Patent Publication Number: US-2020284148-A1

Title: Positive displacement heat machines with scavenging

Description:
FIELD OF INVENTION 
     The invention relates to a positive displacement heat machines. More particularly the invention relates to a positive displacement heat machine for applications such as:
         Heat pumps for ecology clear coolers or heaters, high COP, no refrigerant, working with any gas in closed or open cycle from any source of mechanical energy, for example wind.   Engines with external heating, for example by concentrated Sun light.   Engines with internal combustion and reduced emission of dirty products, capable of burning a wide variety of fuels;
           for transport, engines with high compression and small weight, efficiency 50-60% for every working mode;   for transport and power plant, with low compression and regeneration, efficiency more 60% for every working mode.   
               

     BACKGROUND OF INVENTION 
     Description of Prior Art 
     1. U.S. Pat. No. 4,333,424A discloses an Internal combustion engine which has a compressor which compresses air for delivery via a heat exchanger to an expander. The expander receives the compressed air and fuel and, while combustion occurs during a power stroke, the air pressure is reduced to atmosphere and the expander drives a crankshaft. The fuel is injected at a rate to maintain the air temperature at the entry temperature. The exhaust passes through the heat exchanger to heat the incoming flow of compressed air to the expander. Energy may be stored via the crankshaft or used directly (The description recites: “The compressor  40  has two stages  43 ,  44  with an intercooler  45  there between.”, “ . . . the compression is assumed to take place isothermally . . . ”; “ . . . . Both the large crankshaft and the large flywheel can also be eliminated by using the expander to drive a hydraulic pump which in turn drives a small hydraulic motor connected to a small crankshaft and flywheel rotating in unison at high speed . . . . This crankshaft also drives a high speed compressor as well as the load.”). 
     Problems of U.S. Pat. No. 4,333,424A 
     Thermodynamic cycle of this engine give the same large efficiency as cycle Carnot, if compressor is isothermal; efficiency no depend from compression ratio. Mentioned two stages compressor with intercooler may approximate the isothermal compression, but cause addition vortex and friction loss. If compression ratio is small, for example, kp=2, a single stage compression is near isothermal, but the small kp cause large size cylinders of compressor and expander and so large loss caused by transfer energy between compressor and expander with crankshafts or hydraulic means, Any case, this engine have a small ratio power/volume and so large weight and inertial forces, that make it very sensitive to friction loss in crankshaft bearings and to vortex loss. For this and another prior art with crankshaft, regulation to a small rotation moment (load) diminish efficiency, so as part of friction loss, caused by inertial forces, no depend from the load; regulation to a small rotation speed with gear increase friction loss, and regulation with hydraulic means cause vortex loss. 
     2. U.S. Pat. No. 4,369,623, discloses an engine with positive displacement piston chambers, an external combustion chamber from which combustion gases pass . . . to piston chambers, an air compressor, a heat exchanger where exhaust gases from the piston chambers preheat compressed air which then flows to the combustion chamber, and an accumulator for storing . . . compressing air from the compressor . . . . (The description recites: “ FIG. 1  . . . preferred embodiment . . . different pistons form the air compressor and the power unit.”, “high pressure gases . . . force . . . pistons  48  . . . connected to a crankshaft  58  . . . Pistons  12  of the air compressor are also connected to the crankshaft  58 .”, “ FIG. 2  . . . in which the same pistons . . . function as a compressor during one stroke of the cycle and during the other strokes is driven by the hot gases from the combustion chamber.” From Claim  1 : “ . . . for allowing compressed air to exit said displacement chamber . . . during about each fifth stroke of said piston during the normal steady state mode of the engine; . . . ”). 
     Problems in U.S. Pat. No. 4,369,623 
     Friction loss, caused by transfer energy with crankshaft. Regulation by compression “during about each fifth stroke” cause pulsation of pressure in the combustion chamber and so diminish efficiency. For this and another mentioned below prior art with crankshaft, regulation to a small rotation speed increase thermal loss to wall of cylinder and to piston. 
     3. U.S. Pat. No. 7,281,383 discloses a four stroke Brayton refrigerator or heat engine which is a thermal machine that can function as either a refrigerator or an external combustion heat engine . . . Bravton cycle . . . adiabatic compression and adiabatic expansion, take place in the same cylinder, within which a piston, driven by a crankshaft, reciprocates. The remaining two processes, each of which is a transfer of heat at constant pressure, take place in a high pressure heat exchanger and a low pressure heat exchanger. A rotary valve . . . creates passages between the cylinder and the heat exchangers, and is constructed so that compression and expansion ratios are equal.” From description: “ . . . conditioner according to a basic embodiment (Tc=16 C, Th=32 C, nitrogen refrigerant, P(low)==23 bar) gives cycle C.O.P.=8.03.”; “Th=Temperature at the outlet of heat exchanger H, . . . Tc=Temperature at the outlet of heat exchanger L”. 
     (“L” to cool a room air, “H” to cool compressed air. No examples for temperatures at inputs of the heat exchangers.) 
     Problems in U.S. Pat. No. 7,281,383 B2 
     For good efficiency, compression and expansion ratios must be equal; the rotary valve, constructed for it, cause a vortex loss. For engine, volume after expansion is more, than before compression, for heat pump—vice versa, so both cases, part of the cylinder volume is not used, that increase friction loss in crankshaft bearings. Part of piston stroke is used for displacing compressed gas between the cylinder and heat exchanger “H”, that increase loss in piston sealing and crankshaft bearings; near a dead point, no any useful process, but crankshaft bearings rotating under maximum pressure that cause addition friction loss. During begin output to “H” and end input from “H”, surfaces of openings are small, so velocity of gas is large that cause addition vortex loss. Large velocity current of hot gas during input increase loss of heat to surface of the cylinder. Due to parasite volume of the cylinder, part of compressed gas no make useful work. This part, mixing with a hot input gas, diminishes maximum temperature of a cycle, so diminish efficiency and power. If volumetric compression is 10 and the parasite volume is 1% of maximum volume of WC, 10% of gas no work. 
     A problem of any heat machine is: when Energy of Compression (EC) is close to Energy of Expansion (EE), the heat machine is very sensitive to loss during compression and expansion, so to the vortex and friction loss. Suppose, that conditioner work with open Brayton adiabatic cycle and get air from a room with Tbc=27° C.=300° K; This air is compressed to Tec=317° K, so kt=1.057, then cooled in heat exchanger “H” to Tbe=305° K, then expanded in the cylinder to Tee=Tbe/kt=289° K, then mixed with a room air. If no loss, COP=289/(305−289)=18. Compression and expansion are between the same pressures, so EC/EE=Vbc/Vee=Tbc/Tee=1.038. If EE=100 J, EC=103.8 J, no loss: MW=EC−EE=3.8 J. If efficiency of compression and expansion is 0.97: MW=103.8/0.97−100*0.97=10 J. So, really COP=18*3.8/10=6.8&lt;&lt;18, even with ideal heat exchanger. In the prior art with preferable closed system, C.O.P. is good due to large Pbc=“P(low)===23 bar”, so, mechanical efficiency and volumetric power of cylinder are better, then for the open system. But, the closed system have disadvantages comparing to the open system: large sizes and cost of heat exchangers; heat exchanger “L” is a source of infection, collected on a large wet surface; temperature at input of “L” is smaller, then Tee in open system, that diminish COP; temperature Tc at output of “L” is smaller, then Tbc, that diminish heat power, EC/EE is closer to 1 and the system is more sensitive to loss during compression and expansion; possible leak. The vapor compression refrigerators, that are in common use, include the same problems. Open system no have this problems, but friction loss in bearings of crankshaft and piston rings, vortex loss in the rotary valve, make the open system no practical for conditioner. So, the problems are vortex and friction loss, and in addition for closed system: possible leak, diminish COP and possible infection, larger cost and size, caused by heat exchanger “L”. 
     4. U.S. Pat. No. 8,360,759 Discloses a Rotary Engine Flow Conduit Apparatus and Method . . . . 
     It describes an Internal Combustion Engine (ICE) with vanes, moving in slots of eccentric rotor, with using slots to displace air between atmosphere and working chambers, that are between vanes, rotor and housing. 
     Problems in U.S. Pat. No. 8,360,759B2: 
     Friction loss by vanes, vortex loss inside slots, a short time for combustion—a common problem for Internal Combustion Engines. large loss of heat to surfaces of WC—a common problem for rotor engines. 
     5. US20070199299A1 discloses a combustion engine that has at least a plurality of power strokes during a complete cycle . . . piston—cylinder arrangement is used to compress air and deliver it to a combustion chamber . . . ” (From description: “ . . . two . . . eight or even more power strokes . . . ”; “[0021] Valve control . . . to optimize compression, combustion, expansion and exhaust during engine operation”; “Piston displacement is translated by a connecting rod linking it to a crankshaft into rotary power engine output”). 
     Gist: the same cylinder with several working strokes for single compression stroke; or mixing, with several cylinders, one 
     only for working strokes [0025]; transfer energy by crankshaft. 
     Problems in US20070199299A1 are the same that mentioned above for [2] U.S. Pat. No. 4,369,623. 
     6. DE102009049974 discloses a heat engine device for converting heat into mechanical work that has two stroke piston engines with one or multiple cylinders and crank shaft. It comprises “ . . . a two stroke piston engine with one or multiple cylinders and a crank shaft. A cool working gas is supplied into an area over a piston . . . compressed during the piston movement . . . pushed in an external heater . . . .” 
     Problems in DE102009049974 A1: About increased friction, vortex and thermal loss in prior art EHE during displacing compressed gas, see explain to prior art 3. 
     7. WO1998057038 discloses a Multi vane rotary piston engine, in which the compressed air is introduced in the combustion space through outlets on the side covers, while the exhaust gases are introduced, through outlets on the side covers, . . . .” 
     Problems in WO1998057038 A1: the vanes are moving inside slots under pressure force, that cause friction loss. The outlets are in side covers, so with increasing length of the rotary piston engine, increasing vortex loss. Optimal Vee/Vbc is only for a single working mode, else part of expansion energy will be lost. 
     8. WO2011046975 discloses a hydraulic internal combustion engine with “ . . . at least one combustion piston . . . acting on hydraulic plungers through valving to control the piston position and velocity . . . ”. It is a free piston engine with Pulse Pause Modulation (PPM). 
     Problems in WO2011046975 A1: Hydraulic valves, used for the PPM and another purposes, cause addition vortex loss. A short time for combustion, is a common problem for ICE, and it is very short for the free piston engine, that may cause dirty “Output products” (see GLOSSARY . . . ). Partly loss of expansion energy that is a common problem for prior art machines with the same working chamber for compression and expansion of all working fluid. 
     9. Peter A. J. . . . “ Horsepower with brains: The design of the CHIRON Free Piston Engine ” (Society of Automotive Engineers, Inc., January 2000) discloses a free piston engine with PPM, with the same problems, as for prior art 8. 
     Summary of Prior Art Problems 
     
         
         
           
             At a partly power, that is most used mode for transport, engine efficiency may be twice smaller, than at optimal mode; see explain to prior art 1 and 2. 
             In engines, must Vee&gt;Vbc, else part of expansion energy will be lost, see prior art 2, 3, 7, 8, 9. In prior art 2, “each fifth stroke” used for compression: Vee=5*Vbc, that diminish efficiency, as mentioned for prior art 2. 
             Short time for combustion in ICE causes a bad combustion with ecology dirty emissions. 
             Prior art with increasing vortex moving for better combustion, have more vortex loss and loss of heat. 
             EHE, designed to use combustion energy, have large external combustion chamber (see “HPC”) and so a large time for mixing and combustion, but prior art have increased friction, vortex and thermal loss during displacing compressed gas by piston, see explain to prior art 3. 
             Regulation to a small load or small rotation speed diminish efficiency, see prior art 1, 2. 
             Free piston engines have hydraulic loss, loss of expansion energy, short time for combustion—see prior art 8, 9. 
           
         
       
    
     List of Prior Art Problems 
     Loss of efficiency at partly power. Partly loss of expansion energy. Friction loss in bearings of crankshaft, by piston rings, by vanes. Vortex loss in valves and cylinder. In ICE, short time for combustion. Loss of heat to surfaces of WC. In EHE, parasite volume of the WC, and addition (comparing to ICE) friction, vortex, and thermal loss. 
     Description of this problems see above and solving by this invention see below. 
     It is therefore an object of the present invention to provide a method of operating a Positive Displacement Heat Machine, which overcomes the drawbacks of prior art. 
     Other objects and advantages of this invention will become apparent as the description proceeds. 
     SUMMARY OF THE INVENTION 
     A method of operating a Positive Displacement Heat Machine (PDHM), the PDHM provided with at least a single Working Chamber (WC), arranged to change its volume during at least a part of a thermodynamic cycle and to transfer mechanical energy to/from a compressible Working Fluid (WF); the thermodynamic cycle including compression and expansion entailing Lower Pressure (LP) of the WF; the thermodynamic cycle further including Higher Pressure (HP), HP&gt;LP; the thermodynamic cycle also including a Lowest Temperature (LT) of the WF; the thermodynamic cycle further including a High Temperature (HT), HT&gt;LT; the PDHM is further provided with at least a single Low Pressure Chamber (LPC,  40 ), containing the WF with the LP; the LPC may be the atmosphere, otherwise the LPC is provided with means, arranged for thermal transfer between the LPC and an external medium; the LPC is provided with an LPC Input Part (LPCIP) for the WF and an LPC Output Part (LPCOP) for the WF with changed temperature; at least a single Low Pressure Input Mean (WCLPIM,  20 ) is provided between the WC and the LPCOP, and at least a single Low Pressure Output Mean (WCLPOM,  21 ) is provided between the WC and LPCIP, both arranged as controllable openings; the PDHM providing with at least a single High Pressure Chamber (HPC,  8 ), that contains the WF with the pressure HP; if the PDHM is the heat pump, the HPC  8  arranged for cooling the WF by heat transfer to external medium; at least a single High Pressure Controllable Opening (WCHPCO,  18 ) is provided between the WC and HPC; the thermodynamic cycle comprising:
         1.1. moving at least a part of the WF from the WC to the LPCIP across the WCLPOM  21 ;   1.2. moving at least a part of the WF from the LPCOP to the WC across the WCLPIM  20 ;   1.3. changing a temperature of the WF in the LPC  40 , and/or in the WC, and/or in the HPC  8 ;   1.4. compressing the WF in the WC with closed WCLPOM  21 , WCLPIM  20 , WCHPCO  18 ;   1.5. moving the WF across the WCHPCO  18 ;   1.6. expanding the WF inside the WC with closed WCHPCO  18 , the method is characterized in that:       

