled Coriolis effects. (As documented in Patent EP 3,025,421 , conventional rotary systems exhibit significant degradation in entrainment ratio at high rotational speeds (exceeding1500 RPM) [8],• CN 106,194,183 (2017) achieved high efficiency using internal guide vanes to manage rotational flow dynamics [9],• DE 10,2018, 112,789 (2020) featured active Coriolis compensation mechanisms for stable operation

[0010] ,• US 8,123,491 (2012) demonstrated Coriolis-enhanced fluid pumping principles applicable to ejector systems

[0011] ,

[0011] Despite the aforementioned efforts, Ejector-Based Refrigeration Systems have not gained widespread popularity due to their relatively low coefficient of performance (COP) in comparison with vapor-compression and absorption systems. The low COP is caused by the low entrainment rate.

[0012] The coefficient of performance (COP) in ejector-based refrigeration systems is critically dependent on the entrainment ratio, which defines the mass flow rate ratio of the secondary (evaporator) stream to the primary (generator) stream. Empirical studies confirm that optimizing ejector geometry to maximize entrainment ratio directly enhances system COP. For instance, Huang et al. demonstrated that a 23% COP improvement was achieved by increasing the entrainment ratio to 0.45 through ejector geometric refinements

[0012] ,

[0013] Therefore, enhancing the COP in Ejector-Based Refrigeration Systems requires a comprehensive redesign of the layout, geometry, and structure of the ejector and the coil assemblies in rotary ejector-based systems.

[0014] In conventional Steam Power Plant Cycles, the boiler operates under essentially isobaric conditions.

[0015] One theoretical approach is for the fluid inside the boiler to perform expansion work while simultaneously absorbing energy, but to date, this has not been achieved in practice.

[0016] No previous technology has simultaneously succeeded in integrating centrifugal pumping, rotational supercharging influenced by the Coriolis force, and performing expansion work during heat addition within a single rotary ejector system.Summary of Invention

[0017] 1. Thermodynamic Cycle Enhancement

[0018] Expansion Work During Heating:

[0019] The Helical Tapered Conical coil design of the generator (by decreasing radius Ri —> R2) enables the working fluid to perform mechanical work while absorbing heat.

[0020] Advantages:• Lower operational temperature requirements in the generator compared to the conventional isobaric systems• The Cycle efficiency approaching theoretical limits

[0021] Energy Conversion:

[0022] Radial inward flow converts kinetic energy into reusable potential energy

[0023] 2. Optimization of Rotational Fluid Dynamics

[0024] Entrainment Ratio Improvement:• Asymmetric ejector geometry utilizes Coriolis effects to enhance secondary flow mixing• Maintains stable performance at high rotational speeds

[0025] Simplified Fluid Circulation:

[0026] Centrifugal pressure differentials enable pump-free operation

[0027] 3. Integrated System Architecture

[0028] Unified Rotating Assembly:• All primary components mounted on a single rotating frame• Eliminates need for separate electric fans• Reduces mechanical complexity

[0029] Enhanced Heat Transfer:• Rotational motion improves convective heat exchange• Enables direct coupling to heat sources

[0030] 4. Operational Advantages

[0031] Heat Source Flexibility:

[0032] Effective operation with low-grade thermal inputs

[0033] Application Diversity:• Suitable for both cooling and energy recovery applications• Adaptable for industrial, commercial and specialized uses

[0034] 5. Performance Characteristics

[0035] Efficiency Improvements:• Demonstrable increase in coefficient of performance• Reduced thermal requirements for equivalent outputTechnical Problem

[0036] Despite the efforts made, Ejector-Based Refrigeration Systems have not gained widespread popularity due to their relatively low Coefficient of Performance (COP) in comparison with vapor-compression and absorption systems. The low Coefficient of Performance (COP) is caused by the low entrainment rate.

[0037] Therefore, enhancing the Coefficient of Performance (COP) in Ejector-Based Refrigeration Systems requires a comprehensive redesign of the layout, geometry, and structure of the ejector and the coil assemblies in rotary ejector-based systems.

[0038] Theoretically, one could imagine a device that combines heat absorption with expansion in an almost isothermal process, akin to a piston expanding within a heated chamber while performing work. Realizing such a system in practice would demand operation at very high pressures and temperatures, precise sealing, specialized lubrication, and materials capable of withstanding extreme conditions. The resulting mechanical complexity, cost, and reliability challenges outweigh any potential efficiency gains when compared to established boiler technologies.

