Portable waste heat driven heat pump integrating vapour power cycle and multistage vapour recompression systems

Abstract

The invention provides a portable high-efficiency heat-pump system that integrates a Vapor Power System (VPS) and a Vapor Compression System (VCS) with a Linear Pressure Distribution System (LPDS), into a single coaxial assembly driven by a shared rod (500). A float-based linear LPDS alternately routes vapor to opposing VPS chambers (204), enabling autonomous reciprocation, force-balanced operation and Primary Boundary Compression (PBC). The system induces a thermodynamic process termed Sensible-Heat-Induced Saturation (SHIS), wherein rapid condensation in the condenser triggers flash-vaporization in the evaporator, allowing ambient sensible heat to provide the dominant portion of the latent heat of vaporization. The PBC stage compression and a hydraulically assisted hard recompression stage ensure near-complete condensation before liquid delivery to the next cycle. The architecture supports multiple independently controllable thermal zones for heating or cooling and operates efficiently with low-GWP refrigerants. The system offers scalable, self-regulating climate control with significantly enhanced energy efficiency.

Description

TITLE OF THE INVENTION: PORTABLE WASTE HEAT DRIVEN HEAT PUMPINTEGRATING VAPOUR POWER CYCLE AND MULTISTAGE VAPOUR RECOMPRESSIONSYSTEMS

[0001] TECHNICAL FIELDThe invention relates to thermal-energy conversion, refrigeration, and heat-pump technologies. More specifically, it concerns a portable thermally driven heat-pump architecture integrating a Vapor Power System (VPS), a Linear Pressure Distribution System (LPDS), and a Vapor Compression System (VCS) within a single hermetically sealed coaxial assembly. The system achieves high-efficiency heating and cooling through Sensible-Heat-Induced Saturation (SHIS) and boundary-induced flash boiling (BIFB), enabling autonomous vapor circulation and compression without electrically driven compressors or throttling valves.

[0002] TECHNICAL PROBLEMConventional vapor-compression systems achieve evaporator saturation through a de facto reliance on two coupled mechanisms: the primary Pressure-Induced Saturation (PIS) from the compressor, and a secondary, dependency on Sensible-Heat-Induced Saturation (SHIS) from ambient airflow — a critical yet often overlooked factor.

[0003] This architectural dependency creates intrinsic limitations. The system first uses PIS to lower the saturation pressure and temperature, but it then depends entirely on ambient airflow to provide the sensible heat required to complete the vaporization process.

[0004] However, the reliance on PIS is systemically problematic. While the ultimate goal is direct heat transfer, PIS attempts to achieve this indirectly by manipulating fluid pressure — a self-defeating approach. The act of vaporization inherently raises saturation pressure (Psat), while condensation lowers it, thereby actively destroying the hardly earned pressure differential, PIS system creates.This fundamental conflict forces a thermodynamic trade-off where the intended phase-change process erodes its own driving force. Each cycle retains entropy as superheat, requiring extra work to reestablish VLE, while the throttling valve destroys Exergy via an isenthalpic pressure drop.Thus, the conventional architecture is constrained by the inherent inefficiencies of its primary pneumatic control mechanism (PIS) and its passive reliance on ambient conditions.

[0005] With PIS system, apart from the engaged power intensive compressor, the pressure-flow control using a TXV introduces additional limitations: high sensible load widens the aperture, reducing pressure differential and climate change; low load narrows it, limiting mass flow. Thus there exists a trade-off between thermal load and COP - evident in extreme hot weather or at the onset of cooling. System performance must then be corrected by variable-speed compressors and sophisticated electronic controls, increasing cost and complexity without solving the underlying thermodynamic inefficiency.

[0006] Existing architectures also lack efficient zoning capability. The entire evaporator loop forms a single low-pressure region with a uniform saturation temperature (Tsat), rendering the creation of multiple, independently controlled zones thermodynamically impossible. Employing multiple sequential expansion valves (TXVs) is an impractical solution, as it fails to create distinct Tsat zones, progressively erodes the system's pressure differential, and compounds Exergy destruction through repeated throttling. Furthermore, insufficient heat absorption downstream of a TXV can lead to incomplete vaporization, resulting in liquid refrigerant flood-back that compromises compressor safety.

[0007] Also a portion of the delivered cooling is diverted merely to offset superheat, further degrading effective COP. Chemical degradation of refrigerant-oil mixtures produces sludge that accumulates in coils and throttling elements, while high-speed compressor operation introduces frictional and dissipative losses that contribute additional Exergy destruction.

[0008] No existing system fluidically or mechanically couples a power-producing cycle and a vaporcompression cycle within the same hermetic housing. Shaft-based compressors depend on gland seals, none of which are leak-proof under continuous reciprocation. As a result, no heat-pump architecture exists that convert ambient sensible heat into the dominant driver of vaporization, recovers phase-change volume effects as useful work, and maintains stable COP across varying thermal loads.