     during step 1.5, after ending compression in the WC, and when pressure in the WC is close to pressure in the HPC  8 , opening the WCHPCO  18  and displacing at least a part of the WF between the WC and HPC  8 , such that displacement of the part is not caused by changing the volume of the WC. 
     A two stroke reciprocating piston engine apparatus, comprising: 
     a) at least single thermally isolated High Pressure Chamber (HPC)  8  with Working Fluid (WF) compressed to High Pressure (HP), volume of the HPC  8  is sufficiency more, than end compression volume Vec; 
     b) at least single Cylinder  15  with two Assemblies  16 , each Assembly includes: 
     b.1) two Crankshafts having minimal Inertial Moment, each Crankshaft is not connected to external load; 
     b.2) a Piston, connected to a central part of a Beam; 
     b.3) a Buffer  51 , connected to central part of the Beam opposite to the Piston, for accumulating Energy from Expansion (EE) of WF (gas) during working stroke of the Piston, and return the EE during compression stroke as Energy for Compression (EC), while EE and EC are approximately the same, EE=EC; 
     b.4) two connecting rods, one side of every connecting rod connected with bearing to a tip of the Beam, and another side with another bearing connected to corresponding Crankshaft being connecting to a synchronization gear; the crankshafts are arranged to rotate to opposite directions due to the gears; at least one of the crankshafts with addition gear and synchronization Belt connected to corresponding crankshaft of another the Assembly; 
     c) the two Assemblies  16 , are arranged such, that: 
     c.1) symmetrically moving each of the two Pistons inside the Cylinder  15  between High Pressure Dead Point (HPDP), that is near a central part of Cylinder  15 , and a Low Pressure Dead Point(LPDP), that is near a tip of Cylinder  15 , so in Cylinder  15  there are two the HPDPs and two the LPDPs; 
     c.2) symmetrically moving all parts, such that inertial forces are balanced; 
     c.3) symmetrically loading all parts by gas forces, such that there are no forces between the pistons and Cylinder  15 ; 
     c.4) volume (Vmin) between the two HPDP is equivalent or smaller than the Vec, such that the pistons are not displacing all compressed WF to the HPC  8 , thereby diminishing moving pistons under the HP; 
     c.5) Assemblies  16  and all rotating means in it or connected to it, including the Belt, have a minimum Inertial Moment, limited only by mechanical strength, but the Reciprocating Parts in the Assemblies  16  may have a large mass, thereby diminishing dynamic load on the bearings; 
     d) a Working Chamber High Pressure Controllable Opening (WCHPCO)  18  in the central part of Cylinder  15 , between two the HPDP, the WCHPCO  18  arranged to control a flow of WF between the Cylinder  15  and HPC  8 , such that: 
     d.1) the flow begins after ending compression and when the pressure in Cylinder  15  is approximately equivalent to the HP; 
     d.2) the flow ends when volume in the Cylinder  15  is increased to Vbe, and Vbe is equivalent or more than the Vec; 
     e) a fuel Injector  25 A between two the HPDP, remote from the WCHPCO  18 ; the Injector  25 A arranged for combustion after end compression, such that: 
     e.1) after opening the WCHPCO  18 , displacing at least a part of compressed WF to the HPC  8  due to heat expansion of combusted product, thereby diminishing moving of the Piston under the HP; 
     e.2) minimum mixing between the displacing part and the combusted product; 
     e.3) preferably ending combustion before expanding to the Vbe; 
     f) a sensor HPCIMTS  27 , arranged to measure temperature T 27  of the WF in the HPC  8  after the WCHPCO  18 ; 
     g) a Remote Expander  19 , arranged as power output of the engine, without transferring energy from, or to, Assembling  16 , with expansion from the HP to Atmospheric pressure; 
     h) at least a single Electrical Machine  22 , mechanically connected to any of the Crankshafts, for receiving energy, for providing energy, arranged to control rotation of the Crankshafts, the power of the Machine  22  is sufficiency smaller, than the power of the Expander  19 ; 
     i) a Rotating Speed and position Sensor (RSS)  31 , mechanically connected to the Electrical Machine  22  or to the Crankshaft; 
     j) a pressure sensor HPCPS  32 , arranged to measuring differential pressure between HPC  8  and Atmosphere; 
     k) a Controller  29 , arranged to: 
     k.1) control the WCHPCO  18  and Injector  25 A, such that EE=EC, with using feedback from the RSS  31 ; 
     k.2) control the WCHPCO  18  and Injector  25 A, such that if need fast changing of mean speed of the Crankshaft, EE&gt;EC, or EE&lt;EC according to desired changing; 
     k.3) control the Electrical Machine  22 , such that kinetic energy of the Assembling  16  at position according to at least one of the HPDP or LPDP, will be desired volume, including zero, with using for this control feedback from the RSS  31 ; 
     k.4) if the speed of the Crankshaft near at least one of the HPDP or LPDP is near zero, optionally fixating the Assembling  16  during desired Fixation Time, using the Electrical Machine  22  for this fixation; 
     k.5) initiating moving of the Crankshaft with the Electrical Machine  22 ; 
     k.6) synchronization the mean cycle speed of Assembling  16  with throughput of the Expander  19 , such that the pressure HP in the HPC  8 , measured by the HPCPS  32 , will be as desired; 
     k.7) controlling the Injector  25 A and WCHPCO  18  for minimum mixing, mentioned in e.2, with using signal from the RSS  31  and HPCIMTS  27 ; for optimal case, T 27  is not sufficiency more, than temperature at end compression Tec; 
     k.8) controlling the Injector  25 A and WCHPCO  18 , such that pressure at the end, expansion will be not substantially more than Atmospheric pressure; 
     l) at least a single Fuel Injector  25 B, preferably inside the HPC  8 , and optionally in Expander  19 . 
     In heat machine (see explain to prior art 3) take place compression process that get energy EC, and expansion process that give energy EE. Efficiency of compressor Efc&lt;1, expander Efe&lt;1. For engine, EE&gt;EC, for heat pump, EE&lt;EC. Mechanical Work from engine or input work for heat pump is: MW=EE*Efe−EC/Efc. For heat pump MW&lt;0. 
     Main principle (gist) of the present invention is to make Efc, Efe close to 1, by another words, diminishing the loss, caused by circulation energy inside heat machine. 
     Combination of principles, explained below, give the best result. In most embodiments used all principles. 
     Gist: Displacing at Least a Part of the WF Between Said WC and HPC, without Changing Volume of the WC. 
     The gist includes scavenging between the WC and HPC, and combustion at least a part of fuel outside the WC. 
     Are embodiments with combustion a part of fuel inside the WC, so pushing any part of WF to the HPC. 
     Advantages for ICE, EHE and Heat Pump 
     
         
         
           
             Smaller stroke of piston and so smaller friction loss, against prior art, where compressed gas is displaced by piston; 
             part of cylinder with high P is not in contact with piston and may be optimal T of this part to diminish thermal transfer. 
             Smaller vortex and so smaller thermal loss. Minimum volume of WC may be (maximum volume)/kv, so possible to make a good aerodynamic shape of piston and large valves in wall of cylinder; in prior art, this minimum volume prefer to be zero, and named a “parasite” volume. So, no mentioned problems caused by the “parasite” volume. 
             Possible opposite pistons in the same cylinder without head (so smaller heat loss), with valves in a wall of the cylinder. 
             Smaller compression work. If used the buffer ( 51 ) for this work, smaller size of it and so smaller friction loss. 
             So as smaller stroke of piston, diminish size, mass and inertial moment of crankshaft, that cause the best realization of Pulse Pause Modulation (PPM, see below), diminish friction loss caused by inertial forces. 
             Combustion of all or most fuel take place in HPC, so may be a short time when a hot pressured gas is in the WC, so smaller thermal loss. 
           
         
       
    
     Gist: Pulse Pause Modulation (PPM) of the Crankshaft Speed, that Include Possibility for Reducing Rotation Speed Approximately to Zero at Least Near One Dead Point (DP) and Fixation of Crankshaft in this DP 
     Advantages for ICE, EHE and Heat Pump 
     
         
         
           
             Regulation of cycles per second from zero, with maximum efficiency at every load. This regulation may be very fast, that is most important, if for power output used addition expander (see below), working according to demands of load. 
             Small load and friction in crankshaft bearings, caused by PPM and by small inertial moment of crankshaft. 
             Regulating a time for optimal combustion and small thermal loss. 
             Regulating a time for displacing WF between WC and HPC and WC and LPC, that diminish vortex and thermal loss. 
             If transfer energy by hydraulic means, smaller loss, so as may use automatic valves, against the free piston prior art with controllable valves. 
           
         
       
    
     Gist: Providing Expander or Compressor, Arranged without Transferring Energy from or to ECM (See GLOSSARY), Using the Expander as Output of at Least a Part of Power of the Engine, or Using the Compressor as Input of at Least a Part of Power of the Heat Pump 
     Advantages for ICE, EHE and Heat Pump 
     
         
         
           
             Full expansion in engine, matched compression and expansion in heat pump that increase efficiency. 
             Smaller friction loss in the WC. 
             Better arrangement of a full design. For example, in Sun power plant, a large assembling with expander and electrical generator is remote from a small size WC, placed near focus of Sun ray concentrator. This WC may work in hermetic envelope and no transfer energy to external means. 
           
         
       
    
     Gist: In the “Multi Vane Rotary Machine”, Scavenging Compressed WF Between the WC and HPC. 
     Advantages:
         Sufficiency smaller stroke of vane, so smaller friction loss.   Vortex loss/power, no increased with length of body, this length is proportional to power.   Optimal Vee/Vbc for every working mode.       

     List of Advantages, Comparing to List of Problems 
     No loss of efficiency at partly power. No loss of expansion energy. Smaller friction loss in bearings of crankshaft, by piston rings, by vanes. Smaller vortex loss in valves and cylinder. In ICE, regulated time for combustion. Smaller loss of heat to surfaces of WC. In EHE, no parasite volume of the WC, and no addition friction, vortex, and thermal loss. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1A  is a Simplified view on the prior art according to [7] WO1998057038 A1. 
         FIG. 1B : shows a PDHMR according to the present invention, preferable as home conditioner. 
         FIG. 1C : shows a Version with no circular symmetrical body, so the rotor no load from pressure force. 
         FIG. 1D : shows a View on body. 
         FIG. 2A : shows a the ICE,  2  stroke, with remote expander and PPM; displacing a part of the WF from the WC to HPC due to diminishing volume of the WC and due to combustion in it; preferable as engine for car. 
         FIG. 2B : shows a Changing volume of WC during working cycle. 
         FIG. 2C : shows a Parameters of working cycle of the engine versus isothermal part of expansion in the expander. 
         FIG. 2D : shows a Valves WCLPOM, WCLPIM in closed and open position. 
         FIG. 3A : shows a The ICE for power plant and transport, with PPM, efficiency&gt;63%, with isothermal remote expander and regenerator. It is improvement of prior art [1] U.S. Pat. No. 4,333,424A. 
         FIG. 3A : shows a The ICE for power plant and transport, with PPM, efficiency&gt;63%, with isothermal remote expander and regenerator. It is improvement of prior art [1] U.S. Pat. No. 4,333,424A. 
         FIG. 3B : shows a Cycle of engine with regulating input-output time Tio. 
         FIG. 3C ,  FIG. 3D ,  FIG. 3E : show Versions of engine with multistage compressor. 
         FIG. 4A : shows the EHE for Sun power plant, ISC between the WC and HPC; PPM, remote expander connected to electrical generator. 
         FIG. 4B : shows Piston and crankshafts assembling  16  with buffer  51 , adjusted for PPM. 
         FIG. 4C : shows Inertial Scavenging (ISC). 
         FIG. 5A : shows External Combustion Engine (ECE) with hybrid Sun heating and combustion and remote expander. 
         FIG. 5B : shows Scavenging. 
         FIG. 6 : shows the heat pump for combined heat pumping and producing energy from a wind source. 
         FIG. 7 : shows the ICE, 2 strokes. Distinction from version  FIG. 2A  is that version  FIG. 7  comprises a regulated hydraulic pump as energy receiver, to use no-zero Zwork for charging a hydraulic accumulator. Combined mechanical and hydraulic power need, for example, in construction engineering. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Glossary and Abbreviations 
     “Adiabatic process” takes place when no heat transfers. Parameters of adiabatic process:
         P, V, T—Pressure, Volume, Temperature (gradus K) of Working Fluid (WF, any gas);   bc, ec—begin, end compression; for example, Pbc, Pec.   be, ee—begin, end expansion.   Cp and Cv—are the thermal capacities of WF when P or V is constant.   ka—the adiabatic coefficient, ka=Cp/Cv; for Air, ka=1.4.   For compression: kv=Vbc/Vec&gt;1; kp=Pec/Pbc=kv ka &gt;1; kt=Tec/Tbc=kv (ka-1) &gt;1.   There, most cases for compression and expansion, parameters kv, kp, kt are the same.   For expansion: kv=Vee/Vbe&gt;1; kp=Pbe/Pee=kv ka &gt;1; kt=Tbe/Tee=kv (ka-1) &gt;1.   W—Work of gas; for expansion and compression, |W| is the same, if Vbc=Vee, Vec=Vbe, Pbc=Pee, Pec=Pbe:       

       Expansion:  W =( Pbe*Vbe−Pee*Vee )/( ka− 1)= Pbe*Vbe /( ka− 1)*(1−1/ kt )&gt;0;
 
       Compression:  W =−( Pec*Vec−Pbc*Vbc )/( ka− 1)=− Pec*Vec /( ka− 1)*(1−1/ kt )&lt;0;
         EE—is the Energy from Expansion of the gas in the WC, defined as:       

         EE=W+W (input to expander)− W (work against atmospheric pressure).
         CE—Energy for Compression of the WF in the WC, defined as:       

         CE=W (input to compressor)− W (output from compressor)− W.  
         MW—Mechanical work; MW=EE−CE. For engine, MW&gt;0; for heat pump, MW&lt;0.   Ef—Efficiency of engine, defined as: Ef=MW/TE, TE is thermal energy.   Efa—Efficiency of engine for adiabatic compression and expansion.       

     “Brayton adiabatic cycle” consist adiabatic compression and expansion and constant pressure heating and cooling. Engine efficiency: Efa=(Tec−Tbc)/Tec. Heat pump, if cooling: COP=Tee/(Tbe−Tee). 
     “Blower” ( 9 ) implies a separate design or set of parts, arranged to displace the WF inside the heat machine, if for this displacing need a small difference of pressure. 
     “Components of air” are N 2 , O 2 , CO 2 , H 2 O, etc. as they are in a normal air with appropriate concentrations. 
     “Clear output” implies Output products of engine with CO 2  and H 2 O or only H 2 O, with concentrations of the dirty output products below than appropriate standard. 
     “Coefficient of Performance” (see “COP”, “Heat Pump”), this term is used for Heat Pump. 
     “COP”=Thermal Energy (TE)/Mechanical Work (MW). TE transferred between “cool” and “heat” objects. 
     “Compressor of inertial type” converts mechanical energy to pressure and kinetic energy of the WF. 
     “Compressor of positive displacement type” converts mechanical energy to pressure energy of the WF. 
     “Controllable Opening”: “Controllable” imply any type of control, including, for example, changing position of any mean relatively to the opening; piston may close and open a scavenging window, a valve driver may close or open a valve, the valve may be any type. 
     “Cylinder” is positive—displacement working chamber in general, not restricted to circular cross-section. 
     “Dirty output products” are output products of engine, except components of air. 
     “Efficiency” of the heat engine is Mechanical Work (MW)/Thermal Energy (TE). 
     “Expander of inertial type” is a Turbine, using compressible WF. 
     “Expander of positive displacement type”—see “Positive displacement”. 
     “External heating engine”, have the WC where take place near adiabatic thermodynamic processes. Heat is transferred to external volume that may be a heat exchanger or external combustion chamber. 
     “Heat machine” convert a part of Thermal Energy (TE) to Mechanical Work (MW) or vice versa (see “Heat pump”). 
     “Heat pump” uses MW to move TE opposite to spontaneous heat flow; may work as cooler or heater. 
     “Internal heating engine” (IHE), for example a spark ignition or Diesel type, have a working chamber (WC), for example a space bounded by a piston and a cylinder, where take place thermodynamic processes, including combustion of a fuel inside compressed air. 
     “Inertial Scavenging” (ISC), see “Scavenging”. Initiating moving a part of a WF from and (or) to WC and continue this moving due to kinetic energy of the WF and, in addition, due to kinetic energy of any mean, if it designed for ISC. 
     “Local minimum” of a velocity, V1 min, defined there according: V1&gt;V1 min&lt;V2, where V1, V1 min, V2 are velocity points inside any part of cycle at appropriate time points t1&lt;t1 min&lt;t2 with minimum detectable differences V1−V1 min and V2−V1 min. Local minimum of piston speed=0 at ‘dead points’ (crankshaft angles 0° and 180°), and it is absolute minimum as well. The crankshaft rotation speed may have a local minimum after end compression. 
     “Main shaft”, means the shaft which converts reciprocating piston motion into rotary motion or vice versa. 
     There, term “crankshaft” means the shaft which converts reciprocating piston motion into rotary motion or vice versa, but “main shaft” means the shaft which converts any motion into rotary motion or vice versa. For example, in “Vankel” engine, planetary motion converted to rotation by main shaft. So, the “main shaft” is wider definition than “crankshaft”. 
     “Output products” are CO 2 , H 2 O, CO, N x O y  (for example, NO), etc., depended upon the fuel type and the combustion quality. After ideal combustion of good fuels, output products are CO 2  and H 2 O, or only H 2 O if Hydrogen (H 2 ) is used. 
     Dissociation of N 2  and O 2  begin approximately above 2000° K and increase concentration of N x O y  in output products. 
     Combustion temperature in prior art ICE is more than 2000° K and is sufficiency more in local volumes if bad mixing. 
     After cooling, not all N x O y  is decomposed to N 2  and O 2 . So, N x O y  in output may be with using every type of fuel. 
     “Positive displacement”, according to IPC (International Patent Classification), means the way the energy of the WF is transformed into mechanical energy, in which variations of volume created by the WF in the WC produce equivalent displacements of the mechanical member transmitting the energy, the dynamic effect of the WF current being of minor importance. 
     “Pump”, according to IPC, means a device for raising, forcing, compressing, or exhausting fluid by mechanical or other means. “Pump” includes fans or blowers. 
     “Scavenging”, according to IPC, means forcing the combustion residues from the cylinders other than by movement of the working pistons, and thus includes tuned exhaust systems. There, term “scavenging” is used not only for the combustion residues and exhaust, and imply displacing at least a part of the WF from the WC and displacing another part of the WF to the WC by any way, that cause essentially more displacing than according to changing volume of the WC during this displacing process, including a case with constant volume of the WC or even changing this volume against direction of this displacing. See above “Inertial Scavenging”, ISC. 
     “Sterling cycle”, in ideal, includes constant volume heat transfer in regenerator, isothermal compression and expansion, constant volume heating and cooling. 
     “Turbine” converts kinetic energy of the WF to mechanical energy. 
     “Working fluid” (WF), according to IPC, means the driven fluid in a pump and the driving fluid in an engine. The WF may be in a gaseous state, i.e., compressible, or liquid. In the former case coexistence of two states is possible. There, term “working fluid” used as well for heat pump. During working cycle in engine or heat pump, the WF may be converted from gaseous to liquid state or vice versa. 
     Abbrevations 
     
         
         
           
             DP—Dead Point, it is position of crankshaft in reciprocating piston machine, and appropriate position of the piston, where the piston change direction of moving. At the DP, the piston cannot change rotation speed of the crankshaft. For free piston machines, DP is position of piston, where it change direction of moving. 
             EHE—External Heating Engine. 
             ECE—External Combustion Engine (ECE is the type of EHE). 
             HM—Heat Machine, there may be engine or heat pump. 
             HPDP—High Pressure Dead Point—the DP, where pressure in the cylinder is approximately equivalent to the High Pressure level. 
             ICE—Internal Combustion Engine. 
             IPC—International Patent Classification. 
             ISC—Inertial Scavenging, see above “Scavenging”, “Inertial Scavenging”. 
             LPDP—Low Pressure Dead Point—the DP, where pressure in the cylinder is approximately equivalent to the Low Pressure level. LPDP is equivalent to the Bottom Dead Center, where scavenging between combustion gas and free air. 
             PDHM—Positive Displacement Heat Machine. 
             PDHMR—PDHM with multi vane Rotor. 
             PPM—Pulse Pause Modulation. Working mode of the PDHM with reciprocating piston, when it may be stopped at the Dead Point and begin moving after a controllable time. 
             RPC—Reciprocating Piston and Crankshaft, wide using type of the PDHM. 
           