[0039] One theoretical approach is for the fluid inside the boiler to perform expansion work while simultaneously absorbing energy, but to date, this has not been achieved in practice. Solution to Problem

[0040] This invention utilizes the effects of rotational motion to enhance the efficiency of a refrigeration system, as follows:(a) It is known that moving a mass system on a rotating object requires a mechanical work to be performed on the mass system when moving toward the center of rotation, whereas moving outward from the center allows the mass system to return (or release) mechanical work (or energy). Accordingly, in the refrigeration cycle of this invention, energy exchange consistently occurs between the refrigerant fluid and the rotating mass. Where necessary, energy (or work) is extracted from the fluid, and where required, energy (or work) is returned to it, as follows.1. When the high-speed working fluid moves radially inward within the ejector toward the center of rotation — i.e. , from a region of larger radius (generator) to a region of smaller radius (condenser) For example R20.5R1 — a portion of its kinetic energy is converted into potential energy and stored in the mass system. This contrasts with conventional systems where such energy is solely dissipated as heat in the condenser.2. This stored above-mentioned potential energy is returned to the system in the pumping process without the need for complex equipment.3. As the working fluid flows through the generator coil, it is forced inward toward the smaller radius. This radial movement induces both fluid expansion and mechanical work - because at the reduced radius, the fluid pressure drops, thereby generating expansion work through this pressure reduction.

[0041] The working fluid performs expansion work as it moves inward, governed by:AE = 72pco2(Ri2- R22) [J / kg], where:• p: fluid density [kg / m3],• co: angular velocity [rad / s],• Ri, R2: inlet / outlet radius [m],

[0042] “As discussed by White, F. M. (2011 ). Fluid Mechanics (7th ed.), McGraw-Hill

[0013] ”.

[0043] With this highly significant feature — going beyond mere energy exchange — the system achieves two key advantages: As shown in the left half of Figure 5, in steam power cycles (on behalf of driving cycle in an ejector system), the superheating process occurs at constant pressure. Consequently, in the superheat region, the constant-pressure curve (section 3-3') shifts locally toward higher temperatures, necessitating higher boiler operating temperatures. However, in this invention (as illustrated in the right half of Fig. 5), no local temperature increase occurs, and the heating process in the generator (2'-3-3") maintains a uniform horizontal profile at constant temperature. This means that at a given generator temperature, the work output produced by this invention (area: 1 -2-2'-3-3"-4'-1 ) is significantly greater than that of conventional cycles (area: 1 -2-2'-3-3'-4'-1 ).

[0044] The cycle efficiency is equal to the ratio of work output to total heat input:

[0045] q = Area(1-2-2'-3-3'-4'-1 ) / Area(a-2-2'-3-3'-c-a)

[0046] q' = Area(1-2-2'-3-3"-4'-1 ) / Area(a-2-2'-3-3"-c-a)

[0047] q: Conventional cycle efficiency,

[0048] q': Efficiency of this invention's cycle.

[0049] “As discussed in Fundamentals of Classical Thermodynamics, 3rd Edition, by Van Wylen & Sonntag (Wiley, 1985)

[0014] ”.

[0050] Therefore, under equal temperature conditions, this invention's thermodynamic cycle consistently outperforms traditional steam power cycles. This is because, mathematically, we add equal positive constants to both the numerator and denominator of the efficiency ratio, resulting in systematically higher efficiency values for our novel cycle.

[0051] If A / B < 1 and K > 0, then A / B < (A + K) / (B + K) always holds.

[0052] (b) Both Coriolis acceleration and centripetal acceleration are utilized to enhance the entrainment ratio and consequently improve the coefficient of performance (Secondary flow supercharging is achieved via two mechanisms):