[0009] SUMMARY OF THE INVENTIONThe invention uses thermal input to drive refrigerant circulation, phase change, and temperature lift. The system leverages the parasitic volume collapse of condensation to generate thrust amplification using a bore-differentiated cylinder-piston configuration analogous to the mechanical advantage of Pascal's law. By combining bore difference with the source-sink temperature differential, system performance becomes not entirely dependent on temperature gradient alone. This decoupling allows effective use of low-grade thermal input, including waste heat, like the inherent enthalpy of enclosure such that the thermal load itself is being converted as driving fuel for system functioning.

[0010] The system is adaptable to low-grade waste heat sources through a cascade configuration where a thermoelectric cooler (TEC) array supplements a vapor-based cycle. In this architecture, the vapor system acts as the primary workhorse. The TECs operate at a stabilized saturation temperature that enhances their coefficient of performance (COP), and their total rejected heat (Qh) — comprising both absorbed environmental heat (Qc) and internal Joule heat (J) — is utilized to drive the Sensible- Heat-Induced Saturation (SHIS) mechanism. This approach effectively converts ambient enthalpy into a useful form and leverages the full heating capability of the TEC cascade, aligning with the system's partly waste-heat-driven nature.

[0011] Additionally the new system employs a Boundary Induced Flashing Boiling (BIF) that enhances COP by leveraging phase-change dynamics without requiring additional energy input.

[0012] A float-based LPDS that alternate high pressure vapour to two ports of VPS cylinder, low pressure vapor condenser side, enabling autonomous reciprocation work and isenthalpic translocation of vapor parcels. Internal force cancellation mechanism due to LPDS that enables operation at low driving pressures, while hard recompression in ensures near-complete condensation.

[0013] The system is scalable, self-synchronizing, and capable of heating or cooling, making it suitable for residential, commercial, industrial, and off-grid applications (like with 12 Volt solar power).

[0014] The LPDS couples VPS and VCR; 1. Physically - using a single hermetic structure without shaft seals, 2. Mechanically - for leveraging hydraulics out of bore difference, 3. Fluidically - for sealed transfer of the same vapor parcel between stages, 4. Thermodynamic - for spontaneous condensation under partial pressure due to the changed environment that allows heat removal instead of heat addition.

[0015] BRIEF DESCRIPTION OF DRAWINGSFIG. 1 — Longitudinal Section of Integrated VPS-LPDS-VCS AssemblyFIG. 2 — System-Level Fluid Routing Diagram (Cooling)FIG. 3 — System-Level Fluid Routing Diagram (Heating Mode)FIG. 4 — LPDS Float Switching Sequence [Fig. 4(a) Post-Forward & Fig.4(b) Post-Reverse Stroke]FIG. 5 — Air-Cycle Subsystem (ACS) with Mechanical VAV and TEC-Block Assembly

[0020] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTSThe invention integrates three coaxial subsystems — a Vapor Power System (VPS) which is driven by thermal input, a Linear Pressure Distribution System (LPDS), and a Vapor Compression System (VCS) — into a single hermetically sealed assembly driven by a shared rod. VPS cylinder is double acting and has a significantly larger bore allowing it to generate extra thrust from given system pressure. This extra thrust is then conveyed through the shared piston rod as shaft work.

[0021] CORE MECHANICAL ASSEMBLYReferring to FIG. 1, the core assembly comprises three aligned cylinders: First cylinder (100) containing large bore sized power piston head PH-1 (202). Second small cylinder (200) contains piston PH-2 head (302). Third small cylinder (300) contains compression piston PH-3 (402).

[0022] A shared rod (500) connects PH-1, PH-2, and PH-3 for axial synchronization.

[0023] Each piston head and float head carry sealing rings housed in O-ring grooves (207) to maintain hermetic integrity.

[0024] CHAMBER DEFINITIONSPiston heads define four operative chambers: CM-1 (204): Isobaric Expanding side of VPS power chamber. CM-2 (304): Isothermal Primary Boundary compression (PBC) chamber. CM-3 (403): Buffer pressure chamber between PH-2 and PH-3 enabling force cancellation.CM-4 (404): Hard-compression chamber of the VCS.

[0025] Because PH-2 and PH-3 have equal bore diameters with the pressure head directed opposite from CM-3, they cancel each other, allowing PH-1 to dominate the stroke dynamics at very low driving pressures, at the initial phase of a stroke.