         
       
    
     Abbreviations of Parts 
     The referenced numbers are from drawings; see section “Numbers of parts for all drawings”. 
     Buffer ( 51 ), a mean that combine functions of Energy Receiver (ER) and Energy Source (ES), see ER, ES. Preferable a gas buffer.
         C ( 7 )—Compressor, with input from LPC, output to HPC, a volumetric ratio arranged so, that pressure at end compressing approximately equivalent to HP in HPC; using the compressor as a receiver for at least a part of input power of the heat pump.   E ( 19 )—Expander, with input from HPC, output to LPC, a volumetric ratio arranging so, that pressure at end expanding approximately equivalent to LP; using the expander as a source for at least a part of output power of the engine, with regulating the expander according to demands of a load.       

     ECM—Energy Conversion Means, arranging to work with at least a part of the WF, used in a thermodynamic cycle of the heat machine, with converting energy of compressed WF to mechanical work, and reverse converting, with conversion algebraic sum of compression and expansion energy to a work, named Zwork; supposing, that expansion work is positive, and compression negative, Zwork&lt;0 is according to receiving external work, Zwork&gt;0 is according to producing output work; all parts, that need to make the Zwork, named Zmachine.
         ECM of positive displacement type named Working Chamber (WC);   WC, arranged only for compression, named WCC and is a part of the ECM;   WC, arranged only for expansion, named WCE and is a part of the ECM; the WC may include separated parts WCE and WCC or arranged as a single chamber for both functions.   A part of ECM, converting energy of compressed WF to kinetic energy of moving WF and then to mechanical work, named turbine;   A part of ECM, converting mechanical work to kinetic energy of moving WF and then to energy of compressed WF, named axial or radial compressor according to working principle;   A turbine, mechanically connected to radial or axial compressor, named turbo-compressor.   EIH—Expander Input Heater.   ER—Energy Receiver.   ES—Energy Source. ER, ES may be mechanical, hydraulic, electrical means, or another; separated, or both in the same design. Examples for the same design: electrical machine, hydraulic machine, gas buffer ( 51 ), inertial mass. An example for ER is a hydraulic pump with a single direction input and output valves.   FC—Fixation of Crankshaft, a mean to fixate the crankshaft near at least one of Dead Point if the rotation speed near it, is approximately zero;   HA—Hydraulic Accumulator, with separated liquid and compressed gas volumes inside a common envelope with a common high pressure.   HMP—Hydraulic Motor—Pump.   HPC ( 8 )—High Pressure Chamber, include function of pressure buffer volume (it is not buffer  51 ), heating or cooling.   HPCPS ( 32 )—pressure sensor arranged to react to the HP in the HPC; most cases may be electrical or mechanical output.   HPCBPS ( 56 )—HPC buffer volume pressure sensor. About 32 and 56 see description to  FIG. 6 .   HPCIM ( 26 )—HPC Input Mean for the WF from WC, include a channel arranged with gradual increasing a transverse section from WCHPCO (see below)  18  to HPC  8 , and for the heat engine have a thermal isolation.   HPCIMTS ( 27 )—sensor to measure a mean temperature T 27  of the WF in the HPCIM.   HPCOM ( 44 )—HPC Output Mean for the WF to WC, that include a channel between the HPC and the WCHPIM, this channel arranged with gradual decreasing a transverse section from the HPC to WCHPIM, whereby to diminish loss of kinetic energy of the WF, and in the heat engine, the HPCOM is thermal isolated.   HPCIP—Input Part of the HPC.   HPCOP ( 8 OP)—Output Part of the HPC.   HPSDV ( 47 )—Single Direction Valve, that makes possible current inside the HPC from the HPCIP to HPCOP.   ICM—Initiator of Crankshaft Moving.   KEC—Kinetic Energy Controller, to compensate a difference between Expansion Energy and Compression Energy (see EE, CE), so that at end of the thermodynamic cycle, kinetic energy of the MP will be approximately the same as at begin of this cycle, using for this compensation the ES, ER and feedback from RSS.   LPLV—Low Pressure Liquid Volume.   LPC ( 40 )—Low Pressure Chamber.   LPCIP—Input Part of the LPC.   LPCOP—Output Part of the LPC.   MP—Moving Parts: piston and other parts, connected to it.   NHM—Near Heater Means (in Sun power plant);   RM—Remote Means (in Sun power plant);   RSS ( 31 )—Rotating position and Speed Sensor, to measure a rotating angle and speed of the crankshaft and so position and speed of piston.   TSBC ( 45 )—Temperature Sensor, arranged to measure the Tbc.   TSBE ( 55 )—Temperature Sensor to measure Tbe.   TSHT ( 42 )—Temperature Sensor, arranged to measure the HT.   TSSH ( 48 )—Temperature Sensor at output of Sun Heater. It measure temperature T 48 .   WCC ( 35 )—Working Chamber for Compression, see ECM.   WCE ( 34 )—Working Chamber for Expansion, see ECM.   WC—Working Chamber, that may include separated parts WCE and WCC or arranged as a single chamber for both functions, see ECM.   WF—Working Fluid.   WCLPOM ( 21 )—Low Pressure Output Mean of the WC.   WCLPIM ( 20 )—Low Pressure Input Mean of the WC.   WCHPCO ( 18 )—Working Chamber High Pressure Controllable Opening, arranged to control possibility to displace at least a part of the WF between the WC and HPC.   WCHPIM ( 41 )—High Pressure Input Mean of the WC.   WCHPCIMDPS ( 28 )—Sensor to measure Differential Pressure between WC and HPCIM.   WCHPCOMDPS ( 43 )—Sensor to measure Differential Pressure between WC and HPCOM ( 44 ).   WCLPCDPS ( 33 )—Sensor to measure Differential Pressure between WC and LPC.   Zmachine—see ECM. Summed work of Zmachine during thermodynamic cycle may be near zero. In engine, Zmachine generate a compressed gas that used in expander to produce mechanical work. In heat pump, Zmachine generate a cool gas.       

     Parameters of Heat Machines
         ABC—Acceleration Between Cycles, according to difference between kinetic energy of Moving Parts (MP) at begin and at end of the thermodynamic cycle.   CE—Energy for Compression of the Working Fluid (WF) in the Working Chamber (WC).   d (any parameter)—delta, a small changing of any parameter, for example dHP.   EE—Energy from Expansion of the WF in the WC.   HP or PH—High Pressure, there most cases it is pressure at end compression (Pec), but sometimes due to combustion, HP&gt;Pec.   HT or TH—High Temperature, measured by sensor TSHT ( 42 ).   LP or PL—Low Pressure, most cases it is pressure at begin compression.   LT or TL—Low Temperature.   MW—Mechanical Work.   M—reciprocating mass of assembling  16 .   mR—Rotating mass on radius R, this mass equivalent to sunmed inertial moment.   OE—Over Energy, energy of buffer  51  minus compression energy, see explain to  FIG. 2 , “Acceleration of crankshaft”.   TE—Thermal Energy.   Tbc—Temperature of the WF in the WC at Begin Compression.   Pbc—Pressure of the WF in the WC at Begin Compression.   Tec, Pec—Temperature, Pressure of the WF in the WC at End Compression.   T 27 —Temperature in HPCIM  26 ; T 27  measured by HPCIMTS  27 ; for engine, T 27 &gt;=Tec.   T 48 —Temperature after Sun heater  8 SH, measured by sensor  48 .   Tbe, Pbe—Temperature and Pressure of the WF in the WC at Begin Expansion.   Tmax—Maximum temperature of the WF in the WC, caused by combustion.   Tee—Temperature of the WF in the WC at End Expansion.   Pee—Pressure of the WF in the WC at End Expansion.   Tcvol—Temperature of a Cooling Volume. Tcvol is used for heat pump.   Thvol—Temperature of a Heating Volume. Thvol is used for heat pump.   TimeP—Time of Pause, while piston is fixated in a dead point.   TimeBH—time point when Begin Heating,   TimeEH—time point when End Heating inside the WC.   TimeOH—Over Heating Time, only for the ICE.   Vbc—Volume of the WF in the WC at Begin Compression.   Vec—Volume of the WF in the WC at End Compression.   Vbe—Volume of the WF in the WC at Begin Expansion.   Vee—Volume of the WF in the WC at End Expansion.   Veex—Volume of external expander at end expansion.   Vwc—Volume of the WC.   Vmax—a Maximum Volume of the WC; Vmax&gt;=Vee, Vmax&gt;=Vbc.   Vmin—a Minimum Volume of the WC; Vmin&lt;=Vwc&lt;=Vmax.   VCR—Volumetric Compression Ratio, defined as VCR=Vbc/Vec&gt;1.   VER—Volumetric Expansion Ratio, defined as VER=Vee/Vbe&gt;1.   Wr—rotation speed.   workv—virtual work. This work named “virtual”, so as it may be used, for example, by turbine, with expansion from Pee to 1 atmosphere. Often it is not used even in prior art, where workv is large. There, workv is small and used for inertial scavenging.   Zwork—algebraic sum of compression and expansion work in the ECM. It is summed work of Zmachine (see above ECM, Zmachine).       

     NUMBERS OF PARTS FOR ALL DRAWINGS
       1 . Body with non-limited length.     2 . Rotor with specific shape.     3 . Vanes.     4 . Slots, sizes according to the vane.     5 . Separator.     6 . Driver for the separator.     7 . Compressor.     8 . High Pressure Chamber (HPC), include function of pressure buffer volume (it is not buffer     51 ), heating or cooling.     8 B—HPC, thermal isolated buffer volume.     8 C—HPC, cool part.     8 F—Tubes with combustion product inside HPC.     80 P—HPCOP—HPC Output Part.     8 H—HPC, hot part.     8 SH—Sun Heater (a part of the HPC).     8 R—HPC with function of regenerator.     9 . Blower.     10 . Heat exchanger, counter flow type.     11 . LP scavenging window.     12 . Separated HP scavenging window.     13 . Main shaft. In the prior art,  FIG. 1A , main shaft get all power. In the invention,  FIG. 1B ,  FIG. 1C , the main shaft gets a small part of power, which needs to compensate friction and vortex loss.     14 . Side wall (left or right).     15 . Cylinder.     16 . Piston and crankshaft assembling with buffer  51 , piston, beam, two crankshafts and connecting rods, roller bearings.     16 S—Piston and crankshaft assembling, no buffer, separated pistons for compressor and expander.     16 P—Piston and crankshaft assembling with buffer  51  and hydraulic pump.     16 GP—Hydraulic pump.     16 V—Input Valve of Hydraulic pump.     16 O—Output valve of Hydraulic pump.     17 . Synchronization belt and gears, no load and small mass.     17 G. Synchronization gears, no belt.     18 . WCHPCO, Working Chamber High Pressure Controllable Opening.     19 . Remote Expander, power output.     20 . WCLPIM, Working Chamber Low Pressure Input Mean.     21 . WCLPOM, Working Chamber Low Pressure Output Mean.     22 . Electrical machine, a small power, may include functions of Energy Receiver (ER), Energy Source (ES), Fixation of Crankshaft (FC), Initiation of Crankshaft Moving (ICM).     23 . Regenerator, counter flow type, prefer with laminar current in micro channels.     24 . Thermal isolated tubes.     25 . Fuel Injector; design of injectors  25 A- 25 D may be according to working place.     26 . HPCIM, HPC Input Mean, include a channel arranged with gradual increasing a transverse section from the WCHPCO  18  to HPC  8 , and for the heat engine have a thermal isolation.     27 . HPCIMTS, temperature sensor, for example a thermo-coupler, arranged to measure temperature T 27  of the WF in HPCIM  26 .     28 . WCHPCIMDPS, sensor to measure a differential pressure between WC (Cylinder)  15  and   HPCIM  26 . It may be a mechanical mean, arranged to open WCHPCO  18  when the differential pressure is near zero, but prefer a sensor, matched to electrical controller.     29 . Electrical controller. Includes electrical accumulator and Kinetic Energy Controller (KEC) and arranged for functions according to input and output signals signed on drawings.     30 . Valve driver, that may include mechanical oscillator, fixated at 2 points by electrical magnets.     31 . RSS, Rotating Speed and position Sensor.     32 . HPCPS, pressure sensor in HPC (between HPC and Atmosphere).     33 . WCLPCDPS, differential pressure sensor between WC  15  and LPC  40 .     34 . WCE expander.     35 . WCC compressor.     36 . Valve LP_out.     37 . Valve HP_in.     38 . Valve LP_in.     39 . Valve HP_out.     40 . LPC—Low Pressure Chamber, or Atmosphere.     40 R. LPC part of regenerator (output connected to atmosphere).     41 . WCHPIM, High Pressure Input Mean of the WC.     42 . TSHT—Temperature Sensor, arranged to measure the HT.     43 . WCHPCOMDPS—Sensor to measure Differential Pressure between WC and HPCOM  44 .     44 . HPCOM—HPC Output Mean for the WF to WC, that include a channel between the HPC and the WCHPIM ( 41 ), this channel arranged with gradual decreasing a transverse section from the HPC to WCHPIM, whereby to diminish loss of kinetic energy of the WF, and in the heat engine, the HPCOM is thermal isolated.     45 . TSBC—Temperature Sensor, arranged to measure the Tbc.     46 . Electrical Generator.     47 . HPSDV—Single Direction Valve, that make possible current inside the HPC from the HPCIP to HPCO.     48 . TSSH—Temperature Sensor at output of Sun Heater  8 SH. It measure temperature T 48 .     49 . Wind turbine.     50 . Distributor.     51 . Buffer.     52 . Valve with sections  52   c IR,  52   c OR,  52   c EA,  52 HER,  52 HIA,  52 HOA.     53 . Cooling tube.     54 . On/off valve.     55 . TSbe—Temperature Sensor to measure Tbe.     56 . HPCBPS—HPC buffer volume (it is not buffer  51 ) pressure sensor.     58 . TSILPC—Temperature sensor at Input of LPC.   

     Parameters are examples by computer simulations. Parts according to NUMBERS OF PARTS FOR ALL DRAWINGS. 
     With reference to  FIG. 1B , there is shown the PDHMR in accordance with the present invention, the embodiment is heat pump for home conditioner or refrigerator.  FIG. 1A  is a simplified view on the prior art for it, according to [7] WO1998057038 A1.  FIG. 1C  is a version with no circular symmetrical body, so the rotor no load from pressure force.  FIG. 1D  is a view on body.  FIG. 1 (A-D) include parts:
           1 . Body with no-limited length (for the prior art,  FIG. 1A , the length is limited, see explain below).     2 . Rotor with specific (see explain below) shape.     3 . Vanes (for the prior art, vanes have sufficiency more radial length).     4 . Slots, sizes according to the vane.     5 . Separator (no exist in the prior art).     6 . Driver for the separator.     7 . Compressor (no exist in the prior art).     8 . High Pressure Chamber (HPC).  8 C—cool part,  8 H—hot part.     9 . Blower.     10 . Heat exchanger, counter flow type, cooling water inside tubes.     11 . LP scavenging window. In the invention, a large window along the length of body L, separated to input and output part. In the prior art, a small input and output windows in a side walls.     12 . Separated HP scavenging window (no exist in the prior art).     13 . Main shaft. In the prior art,  FIG. 1A , main shaft get all power. In the invention,  FIG. 1B ,  FIG. 1C , the main shaft gets a small part of power that need to compensate friction and vortex loss, and main power source connected to compressor  7 . Power sources are not on drawings.     14 . Side wall (left or right).       