[0053] (1 ) The first Supercharging Mechanism of the Secondary flow passage of ejector: Within the nozzle, the very high-speed primary flow generates a strong Coriolis force (Fig. 3). The trajectory of the high-speed fluid motion within the ejector lies within a plate perpendicular to the rotational axis. The high-speed fluid motion within the ejector must not be aligned in the space parallel to the rotational axis. Depending on the design, the closer this angle approaches 90 degrees, the greater the resulting cross product magnitude. The direction of Coriolis acceleration, according to the right-hand rule, is directed toward the center. This means the fluid tends to touch the outer wall in relation to the center resulting in creating a vacuum near the inner wall. Likewise, the primary flow, this effect enhances the secondary flow, which is drawn more effectively into the mixing region, the secondary fluid similarly inclines off-center as it is speeding up continuously. Therefore, it mixes with the first fluid in an increasing manner. The vital factor is that, the ejector (Fig.3) is axial asymmetric (the secondary flow passage in the mixing chamber and Suction Chamber exhibits axial asymmetry relative to the nozzle axis, and the Coriolis force inclines both the flow passing through the nozzle and the entrained flow opposite to the secondary flow passage direction, thereby increasing the entrainment ratio) in a way that the inlet of the secondary fluid is exactly driven to the region with maximum vacuum. Having said that all, the quantity of entrainment escalates. According to this design, no entrainment ratio reduction occurs at rotational speeds above 1500 RPM. “As discussed by Meriam and Kraige in Engineering Mechanics: Dynamics (8th ed., John Wiley & Sons, 2015)

[0015] ”.

[0054] (2) The second Mechanism Supercharging of the Secondary flow passage of ejector (with lower effect): Centripetal acceleration on the secondary fluid column forces its molecules into the high-speed primary stream, further enhancing mixing. (See Fig. 2) Advantageous Effects of Invention

[0055] This invention introduces fundamental modifications to the structure of existing ejector refrigeration systems (through simplification, reduced size, lower maintenance costs, and improved coefficient of performance and cooling efficiency) has a significant impact on energy savings, global warming mitigation, and environmental protection, for the following reasons:(1 ) In the classic ejector refrigeration systems (non-rotating and non-supercharging), the upper cycle (Fig.1 ) comprising the generator, ejector, condenser, and pump which resembles a steam power cycle but deviates from the ideal (as shown in Fig. 4.) due to two key limitations:• The first limitation is related to the pumping process. At state T, the working fluid is a mixture of liquid and vapor (See Fig. 4). A pump that handles such a mixture would face serious mechanical difficulties. It is much simpler to condense the vapor completely and pump only the liquid. This is the basis of the Rankine cycle.• According to (Fig. 4), the second limitation is related to the superheating of steam. In the Rankine cycle, steam is superheated at constant pressure during process 3-3' In the Carnot cycle, all heat transfer occurs at constant temperature, so the steam would be superheated during process 3-3". Note that during this process, the pressure drops, which means heat must be transferred to the steam while it is expanding and doing work. In practice, achieving such a process is very difficult.• As discussed in Fundamentals of Classical Thermodynamics, 3rd Edition, by Van Wylen & Sonntag (Wiley, 1985)

[0014] ,• Both of these limitations have been resolved in the present invention. As under this invention, the pump utilizes centrifugal force to separate the liquid from the vapor, and due to the geometry of the generator coil — as described in paragraph

[0043] — the working fluid performs more effectively, resulting in a behavior more closely resembling the Ideal Cycle.(2) In this system, the centrifugal force enables two working fluids with distinct physical properties to operate simultaneously in two separate cycles, with each fluid being separated based on its density and directed into its corresponding cycle, because a centrifugal separator in the downstream of the condenser can divide the refrigerant mixture based on density differences, enabling selective routing of each one of those two components to eitherthe refrigeration or Ejector-Driven Power Cycles. This allows optimal utilization of each fluid’s thermodynamic properties.(3) In conventional ejector refrigeration systems, three separate sets of electric motors and blowers are typically required to: (a) dissipate condenser heat to the atmosphere, (b) deliver cooled air from the evaporator to the user, and (c) supply hot air to the generator. In this invention, the rotational motion of the evaporator, condenser, and generator coils - combined with multiple air passage holes in the rotating frame that allow air to easily flow across each coil and be ejected outward - enables each coil to inherently function as a centrifugal blower, simultaneously generating airflow without requiring additional fans. As discussed in the heat transfer coefficient is calculated using methods described in the literature (Incropera & DeWitt, 1981 )