[0026] PORTS AND FLUID CONNECTIONSThe stationary LPDS sleeve (310) houses essential routing ports:EVP-IN (305) — from evaporator Buffer chamber CM-3 (403);VPS-A (306) CM-1 (204) - expanding side of PH-1 (here, Cap end of PH-1).VPS-B (307) — collapsing side PH-1 via 307 CND-OUT (405) (here, Rod end of PH-1);CND-OUT (405) for Primary Boundary Compression (PBC).

[0027] These ports are selectively exposed or blocked by the float (311) within the LPDS.

[0028] LINEAR PRESSURE DISTRIBUTION SYSTEM (LPDS)The Pressure Distribution System (LPDS) is the central switching subsystem that governs the routing of high-pressure (HP) and low-pressure (LP) vapor to the VPS chambers. It performs both mechanical and thermodynamic continuum control.

[0029] The LPDS includes a sleeve (310) with port windows, a float (311) serving as the dynamic shuttle element, and a stationary annular inward bulge (313). The bulge (313) functions as a hardstop for the float heads (315 and 316) and also provides detent action that energizes both the snapcantilever (312) and the axial springs (314). Two axial springs (314) are attached to the float heads (315 and 316).

[0030] The float, is mechanically pushed by either PH-2 or PH-3, momentarily resists motion via snap-cantilever (312) - bulge (313) encounter, thereby energizing the spring (314).

[0031] Once sufficient differential force accumulates, the float flips into its alternate position, closing the earlier opened ports and exposing the opposite ports of LPDS sleeve (310).

[0032] GEOMETRY AND ROLE OF FLOAT (311)Referring to FIG. 1, the float (311) is a hollow cylindrical shuttle element with two sealing heads separated by an external annular recess. Its central axial bore allows passage of the shared rod and the high-pressure fluid of CM-3, while the outer annular recess accommodates the low-pressure region of CM-2 and houses the snap-cantilever (312). Because CM-3 applies equal pressure to both sides of the float heads (315 & 316), hydraulic forces cancel out, ensuring that the float experiences no net pressure- induced motion. The float therefore shifts position solely through mechanical push from PH-2 and PH-3, assisted by the preloaded springs (314) and the snap-cantilever detent. This LPDS float arrangement enables coordinated fluidic, mechanical, and thermodynamic coupling between the system’s chambers.

[0033] The float alternately and instantaneously connects: EVP-IN (305) VPS-A (306) or EVP-IN (305) VPS-B (307), while simultaneously venting the opposite chamber to CND-OUT (405) which pierces through the bulge. Refrigerant parcel belonging to CM-1 is instantaneously transferred to CM-2 with float shuttling. Thus, the float is not simply a directional valve; it is a dynamic continuum switcher that determines the thermodynamic environment of each vapor parcel.

[0034] ROLE OF BULGES (313) AND SNAP-CANTILEVER (312)The bulges (313) act as hard limiters defining the two stable float positions. The snap-cantilever (312) produces a momentary resistance during float travels, ensuring Crisp port alignment and clean HP / LP separation without partial port overlap.

[0035] SPRING FUNCTION (314)The spring (314) is preloaded and compressed alternately by PH-2 and PH-3. Its role is;To store energy during float actuation - with push either by PH-2 or PH-3,To ensure the float completes its snap-over action with precise slotting.

[0036] INTEGRATED WORK TRANSFER & EXTERNAL PHASE-CHANGE PATHWAYSThe system utilizes two distinct forms of mechanical work transfer.Primary Boundary Compression (PBC): This is boundary work performed by the expanding vapor parcel in CM-1 (204) directly on the vapor parcel in CM-2 (304) through motion of the shared power piston PH-1 (202). The expansion in CM-1 actively absorbs heat through isobaric vaporization (Qc + J), supplemented by passive flash boiling (BIFB) at the free metallic surface of the subsystem block; together with the TEC’s smaller active contribution of Qc, these processes complete the vapor-side heat absorption.Shaft Work: This is the useful work delivered by the shared rod (500) to the Vapor Compression System (VCS). The thrust amplification produced by the bore-differentiated pistons provides the mechanical force for Secondary Hydraulic Compression (SHC) within CM-4 (404). Following this compression, the vapor undergoes external condensation in the associated subsystem (either Z-n or L-n, depending on the operating mode). This condensation follows four sequential conditions: (1) the TEC’s active Qc contribution; (2) spontaneous condensation under partial pressure as the parcel retains its VLE under a changed environment; (3) Primary Boundary Compression driven by CM-1 expansion; and (4) Secondary Hydraulic Compression enabled by amplified thrust, with latent heat released as sensible heat in the designated subsystem.

[0037] COOLING MODE OPERATIONReferring to FIG. 2, the system is configured for cooling mode, wherein high-pressure vapor produced at the active Zone unit (701-703) is routed to the LPDS buffer chamber CM-3, through the permitted side of Solenoid Valve 911, whose right-side channel remains open in this mode.