     The counter flow heat exchanger  10  transferring heat from air with parameters Pec, Tec to water, that is with atmospheric pressure (0.1 MPa) inside tubes. Hot water may be used, or cooled by atmospheric air in external heat exchanger. Every WC formed by surfaces of neighboring vanes  3 , parts of surfaces of the side walls  14 , a part of surface of the body  1 , and a part of surface of the rotor  2 . During rotation of the rotor  2 , volume (Vwc) of every WC is changing between Vmin and Vmax, kv=&lt;Vmax/Vmin. A space, where the Vwc is diminished to Vmin, named a High Pressure Space (HPS); a space, where the Vwc is increased to theVmax, named a Low Pressure Space (LPS). Prefer a small as possible gap between tip of separator  5  and rotor  2 . For example, if swing of oscillation of Separator  5  is 15 mm, may be: 0&lt;gap&lt;0.3 mm, even larger gap is not critical. Synchronization gear between rotor  2  and driver  6  is not shown. Shape of rotor  2  is according to oscillation of separator  5  and caused by design of driver  6 . 
     WORKING CYCLE include scavenging by blower  9  at LPS, so output cool air with parameters LP=Pee, Tee, is displacing by room air with Pbc=LP, Tbc. During moving WC from LPS to HPS, take place compression to HP=Pec, Tec. Then scavenging in HPS between the WC and HPC  8 , so air with Pec, Tec, is displacing by air with Pbe=HP, Tbe. During moving WC from HPS to LPS, take place expansion to Pee, Tee. Length of scavenging windows  11 ,  12  is according to length L of body  1 , so L may be large (see example below). In the prior art, all windows are inside side walls, so L limited by speed of air during scavenging. 
     So, the main principle is: displacing the WF between WC(HPS) and HPC  8 , with very small changing volume of the WC. 
     Scavenging across WC by a blower (Separator  5 ); the blower is based on the positive displacement principle. 
     Below Example According Computer Calculations for this Home Conditioner. 
     Rotation speed Wr=63 rad/s, length of body L=1 m (this large L is practically impossible for the prior art), internal radius of body  1 , Rb=72 mm, throughput V=0.045 m 3 /s, kv=1.358, kp=1.535, kt=1.13; Pbc=0.1 MPa, Pec=0.1535 MPa, Tbc=300° K, Tec=339° K, Tbe=308 0 K=35° C., Tee=273° K=0° C. COP=Tee/(Tbe-Tee)=7.8 (if no loss). Density of Air at 0° C. is 1.27 kg/m 3 . Power: Pcool=(Tbc-Tee)° K.*1000 J/kg/° K.*1.27 kg/m 3 *0.045 m 3 /s=1549 W; mechanical power: Pmech=Pcool/COP=199 W, it is power that need for Air compressor  7  if no loss. In assembling, that include body  1 , rotor  2  and vanes  3 , compression and expansion energy are the same (EC−EE=Zero); if no loss, it no send and no get mechanical energy and so named Zmachine (see GLOSSARY . . . ). It get from a room V=0.045 m 3 /s with Tbc (see above WORKING CYCLE) and send to the room the same V, but with Tee. To keep BALANCE OF AIR MASSE, throughput from air compressor  7  is: V7=V*Tbc/Tee−V=0.00945 m 3 /s. May to place it out of the room, and connect input to external air. If dT between external hot air and the room air is 5° K, ventilation by V7 add to the room heat power 54 W. 
     Example for Cooling Power for a Room 20 m 2 : 
     Thermal transfer coefficient x=8 W/M 2 /° K; surface for thermal transfer S=90 m 2 ; mean dT between room air and walls 2.5° K; cooling power=8*90*2.5=1800 W. Calculated above Pcool=1549 W is for Wr=63 rad/s. May increase Wr to 16% and get Pcool=1800 W. 
     Below are Calculations for Loss (“A”−“G”), in “G”, Calculated that Increasing Wr to 16% May Diminish COP to 2%. 
     A. For compressor  7 , with output power 199 W, suppose loss7=20 W. 
     B. If air speed during scavenging is 9 m/s (twice more than linear speed of rotor  2 ), and volume V=0.045 m 3 /s loss all kinetic energy 4 times during cycle, vortex loss is: loss V=9 W. 
     C. Sizes of Capron vane  3  is (1*8*1000) mm 3 . For 6 vanes and Wr=63 rad/s, inertial force on surface of body  1 , is: Pw=16N. If friction coefficient kfr=0.2, sliding of vanes along surface of body  1  cause loss Pw=14.5 Watt. 
     D. Pressure in slot  4  is maximum between pressures from a left and right sides of vane  3 , and it is Pec. According to computer simulation, mean difference of pressures that press vane to body, is: dp12 m=0.33*(Pec-Pbc)=1.8N/cm 2 . Suppose that dp12 m placed on ½ from vane width, so on 0.5 mm, and pressure forces on the rest part are compensated. So mean radial pressure force from all vanes is 54 N, and for mentioned kfr and Wr, it cause loss Pfr=49 W. 
     E_. Load from pressure force (for version at  FIG. 1C , this load no exist), on two rolling bearings, supporting rotor  2 , is 3600 N. With roller friction coefficient 0.001 and diameter of main shaft  13  is 20 mm, power loss: Pbearing=2.3 Watt. 
     F. Pressure force PN, normal to side surface of vane  3 , cause friction force X, directed along radius. When vane  3  is moving from slot  4 , force SF, pressing vane  3  to body  1 , is: SF=PI−X, where PI is sum of pressure and inertial forces along radius. Must PI&gt;X, else vane  3  cannot move from slot  4 . When vane  3  is moving to slot  4 , SF=PI+X. So, mean SF=PI, and force X cannot cause addition loss caused by sliding vane  3  along body  1 . But, friction between vane  3  and surface of slot  4  cause loss: lossX=PN*FRN*S*Wr/6.3, where S is sliding distance, for this example S=8 mm per revolution; FRN is friction coefficient, suppose it is 0.1. So, loss caused by friction between slots and vanes: lossX=3.6 W. 
     G. With loss, mechanical power (see A-F) is: 199+20+9+14.5+49+2.3+3.6=297 Watt; COP_real=1549/297=5.22. 
     It is true for car conditioner, connected directly to engine. If compressor  7  work from electrical motor, and addition motor is connected to Zmachine to compensate loss, both motors with efficiency 0.9, COPe=5.22*0.9=4.69. For car, electrical energy produced by generator with efficiency 0.9 (the best case), so COPee=4.69*0.9=4.22. Separated HP scavenging window  12  ( FIG. 1B ) may be not symmetrical, so possible to compensate any part of calculated loss 297 W by addition power from compressor  7 . For this case power of mentioned addition motor may be very small. 
     If increase Wr to 16%, Pcool*1.16=1800 W (see Example for cooling power for a room 20 m 2 ), but loss increase. 
     Are loss, proportional to Wr 2  or to Wr 3 . So, 1.16 2 =1.35, and 1.16 3 =1.56. For this case, mechanical power for Wr*1.16, is: 
       199*1.16+20*1.16+9*1.35+14.5*1.56+49*1.16+2.3*1.16+3.6*1.16=353; 
     COPw=1800/353=5.1. So, when Wr increased to 16%, COP diminished to 2%, that mostly caused by loss from inertial force, proportional to Wr 3 . With reference to  FIG. 1C , there is shown version with no-circular body  1 , this version is important for large power machine. With long, but symmetrical plastic rotor, no deformation and no load on bearings (see “E”, 3600 N). In this version, no load on vane  3  during moving across a scavenging zone (see below). 
     With reference to  FIG. 1D , there is shown view on body  1 , with large window  12  for scavenging between the WC and HPC. When vane  3  is moving across a scavenging zone (LP window  11  or HP window  12 ), vane  3  is supported by at least two small parts of body  1 . These parts seems as “bridges”, with small gap according to width of separator  5  that not get load from pressure and may be, for example, 0.2 mm, sufficiency smaller, then width of vane  3 . 
     Comparing with Prior Art 
     For the prior art ( FIG. 1A ), radial length of vane  3  must be 24 mm, 3 times more, then for this invention ( FIG. 1B ), and width is 3 times more, to stand against pressure force. This advantage of the invention caused by scavenging in HPS. According to calculations C, D, loss from inertial force in prior art may be 14.5*9=131 W, and so as width is 3 times more, loss from radial pressure force may be 49*3=147 W, at all 131+147=278 W. For invention, 14.5+49=64 W. But, in the prior art, vanes  3  are not sliding along surface of body  1 ; they supported by rotation ring (no on  FIG. 1A ). Sliding distance of vanes along this ring is small and caused by distance between centers of rotor  2  and body  1 , so loss caused by this sliding is small. But, the rotating ring get pressure force 3600 N (see “E”), that cause addition loss. In the invention, a large sliding speed and a small load may cause useful effect of “gas bearing” between vanes  3  and body  1 , this case Pw+Pfr&lt;&lt;64 W. It seems, in the prior art Pw+Pfr is not sufficiency smaller, then in invention. Problems caused by this ring explained below. 
     According to “F”, lossX=3.6 W, but for the prior art, 3.6*3*3=32 W, so as 3 times more PN and 3 times more S. Note, that lossX calculated for friction coefficient FRN=0.1. Larger FRN is problematic for the prior art. 
     The rotating ring restrict version with no-load rotor  2 , that is important for large power, see above explain to  FIG. 1C . 
     The rotating ring restrict possibility for current of gas across windows in body  1 , and are possible only windows in side walls  14 . So length of body is very small (or must small Wr), else vortex loss is too large. 
     Without the rotating ring, the prior art practically cannot work so as large friction loss. With the rotating ring, must be only a small length of body or small Wr. 
     To keep BALANCE OF AIR MASSE (see above), relation between volumes of hot and cool gas must be according to Tbc/Tee, but Tbc and Tee are not constant. In the prior art, this relation caused by “hard” design, that cause loss of COP and sound noise if Tbc/Tee is not optimal. In the invention, this problem is solved by regulation of compressor  7 . Another advantage of invention is that compressor  7  is small (V7=0.00945 m 3 /s). Zmachine with V=0.045 m 3 /s is placed in the cooling room, but compressor  7 , that get main power, may be directly connected to engine of car, to wind turbine, etc., 
     and placed out of room—see above example with “recommended ventilation rate . . . .” 
     With reference to  FIG. 2A , there is shown the Internal Combustion Engine (ICE) in accordance with present invention. The ICE is 2 strokes, 2 opposite pistons in the same cylinder (WC), with at least a single remote expander. 
     In the cylinder take place a thermodynamic cycle with summed compression and expansion work may be near zero (Zwork=0, see GLOSSARY . . . ), so it is Zmachine that generates compressed gas to make mechanical work by the expander. Displacing a part of the WF from the WC to HPC due to diminishing volume of the WC and due to combustion in it, with Pulse Pause Modulation (PPM) in Zmachine. Due to PPM, time for combustion is optimal and not caused by mean rotation speed, so, efficiency of the engine and quality of combustion is maximal for every working mode. Engine of a car most time is working at a partly load, and for prior art, mean efficiency may be twice smaller than optimal. Remote expanders may be connected directly to wheels. Due to PPM, throughput of Zmachine is according to demand of the expanders. For maximum power, it is possible combustion in HPC and in expanders. 
     The embodiment at  FIG. 2A  comprising parts  8 ,  8 F,  9 ,  15 - 24 ,  25 (A-D)- 33  with names according to NUMBERS OF PARTS FOR ALL DRAWINGS section. 
     Assembling  16  include the piston, beam, buffer  51 , connecting rods, crankshafts, bearings, and synchronization gears  17  with belt. All these parts are referenced as  16 , see in addition  FIG. 4B . Buffer  51  filled with compressed gas and may be connected to HPC  8  with long and small diameter tube (no shown). Crankshaft  16  may no transfer power if Zwork is near zero, and it is the preferred working mode, so crankshaft  16  has a small mass, that with using PPM, cause a small gas load on roller bearings (see below EXPLAIN FOR PPM . . . ). Expander  19  is power output of the engine, connected to HPC  8  with thermal isolated tubes  24  across optional counter flow regenerator  23 . Output gas from cylinder  15  with temperature Tee may go to appropriate part of regenerator  23  if Tee is more then temperature in this part, whereby transfer heat to input of expander  19 . Below supposed, that mentioned gas with Tee goes to atmosphere or to heater of any EHE. Electrical machine  22  and position sensor  31  connected to one of crankshafts  16  for fine PPM regulation by electrical controller  29 . 
     Working cycle include scavenging in cylinder  15  by blower  9  across at least a single valve WCLPIM  20  and WCLPOM  21 , but prefer using several valves to diminish vortex and thermal loss; in addition, for this purposes, head of piston  16  have a streamlined shape. Below see more after “scavenging.” After end compression in cylinder  15 , begin opening WCHPCO  18 , and compressed air, during output time Tout ( FIG. 2B ), is pushing to HPC  8 . Kinetic energy of current across WCLPOM  21  is partly restoring inside HPCIM  26  (see ABBREVATIONS). 
     Opening WCHPCO  18  begin by driver  30  when differential pressure dPx from sensor  28  is near zero. Appropriate value dPx is defining with controller  29  by feedback to avoid a fast jump of dPx. Inside interval Tout ( FIG. 2B ), take place fuel injection to cylinder  15  by Injector  25 A, placed far from WCHPCO  18 . Combustion in this “heating part” cause pushing “removing part” of the WF, that is near WCHPCO  18 , to HPC  8  in addition to pushing by piston  16 ; so, moving of piston  16  under HP is small. The “removing part”, and so air in HPC  8 , includes a small (prefer zero) quantity of fuel that will be combusted in HPC  8 . So temperature T 27  in HPCIM  26  may be more then Tec; T 27  measured by sensor HPCIMTS  27 , about T 27  see below. HPC  8  is thermal isolated (see thermal isolated tubes  24 ) and to diminish thermal transfer caused by vortex, HPCIM  26  have streamline shape. May increase power by injectin fuel to HPC  8  with Injector  25 B. If work regenerator  23 , instead Injector  25 B may use Injector  25 C, placed after regenerator  23 . Any case may use Injector  25 D inside expander  19 , that may be arranged for controlled combustion, for example with approximately constant temperature during at least a part of expansion. After output from expander  19 , a part of heat returned in regenerator  23 , and so temperature at input of expander is more than Tec, but limited by properties of material; this case, expander  19  is not cooled and so no heat loss in it. Any case T 27  sufficiency smaller than maximum temperature Tmax in cylinder  15 , that may be 2000° K, as in prior art ICE. If WCHPCO  18  not closed when volume of cylinder  15  begin increase, during Output/Input Time (Toin at  FIG. 2B ), direction of current across WCHPCO  18  is according to power of combustion. 
     After closing WCHPCO  18  and end combustion, begin expansion, at this point volume of cylinder  15  is Vbe. If Vec=Vbe, and no combustion during expansion, and no loss, summed work of cycle is zero (Zwork=0), and all output work is from expander  19 . 
     Possible mode “d”, with end combustion after closing WCHPCO  18 , or mode “e”, with Vbe&gt;Vec, or mode “f” with combination “d” and “e”, this causes Zwork&gt;0 and may be Pec&gt;LP. According to parameters in “Explain to Table_Z1” (see below), may calculate, that if dP=Pee−LP=0.01 MPa, it cause loss 0.4 J, while useful work is at least 635 J. 
     A small Zwork may compensate friction loss, may be used by electrical machine  22  and stored in electrical accumulator (no shown). According to working mode of electrical machine  22 , mean speed of crankshaft  16  may be changed. At end expansion in cylinder  15 , must open valves  21 , then 20. As mentioned, scavenging may be initiated by blower  9 . During scavenging, piston  16  may stay any controlled time (see below EXPLAIN FOR PPM), that cause a good scavenging with a small power of blower  9 . If Pee&gt;LP, may use ISC (see GLOSSARY . . . ). To begin scavenging, at end expansion stroke, with using signal from Rotating Speed and position Sensor (RSS)  31 , controller  29  with one of drivers  30  (not shown) open valve  21 . Due to long tube with diffuser, energy of over pressure (Pee&gt;LP), is converted to kinetic energy of moving gas. When according to signal from sensor  33 , pressure in cylinder  15  is near Atmospheric pressure, another driver  30  (not shown) open valve  20  and take place ISC. For mentioned parameters in “Explain to Table_Z1”, dP=0.01 MPa cause beginning scavenging speed: (2*dP/density) 0.5 =200 m/s, that is good to initiate ISC even for maximum power. 
     Version “g”: 
     Selecting the Volumetric Compression Ratio (VCR) such that Pec&lt;HP, then performing combustion in approximately constant volume Vec, and when the pressure in the WC increases to HP or exceeds HP, according to the dPx, opening WCHPCO  18 . A small part of fuel, prefer Hydrogen, injected before end compression, and combustion may be initiated by spark (a sparker and injector not shown). Version “g” cause preheating for good and fast combustion of fuel from Injector  25 A. For minimum power, used only Injector  25 A. 
     Displacing the “Removing Part” May be, for Example, According to the Following Several Versions: 
     Version a. 
     Selecting the Vec to be approximately equivalent to Vmin, and displacing the “removing part” mostly by heat expansion of the “heating part”, whereby will be near zero moving of piston  16  under pressure HP, and so minimum friction loss. Version ‘a’ cause partly mixing between the “heating” and “removing” parts, so T 27 &gt;Tec. Vmin is a construction parameter. Vec is according to begin opening WCHPCO  18  that cause regulation of VCR. Volumetric Expansion Ratio (VER) in cylinder  15 , caused by Vbe, that is according to end closing WCHPCO  18  if then there is no combustion. If after closing WCHPCO  18  there no combustion, preferably Vbe will be slightly above Vec (Vbe&gt;=Vec for example, Vbe=1.1*Vec). 
     Version b. 
     Selecting Vec&gt;Vmin, and displacing the WF mostly by moving piston  16 , performing combustion mostly when WCHPCO  18  is closed, so T 27  is near Tec=Tbc*VCR (ka-1) , ka=1.4. T 27 =Tec cause the best using of regenerator  23 , minimum heat loss in HPC  8  and the widest regulation of cycle power: minimum power with temperature Tec inside HPC  8 , and maximum power with using Injectors  25 (B, C, D), as explained above. Version b cause more friction loss, than Version a. 
     Version c. 
     Compromises between Versions “a” and “b”, with Vec&gt;Vmin and begin combustion before closing WCHPCO  18 . 
     Version h. 
     Combination of the following three processes:
         After ending compression, opening WCHPCO  18  and by diminishing Vwc to Vmin, displacing a part of the WF (air) to HPC  8 .   Additional displacing WF to HPC  8  with combustion inside Cylinder  15 , caused by Injector  25 A.   During increasing Vwc from Vmin to Vbe, displacing combustion product from tube  8 F to Cylinder  15 . For this purpose, using the inertial property of the gas flowed from WCHPCO  18 . Due to the high speed of this flow, the WF cannot return to Cylinder  15 , and without mixing with the combustion product that has been partly directed to cylinder  15  from at least single Tube  8 F. This product is created by combustion in Tube  8 F due to Injector  25 B. Due to appropriate volume of Tube  8 F, combustion in Tube  8 F has been finished before input to Cylinder  15 . After closing WCHPCO  18 , expansion of combustion product inside Cylinder  15  begins. So, only a part of exhaust from Cylinder  15  caused by combustion during a short time.       

