MX2007004555A - Fluid pump - Google Patents

Abstract

A fluid pump for moving a fluid from a first fluid source of the fluid in a low pressure state to a second fluid source of the fluid in a high pressure state, includes a chamber;a partitioning member displaceable in the chamber and dividing the chamber into first and second sub-chambers of varying volumes;the first sub-chamber having an opening controllably communicable with either the second fluid source or a third fluid source;the second sub-chamber having inlet and outlet openings controllably communicable with the first and second fluid sources, respectively;and a cooling element for cooling a fluid in the first sub-chamber.

Description

FLUID PUMP The present Patent Application claims the priority for Provisional Application No. 60 / 618,749 filed on October 15, 2004, the entirety of which is expressly incorporated by reference herein. The complete contents of U.S. Patent Nos. 4,698,973, 4,938,117, 4,947,731, 5,806,403, 6,505,538, Provisional Applications of the United States of America No. 60 / 506,141 and 60 / 618,749, and the International Application case number of attorney-in-fact No. 233-016PCT entitled "MULTI-CYLINDER RECIPROCATING UNIFLOW MOTOR" filed with the USPTO as the Receiving Office on October 7, 2005 are also incorporated herein by reference.

BACKGROUND The described embodiments relate to a fluid pump and, more particularly, to a fluid pump for use in a thermal system with a boiler and a heat engine. It is known in thermodynamics that a heat engine requires the circulation of working fluid from a cold reducer or engine exhaust to a heat source such as a boiler. Fluid pumps are used for this purpose. As is also well known in the field, the Rankine Cycle usually employed in such thermal systems requires a phase change to pass the working fluid from the low pressure level of the heatsink or engine exhaust to the high pressure level of the boiler. In other words, the low pressure vapor of the working fluid should be cooled to a liquid before it is pumped back into the high pressure level of the boiler for recycling. During the Rankine Cycle, the low-pressure semi-saturated steam after the engine exhaust must be cooled using a condensing coil so that the vapor can change from phase to liquid state. The cooled liquid is subsequently pumped back into the high pressure boiler to be reheated again to the vapor state, thus requiring a phase change from liquid to vapor. It requires a large amount of additional heat input to reheat and re-vaporize the liquid to steam, causing a large amount of loss in the thermal efficiency of the cycle.

BRIEF DESCRIPTION OF THE INVENTION In one embodiment, a fluid pump is provided to move a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the fluid pump comprising a camera; a partition member movable in the chamber and dividing the chamber into first and second sub-chambers of variable volumes; the first sub-chamber having an opening controllably communicable with the second fluid source or a third fluid source; the second sub-chamber having inlet and outlet openings controllably communicable with the first and second fluid sources, respectively; and a cooling element for cooling a fluid in the first sub-chamber. In a further embodiment, a fluid pump is provided to move a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the pump fluid comprising: first and second chambers; a first partition member movable in the first chamber and dividing the first chamber into first and second sub-chambers of variable volumes; a second partition member movable in the second chamber and dividing the second chamber into third and fourth sub-chambers of variable volumes; each of the first and fourth sub-chambers having an aperture controllably communicable with the second fluid source or a third fluid source; each of the second and third sub-chambers having inlet and outlet openings controllably communicable with the first and second source of fluids, respectively; and a cooling element for cooling a fluid in the first and fourth sub-chambers, thereby reducing fluid pressures in the first and fourth sub-chambers and creating suctions in the second and third sub-chambers, respectively, to extract the low pressure fluid from the first fluid source within the second and third sub-chambers, respectively; wherein the first fluid source is at all times in fluid communication with at least one of the second and third sub-chambers through the respective inlet openings, whereby the low pressure fluid is extracted substantially continues outside the first source of fluid. In a further embodiment, a fluid pump is provided to move a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the fluid pump comprising: a camera controllably communicable with the first and second source of fluids; closure element for communicating the chamber only with one of the first and second fluid sources at the same time; and suction element to generate a suction in the chamber and extract the low pressure fluid from the first fluid source inside the chamber when the closure element communicates the chamber with the first source of fluid and isolates the chamber from the second fluid source; the closing element which is furthermore to isolate the extracted low pressure fluid trapped in the chamber of the first fluid source, and then communicate the chamber with the second fluid source, thereby moving the trapped low pressure fluid to the second source of fluid. In a further embodiment, a system comprising a boiler for supplying a high pressure fluid is provided; an engine coupled to said boiler, which displaces the high pressure fluid, and discharges the fluid in a low pressure state; and a fluid pump for returning the low pressure fluid from the engine exhaust to the boiler, the fluid pump comprising: a chamber; a partition member movable in the chamber and dividing the chamber into first and second sub-chambers of variable volumes; the first sub-chamber having a controllable communicable opening with either the boiler or with an additional fluid source; the second sub-chamber having inlet and outlet openings controllably communicable with the exhaust of the engine and the boiler, respectively; and a cooling element for cooling a fluid in the first sub-chamber, thereby reducing the fluid pressure in the first sub-chamber and creating a suction in the second sub-chamber to extract the low pressure fluid from the exhaust of the motor inside the second sub-chamber from which the low pressure fluid is moved additionally towards the boiler at the opening of the outlet opening. In a further embodiment, a method is provided for pumping a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the method comprising: providing a camera having a partition member movable therein and dividing the chamber into first and second sub-chambers of variable volumes; cooling a fluid medium in the first sub-chamber in order to reduce a pressure in the first chamber, causing the partition member to move to expand the second sub-chamber thereby generating a suction in the second sub-chamber; communicating the second sub-chamber with the first fluid source, thereby extracting the low pressure fluid within the second sub-chamber by means of the suction generated; isolating the second sub-chamber of the first fluid source and then communicating the second sub-chamber with the second fluid source, thereby causing the extracted low-pressure fluid to move to the second fluid source without a change of phase. Additional aspects and advantages of the modalities described are set forth in part in the description that follows and in part are obvious from the description, or can be learned by practicing the described modalities. The aspects and advantages of the described modalities can be achieved and also obtained by means of the instrumentation and combinations indicated in a particular way in the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS The embodiments described are illustrated by way of example, and not by limitation, in the figures of the accompanying drawings, wherein the elements having the same reference numerical designations represent similar elements in all of them and where the elements having the The same numerical reference designations represent similar elements. FIGURE 1 is a schematic diagram of a thermal system according to one embodiment.