[0017] ,(4) In conventional blower design, efforts are made to minimize turbulence to improve efficiency. Conversely, in heat exchange processes, high airflow velocity and turbulence are desirable to disrupt boundary layers and enhance convective heat transfer. This invention harmonizes both objectives: the inherent turbulence and high-speed airflow generated around the rotating evaporator, condenser, and generator naturally enhance forced convection heat transfer coefficients (h), simplifying the system and improving its compactness and operational efficiency.(5) In classical ejector-based systems without supercharging, substantial quantities of high- energy primary fluid are necessary to entrain minimal secondary flow, leading to considerable energy dissipation. The majority of the primary flow's kinetic energy converts to waste heat in the condenser, ultimately being rejected to the atmosphere. By contrast, the proposed system delivers dual advantages through secondary flow supercharging: firstly, it reduces the required initial flow rate to a measurable extent; secondly, it converts and conserves a portion of the fluid's kinetic energy as recoverable potential energy within the condenser. This stored energy is then effectively utilized during subsequent pumping and re-injection phases into the ejector.(6) In this invention, the key limitations of gravitational ejector systems — such as large volume and low efficiency — have been resolved, while the main challenges of rotary ejector systems, are also addressed (specifically, the difficulties in controlling the fluid column height across different parts of the system and their poor performance). Due to the rotational acceleration acting on the fluid column, the pressure of the secondary fluid entering the ejector is consistently slightly higher than the actual evaporator pressure. As a result, the ejector perceives a higher operating pressure (and consequently a higher saturationtemperature) for the evaporator than its true value. This apparent increase in evaporator temperature leads to an improvement in the system’s coefficient of performance (COP).(7) The system can be mechanically or thermally coupled to rotating components of various machines such as the crankshaft of an internal combustion engine, the rotor of an electric motor, or a jet engine. This enables: Supplying rotational and or thermal energy to the generator, Cooling of high-temperature rotating equipment, generating refrigeration using waste or low-cost heat sources.(8) This system does not require a mechanical pump with an electric motor-driven impeller, nor any associated components.Brief Description of Drawings

[0056] Figure 1 : Schematic, Conventional classic ejector-based refrigeration system

[0057] Figure 2: Schematic Rotary Supercharger Ejector Refrigeration System, (in the right half of the figure, instead of illustrating completed coils, only a part length of the coils has been illustrated to make it simple)

[0058] Figure 3: Schematic of the asymmetric ejector used in the system

[0059] Figure 4: Comparative Analysis of the Rankine and Carnot Cycles on a Thermodynamic Temperature-Entropy (T-S) Diagram

[0060] Figure 5: Comparative efficiency analysis of conventional cycles versus the invention's cycle at equal temperatures on a Temperature-Entropy (T-S) diagramDescription of Embodiments

[0061] The present invention, referred to as the Rotary Supercharger Ejector Refrigeration System, comprises the same components as the classic ejector-based refrigeration system described in (Fig. 1 ) plus two features that fundamentally improves the performance of the classic system.

[0062] The First feature: All primary components of the refrigeration cycle — namely the evaporator, condenser, expansion valve, generator (or boiler), pump (simplified), ejector, and the interconnecting piping — are mounted on a single integrated rotary frame (See Fig. 2) that is rotatable collectively around a central axis. The rotational motion is driven by an external electric motor or other rotational power sources. Due to the rotation of the equipment, it is necessary that none of them consume any electricity, this condition thus being established.

[0063] The rotary coils of the evaporator, condenser, and generator simultaneously serve as centrifugal blowers, eliminating the need for electrically powered fans or an external heat exchanger. Furthermore, as will be detailed later, the pump’s electric motor has also been eliminated.

[0064] The generator coil is configured to rotate about a common central axis shared with the evaporator and condenser coils, wherein the generator coil has a greater radial dimension relative to both the evaporator coil and the condenser coil.

[0065] When heat is supplied to the generator, the working fluid vaporizes and enters the ejector’s primary inlet. As the flow passes through the ejector throat, its velocity increases significantly, resulting in a pressure drop. This pressure drop induces suction from the evaporator through the ejector’s secondary inlet. The high-speed primary flow then mixes with the secondary flow. The output is a mixed flow with high kinetic energy (see Fig. 2). Upon exiting the ejector and entering the condenser, this high-energy mixture undergoes two energy transformations based:(a) The increase in pipe cross-section reduces velocity and raises pressure above that of the evaporator.(b) As the high-speed working fluid is propelled radially inward i.e. , from a region of larger radius (generator) toward a smaller radius (condenser) a portion of its kinetic energy is transformed into potential energy and gets stored in the system.