     Explain to Table_Z1 
     So as Table_Z1 used only to compare parameters, supposed, that no loss of heat to walls of WC and expander. If calculate this loss according to empiric formula for ICE (from many versions, selected not too optimistic and not too pessimistic), efficiency (Ef) diminish to (1.5-2.5)%. Comparing to prior art ICE, this small drop of Ef caused by mentioned smaller time for heat transfer, smaller temperature of gas, larger temperature of walls and using 2 pistons in the same cylinder—see SUMMARY OF THE INVENTION . . . This empiric formula is for large vortex, that need for better combustion, but increase thermal loss, while in this invention, vortex is smaller and so smaller thermal loss. The formula is: X=(1+1.24*pvm)*(T*P 2 *10 −10 ) 0.33 , where X—thermal transfer coefficient, pvm—piston mean velocity. 
     In Table_Z1, “Ef” includes viscosity loss in regenerator, vortex and friction loss. For example, in string 6, Ef=63.0%, but without this loss, Ef=63.5%; this small distinction due to roller bearings (that is problematic for prior art, see below Regulation near HPDP) and a small moving of piston under maximum P (large moving in prior art, up to Virtual zero Volume,  FIG. 2B ). 
     Working mode is according “Version c” (see above). Zwork=0, adiabatic expansion in WC (cylinder  15 ), partly isothermal expansion in expander  19 . kv=12, kt=2.7, Pbc=0.1 MPa, Pec=3.24 MPa, Tbc=300° K, Tec=806° K, Vbc=Vee=1090 cm 3 , Vec=Vbe=91 cm 3 , Vmin=45 cm 3 , Tmax=1700° K, Tee=634° K. During closing WCHPCO  18 , near Vmin, begin combustion in WC with using Injector  25 A. Supposed combustion with constant P=Pec, with expansion to Vbe due to appropriate work of Injector  25 A. WCHPCO  18  may be open during this combustion and mistakes compensated by any small current of WF across WCHPCO  18 . End combustion and closing WCHPCO  18  at Vbe=Vec, Tmax, so P=Pee=Pbc, Zwork=0. Mass of input air (in Vbc) is 1.32 g, from it 0.63 g with Pec, Tec is sent to HPC  8 . Inside HPC  8 , THPC=1500° K&gt;Tec, so as before input to expander  19 , take place heating in regenerator  23  (between hot and cool gas, dTr=14° K) and then combustion using Injector  25 C (this combustion no need if minimum power, but Table_Z1 calculated for maximum power). 
     Compression energy CE=1/(ka−1)*(Pbc*Vbc−Pec*Vec)−Pbc*(Vec−Vbc)=367 J. Addition 140 J caused by output a part of compressed air dV=Vec−Vmin=46 cm 3  to HPC  8 , the same dV and 140 J returned by heat expansion during mentioned combustion from Injector  25 A. Pair of buffers  51  must supply 367+140=507 J. Moving piston cause addition friction loss according dV=46 cm 3 . For “Version a” (above), dV=0. In prior art, piston push all volume Vec=91 cm 3 . 
     In Table_Z1 named: Qreg—heat, transferred in regenerator  23 ; Veex—part of volume of expander  19  with isothermal expansion, begin combustion after end input from HPC; J/cycle—work in cycle; Ef—efficiency. 
     
       
         
           
               
             
               
                 TABLE_Z1 
               
             
            
               
                   
               
               
                 Engine with partly isothermal expander 
               
            
           
           
               
               
               
               
               
            
               
                 Qreg, J 
                 Veex, % 
                 J/cycle 
                 Ef, % 
                 string 
               
               
                   
               
            
           
           
               
               
               
               
               
            
               
                 0 
                 0 
                 635 
                 62 
                 1 
               
               
                 0 
                 11 
                 799 
                 60.9 
                 2 
               
               
                 4 
                 18 
                 858 
                 60.4 
                 3 
               
               
                 39 
                 22 
                 878 
                 60.9 
                 4 
               
               
                 75 
                 26 
                 901 
                 61.5 
                 5 
               
               
                 219 
                 47 
                 964 
                 63 
                 6 
               
               
                 454 
                 96 
                 997 
                 63.7* 
                 7 
               
               
                   
               
               
                 *Examples for dTr and gas friction loss QrL in regenerator: dTr = 14° C., QrL = 4 J, Ef = 63.7%; dTr = 24° K, QrL = 2 J, Ef = 63.5%; dTr = 5° K, QrL = 11 J, Ef = 63.5%. So, dTr = 14° K seems the best (Ef = 63.7%), but prefer dTr = 24° K, so as near the same efficiency may get with twice smaller regenerator and so lower cost and weight. 
               
            
           
         
       
     
     From Table_Z1 may see that for engine without regenerator, a good efficiency, but a small power (J/cycle), may get with adiabatic expansion in expander (string 1). The same engine with partly isothermal expansion have a smaller efficiency, but power increase (string 3 is local minimum of efficiency, when regenerator only begin to work). 
     The best mode seems at string 7, but even a mean size regenerator with optimal dTr improve parameters of engine (string 6) and this case seems as optimal, see  FIG. 2C . If use output gas of this engine with temperature Tee+dTr&gt;806° K as heat source for EHE ( FIG. 4 ), that give Ef=42% for HT=750 0 K, the integrated design may give efficiency approximately: Ef=60+(100−60)*0.42=77% (after thermal loss). Note, that for Carnot cycle, Ef_Carnot=(1700−300)/1700=82%. 
     There are Mentioned Injectors  25  (A-D) on FIG.  2 A 
     A. Prefer using a “good” fuel, so as a short time for combustion in cylinder  15 . At a full power mode, using&lt;30% from fuel inside cylinder  15 . Prefer using CH4 or H2. 
     B. Option if no used regenerator  23 . So as a large time for combustion in the HPC, may use a “bad” fuel. 
     C. Option for over-heating after regenerator  23 , or addition heating before expander  19  to avoid thermal loss in a long tube  8 . A mean time for combustion, but a large temperature before combustion, so may use a “bad” fuel. 
     D. Heating in expander  19  if used regenerator  23 . If no regenerator, Injector  25 D is option for a pic power. Time for combustion in expander  19  is according to working mode. 
     If expander  19  directly connected to a wheel, for the wheel D=50 cm and velocity 120 km/h, need 1270 rev/min that is not a large speed for combustion. 
     Combustion in expander  19  begin at a temperature T 4 &gt;Tec (if used regenerator or Injector  25 B or  25 C), that help for combustion. Output gas from expander  19  goes across regenerator  23 , so is a large time to end combustion. 
     So, in the expander  19  no must be used a “good” fuel. 
     Explain for PPM (Pulse Pause Modulation) 
     Free piston engine (prior art 8, 9) may work with PPM, when piston is fixated at Low Pressure Dead Point (LPDP). Advantage of PPM is wide regulation time for scavenging at LPDP with optimal compression, combustion and expansion time. No crankshaft; output energy used by hydraulic plunger pump and stored in accumulator. For PPM in the prior art used controllable hydraulic valve, that cause large loss. Between other problems of free piston engines, is very small time for combustion. 
     In the invention, speed of crankshaft  16  near LPDP and HPDP have independent regulations by controller  29 , including possibility to fixate crankshaft  16 . So have advantages of prior art, but without problems of it. Time for combustion is regulated, PPM not cause addition loss, the crankshaft no transfer power, small masse, small load on bearings, so used roller bearings, may use plastic or Aluminum crankshaft. 
     Due to PPM, possible fine synchronization between working cycle of cylinder  15  and expander  19 , for example with input stroke of expander  19  when WF is pushed from cylinder  15  to HPC  8 . So, may be used a small volume HPC  8  without large changing of pressure HP_in it (this changing may cause loss efficiency). 
     Regulation Near LPDP 
     For embodiment  FIG. 2A , sum of compression and expansion works and work of buffer  51  (see  FIG. 4B ) near LPDP may be near zero; is it zero or not, this sum named Zwork. To regulate speed of crankshaft  16  near LPDP, used a course and a fine regulation. The course regulation caused by appropriate adjusting of combustion process with Injector  25 A and with control of WCHPCO  18 , whereby kinetic energy of assembling  16  when piston is near LPDP, is according to desired velocity of crankshaft or near zero, if need fixation in LPDP. Near LPDP, take place the fine regulation by controller  29  with using RSS  31  and Electrical Machine  22  that may send energy to electrical accumulator or get energy from it. If need fixation, kinetic energy at LPDP must be near zero and so crankshaft  16  is fixated by friction force of bearings, loaded by a force from buffer  51 . So bearings include function of FC (Fixation of Crankshaft). If crankshaft  16  is not exactly at LPDP, moment of force from buffer  51  may be more than moment from the friction force, but Electrical Machine  22  may compensate this mistake, including function of FC. Controller  29  uses information from RSS  31 . 
     Near LPDP, force caused by buffer  51  is sufficiency smaller than pressure force in HPDP. Prefer, that regulation of cycles per second or fixation of crankshaft  16  take place only at LPDP, and near HPDP a large pressure force partly compensated by inertial force for every working mode. For this purpose, energy from buffer  51  must be more, then Compression Energy CE, and this over energy transferred to kinetic energy near HPDP. So moving parts of assembling  16  include functions of ER and ES (see ABBREVIATIONS OF PARTS). This compensation is not possible in prior art. 
     Acceleration of Crankshaft 
     When crankshaft  16  is fixed at any DP (Dead Point), roller bearings are under static load. When crankshaft  16  is moving, roller bearings are under dynamic load. For good lifetime, permissible dynamic load must be 5-20 times smaller, than static. During moving, inertial forces are against loads from gas forces or from buffer  51 , so, dynamic load diminish. It is very useful effect. With smaller dynamic loads, not only roller friction diminish, but may use light roller bearings and so diminish slide friction between rollers and separator, caused by inertial forces from reciprocating moving. To increase mentioned useful effect, may increase masse of parts with reciprocating moving, but prefer diminish inertial moment of rotating parts. For electrical machine with magnetic rotor: Me=L*D*a; I=b*L*D 4  so I=C*Me*D 3 , where Me is moment of magnetic force; L, D, I are length, diameter, inertial moment of rotor; C=b/a=constant. “I” may be very small (with the same Me) if diminish “D”. So, summed inertial moment is mostly caused by inertial moment of crankshaft  16 . Main power output is from expander  19 , crankshaft  16  no send power (except a small power to or from electrical machine  22 ). So, rotating moment, transferred by crankshaft  16 , is very small. Crankshaft  16  from Aluminum or plastic may be fast accelerated near any DP by at least a single electrical machine  22 . Prefer, that every side of every crankshaft is connected to electrical machine  22 . Example below explains mentioned useful effect (partly compensation of gas force). 
     Suppose, that radius of crankshaft  16  is R=5 cm, Vbc=1090 cm 3  (see Explain to Table_Z1). Used 2 pistons  16  in the same cylinder  15  ( FIG. 2A ), so surface of piston is: S=Vbc/2/2/R=54.5 cm 2 ; for Pec=3.2 MPa, LP=0.1 MPa, gas force Fgas=S*(Pec−LP)=16895 N. So as pair buffers supply 507 J, a single buffer  51  send Eb=253.5 J, force from it: Fb=Eb/2/R=2535N, it is static force on bearings when fixation in LPDP. Maximum static load on bearings may be if fixation in HPDP: Fmax=Fgas−Fb=14360 N. Rotating mass on radius R, this mass equivalent to summed inertial moment of two crankshafts ( FIG. 4B ) is mR=0.3 kg, and reciprocating mass of assembling  16  is: M=5 kg (design on  FIG. 2A  is symmetrical and so balanced). When rotating angle is 90°, only mR/M=0.06 of gas force (that caused by Fb and by current P&lt;Pec) is placed on crankshaft bearings when rotating angle is 90°. For prior art, mR&gt;&gt;M and all gas force is placed on bearings. 
     Prefer to avoid fixation near HPDP, so exist kinetic energy near HPDP (see above). To compensate Fmax=14360 N, acceleration A of reciprocating parts mast be: A=Fmax/M=2872 m/s 2 . Rotation speed Wr is not constant. To get A, must Wr=(A/R) 0.5 =240 rad/s=2290 rev/min. To get this Wr at HPDP, energy of buffer  51  ( FIG. 4B ) must be more than compression energy, this “Over Energy” OE is transferred to kinetic energy of rotating parts of assembling  16  near HPDP: OE=(Wr*R) 2 *mR/2=21.6 J. So, mentioned above energy Eb=253.5 J must increase to 21.6/253.5=8.5%. If buffer is connected to HPC (as mentioned, with “long and small diameter tube”), for this purpose may adjust HP. Prefer, that volume of buffer  51  is sufficiency more, than changing of it. For example, for buffer kv=1.1, kp=1.14, kt=1.04, so for T=300° K swing=12° K practically not cause loss of energy from thermal transfer between gas and body of the buffer. 
     As calculated, near HPDP, Wr=240 rad/sec. So as was fixation, Wr=0 at LPDP. What “Wr” is, for example, at angle 90° ? At this angle, near Eb/2=127 J is converted to any kinetic energy “C” and to energy of pressured gas. If was moving from LPDP, energy used for compression is small (most energy converted near HPDP). Suppose, that C=100 J, so, near angle 90°: Wr=(2*C/(mR+M)/R 2 ) 0.5 =124 rad/s=1185 rev/min. It is approximately maximum mean rotation speed if fixation near LPDP was “zero” time, or, without fixation, Wr at LPDP was very small. With mentioned parameters mR=0.3 kg and M=5 kg, cannot sufficiency increase “mean” speed, so as it cause too large inertial force at HPDP. Due to fixation at LPDP, regulation to low mean speed is unlimited, but Wr at HPDP is near mentioned optimal 240 rad/s. If M=1.25 kg, instead 240 rad/s get 480 rad/s with full compensation of gas force. To calculate minimum “M”, suppose, that used two Aluminum rods ( FIG. 4B ), length=3*R=15 cm. Due to compensation, the rod not get maximum load, but must calculate it for this case, so load=14360/2=7180 N/cm 2 . For stress 10000 N/cm 2 , masse of 2 rods is near 0.08 kg, bearings 0.08 kg; with piston beam suppose minimum M=0.3 kg. So maximum Wr is limited by combustion, and relatively small Wr near LPDP is good for scavenging. 
     Regulation near HPDP By OE (see “Acceleration of crankshaft”), is possible regulating a time Tout+Toin ( FIG. 2B ), when take place out of the WF to HPC  8  and combustion in cylinder  15 , this regulation is according to a compromise between a good combustion (prefer the large time) and a small thermal loss (prefer the small time). As calculated, with compensation of gas force near HPDP, for M=1.25 kg, get Wr=480 rad/s and OE=21.6 J. If for better combustion need Wr=240 rad/s, with the same M=1.25 kg must OE=5.4 J, regulation of OE is explained above. If OE=0 and crankshaft  16  was fixated near LPDP, it may be fixated near HPDP and every bearing get static load Fmax/2=7180 N. May use standard roller bearing (HK2512) with permissible static load Co=15300 N, masse 21 g, internal d=25 mm, external D=32 mm, width b=12 mm. Example for rotating masse mR=0.3 kg is for this bearings (21*2=42 g), Aluminum shafts (tubes) with Chrome covering, d=25 mm length=30 mm (2*19=38 g), the rest 220 g are Aluminum crankshafts ( FIG. 4B ), plastic gears and belt  17  (no load, only synchronization), magnet rotors of electrical machines  22 . For prior art with constant Wr, Fmax is dynamic load, so for prior art may use the same bearings, but 5-10 in parallel. As mentioned, in reciprocating roller bearings take place slide friction between rollers and separator, this friction loss is proportional to weight of rollers and separator. 
     Synchronization to Expander  19   
     Expander  19  may be directly connected to wheel of a car. To regulate rotation moment, may regulate input valve of expander, combustion in expander, regulate output valve of the expander to avoid a large mistake of VER in the expander, or using more than a single expander. Controller  29  with using PPM, regulation of valve  18  and feedback from pressure sensor  32  inside HPC  8 , must control frequency of cycles in cylinder  15  according to throughput of expander  19 , so that pressure HP_in HPC  8  will be approximately constant. 
     With reference to  FIG. 2B , there is shown changing volume of WC during working cycle. 
     With reference to  FIG. 2C , there is shown parameters of working cycle of the engine ( FIG. 2A ) versus isothermal part of expansion in expander  19 . It is close to graphical interpretation of mentioned Table_Z1. Due to isothermal expansion caused by combustion in expander  19 , cycle work increase from 626 J (adiabatic expansion, efficiency Efa=62.1%) to 986 J (isothermal expansion, Ef=63.7%). Between this 2 points, Ef have a local minimum 60.1% if isothermal expansion take place up to volume in expander  19  is 18% from maximum volume of expander Veex, then expansion is adiabatic. Cycle work at this point is 842 J and power Qreg, transferred in regenerator  23 , is only 4 J. This mode is bad. With isothermal expansion up to 47%, Ef=62.9%, cycle work 950 J, Qreg=207 J. This mode is near optimal. Full isothermal expansion cause large regenerator (Qreg=454 J), but useful effect is small: efficiency 63.7%, cycle work 986 J. Computer calculation include air friction loss in regenerator  23 , supposing ideal thermal isolation. It is possible with vacuum “thermos”, but increase cost. Conclusion from  FIG. 2C : For a small engine prefer adiabatic expander  19  and no regenerator (626 J, efa=62.1%). This engine is a small weight and cost. 
     With reference to  FIG. 2D , there is shown valves WCLPIM  20 , WCLPOM  21  for LP scavenging. 
     Drivers for all valves ( 20 ,  21 , and  18 ) may include a spring with a large energy and power, to fast open and close a valve. When opened and closed, a valve fixated by electrical magnet, that can produce a large force to fixate it. This type of driver may find in prior art. If instead output valve  21  used a simple window, diminish useful part of piston stroke. 
     With reference to  FIG. 3A , there is shown the ICE for power plant and transport, with PPM, efficiency&gt;63%, with isothermal remote expander  19  and counter flow regenerator ( 8 R and  40 R). Main distinctions from prior art [1] U.S. Pat. No. 4,333,424A are: Hard connection between pistons of compressor  35  and expander  34  with the same compression and expansion energy, so they arranged as mentioned Zmachine; remote expander  19  arranged without transferring a work from this Zmachine; using mentioned PPM and synchronization Zmachine with remote expander  19 . 
     Main distinctions from  FIG. 2A  are: Instead cylinder  15  used separated compressor  35  and isothermal expander  34  with small “kp”. Adiabatic compression with kp=1.5 (for example) is close to isothermal and thermodynamic efficiency of this engine with regenerator is as for cycle Carnot, but large size cause more vortex loss; so for  FIG. 3C  with 4 stage compressor, kp=12. No need blower  9  and no scavenging. Assembling  16 S is without buffer  51 , so as expansion work cause compression. Design is no balanced, but it may be balanced if add exactly the same “mirror” part as in  FIG. 2A . Prefer that rotation speed is small, that cause better combustion and compression is closer to isothermal process (cooling not shown). Any case no thermal loss during isothermal expansion, caused by appropriate combustion, so Tbe=Tee and internal surface of expander  34  is with the same Tee (thermal isolation not shown). Output gas with temperature Tee from isothermal expander  34  and from remote isothermal expander  19  with the same Tee go to LPC  40 R, that includes function of LP part of regenerator, and HPC  8 R includes function of HP part of regenerator. At  FIG. 2A , regenerator  23  is only optional. PPM is like for  FIG. 2A , but distinctions, caused by absent of buffer  51 , see below. 
     The embodiment on  FIG. 3A  comprising parts:  8 R,  16 S,  17 G,  19 ,  22 ,  24 ,  25 A,  25 D,  28 - 33 ,  34 - 39 ,  40 R. Below explains for several parts; all parts explained in NUMBERS OF PARTS FOR ALL DRAWINGS.
       8 R. HPC with function of regenerator, HP part.     16 S. Piston and crankshaft assembling, no buffer, separated pistons for compressor  35  and expander  34 .     17 G. Synchronization gears; belt is needed, if a second Assembling  16 S is used.     19 . Expander, power output. There it named “remote isothermal expander”.     28 . WCHPCIMDPS (sensor to measure a differential pressure between compressor  35  and HPC  8 ).     33 . WCLPCDPS (Differential Pressure Sensor between WCE and LPC; at  FIG. 2A , it is between WC and Atmosphere.   