[0038] Fluid routing and pressure levels are governed by the solenoid valves (911-914), non-return valves NRV 902 and NRV 903 along with float orientation within the LPDS.

[0039] The Z-n (701-703) and L-n (801-802) subsystems serve as the primary heat-exchange interfaces, integrating the air cycle, the refrigerant cycle, and the thermoelectric cooler (TEC) assembly. In the depicted embodiment, each unit includes a heat-conducting block with integral refrigerant passages. A commutator master switch (not shown) controls the electrical polarity applied to both the TEC cluster and the solenoid valves. In cooling mode, the applied polarity is selected such that the TECs of the Z-n units absorb heat from the conditioned space and reject Qh into the block, while the TECs of the L-n units absorb heat from the block and reject Qh to the surrounding air.

[0040] In the constructed prototype, the TECs are thermally coupled to one face of aluminum cooling block. Heat exchange fins are affixed to both the active surface of the TECs and the opposing, free surface of the aluminum block. This unified assembly is housed within a dedicated air chamber.

[0041] The configured airflow within this chamber traverses both sets of fins simultaneously, enabling combined active heat pumping (via the TECs) and passive sensible heat exchange (directly with the block). This configuration bridges the air, refrigerant, and solid-state thermal cycles within a single, multifunctional interface.

[0042] COOLING MODE OPERATION:Z-n units (701-703) function as evaporators.Heat pumping: Air — TEC — Refrigerant (active);Air — Heat conducting metallic block (passive).L-n units (801-802) function as condensers(Heat flow: Refrigerant TEC Air).Heat pumping: Refrigerant TEC Air (active);Heat conducting metallic block — Air (passive).NRV 902 ensures that the vapour compression happens within the L-n blocks.

[0043] FORWARD STROKE SEQUENCEStep 1 — Float Position: The float (311) exposes EVP -IN (305) to VPS-A (306).Thus, CM-1 receives the high-pressure vapor.Step 2 — Pressure Action: High Pressure acts on PH-1 (202), pushing the rod (500) rightward.Step 3 — Compression: As PH-1 moves rightward, L-n undergoes primary boundary compression.Step 4 — Hard compression: As PH-3 moves rightward, L-n undergoes secondary hydraulic recompression. NRV-902 remains oriented to ensure that the hard-compression pressure is retained within the L-n units (801-802) and does not spill back into CM-2.Step 5 — Condensation: Near complete condensation and Latent heat release occur at L-n due to: Primary boundary compression (PBC) and secondary hydraulic recompression (SHC)

[0047] HEATING MODE OPERATIONIn heating mode, the thermodynamic roles of the Z-n and L-n units are reversed.The commutator master switch changes state, thereby reversing the polarities of the TECs in the Z-n and L-n units, and the states of the associated solenoid valves.The mechanical cycle of the VPS-LPDS-VCS assembly remains unchanged.

[0048] FIG. 3 illustrates the fluidic routing and operational state in heating mode, showing vapor flow between Zone units (Z-n, 701-703), Load units (L-n, 801-802), the buffer-pressure chamber (CM-3 / 403), the power chamber (CM-1 / 204), the primary boundary compression chamber (CM-2 / 304), and the recompression chamber (CM-4 / 404). The switching states of Solenoid Valves 911- 914, together with the directional constraints of NRV 901 and NRV 904, are shown in their heatingmode configuration.

[0049] High-Pressure Admission Path (Heating Mode)In heating mode, L-n units (801-802) act as the evaporator. In cold climate, TEC absorbs heat by cooling below ambient temperature. While it's hot side contacting the Heat conducting metallic block, vaporizes & pressurize the refrigerant with Qh (Qh = Qc + J). Thus, high-pressure vapor originates at L-n. SV-912 admits high-pressure vapor into CM-3 exclusively through the right-side channel of SV-912. From SV-912, the vapor flows into CM-3, the Buffer Pressure continuum.

[0050] LPDS Handling (CM-3 — Buffer Pressure Region)CM-3 (403) retains its universal role in both modes: Receives high pressure from the active evaporator. CM-3 never expands or compresses - serves as thermodynamic buffer and routing hub. The LPDS float (311) and sleeve (310) maintains the following invariants: CM-1 has high-pressure & CM-2 has the low-pressure - regardless of mode.

[0051] VPS Operation in Heating ModeHigh-pressure vapor entering CM-1 undergoes isobaric expansion absorbing heat at the designated subsystem (L-n). PH-1 (202) is driven left / right, powering the primary stroke.