[0066] Experimental data confirms that increasing backpressure (up to the critical point) does not degrade ejector performance. “As reported by Pradeep Gupta et al. in ‘Numerical Analysis of Ejector Performance Near the Critical Back Pressure’

[0016] ”, increasing back pressure up to the critical back pressure does not adversely affect the entrainment rate.

[0067] Within the rotating condenser coil around the previously- mentioned axis, the fluid releases heat and condenses into liquid. To facilitate liquid transport, the radius of the condenser coil at its outlet is slightly larger in comparison with its inlet.

[0068] At the end of the condenser there is a separator which operates based on the difference of specific gravity of the liquid, and separates the condensed liquid into the following two streams:

[0069] First Stream: Passes through the expansion valve into the evaporator, where it absorbs ambient heat and evaporates (see Fig. 2). The exiting vapor from the other end of the pipe of the evaporator is then supercharged into the ejector’s secondary inlet by rotational forces.

[0070] Second Stream: Flows through a pipe connecting the condenser outlet (at a smaller radius) to the generator inlet (at a larger radius). As the liquid moves outward, it is pumped by centrifugal force. This pipe acts as a pump. In this pipe, the centripetal acceleration makes the liquid pressure increase and the potential energy previously given to the liquid is released and transforms to work.

[0071] The high-pressure liquid is directed through a flow-controlling orifice to control the flow rate and is then returned to the generator coil, where it is reheated and vaporized before re-entering the ejector as the primary flow. This cycle repeats continuously.

[0072] The orifice dynamically adjusts (or is permanently calibrated) to modulate refrigerant flow based on system rotational speed, thermal load requirements, and refrigerant pressure differentials.

[0073] The frame is constructed as a cylindrical structure, with the components such as: the evaporator coil, the condenser coil, the generator coil, and the other components of the refrigeration cycle all of them assembled inside this cylinder (as illustrated in Figure 2).

[0074] The cylindrical wall is perforated with air passages that allow incoming air to flow over each coil, undergo heat exchange, and then be discharged outward through these openings.

[0075] The second feature: The generator coil is designed in a conical spiral (tapered helical) a Helical Tapered Conical Coil shape with a bell-like profile, featuring a calculable rate of change in the conical radius (where, at maximum slope, it becomes a Flat Spiral Coil). It is installed in such a way that it rotates around its axis of symmetry (the system’s rotational axis), with its discharge end positioned at a smaller radial distance from the axis compared to its input end.• Inlet radius (R : Positioned at maximum radial distance from the rotation axis,• Outlet radius (R2): Positioned at a reduced radial distance (R2< Ri).In Figure 1, reference numeral denotes the pump (10), the generator (20), the evaporator (30), the condenser (40), the expansion valve (50) and the ejector (60).In Figure 2, The drive motor (1500) rotates the assembly comprising the primary disk (100), the secondary disk (1000), and the blades positioned between them (1900). This rotating assembly operates within chamber (400). Air-sealing strips (1400) isolate both sides of each disk, effectively dividing the chamber into three independent zones. The generator tubes (800), condenser tubes (1100), and evaporator tubes (900) are separately wound onto the rotating assembly.Hot gas or exhaust air (300) enter the system, Flow around the generator tubes (800), exchange heat, and are expelled through outlet (500). Incoming air (200) flows in, exchanges heat with the condenser (1100), and exits through outlet (600). Another portion of the incoming air (200), or an alternative air source, exchanges heat with the evaporator tubes (900) and exits through outlet (700) as cooled air.The expansion valve (or capillary tube) (1300) is located at the inlet of the evaporator (900). The ejector (1200) is positioned at the outlet of the generator (800). The outlet pipe of the evaporator (900) connects to the secondary inlet of the ejector (1200). The ejector’s output flows into the condenser (1100).The expansion valve, evaporator, and condenser are positioned closer to the center of rotation than the generator. The pipe connecting the condenser to the generator inlet is arranged radially or semi-radially and functions as a pump.The evaporator, condenser, and generator assemblies (with or without fins) rotate together. Due to their relative velocity with respect to the surrounding air, they achieve enhanced convective heat transfer coefficients and simultaneously act as three independent air blowers.In Figure 3, reference numeral Primary Flow (4001 ), Secondary flow (4002), Suction Chamber (4003), Mixing Chamber (4004), Mixed Flow (4005).Example