     For  FIG. 3A , pressure at input of LPC is a-little more then Atmospheric, that caused by gas friction loss.
       34 . WCE expander (instead cylinder  15 ; output of WCE go to regenerator  40 R).     35 . WCC compressor (instead cylinder  15 ).  36 . Valve LP_out (instead 21).  37 . Valve HP_in (no exist on  FIG. 2A ).     37 . Valve HP_in (no exist on  FIG. 2A ).  38 . Valve LP_in (instead 20).  39 . Valve HP_out (instead 18).   

     Working cycle include simultaneously input stroke by compressor  35  and output stroke by expander  34 , kinetic energy of assembling  16 S diminish that caused by friction and vortex loss; then, simultaneously compression and expansion strokes, kinetic energy of assembling  16 S increase, so as expansion energy a-little more then compression energy to compensate mentioned loss. Zwork=0. Air from compressor  35  with Tec goes to HPC  8 R, where heated by combustion product from isothermal expander  34  and remote isothermal expander  19 , this gas with Tee=Tbe go to input part  40 R and then to Atmosphere with output temperature a-little more than Tec (if ideal regeneration, with Tee). Tec is a-little more than Tbc so as kv is small and so as compressor  35  is cooled. If Tec=Tbc and no loss, efficiency is as for cycle Carnot: Ef=1−Tbc/Tee. As mentioned, isothermal expansion is due to appropriate speed of combustion, caused by injectors  25 A and  25 D. Work of Expander  19  is output work, produced by the engine. If the engine used for a car, prefer placing expander  19  near a wheel, and regenerator  8 R,  40 R near expander  19 , to diminish length of tubes  24  with hot compressed gas. Zmachine ( 34 ,  35 ) work with PPM algorithm with synchronization to expander  19  as explained for  FIG. 2A . As option, Zmachine (for every embodiment) may include hydraulic piston pump, directly connected to assembling  16 ; this case, work of expander is more than work of compressor and over work is used by mentioned pump. Option with hydraulic pump cause addition loss and regulation problems and at  FIG. 3A  not shown. 
     With reference to  FIG. 3B , there is shown cycle of Zmachine ( FIG. 3A ). On  FIG. 3B : tce—compression and expansion time; tio—wide regulated time for input to compressor  35  and output from expander  34 . For PPM are used principles explained for  FIG. 2A . At crankshaft angle θ0 (according to  FIG. 3A ), rotation velocity is W0. Then begin compression, using energy from working stroke of Expander  34 . At 180°, after tce, end compression and expansion, and rotation velocity is W180. From 180° to 360° (0°), during time tio, output from Expander  34  and input to Compressor  35 ; kinetic energy a-little diminish, that caused by vortex and friction loss. To compensate this loss, must W180&gt;W0, and must EE&gt;CE. Time tce caused by EE, by moving masses, by W0 and by loss. Time tio caused by moving masses, by W0 and by loss. Regulating W0 and tio is possible by small power electrical machine  22  that may work as engine, or generator, or no convert energy. For case “W180′(small)”, may see, that tce a-little depend from tio. If W0=0, or W180=0, may fixate crankshafts  16 S. If need fast acceleration, may increase a time, when input valve ( 37 ) of WCE  34  is open, and vice versa. 
     With references to  FIG. 3C ,  FIG. 3D ,  FIG. 2E , explain engine with multistage compressor, for example 4 stages. Signed: B—Buffer ( 51 ), E—Expander ( 34 ), C—Compressor ( 35 ). Expander  34  or remote expander  19  may be multistage as well, but this version not shown. For multistage compressor, must be several HPC with cooling in every HPC, except HPC with a largest HP, this HPC is regenerator ( 8 R,  40 R). Every stage comprising two cylinders for symmetrical load on beam ( 16 ). 
     With reference to  FIG. 3C , explain engine with multistage compressor, using examples from Table_n. 
     Distinction between  FIG. 3C  and  FIG. 3A : on  FIG. 3C , n=4 stage compressor  35 , with 8 pistons for symmetrical load. Output of every stage go to appropriate pressure storage HPC 1  . . . HPC 3  (not shown), where compressed air is cooled with constant pressure, but not cooled in HPC 4  (not shown), so as the last stage, HPC 4 , is regenerator ( 8 E,  40 R). As at  FIG. 3A , Zwork=0 and output of engine is from Expander  19 . 
     Example for n=4 Stage Compressor According to Table_n, String 4.2 
     Input to every Compressor stage (C) and output from Expander (E) begin from 180° with force Cfi=2127N. Cfi cause acceleration and input work: wcp=213 J, so during this input, wcp is converted to kinetic energy. Return this wcp will be during compression, from 0° to 180°. Fixation of crankshaft is possible near angle 180°, where static load on bearings is minimum, it is mentioned Cfi. Maximum acceleration caused by force Efz from expander and begin from 0° with force Efz−Cfi=12774−2127=10647N. For compression used mentioned wcp, returned from kinetic energy, and expansion energy (285 J), at all 213+285=498 J. In the table, instead mentioned expansion energy, may see negative energy we (−285 J), that get compressor from expander. All expansion energy used for compression (Zwork=0). 
     Due to converting between expansion and compression energy, stroke from 00 to 1800 is fast, with large accelerations, and stroke from 180° to 0° is slower, with only kinetic energy, redistributed between moving masses. Moving masses and compressed gas make functions of ES (Energy Source) and ER (Energy Receiver). Note: For n=1, expansion energy is 365 J&gt;285 J, so as near isothermal 4-stage compressor (string 4.2) is better, then adiabatic (n=1). So, for n=1, Ef=63.5, but for string 4.2, Ef=71.5%, that is closer to Carnot cycle with Ef=75%. 
     In Table_n, n is Quantity of Stages with Adiabatic Compression 
     Pbc=0.1 MPa. After last stage: Pec=Pbe=1.22 MPa. For 4 stages: kp1=kp2=kp3=kp4=1.87; kp1*kp2*kp3*kp4=12.2. Vbc=1000 cm 3 , Tbc=300° K. Cooling after 1 and 2 stages to Tbcn=322° K, but after 3 stage, to TbcN=305° K=Tbc for last, 4 stage. After regenerator ( 8 R,  40 R): TH=Tbe=Tee=1200° K. For Carnot cycle: Ef=1−Tbc/TH=75%.
     Ef is efficiency of engine;   wcp is input work from all compressor stages;   we is work from expander, all this work used for compression (so Zwork=0);   Cf is summed forces from compressors  35  during output from all stages;   Cfi is summed forces from compressors  35  during input to all stages;   Efz is pic force from expander  34  of Zmachine.   Tec is output temperature of a last stage of compressor (gradus C). If dT in regenerator is 5° C.,   Tec+5° C. is temperature of output to atmosphere. The smaller Tec, the larger Efficiency Ef.   Tbcn is temperature after cooling in every stage, but TbcN is temperature before a last stage.   

     
       
         
           
               
             
               
                 TABLE_n 
               
             
            
               
                   
               
               
                 Engine with multistage compressor. 
               
            
           
           
               
               
               
               
               
               
               
               
               
               
            
               
                 n 
                 Ef, % 
                 wcp, J 
                 wc, J 
                 Cf, N 
                 Cfi, N 
                 Efz, N 
                 Tec, ° C. 
                 Tbcn, ° K 
                 TbcN, ° K 
               
               
                   
               
            
           
           
               
               
               
               
               
               
               
               
               
               
            
               
                 6 
                 72.1 
                 350 
                 −280 
                 6769 
                 3501 
                 12521 
                 70 
                 322 
                 305 
               
               
                 n 
                 Ef, % 
                 wcp, J 
                 wc, J 
                 Cf, N 
                 Cfi, N 
                 Efz, N 
                 Tec, ° C. 
                 Tbcn, ° K 
                 TbcN, ° K 
               
               
                 5 
                 71.9 
                 282 
                 −282 
                 6219 
                 2815 
                 12622 
                 79 
                 322 
                 305 
               
               
                 4.1 
                 71.1 
                 217 
                 −289 
                 5845 
                 2175 
                 12948 
                 112 
                 322 
                 322 
               
               
                 4.2 
                 71.5 
                 213 
                 −285 
                 5748 
                 2127 
                 12774 
                 91 
                 322 
                  305* 
               
               
                 4.3 
                 71.9 
                 211 
                 −281 
                 5679 
                 2108 
                 12600 
                 112 
                 305 
                 322 
               
               
                 4.4 
                 72.3 
                 206 
                 −277 
                 5583 
                 2060 
                 12422 
                 91 
                 305 
                 305 
               
               
                 3 
                 70.9 
                 143 
                 −291 
                 5462 
                 1432 
                 13036 
                 114 
                 322 
                 305 
               
               
                 2 
                 69.7 
                 73 
                 −303 
                 5760 
                 726 
                 13580 
                 162 
                 322 
               
               
                 1 
                 63.6 
                 0 
                 −365 
                 11226  
                 0 
                 16344 
                 348 
               
               
                   
               
            
           
         
       
     
     From Table_n see, that efficiency ‘Ef’ increase with quantity of stages n, but n&gt;4 seems too large, so as a small increasing of ‘Ef’ may be covered by loss in valves. Loss no including in calculations.
         Distinctions between strings 4.1-4.4 are cooling Tbcn, TbcN, that cause changing of Ef and other parameters.       