[0052] CM-2 — Primary Boundary Compression (PBC) Chamber (304)CM-2 contains the vapor trans-located from CM-1 (isenthalpic event). Condensation due to translocation follows the same universal four-stage mechanism:1. Condensation under partial pressure of vapour (due to changed environment out of isenthalpic continuum switching),2. Primary Boundary Compression (PBC) chamber of PH-1,3. Latent heat removal at Z-n (Because of TECs of Z-n; Z-n acting as condenser in heating mode),4. Hydraulics-assisted hard compression in CM-4.The only change in heating mode is the destination of the condensed vapor (Z-n instead of L-n).

[0053] Recompression Chamber CM-4 (404)PH-3 (402) performs hydraulically amplified hard recompression,Raising Psat of Z-n equal to that of L-n just before liquid feed to L-n.Critical NRV-904 blocks upstream pressure from L-n until pressure equalization.

[0054] Solenoid Configuration (Heating Mode)Heating mode is the inversion of cooling mode:SV-911 & SV-912 ALWAYS Opposite States.SV-912 admits high pressure (right path open).SV-911 blocks its right branch.SV-913 & SV-914 — is always the Same State, irrespective of cooling or heating modes.In heating mode both route their " x" marks to the left side:Enabling: Liquid feed — L-n, Compresses vapour within Z-n,Releasing near complete latent heat at indoor (Z-n), absorbed from outdoor (L-n).

[0055] At L-n (Outdoor Unit — Evaporator)With reversed polarity, TEC absorbs heat with its cold side, contacting the ambient air.Hot side pumps this absorbed heat + Joule heat,Vaporizing the refrigerant in the heat conducting metallic block.

[0056] At Z-n (Indoor Unit — Condenser)Cold side of TEC contacts the heat conducting metallic block.Latent heat is released through the four condensation processes.TEC's cold side absorbs the latent heat released with complete condensation.TEC's hot side pumps this absorbed heat + Joule heat to the hot side (air side).Room air is heated with Z-n operating as a condenser.Heat pumped by each indoor unit (Z-n) varies withApplied voltage to TECs engaged at that particular zone (Z-n),Even though the heat absorption due to flash boiling (BIFB) is the same for all zones.

[0057] Final Vapor / Liquid Routing (Heating Mode)Full working-fluid path: L-n (SV-912) CM-3 CM-1 CM-2 (NRV-901) Z-n.Where CM-1 is expansion chamber, CM-2 is PBC chamber, Z-n is for latent heat release.Recompression path: CM-4 — NRV-901 — Z-n. This completes the heating-mode cycle.

[0058] FIG. 4 — LPDS Float (311) Switching SequenceFIG. 4(a): Post-Forward Stroke; FIG. 4(b): Post-Reverse Stroke. FIG. 4(a) illustrates the LPDS condition immediately after the forward stroke, where PH-2 (302) mechanically pushes the float (311) rightward, aligning the lower outlet with HP continuum. FIG. 4(b) illustrates the LPDS condition immediately after the reverse stroke, where PH-3 (402) mechanically pushes the float (311) leftward, aligning the upper outlet with HP continuum.

[0059] Fixed Pipe Assignments in the LPDS Sleeve (310)Referring to FIG. 4(a) and FIG. 4(b):Upper outlet — permanently connected to cap side of PH-1 andLower outlet permanently connected to rod side of PH-1.

[0060] Float Motion is Push-Driven only; because CM-3 surrounds the float externally with HP and the internal recess carries LP, float heads (315 & 316) cancel axial pressure loads. Thus the float is only pushed - rightward by PH-2 (302) & leftward by PH-3 (402) - at the end of each stroke.

[0061] FIG. 4(a) — Post-Forward- Stroke State. In this alignment, Lower outlet receives HP & Upper outlet — receives LP. This prepares the next (reverse) stroke because HP will next act on the rod side of PH-1, driving the shared rod leftward.

[0062] FIG. 4(b) — Post-Reverse-Stroke State (Float Leftward). In this alignment: Upper outlet —> receives HP & Lower outlet — receives LP. This prepares the next (forward) stroke because HP will next act on the cap side of PH-1, driving the shared rod rightward.

[0063] Snap-Cantilever (312) and Sleeve Bulge (313) InteractionThe interaction between the snap-cantilever (312) and sleeve bulge (313) provides two functions:

[0064] Energy Storage + Deterministic SwitchingAs the snap Cantilever (312) rides over the bulge (313), lateral expansion is momentarily restricted; preload accumulates in the springs (314), producing a clean, and — snap-over II transition into the alternate float chamber. This prevents: partial port overlap, mid-position leakage, ambiguous HP / LP assignment.

[0065] Mechanical Limit Stop for Float Heads (315 & 316) - restricting float over travel.