[0076] Title: Rotary Supercharged Ejector Refrigeration System Coupled to an Internal Combustion Engine via Flywheel and Exhaust Heat Recovery (Currently in prototype phase)

[0077] This embodiment illustrates a practical implementation of the proposed rotary supercharged ejector refrigeration system, integrated with a conventional internal combustion engine. The system is designed to utilize both mechanical rotation and low- grade thermal energy from the engine to drive the refrigeration cycle without requiring additional electrical input.1 . System OverviewThe refrigeration unit is mechanically coupled to the crankshaft of a four-cylinder internal combustion engine (20 kW). The rotating assembly includes the evaporator, condenser, generator (with helical tapered conical coil), ejector, expansion valve, and interconnecting piping — all mounted on a unified rotary frame. The rotation is synchronized with the engine’s crankshaft, enabling continuous operation.2. Dual-Stage Thermal CouplingThe generator coil is thermally coupled to two distinct heat sources:• Stage 1 - Preheating: The pre-heat section of the generator coil is thermally- mechanically coupled to the engine flywheel, simultaneously receiving both thermal energy (through heat conduction and radiation) and mechanical torque (via rotary coupling). This preheating stage raises the working fluid temperature without initiating complete vaporization.• Stage 2 - Primary Heating: The coil then enters the exhaust stream zone, where high-temperature combustion gases transfer sufficient thermal energy to fully vaporize the working fluid. This staged heating approach improves thermal efficiency and reduces the required exhaust temperature for complete vaporization.3. Refrigeration Cycle OperationOnce vaporized, the working fluid enters into the ejector’s primary inlet. As it accelerates through the nozzle, a pressure drop is induced, which draws in vapor from the evaporator via the ejector’s secondary inlet. The high-speed primary and secondary flows mix within the ejector and exit as a combined stream with elevated kinetic energy. This mixed flow enters to the condenser. The condenser also performs phase separation via centrifugal acceleration, dividing the refrigerant into liquid and vapor components.4. Fluid Routing and Pump-Free OperationThe separated liquid is divided into two streams:• Stream A: Routed through an expansion valve into the evaporator, where it absorbs ambient heat and returns as vapor to the ejector’s secondary inlet.• Stream B: Directed through a radially arranged pipe from the condenser outlet (lower radius) to the generator inlet (higher radius). This pipe acts as a centrifugal pump, utilizing rotational acceleration to increase pressure and return the liquid to the generator without mechanical pumping components. A flow-control orifice regulates the refrigerant flow rate based on rotational speed and thermal load.5. Airflow and Heat ExchangeThe rotating coils of the evaporator, condenser, and generator inherently function as centrifugal blowers. Perforations in the cylindrical housing allow ambient air to flow across each coil, facilitating convective heat exchange and eliminating the need for electric fans.6. Operating Parameters (Prototype Data)Parameter Value Range SourceMeasured from engine exhaustExhaust Gas Temperature 280-330 °C streamFlywheel Surface Thermocouple readings on85-100 °CTemperature rotating surfaceStandard generator couplingCrankshaft Rotational Speed 1400-1800 RPM speedEvaporator Outlet Air6-8 °C Achieved in prototype testingTemperatureAmbient Air Inlet Typical environmental25-45 °CTemperature conditions56% R1234ze + 44%Refrigerant UsedR513AODP 0 Montreal Protocol Phase-OutGWP (1OO-yr) 573 EPA 2023 GuidelinesOperating Pressure 0.351-10 bar Ejector Cycle OptimizationFlammability A1 (Non-flammable) ASHRAE Standard 347. Advantages and Industrial Relevance• Energy Independence: Operates without external electricity, relying solely on waste heat and mechanical rotation.• Thermal Load Reduction: Extracts heat from engine components, improving durability and performance.• Off-Grid Suitability: Ideal for remote installations, military applications, and data centers.• Cycle Efficiency: Enhanced by kinetic-to-potential energy conversion and optimized entrainment ratio.• Compact Design: Eliminates electric fans and mechanical pumps, reducing system complexity and maintenance.8. ApplicabilityThis configuration is suitable for:• Waste heat recovery from industrial engines and generators• Combined Heat and Power (CHP) systems• Renewable energy integration (solar thermal, biomass)• Commercial cooling (food processing, pharmaceuticals, IT infrastructure)• Specialized deployments (marine, military, remote facilities)Industrial Applicability