     At string 4.4 is the best efficiency (between 4.1-4.4) due to the best cooling. 
     For a large cost and large power engine with perfect thermal isolated and a large regenerator ( 8 R,  40 R) calculated Ef&gt;63% is close to reality. 
     For n=1, we=−365 J is compression energy, and it is compensated by work of expander  34 . For n&gt;1, summed compression energy for all stages (wcp+|wc|) increase, but it partly compensated by wcp (input to compressor), so the ‘wc’ part, that give expander, diminish and Ef increase. 
     Disadvantage of Embodiment  FIG. 3C : 
     Using crankshaft to get and return energy wcp need large inertial moment of crankshaft, so more load on bearings during moving with PPM, so as inertial moment of crankshaft diminish acceleration an sufficiency part of gas force is placed on bearings; the rest part of gas force accelerate piston and connected parts. 
     Advantage: no need a buffer. 
       FIG. 3D . Distinction from  FIG. 3C : have a buffer (b) at expander side of the beam. Part of work wcp get and return this buffer. If increase mean pressure in the buffer, more energy is stored in the buffer, so diminish rotation speed near 0°, but it increase near 180°. Advantage: Smaller inertial moment of crankshaft and load on bearings. 
     Note: even for 1 stage compressor, may use this buffer to have a large rotation speed near HPDP, but a smaller speed (up to 0) at LPDP. 
       FIG. 3E . A buffer is on crankshaft side, compressors and expander on opposite side. During working stroke of expander and input to compressors, 0° to 180°, charging the buffer, that discharging during compression, 180° to 360°. Both strokes are with the same acceleration. The crankshaft has minimal inertial moment, but maximal energy is in the buffer, minimum load on bearings. Fixation may be near 0° or near 180°. 
     With reference to  FIG. 4A , there is shown the EHE for Sun power plant, ISC between cylinder  15  and HPC  8 SH. The EHE is placed in focus of Sun concentrator. Remote Expander  19  connected to electrical generator  46 . The embodiment comprising parts:  8 ,  9 LP,  15 ,  16 - 22 ,  24 ,  26 - 33 ,  40 ,  41 ,  43 - 46 ,  48 . Valve drivers  30  are not shown. Blower  9 HP is optional. 
     The EHE is working according to Brayton cycle. If closed cycle, need hermetic envelope, and LP may be more than Atmospheric pressure. This cause heat from LPC  40  (long and large volume tubes, current initiated by Blower  9 LP) is dissipated to Atmosphere. HPC  8  includes Sun Heater  8 SH; it may be inside hermetic envelope (not shown) with low thermal conductive gas or vacuum;  8 SH is separated from light source with glass that is low transparence for infra red ray. Heat transfer to and from Working Fluid (WF) is with constant pressure HP and LP correspondingly. Compression and expansion in cylinder  15  is adiabatic, with approximately the same kp=HP/LP and the same compression and expansion work (Zmachine). Volume of WF after Sun heater  8 SH is more, than after compression in cylinder  15 . Addition (due to heating to Tbe) volume of WF with HP=Pbe=Pec, HT=Tbe&gt;Tec, across Thermal Isolated Tube  24  go to Remote Expander  19 , where make useful work that converted to electricity by Electrical Generator  46 . Remote parts are:  9 LP,  19 ,  24 ,  40 ,  46 . Other parts are small and placed from back side of Sun Heater  8 SH and no dashing a Sun Concentrator (not shown). 
     With reference to  FIG. 4B , there is shown piston and crankshafts assembling  16  with buffer  51 , adjusted for PPM (see explain to  FIG. 2A ). Expansion energy is stored in buffer  51  and then used for compression; so, kinetic energy of assembling  16  may be zero at end expansion and end compression, and near these points crankshafts may be fixated if PPM. Buffer  51  may be connected to HPC ( 8 SH) with long, small diameter tube, as explained above for  FIG. 2A . Due to fixation of crankshafts may diminish a throughput across cylinder  15  and increase time for scavenging. This throughput must regulate so that Tbe after Sun Heater  8 SH is optimal. If Tbe is too small, must diminish the throughput, and vice versa. Tbe measured by sensor TSSH  48  ( FIG. 4A ). About optimal Tbe, see below “PPM regulation”. 
     With reference to  FIG. 4C , there is shown Inertial Scavenging (ISC) between cylinder  15  and HPC  8 . 
     Below explain, how works controller  29 . When volume of cylinder  15  is near Vec according to signal from RSS  31 , and dP (measured by sensor WCHPCIMDPS  28 ) is near zero (dP=0), by driver  30  begin opening valve WCHPCO  18 . This condition (must be volume Vec when dP=0) is according to regulation, explained below in “PPM regulation”. During initiating time tini ( FIG. 4C ), WF is pushing by piston of assembling  16  to input mean HPCIM  26 , where WF get any kinetic energy. When dP, measured by sensor WCHPCOMDPS  43 , is near zero, by driver  30  begin opening valve WCHPIM  41 , and due to kinetic energy of WF, begin ISC. Hot WF with Tbe is moving from a hot part of the HPC (from HPCOM  44 ) to cylinder  15  across WCHPIM  41 ; simultaneously, WF with Tec is moving from cylinder  15  to a cool part of the HPC (to HPCIM  26 ). During input time tin, diminish kinetic energy of WF in HPCIM  26 . According to signal from RSS  31 , at volume Vbe, end closing of WCHPIM  41 , WCHPCO  18 . If normal scavenging, T 27  (measured by HPCIMTS  27 ) before Sun Heater  8 SH, is a—little more than Tec: T 27 &gt;=Tec, due to a small mixing between gases with temperatures Tec and Tbe, so as Tec&lt;Tbe. Optimal T 27  (a-little more than Tec) cause maximum efficiency. Tbe measured by TSSH  48 , and Tec=Tbc*(Vbc/Vec) (ka-1)  where Tbc measured by TSBC  45  and Vec calculated from signal of position sensor RSS  31  when begin open WCHPCO  18 . So, comparing Tec (calculated from measured Tbc) and T 27  (measured), may adjust the optimal scavenging. If measuring HP by pressure sensor HPCPS  32  (if exist), may calculate T 27  by another way. Any case, ISC depend from construction parameters (for example Vec/Vmin), by regulation of WCHPIM  41  and WCHPCO  18 , by crankshaft fixation time at point Vmin (this fixation is possible by PPM—see below). 
     End expansion volume Vee detected by RSS  31 , then WCLPOM  21  and WCLPIM  20  are opening by drivers  30 , and due to blower  9 LP, WF with parameters Pbc=LP and Tbc=LT go inside cylinder  15 , while WF with Tee go to LPC  40 . Instead blower  9 LP, possible ISC, for example see explanation of  FIG. 2A . 
     Version with additional Blower  9 HP may be needed in case of large pressure drop across Heater  9 SH, causing bad work of ISC. Blower  9 HP gets addition power, but for this version may be Vec=Vmin and so diminishes friction loss. Every blower  9 HP,  9 LP is arranged as a rotating mean, capable to working as a turbine or as a compressor according to difference of pressure between input and output of the rotating mean. This rotating mean, when connected to electrical machine, is working as electrical generator or electrical motor and is connected to electrical accumulator across electrical Controller ( 29 ). Electrical machine of Blower  9 HP is placed out of the hot zone, with appropriate sealing envelope (not shown). Obviously, appropriate control of valves ( 20 ,  21 ,  18 ,  41 ) may cause large energy of gas flow when scavenging begins. This energy may be accumulated by Blowers  9 LP,  9 HP, but this case is more practical for ICE (see explanation below about dWv to Table_Zwork). 
     PPM Regulation 
     Optimal Tbe selected as a compromise between infrared loss from  8 SH when Tbe is high, and small Ef, when Tbe is small; Tbe measured by TSSH  48 . A throughput of Remote Expander  19  is regulated to keep pressure HP, measured by HPCPS  32 , near optimal. If HP is too small, must diminish throughput of expander  19 , and vice versa. When HP is optimal, mentioned condition “Vec when dp=0” is true. For example, may regulate throughput of expander  19  by regulating input and output valves of expander  19 . Note, that for car, power of expander  19  is according to load, but for Sun Power Plant—vice versa: power of electrical generator  46  and, so, expander  19 , must be according to Sun Heater. 
     If used Electrical Generator  46  synchronous type, this regulation cause changing rotating moment of Electrical Generator  46  and so changing electrical current and power, that must be according to power of Sun Heater  8 SH. Receiving surface of  8 SH is sufficiency more than a surface normal to concentrated Sun rays. Most ray energy, that go across this normal surface, is absorbed by the receiving surface of  8 SH, but infra-red loss is equivalent to loss from the “virtual” normal surface, heated to TH+dt, where dt may be, for example, 20° C. and need for thermal transfer from  8 SH to WF. 
     Example from Computer Calculation. 
     HT=750° K=477° C., LP=7 atm, HP=56 atm, Ef=42% with calculated thermal and friction loss in cylinder  15 . For ideal Brayton cycle: Ef=44.6%; for Carnot cycle: Ef=(HT−LT)/HT=60%. Diameter of cylinder  15  is 45 mm, stroke 2×40 mm, cycle work=81 J, so power is 4 kW for 3000 cycles/min. If common efficiency (including loss in Sun concentrator, heater  8 SH, expander  19 , generator  46 ) is 25%, and power of Sun radiation is 1 kW/m 2 , need Sun concentrator surface 16 m 2 . Calculated for this EHE, good Ef=42% caused by scavenging between Cylinder  15  and HPC  8 , by PPM regulation and due to using large, but low cost, high efficiency remote expander  19  and generator  46 , that impossible for prior art. To increase Ef, must increase HT, that is possible with using special glass (available today), transparent for Sun Spector, but no transparent for infra red loss from heating surface of heater  8 SH. 
     With reference to  FIG. 5A , there is shown the ECE with hybrid Sun heating and combustion and remote expander  19 . The embodiment ( FIG. 5A ) comprising parts:  8 ,  9 ,  15 ,  16 - 22 ,  25 - 33 ,  40 - 48 . Valve Driver  30  not shown. 
     HPC  8  include Sun Heater  8 SH, and HPC  8  separated by valve HPSDV  47  to an input part HPCIP and an output part HPCOP ( 80 P). HPSDV  47  may be directly controlled by dP between two sides of it, or from a driver (not shown), activated by sensor of this dP (not shown), this case dP may be near zero due to high sensitivity of this sensor. 
     By combustion in the HPCOP, initiating scavenging between WC (cylinder  15 ) and HPC, that includes parts  8 SH, 26, and 44. Is used PPM. LPC is Atmosphere, WF is air, open cycle, but Versions “P” and “ 47 P” are without combustion (so may be LP&gt;0.1 MPa, closing cycle). Scavenging between WC and LPC is initiated by blower  9 . 
     With reference to  FIG. 5B , there is shown scavenging, initiated by mentioned combustion. 
     After end compression in Cylinder  15  (at volume Vec), begin opening of WCHPCO  18 , WCHPIM  41 , and begin combustion in the HPCOP, caused by Injector  25 A. Combusted product from previously cycle pushed to cylinder  15 , so as HPSDV  47  is closed and Injector  25 A is placed near HPSDV  47 . Simultaneously, compressed air pushed to the HPCIP. So, heat expansion of WF in HPCOP initiates scavenging between Cylinder  15  and HPC  8 ; scavenging continue when HPSDV  47  is open. When volume of cylinder  15  return Vbe=Vec, end closing of valves WCHPCO  18 , WCHPIM  41 . So as scavenging caused by combustion in HPCOP, possible Vec=Vmin. So as combustion may continue during scavenging, this scavenging may be fast. May end combustion before than valves  18 ,  41  are closed, this causes ISC to begin. Scavenging time, when valves  18 ,  41  are opened, adjusted by controller  29  with feedback from temperature T 27 , measured by sensor  27 , placed in HPCIP. About optimal T 27  see explain to  FIG. 4A-4C ; with or without Sun heating, optimal T 27  cause maximum Ef Optimal T 27  a-little more then Tec. Addition combustion is possible by injectors  25 D (before expander  19 ) and  25 C. Work of these injectors must be synchronistic with work of expander  19  and cylinder  15  to avoid reversed current across cylinder  15  and Sun neater  8 SH. 
     Version “P”. 
     This case does not need combustion. Main principle: Scavenging between WC and HPC proceeds by changing volume in Expander  19 , and then using ISC. By PPM, end compression in Cylinder  15  is synchronistic to at least a part of input stroke of Expander  19 , that cause diminishing pressure in part of HPC named HPCIP, while HPSDV  47  is closed. Signals from WCHPCIMDPS  28  and WCHPCOMDPS  43 , initiate opening WCHPCO  18  and WCHPIM  41  by controller  29  with appropriate drivers  30 , so begin scavenging. Then, due to kinetic energy of WF, pressure in HPCOP and HPCOM  44  diminish, that cause opening HPSDV  47  and scavenging continue with ISC. After scavenging time tsc (see above), valves  18  and  41  are closed. 
     Version  47 P. 
     Instead HPSDV  47 , HPSDV  47 P is used. Scavenging between Cylinder  15  and HPC  8  proceeds by combination of two factors: increasing pressure in part  8 SH due to heating from Sun light, and then ISC. HPC  8  is separated to two parts  8 HS and HPCIP with valve HPSDV  47 P. When valves HPSDV  47 , WCHPIM  41 , and WCHPCO  18  are closed, part  8 SH is (temporarily) hermetically sealed by WCHPIM  41  and WCHPCO  18 , and heating by Sun light causes changing ratio between pressures in parts  8 SH and HPCIP. Opening WCHPIM  41  and WCHPCO  18 , initiates flow of the WF between the two parts across Cylinder  15 ; when ratio between pressures in parts  8 HS and HPCIP is close to 1, opening the HPSDV  47 , thereby proceeding with ISC, with control valves WCHPIM  41 , WCHPCO  18  and time tsc as explained. During scavenging, input valve (not shown) of Expander  19  is closed. 
     Comparing Between Versions  FIG. 5A  and  FIG. 4A  (“+” if Version  FIG. 5A  is Better):
         − Heat loss (h_loss) for  FIG. 5A  is more, then for  FIG. 4A . It is so as h_loss to surface is proportional to p (0.3 . . . 0.5) , but power is proportional to P, so h_loss/power is smaller in closed cycle ( FIG. 4A ) if LP&gt;0.1 MPa. Versions “P” and “ 47 P” may work in closed cycle. To switch between open and closed cycle, need: a valve that may connect output from valves  20  to input valves  21  across addition heat exchanger; a compressor to regulate LP; hermetic envelope; all this not shown.   + Obviously, that combustion energy adds power. Even with small combustion energy, scavenging between Cylinder  15  and HPC  8  is good and possible Vec=Vmin, so smaller friction loss, caused by moving piston  16  under HP; smaller time for scavenging due to more energy for scavenging, so diminish thermal loss.   + With combustion, may be more efficiency of using Sun energy. Example: For Brayton cycle, Efa=(Tec−Tbc)/Tec. For  FIG. 4A  and  FIG. 5A , must Tec&lt;T 48  (measured by sensor TSSH  48 ), else Sun heater  8 SH cannot transfer heat. In example for  FIG. 4A , Tbe=HT=T 48 =750° K. T 48  limited by infra red loss and optimal T 48  is the same for  FIG. 4A  and  FIG. 5A . Suppose: For both cases, Tbc=300° K, Tec=700° K. For  FIG. 5A , in cylinder  15 : Tbe=T 42 =1000° K, and the same Tbe for Expander  19  due to Injectors  25 C or  25 D. Both cases, if no loss, Efa=57%, and CE is the same, and Zwork=0. For  FIG. 4A : EE/CE=Tbe/Tec=1.071, EE4=0.071*CE. For  FIG. 5A : EE/CE=1000/700=1.429, EE5=0.429*CE, where EE4, EE5 are Expander Energy (useful work) for  FIG. 4A ,  FIG. 5A  if no loss. Both cases efficiency of compression and expansion strokes in Zmachine (cylinder  15 ) suppose Efz=0.97, efficiency of Expander  19  suppose Efe=0.98. For  FIG. 4A , loss4=(1−Efz)*2*CE+(1−Efe)*EE4=0.061*CE. With this loss: EE4L=0.01*CE; Ef4=Efa*EE4L/EE4=8% (instead 57% if no loss). For  FIG. 5A : loss5=(1−Efz)*2*CE+(1−Efe)*EE5=0.0686; EE5L=0.360; Ef5=Efa*EE5L/EE5=48%. This 48% is Ef for using Sun energy and fuel. If Tec&lt;700° K, Ef4&gt;8%, but Ef5&lt;48%. With separated combustion and Sun engines, may be independent parameters for best Ef of both engines, but cost of the power plant increase. The compromise is version  FIG. 5  with using only Sun or only combustion mode, and combination (Sun and combustion) by computer with using all factors.       