[0066] The system utilizes two distinct forms of mechanical work transfer:Primary Boundary Compression (PBC): This is boundary work performed by the expanding vapor parcel in CM-1 (204) directly on the vapor parcel in the primary boundary-compression chamber CM-2 (304) through the physical motion of the shared power piston PH-1 (202). It is a pressurevolume (P-V) work transfer between two thermodynamic systems within the VPS.Shaft Work: This is the useful work delivered by the shared rod (500) to the Vapor Compression System (VCS). The thrust amplification generated by the bore-differentiated pistons is conveyed as mechanical force along the rod, enabling the hard, hydraulic re-compression of vapor within chamber CM-4 (404), with the resulting latent heat released as sensible heat at the designated L-n.

[0067] Air-Cycle Subsystem (ACS)The Air-Cycle Subsystem (ACS) comprises a tapered horizontal main air chamber (709) configured to supply airflow to a plurality of vertical zone units (Z-n) (70 -703).

[0068] Each Z-n unit (701-703) integrates a thermoelectric cooler (TEC) assembly and aluminum block (704). In a default cooling mode configuration, a hot side (602) of the TEC is thermally coupled to the aluminum block (704), while a cold side (603) of the TEC is oriented toward an incoming static-pressure component (711) of the airflow.

[0069] Air entering the Z-n unit passes through a staggered hexagonal fin array (708), configured to provide a high-surface-area heat exchange interface. The assembly further includes an air treatment neck with an activated carbon filter (707) for purification and deodorization, and a condensate drain (713) for removing moisture condensed on the TEC's cold side.

[0070] The latent heat released during condensation is absorbed by the aluminum block (704), providing a regenerative thermal input that offsets sub-cooling and stabilizes refrigerant saturation conditions, thereby reinforcing the Sensible-Heat-Induced Saturation (SHIS) process.

[0071] A slidable hollow drum (705) at the T-junction of each Z-n unit is configured to modulate a cross-sectional cavity. This action mechanically regulates the static-pressure component (711) driving air into the Z-n unit, independent of the dynamic-pressure component (712), thereby providing autonomous, non-electronic variable air volume (VAV) control.

[0072] Thus, the ACS simultaneously provides: (a) zone-wise conditioned airflow; (b) self- contained dehumidification without latent heat release into the conditioned space; (c) air purification and deodorization; (d) regenerative utilization of latent heat to stabilize the SHIS mechanism; and (e) mechanical airflow modulation.

Claims

What is claimed is;1. A thermal energy conversion system comprising: a hermetically sealed coaxial assembly integrating a Vapor Power System (VPS), a Linear Pressure Distribution System (LPDS), and a Vapor Compression System (VCS); a shared rod (500) mechanically coupling the VPS, LPDS, and VCS for synchronized operation; wherein the VPS includes a first power chamber CM-1 (204) and a primary boundary compression chamber CM-2 (304) defined by opposing faces of a double-acting power piston PH-1 (202) with annular slots (207) for O-rings; a plurality of scalable, independently operable Z-n subsystems (701-703), each configured as an indoor unit; a plurality of scalable L-n subsystems (801-802), each configured as an outdoor unit; wherein Z-n and L-n subsystems are scalable, wherein multiple Z-n subsystems provide user-oriented distributed climate zones, and wherein multiple L-n subsystems provide system-oriented distributed heat-exchange interfaces for enhanced heat exchange rate; a buffer pressure chamber CM-3 (403) in fluid communication with the Z-n and L-n subsystems depending on the mode of operation; wherein the system is configured such that a pressure within CM-3 (403) varies proportionally with a sensible thermal load from engaged Z-n or L-n subsystems; and wherein the system is configured to achieve Sensible-Heat-Induced Saturation (SHIS) and Boundary-Induced Flash Boiling (BIFB) to enable autonomous vapor circulation and compression.

2. The system of claim 1, wherein the LPDS comprises: a sleeve (310) comprising a stationary annular bulge (313) and a plurality of ports including EVP -IN (305), VPS-A (306), VPS-B (307), and CND-OUT (405), wherein the CND-OUT (405) port pierces through the annular bulge (313); a float (311) with two sealing heads (315, 316) with annular slots (207) for O-rings, slidably disposed within the sleeve (310) and defining an internal annular cavity that is in constant fluid communication with CND-OUT (405) port; and a detent mechanism comprising at least two snap-cantilever (312) mounted symmetrically opposite on the float (311) and configured to interact with the stationary annular bulge (313); wherein the float (311) having two sealing float heads (315 and 316) is configured to be mechanically pushed by - either piston PH- 2 (302) or piston PH-3 (402), with annular slots O-rings (207), into one of two stable positions.

3. The system of claim 2, wherein the interaction between the snap-cantilever (312) and the annular bulge (313) provides a momentary resistance to float motion, thereby energizing a spring (314) to ensure a complete snap-over action, the annular bulge (313) further acting as a hard stop to limit float travel beyond precise slot.