[0078] The present invention offers significant industrial utility across multiple sectors, particularly in energy recovery and efficient cooling applications:1 . Waste Heat Recovery Applications: o Effective utilization of low-grade heat (80-150°C) from:■ Industrial processes■ Electrical motors and the electrical power generators o Harvesting of parasitic heat from rotating machinery o Energy recovery from power system losses2. Hybrid System Integration: o Compatible with:■ Diesel / gas-powered generators■ Microturbines■ Combined Heat and Power (CHP) systems3. Renewable Energy Systems: o Solar thermal applications o Geothermal implementations o Biomass energy utilization4. Commercial / lndustrial Cooling: o Central HVAC systems o Food processing and pharmaceutical cooling o Data center thermal management5. Specialized Applications: o Marine and offshore installations o Military field equipment o Remote area implementationsReference Signs List4006 Angle between the ejector nozzle and the tangent to the circular trajectory (Invariably exceeds zero)Citation List

[0080]

[0012] Y. Huang et al., "Experimental investigation of the entrainment ratio and performance of an ejector refrigeration system using R141 b," Applied Thermal Engineering, vol. 115, pp. 697-705, 2017.

[0081]

[0013] F. M. White, Fluid Mechanics, 7th ed. New York, NY, USA: McGraw-Hill, 2011.

[0082]

[0014] G. J. Van Wylen and R. E. Sonntag, Fundamentals of Classical Thermodynamics, 3rd ed. New York, NY, USA: Wiley, 1985.

[0083]

[0015] J. L. Meriam and L. G. Kraige, Engineering Mechanics: Dynamics, 8th ed. New York, NY, USA: Wiley, 2015.

[0084]

[0016] P. Gupta, S. M. V. Rao, and P. Kumar, "Numerical analysis of ejector performance near the critical back pressure," in Proc. Natl. Symp. Shock Waves 6, I IT Madras, India, Feb. 2020.

[0085]

[0017] F. P. Incropera and D. P. DeWitt, Fundamentals of Heat and Mass Transfer,1st ed. New York, NY, USA: Wiley, 1981.Patent Literature

[0086] [7] Centrifugal ejector vacuum generation system, US Patent 9,068,743, 2015.

[0087] [8] Rotating fluid ejector with Coriolis-optimized mixing, European Patent EP3,025,421 , 2016.

[0088] [9] Rotary ejector with internal guide vanes, Chinese Patent CN 106, 194, 183, 2017.

[0089]

[0010] Rotary ejector with active Coriolis compensation, German Patent DE10, 2018, 112,789, 2020.

[0090]

[0011] Coriolis-enhanced fluid pumping ejector, US Patent 8,123,491 , 2012.Non-Patent Literature

[0091] [1] J. Kaperski, "Rotational type of a gravitational ejector refrigerator: A system balance of the refrigerant analysis," Int. J. Refrig., vol. 33, no. 1 , 2010.

[0092] [2] Simultaneous implementation of rotary pressure exchanger and ejectors for C02refrigeration systems, NTNU, Trondheim, Norway, GL2022, Jun. 2022.

[0093] [3] X. Zhang et al., "Supersonic rotary ejectors: Momentum transfer efficiency and Coriolis-induced instabilities," J. Fluids Eng., 2018.

[0094] [4] S. Lee and H. Kim, "CFD analysis of Coriolis-driven secondary flows in rotating ejector systems," Int. J. Heat Fluid Flow, 2020.

[0095] [5] Y. Chen et al., "Experimental efficiency improvement of rotary ejectors in refrigeration cycles," Appl. Therm. Eng., 2019.

[0096] [6] A. Muller et al., "Flow stability in rotational ejector designs: Coriolis compensation requirements," Aerosp. Sci. Technol., 2021.