     With reference to  FIG. 6 , there is shown the heat pump for combined heat pumping and producing energy from a wind, with remote Compressor  7  connected to a wind turbine  49 ; open cycle; at least a single WC ( 15 ) with scavenging by blowers  9 LP,  9 HP and regulation Zwork near zero, with regulated valves and PPM regulation of throughput. 
     The embodiment comprising parts:  7 ,  8 B,  8 C,  8 H,  9 LP,  9 HP,  10 ,  15 - 22 ,  24 ,  26 - 33 ,  40 ,  41 ,  43 ,  44 - 46 ,  49 ,  50 ,  52 - 56 ,  58  and optionally  47 . 
     On View A-A may see items  26  and  44 , designed to improve inertial scavenging. Valve drivers  30  are not shown. 
     The Heat pump working according to open reverse Brayton cycle, LPC  40  is atmosphere. 
     Output of Compressor  7  across Distributor  50  connected to Cool part  8 C of HPC and to thermal isolated Buffer Volume  8 B, that across on/off valve  54  connected to Expander  19 , mechanically connected to Electrical Generator  46 . 
     At cooling mode, the LPC is a cooling room, and the HPC cooled by external air. 
     At heating mode, the LPC is atmosphere, and the HPC cooled by a room air. 
     Blowers (turbines)  9 LP,  9 HP,  9 E are working during all cycle from any small power source. 
     Working Algorithm Includes: 
     Closing WCHPIM  41  and WCHPCO  18 , thereby separating the HPC  8  to two parts ( 8 C,  8 H); changing a ratio between pressures of WF in these parts, using blower  9 HP; opening the WCHPIM  41  and WCHPCO  18 , and so initiating flow of the WF between parts  8 C and  8 H across Cylinder  15 , then using ISC; closing the WCHPIM  41  and WCHPCO  18  to end ISC. So, after compression in Cylinder  15 , scavenging is initiated by Blower  9 HP. 
     After expansion in Cylinder  15 , scavenging initiated by Blower  9 LP. 
     Air current across heating section of Heat exchanger  10  initiated by Blower  9 E. 
     Current of Air During Cooling Cycle 
     Input air from room—Valve  52   c IR—compression in Cylinder  15 —sink heat to Atmosphere in Heat Exchanger  10  with heating section connected by valve  52   c EA—expansion—Valve  52   c OR—to room. 
     Current of Air During Heating Cycle 
     Input air from Atmosphere—Valve  52 HIA—compression in Cylinder  15 —sink heat to room in Heat Exchanger  10  with heating section connected by valve  52 HER—expansion—Valve  52 HOA—to Atmosphere. 
     All sections of Valve  52  may be connected together mechanically. 
     Piston assembling  16  is shown at HPDP (Dead Point when end compression), so volume of Cylinder  15  (WC) is Vmin. Due to scavenging after end compression, Vmin is large and so surfaces of valves WCHPCO  18  and WCHPIM  41  may be large, vortex loss and time for scavenging is small. 
     HP scavenging from volume  8 C across cylinder  15  to volume  8 H is initiated by blower  9 HP when valves WCHPCO  18  and WCHPIM  41  are open. Power of blower  9 HP is regulated by controller  29  for optimal HP scavenging. It is optimal when temperature after output from cylinder  15 , T 27 , measured by HPCIMTS  27 , is a-little smaller than Tec; Tec=Tbc*kv (ka-1) , Tbc measured by TSBC  45 , kv may be regulated by valves  20  and  21 . T 27 &lt;Tec due to partly mixing in cylinder  15  with input air with Tbe, measured by TSBE  55 . In case of over scavenging, a large part of input air with Tbe goes to output from Cylinder  15 , so T 27  sufficiency smaller then Tec. Over scavenging cause increasing of vortex loss. 
     During HP scavenging, air with begin parameters HP, T 27 , is pushed across Heat Exchanger  10  by Blower  9 HP and is cooled. Air across heating section of Heat Exchanger  10 , is pushed by Blower  9 E. 
     If the Heat pump working with cooling mode, heat from compressed air (T 27 , HP) is sinking to Atmosphere; with heating mode, this heat sinking to a room; reconnection between Atmosphere and the room by Valves  52   c EA,  52 HER. 
     After end expansion in cylinder  15 , WCLPIM  20  and WCLPOM  21  must be open, and cooled (due to adiabatic expansion) air across  52   c OR go to the room; at heating mode, this cooled air go to Atmosphere across  52 HOA. 
     Optimal LP scavenging is controlled by: sensor TSBC  45 , measuring Tbc, that is as well temperature of scavenging air in input of cylinder  15 ; by sensor TSILPC  58 , measuring mean temperature after output from cylinder  15 , it is T 58 ; by TSBE  55 , measuring Tbe. For optimal LP scavenging, T 58  is a-little more than Tee, Tee=Tbe/kv (ka-1) . If over scavenging, T 58  is too large, that caused by mixing with air with Tbc. If scavenging is not good (for example, a small time for scavenging), T 58  is close to Tee and throughput of cool air diminish, “pumping” of heat energy diminish, while mechanical loss is approximately the same and so efficiency of the heat pump diminish. 
     Over scavenging not diminish “pumping” of heat energy, but increase vortex loss. For air conditioner, over scavenging is not critical (in any case, output air is mixed with hot air in the room), but prefer avoid over scavenging if the heat pump used for refrigerator. 
     Throughput of the Heat Pump Controlled by PPM. 
     If HP, measured by HPCPS  32 , increase over desired level, part of throughput of Remote Compressor  7  must be directed to buffer  8 B across Distributor  50  and thermal isolated tube  24 . 
     Buffer  8 B is large volume, thermal isolated and used as energy source for Remote Expander  19 , connected to Electrical Generator  46 . Pressure inside Buffer  8 B is measured by HPCBPS  56 . If this pressure is smaller then desired minimum, must close valve  54 , and vice versa. 
     If throughput of Remote Compressor  7  is too small, may using an addition compressor (not shown) from any energy source, for example from Remote Expander  19 , reconnecting it to the addition compressor. 
     One of advantages of Heat Pump ( FIG. 6 ) against prior art [3]: piston stroke is sufficiency smaller than for the prior art, and so diminish friction loss; diminish loss for output from cylinder  15  to HPC due to large surfaces of WCHPCO  18  and WCHPIM  41 . Due to PPM, is possible to fixate crankshaft  16  at LPDP and so to diminish loss for scavenging of air between cylinder  15  and LPC. 
     Version with Valve HPSDV  47  may work without Blower  9 HP, but preferably with using for heat pump only mentioned addition compressor (below named “compressor”). This method for the heat pump, with scavenging at least by changing of an external volume (in this case, the volume in a compressor of positive displacement type). For this version, providing phase difference sensors (not shown), arranged to detect difference between cycle phases of Cylinder  15  and the compressor. Controller  29  provides synchronization between cycles of Cylinder  15  and the compressor, using signals from HPCPS  32  and the phase difference sensors, so that pressure in HPC  8  will be approximately as desired, and after end compression in Cylinder  15 , take place at least a part of an output stroke of the compressor. So, when HPSDV  47  is closed, initiating ISC. Adjusting the optimal scavenging duration, for optimal T 27 , as explained above. 
     Synchronization with Compressor  7 , working from wind energy (and so with wide swing of rotation speed) may be problematic, so this version is practical only with mentioned “additional compressor”. 
     With reference to  FIG. 7 , there is shown the ICE that is very close to explained for  FIG. 2A . Distinction from  FIG. 2A  is comprising a regulated Hydraulic pump  16 GP as energy receiver to use Zwork for charging a hydraulic accumulator (not shown), so Zwork may be large, while for  FIG. 2A , Zwork must be small, so as small power electrical machine  22 , used for PPM, cannot get a large Zwork. So as Hydraulic pump  16 GP is regulated, prefer using regulated pressure in Buffer  51 . Version  FIG. 7  with combined mechanical and hydraulic power need, for example, in construction engineering. Another using is for a car, for example, with hydraulic motors for front wheels, and expanders—for rear wheels, with option to restore energy in hydraulic accumulator. 
     The embodiment ( FIG. 7 ) comprising parts:  8 ,  9 ,  15 ,  16 P,  16 GP,  16 V,  16 O,  18 ,  19 ,  20 ,  21 ,  22 ,  24 - 33 ,  40 ,  42 . Driver  30  for sliding valve  20  is not shown. Instead valve  21  using a window. 
     Calculations are for adiabatic process. Above in “Explain to Table_Z1” mentioned, that heat loss may diminish Ef to 1.5-2.5%. Mass of fuel is smaller than 5% from mass of air. Volume of HPC is 1500 cm 3 ; Vbc=1000 cm 3 , Tbc=300° K, Pbc=0.1 MPa, Pec=3.975 MPa, Tec=859° K; Tbe=Tmax=2000° K; Pee=0.1043 MPa, Tee=697° K. Virtual work, workv=0.06 J, may be caused by expansion from Pee, Tee, Vee=Vbc, to virtual: Pbc, 688° K, 1030 cm 3 . This work named “virtual”, so as it may be used (for example, by turbine), but often it is not used even in prior art, where workv is large. There, workv is small and may be used for ISC. Used heat=826 J. Tbe/Tee=Tec/Tbc=2.87. 
     Work: 0.06 (workv)+20.5 (Zwork)+510 (expander)=530 J; Ef.=530/826=64%, if no loss of heat to walls of WC and expander. Temperature in HPC, THPCes=1246° K, calculated supposing a full mixing inside cylinder  15  during output to HPC, caused by combustion. In Table_Zwork (below) may see, that THPCes caused by Vbe. Really, THPCes is smaller, and without mentioned mixing, THPCes=Tec. To get a full power, must addition combustion in HPC  8  or in expander  19 , and combustion in cylinder  15  to Tmax. Combustion in HPC  8  or expander  19  is better than in WC (cylinder  15 ) so as more time, more temperature at begin combustion, better mixing. So, for the same fuel, output from expander is clearer than output from WC. So, for clearer output, prefer to diminish output from WC. Below, mass of combusted product, that go from WC to atmosphere, named Moutwc, and all output named Mout (for a full power). Both Moutwc and Mout caused by the same proportion coefficient “k” (according to combustion energy of fuel, that is near 47e6 J/kg; mass air/fuel, is 15-20 for a full power). 
     From mass of air in cycle, Mbc=1161 mg, and mass, displaced from WC to HPC, mtoHPC=639 mg, may calculate Moutwc/Mout. So, Moutwc=(Mbc−mtoHPC)*(Tmax−Tec)*k; Mout=Mbc*(Tmax−Tec)*k; Moutwc/Mout=X=(Mbc−mtoHPC)/Mbc=522/1161=0.45. Calculating X by another way: X=300/688*1030/1000=0.45. 
     Due to PPM, combustion inside WC may be optimal, so as possible regulation a time for combustion (see explain of PPM for  FIG. 2A ). So, 45% of fuel is combusted inside WC with the same or better quality than in prior art ICE, and the rest 55% combusted with the best quality inside HPC. To save lifetime of expander valves, and to diminish heat loss in HPC, a part of fuel may be combusted in the expander during input from HPC. Combustion in the expander begins from a high T and so it is good. 
     Zwork used by the Hydraulic pump  16 G, that include electrical controlled input valve  16 V and automatic Output Valves  16 O. As example, mean velocity of piston and plunger (assembling  16 P) is 8 m/s and it is velocity of oil mass 5G; kinetic energy of oil is lost and for 2 pumps and 2 strokes is 0.3 J (for  FIG. 7 , cycle work=530*1256/1000=665 J for 2 pistons). If high pressure of oil in hydraulic accumulator is 200 atm, for working stroke of pump 5 cm 3 , maximum work for 2 pumps is 200 J. Minimum is zero, if input valve  16 V closed at end of working stroke. 
     For oil velocity 4 m/s across valve  16 V, dP=0.8N/cm 2 . Surface of valve  16 V is 2 cm 2 , so an electrical magnet must make 1.6N (in this case, the magnetic gap&gt;0) to compensate this dP. If acceleration of valve  16 V is 1 mm during 1 ms, and mass 5 g, mean acceleration force from spring is 10 N, pic force is 20 N. So, the electrical magnet must make&gt;21.6N when magnetic gap is zero. Electrical magnet at  FIG. 7  with surface of core 1 cm 2  may make force 160 N&gt;21.6N. 
     Calculated above small loss (0.3 J=0.05% from the cycle work) in valve  16 V is due to fixation of assembling  16 G by crankshaft, but not by any valve. For prior art [9], fixation caused by closing a valve (named in the Prior Art a FREQUENCY CONTROL VALVE), and driver of it must compensate force, for this example: 2000 N/2 cm 2 *2 cm 2 =4000 N, so construction of this valve must be another and loss in it is more. From prior art [9]: “ . . . the frequency control valve of 50 bar would for example result in an energy loss of 31 J. Compared to a total pump work of 410 J, this would be a loss of 7.7% . . . . This then sets the requirements for the frequency control valve: a rather large valve with an extremely fast opening response time. An opening time of a few milliseconds is acceptable since the valve can start to open at the end of the previous stroke . . . ”. 
     Compare loss 7.7% in valve of prior art [9], with loss 0.05% in valve according to  FIG. 7 . This small loss is due to PPM, described for  FIG. 2A . 
     Table_Zwork Illustrate Working of Engine with Hydraulic Pump (FIG.  7 ) 
     Zwork (Zw)=EWz−CWz, where EWz is expansion, and CWz is compression works in Zmachine; if Zw&gt;&gt;0, it used by the hydraulic pump. Main output (EW) is from Expander. dWv=virtual work for expansion from Pee, Vee=1000 cm 3 , to 1 atm up to virtual volume Vwcv,cm 3 ; work=Zw+dWv+EW, Ef=work/heat (if no loss). Vwcv no exist in reality in this embodiment; it included to “work”, so as it may be used by any addition volume (Vwcv−Vee), but it is not practical. CWz=376 J, Pec39.7 atm, Tec859K, Tmax in WC=1900° K; gas with THPCes from HPC go to expander; Vec=72, Vmin=67 cm 3 . Changing of parameters caused by begin expansion volume Vbe. 
     
       
         
           
               
             
               
                 TABLE_Zwork 
               
             
            
               
                   
               
               
                 Engine with hydraulic pump 
               
            
           
           
               
               
               
               
               
               
               
               
               
               
            
               
                 Zw 
                 Vbe 
                 Tee 
                 Pee 
                 dWv 
                 Vwcv 
                 Work 
                 EWJ 
                 THPCes 
                 Ef 
               
               
                 J 
                 cm 3   
                 ° K 
                 MPa 
                 J 
                 cm 3   
                 J 
                 J 
                 ° K 
                 % 
               
               
                   
               
            
           
           
               
               
               
               
               
               
               
               
               
               
            
               
                 18.9 
                 71.5 
                 662 
                 0.104 
                 0.05 
                 1026 
                 497 
                 478 
                 1216 
                 64.2 
               
               
                 108 
                 81.5 
                 697 
                 0.124 
                 1.87* 
                 1166 
                 520 
                 410 
                 1179 
                 64.5 
               
               
                 194 
                 91.5 
                 730 
                 0.145 
                 6.09 
                 1303 
                 549 
                 349 
                 1153 
                 64.7 
               
               
                 236 
                 96.5 
                 746 
                 0.156 
                 9.04 
                 1371 
                 565 
                 319 
                 1140 
                 64.8 
               
               
                   
               
            
           
         
       
     
     From TableZwork may see, that Zw (Zwork) may be a sufficiency part of the full output work (530 J); for prior art, Zw is a full work of engine and so dWv, that practically not used (to use it, must expansion from Vee=1000 cm 3  to Vwcv, that for prior art is sufficiency more, than in Table_Zwork), cause a loss of efficiency. In embodiment  FIG. 7 , this loss is very small. Working mode like in the last string may be used when need a large hydraulic power (Zw=236 J). So as for this case THPCes is minimum, addition combustion in expander may sufficiency increase a power (if no regenerator, prefer use combustion in expander only for a short time to get a pic power).
         String with dWv=1.87 J is optimal, and dWv used for inertial scavenging, that helps Blower  9  (if needed)       

     Below example about friction loss in bearings and rings ( FIG. 7 ), this loss is smaller than for Prior Art [3]. This example is true as well for  FIG. 2A  and other embodiments with reciprocating piston. Parameters of Zmachine on  FIG. 7 : cylinder D=112.8 mM, stroke 94 mM, a single ring with height 1 mM and friction coefficient fr=0.3, crankshaft bearings D=35 mM and friction coefficient bfr=0.0025 (needle roller bearings). Cycle work 530 J for Vbc=1000 cm 3 ; Vec=72 cm 3 , Pec=3.975 MPa. In Table_fr: fzr, bfr=friction loss by ring and bearings; dWv, Zw explained for Table_Zwork. 
     
       
         
           
               
             
               
                 TABLE_fr 
               
             
            
               
                   
               
               
                 Friction loss 
               
            
           
           
               
               
               
               
               
            
               
                 Vmin 
                 fzr 
                 bfr 
                 dWv 
                 Zw 
               
               
                 cm 3   
                 J 
                 J 
                 J 
                 J 
               
               
                   
               
            
           
           
               
               
               
               
               
            
               
                 71.5 
                 4.1 
                 0.3 
                 0.07 
                 20.6 
               
               
                 56.5 
                 4.73 
                 2.9 
                 0.05 
                 19.7 
               
               
                 46.5 
                 5.13 
                 3.8 
                 0.03 
                 15.4 
               
               
                   
               
            
           
         
       
     
     From the last string may see, that if after end compression at Vec=72 cm 3 , piston continue moving to Vmin=46.5 cm 3  with pushing compressed gas to HPC, friction loss is maximum: 5.13+3.8=8.93 J, that caused by moving piston and crankshaft against Pec. Then displacing compressed gas continues by any of methods explained above. For Prior Art [3] with proportional sizes, Vmin=0, all gas pushed by piston, and loss is sufficiency more than for Vmin=46.5 cm 3 . 
     Optimal is Vmin=71.5 cm 2 : due to near zero moving piston after end compression, friction loss is minimum (4.4 J). dWv=0.07 J used for inertial scavenging, that help to Blower  9 .