4. The system of claim 2, wherein the float (311) of a Linear Pressure Distribution System (LPDS) is configured to translocate a vapor parcel from the expanding chamber (CM-1 / 204) to the primary compression chamber (CM-2 / 304) upon switching position against ports of the stationary sleeve (310), the LPDS being as defined in claim 13.

5. The system of claim 1, wherein the buffer pressure chamber CM-3 (403) is defined between piston PH-2 (302) and compression piston PH-3 (402) via central bore of float (311) and excluding the central recess in between float heads (315 & 316), and wherein PH-2 (302) and PH-3 (402) have equal bore diameters such that pressure within CM-3 (403) produces cancelling forces.

6. The system of claim 1, wherein each Z-n subsystem (701-703) and each L-n subsystem (801— 802) comprise a common hardware module including: a heat-conducting block (701) with internal refrigerant passages; at least one thermoelectric cooler (TEC) thermally coupled to a first face of the each block; and heat-exchange fins affixed to the TEC side and to an opposing free surface of the block.

7. The system of claim 6, wherein a total rejected heat (Qh) from the TECs, comprising absorbed waste heat of environment (Qc) and internally created waste heat (Joule heat - J), is utilized to drive the Sensible-Heat-Induced Saturation (SHIS) mechanism with designated subsystems.

8. The system of claim 1, configured to leverage a volume collapse of condensation both mechanically, by generating hydraulic-assisted thrust amplification, and thermally, by inducing Boundary-Induced Flash Boiling (BIFB).

9. The system of claim 1, configured to operate in a cooling mode wherein Z-n subsystems ( OIOS) function as evaporators and L-n subsystems (801-802) function as condensers, and wherein an increase in engaged Z-n subsystems increases pressure in CM-3 (403); resulting, increasedpressure differential across the core system, leading to accelerated refrigerant mass flow rate and increased heat transfer.

10. The system of claim 1, configured to operate in a heating mode wherein Z-n subsystems (701-703) function as condensers and L-n subsystems (801-802) function as evaporators, and wherein an increase in engaged Z-n subsystems decreases pressure in CM-3 (403); resulting, increased pressure differential across the core system, leading to accelerated refrigerant mass flow rate and increased heat transfer.

11. A method of thermal energy conversion, comprising the steps of: driving a coaxial assembly having a Vapor Power System (VPS), a Linear Pressure Distribution System (LPDS), and a Vapor Compression System (VCS) with a shared rod (500); varying a pressure within a buffer chamber CM-3 (403) in proportion to a sensible thermal load from one or more engaged Z-n (701-703) or L-n (801-802) subsystems; autonomously regulating system operation based on said pressure variation; supplying high-pressure vapor to the power chamber CM-1 (204), with CM-2 (304) serving as the primary boundary-compression chamber, wherein a float (311) within the LPDS alternately directs CM-1 vapor to the rod end and cap end of PH-1 (202); performing hydraulics-assisted hard recompression with chamber CM-4 (404); and achieving Sensible-Heat-Induced Saturation (SHIS) and Boundary-Induced Flash Boiling (BIFB) with the designated subsystems (Z-n or L-n).

12. The method of claim 11, further comprising, upon a flip of the float (311), trans-locating a vapor parcel from CM-1 (204) to CM-2 (304) using the LPDS of claim 13, such that the parcel enters a changed thermodynamic environment that initiates condensation under vapour partial pressure.

13. A Linear Pressure Distribution System (LPDS) for a thermal energy conversion system, the LPDS configured to provide: a) fluidic coupling by enabling sealed translocation of a working-fluid parcel from CM-1 (expansion chamber) to CM-2 (primary boundary-compression chamber); b) physical coupling between a Vapor Power System (VPS) and a Vapor Compression System (VCS) without an external shaft or gland seal; c) mechanical coupling for conveying shaft work; andd) thermodynamic coupling for isenthalpic translocation of an expanded vapour parcel to induce spontaneous condensation.

14. The LPDS of claim 13, wherein the fluidic coupling is performed by a float (311) configured to deliver the expanded vapor parcel from CM-1 of the prior stroke to CM-2 and to coordinate venting of CM-2 to a condenser port to be compressed during boundary-compression.

15. The system of claim 1, wherein a working-cycle frequency is configured to autonomously increase following an initial condensation event due to a synergistic feedback loop between a mechanical pull-effect generated by vapor-liquid volume disparity and a thermal replenishment inflow via the exposed free area of the heat-conducting block (704) for Boundary-Induced Flash Boiling (BIFB) with designated subsystems.