Claims

ClaimsClaim 1 (Independent):A Rotary Supercharger Ejector Refrigeration System comprising:(a) a synchronously rotating assembly including:1 . an evaporator,2. an ejector,3. a condenser,4. an expansion valve,5. a generator with helical tapered conical coil, and6. interconnecting piping; wherein all components are rigidly mounted on an integrated rotary frame configured to rotate about a central axis;(b) Wherein the coil of said generator comprises:1 . an inlet radius (R at maximum radial distance from the axis, and2. an outlet radius (R2) at a reduced radial distance, wherein the coil tapers continuously from the inlet radius (R to the outlet radius (R2) such that R2is substantially smaller than Ri; and(c) Wherein said radial displacement is configured, whereby the working fluid within the Generator simultaneously:1 . absorbs thermal energy, and2. performs mechanical expansion workClaim 2 (Dependent on Claim 1):The Rotary Supercharger Ejector Refrigeration System according to Claim 1 , wherein: a. the interconnection arrangement and functional configuration of all elements including the evaporator, ejector, condenser, expansion valve, generator, and connecting pipes matches the standard layout of conventional stationary ejector refrigeration systems; b. the refrigerant flow path between elements and their thermodynamic relationships remains identical to stationary systems; c the sole substantive difference being the unified rotational motion of all elements about the central and complex mechanical pump elimination.Claim 3 (Dependent):The system of claim 1 , wherein the condenser comprises:1 . An inlet at radius R3 from the central axis, and2. An outlet at radius R4 from the central axis, where R4 is greater than R3, whereby the condenser is configured to:(i) Autonomously separate liquid and vapor phases through centripetal acceleration, and(ii) Perform condensate drainage using centrifugal acceleration forces.Claim 4 (Dependent):The system of claim 1 , further comprising:A Flow Control Orifice disposed at the generator inlet, configured to:(a) restrict the refrigerant flow rate entering the generator; and(b) autonomously modulate said flow rate in precise accordance with instantaneous cooling load demand.Claim 5 (Dependent):The system of claim 1 , further comprising:A flow-control orifice integrated at the generator inlet, wherein:Centrifugally-induced accumulation of a refrigerant liquid column in a pre-orifice chamber generates hydrostatic pressure sufficient for:(a) Pumping the refrigerant into the generator; and(b) maintaining a continuous circulation cycle without mechanical pumping means.Claim 6 (Dependent):The system of claim 1 , further comprising:A centrifugal phase separator mounted at the condenser outlet, configured to:(a) Receive a multi-component refrigerant mixture;(b) Separate constituent phases by density differential through centrifugal force, wherein:(i) Higher-density components migrate radially outward, and(ii) Lower-density components concentrate radially inward;(c) Outlet ports that direct each separated component to either:(i) The primary cycle, or(ii) The refrigeration cycle.Claim 7 (Dependent):The system of claim 1 wherein:1 . The generator outlet R2is positioned at a greater radial distance than:1.

1. The condenser inlet R3, and1 .

2. The evaporator and expansion valve assembly; and2. The radial differential between R2and R3is configured to:Convert a portion of the ejector discharge flow's kinetic energy simultaneously into centrifugal potential energy for pump utilization, and expansion work.Claim 8 (Dependent):The system of claim 1 , wherein each of the evaporator, generator, and condenser units comprises:1 . Optimized heat transfer surfaces configured for forced convection with the surrounding environment; and / or2. Thermal contact plates for conductive heat transfer when coupled to mechanical equipment surfaces.Claim 9 (Dependent):Rotary Supercharger Ejector Refrigeration System according to claim 1 , wherein:1 . The nozzle of the ejector is positioned in a plane perpendicular to the rotation axis; and2. The mixing chamber is asymmetrically configured about the ejector nozzle axis such that the secondary fluid is exclusively admitted into the primary flow from the rotation center side; and3. The Coriolis force and centripetally-induced acceleration force deflects the Velocity- enhanced fluid toward a region diametrically opposed to the secondary fluid inlet passage; and4. Whereby mixing efficiency is preserved at elevated rotational speeds.Claim 10 (Dependent):A Rotary Supercharger Ejector Refrigeration System according to claim 1 , wherein the evaporator, condenser, and generator coils rotate about the axis within a perforated cylindrical frame, such that :(1) each coil functions as a centrifugal or semi-centrifugal blower; and(2) the relative velocity between the rotating coils and ambient air increases the forced convection heat transfer coefficient compared to a stationary state.Claim 11 (Dependent):The system of claim 1 , wherein the structural interconnection of the primary components together with the basic refrigerant flow pattern is structurally and functionally compatible with conventional stationary ejector cooling systems in accordance with ISO 23148:2022,such that any performance enhancements developed for the stationary systems, when rotationally compatible, are automatically extendable to the rotary configuration and accordingly fall within the scope of the present invention.