16. A method of reducing a thermal load, comprising the steps of: absorbing thermal energy from a conditioned space into a working fluid; directly converting a portion of the absorbed thermal energy into mechanical work via autonomous reciprocation within a hermetically sealed Vapor Power System (VPS); expending the converted portion of thermal energy, thereby actively reducing the thermal load of the conditioned space; wherein any dissipative retarding force results in additional heat expenditure, which is advantageous when the system operates as a cooler; and wherein the reduced thermal load permits the thermoelectric coolers (TECs) to be under-run in later stages, thereby lowering Joule heat formation and increasing the coefficient of performance (COP) of each TEC.

17. The system of claim 1, wherein the Vapor Compression System is configured to perform a dual compression sequence on a vapor parcel, the sequence comprising: a a Primary Boundary Compression (PBC) stage, wherein isobaric expansion in CM-1 (204) exerts compressive force on a vapor parcel in CM-2 (304); and b a Secondary Hydraulic Compression (SHC) stage, performed in CM-4 (404), configured to further compress the vapor parcel subsequent to the PBC stage, wherein, during the SHC stage, the vapor parcel in CM-4 is compressed to a level sufficient for the associated subsystem to reach its saturation pressure, with Z-n in cooling mode or L-n inheating mode — thereby enabling near-complete condensation in the subsystem prior to liquid feed..

18. The system of claim 1, wherein the Vapor Compression System (VCS) is configured to perform a dual compression sequence on a vapor parcel, the sequence comprising: a) a Primary Boundary Compression (PBC) stage, wherein isobaric expansion in CM-1 (204) exerts compressive force on a vapor parcel in CM-2 (304); and b) a Secondary Hydraulic Compression (SHC) stage, performed in CM-4 (404), configured to further compress the vapor parcel subsequent to the PBC stage.

19. The system of claim 1, wherein a bore diameter of the compression piston PH-3 (402) is smaller than a bore diameter of the power piston PH-1 (202), and wherein the swept volume of CM-4 (404) is dimensioned to be substantially less than the swept volume of CM-1 (204), thereby maintaining mass continuity.

20. The system of claim 19, wherein the expanding evaporator side of PH-1 provides a high-volume, low-density vapor, and the collapsing condenser side of PH-1 provides a lower-volume, higher-density vapor that generates a pull-effect on PH-1 toward the condenser side; and wherein the collapsing chamber of PH-3 provides the least volume and the highest-density vapor, producing an additional pull-effect on PH-1 that reduces liquid-feed load; and wherein the disparity in volume at the condenser side enables bore reduction, the resulting thrust amplification decoupling system performance from the source-sink temperature differential and permitting operation even with low-grade heat sources such as the inherent enthalpy of room air when its effective AT is amplified by the TEC.

21. An air-cycle subsystem (ACS) for a thermal energy conversion system, the ACS comprising: a main air chamber (709) configured to convey an airflow; at least one zone unit (Z-n) comprising a vertical pipe (701) in fluid communication with the main air chamber (709) via a T-junction; a thermoelectric cooler (TEC) assembly (702, 703) disposed within the Z-n unit; and a slidable hollow drum (705) surrounding the Z-n unit at the T-junction and configured to modulate a cross-sectional cavity, thereby mechanically regulating a static pressure component (711) to drive orthogonal airflow into the Z-n unit.

22. The ACS of claim 21, further comprising an air treatment assembly disposed within the Z-n unit, the assembly including a charcoal filter (707) and a condensate drain (713).

23. The ACS of claim 21, wherein the Z-n unit further comprises a staggered hexagonal fin array (708) configured to increase heat exchange surface area, leveraging significantly high thermal conductance and thermal diffusivity of stationary metallic matrix compared to those of flowing air along the porosity of the matrix.

24. The ACS of claim 21, wherein the TEC assembly (702, 703) is configured to perform dehumidification, and a method of integrated air cycling and thermal stabilization, comprising the steps of: conveying an airflow through a main air chamber (709); mechanically modulating a static-pressure component (711) at a T-junction with a slidable drum (705) to control airflow into a zone unit (Z-n) (701); cooling and dehumidifying the air within the Z-n unit via a thermoelectric cooler (TEC) (702, 703); and transferring latent heat from condensation to a refrigerant within a heat-conducting block (704) for regenerative stabilization of Sensible-Heat- Induced Saturation (SHIS) process with designated subsystems..

25. A method of enhancing the coefficient of performance (COP) of a thermoelectric cooler (TEC), comprising the steps of: thermally coupling a hot side of the TEC to a heat-conducting block (704) stabilized at a substantially constant saturation temperature (Tsat) of a refrigerant with designated subsystems; applying a thermal load from a conditioned space to a cold side of the TEC; wherein stabilizing the hot side at Tsat mitigates internal negative thermal bleeding within the TEC.

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