FIGURE 2 is a schematic diagram of a fluid pump according to an additional embodiment. FIGURE 3 is a schematic diagram of a fluid pump according to an additional embodiment. FIGURES 4A-4G are cross-sectional views of a fluid pump according to an additional embodiment. FIGURE 5 is a cross-sectional view of a fluid pump according to a further embodiment. FIGURE 6 is a cross-sectional view of a fluid pump according to a further embodiment. FIGURE 7 is a schematic cross-sectional view of a fluid pump according to a further embodiment. FIGURE 8 is a schematic cross-sectional view of a fluid pump according to a further embodiment.

DETAILED DESCRIPTION In the following detailed description, for the purposes of explanation, numerous specific details are set forth in order to provide a full understanding of the modalities. However, it will be evident that the modalities can be implemented without these specific details. In other cases, well-known structures and devices are shown to simplify the drawing. FIGURE 1 is a schematic diagram of a thermal system 1000 in which a fluid pump is used according to the described modes. The system 1000 in one embodiment includes a boiler 001, a motor 1003, and a fluid pump 1007.

The boiler 1001 is a closed vessel in which a working fluid is heated, in one embodiment, under pressure. Water vapor or gases from the heated working fluid, which is now in a high pressure state, is circulated outside the boiler 1001 for use in the engine 1003. The heat source 1002 for the boiler 1001 in a modality can be the combustion of any type of fossil fuels such as wood, coal, oil, natural gas. In a further embodiment, the heat source 1002 may also be solar, electric, nuclear or the like. The heat source 1002 can also be heat rejected from other processes such as automobile exhaust or factory chimneys etc. The motor 1003 is of a type that operates on the heated working fluid. As such, the motor 1003 is a heat engine that converts the energy of the heated working fluid into useful work, for example, through an output mechanism 1006 which may be a crankshaft or an electric generator or the like. The heated working fluid enters the motor 003 through the inlet valve 004 and exits from the motor 1003 through the exhaust or dissipater 1005. During heat transfer from the boiler 1001 to the sink 1005, part of the heat is converted in useful work through the output mechanism 1006. Examples of motor 1003 include, but are not limited to, multi-cylinder continuous flow motors described in the patents and applications listed at the beginning of this specification, especially the patents of the United States of North America Nos. 5,806,403 and 6,505,538. The working fluid used in the described embodiments can be any type of working fluid that is usable in a thermal engine. Examples include, but are not limited to, water, air, hydrogen, helium. In one embodiment, R-134 is used as the working fluid. In a further embodiment, helium is used at approximately 212 ° F. Fluid pump 1007 is provided to forcefully move fluid from work in a low pressure state from heatsink 1005 back to boiler 1001 which is in the high pressure state. As described above, when the Rankine Cycle Cycle is started, a capacitor 1008 (shaded line in FIGURE 1) is connected downstream of the heatsink 1005 to execute a phase change before passing the low pressure working fluid from the heatsink 1005 towards the high pressure level of the boiler 1001. In other words, the low pressure working aqueous vapor in the heatsink 1005 is cooled in the condenser 1008 to the liquid state before being pumped back to the high boiler. pressure to be reheated again to the steam state. Therefore, a large amount of additional heat input is required to reheat the condensed liquid to steam, causing a large amount of loss in the thermal efficiency of the cycle. The fluid pump of the embodiments described hereinafter allows the use of the Stirling Cycle which does not require a phase change. Instead, the vapor of the semi-saturated low pressure fluid in the engine exhaust, ie, in the heatsink 1005, is allowed to pass through the fluid pump 1007., back to the high pressure of the boiler 1001 without a phase change, so that the steam of the working fluid can be used again to drive the motor 1001. Because this occurs by avoiding the aforementioned phase change , the thermodynamic efficiency of the general thermal system 1000 is driven considerably. The fluid pump 1007 according to the embodiments described hereinafter includes Cycling Stirling means for passing steam from the low pressure fluid which accumulates in the engine exhaust, ie the heatsink 1005, back into the level High pressure boiler 1001 without a phase change from low pressure to liquid vapor. However, it will be noted that the fluid pump of the described modalities is not limited to pump only steam; the fluid pump of the described embodiments can pump liquids and / or liquid and vapor mixtures that are frequently found in the engine exhaust 1005. FIGURE 2 is a schematic diagram of a fluid pump 1007 according to one embodiment. The fluid pump 1007 includes a chamber 2101 divided into two sub-chambers 2102, 2103 by means of a displaceable partition member 2104. The first sub-chamber 2102 and the second sub-chamber 2103 are communicable with the boiler 1001 through a controllable opening which, in one embodiment, is closed / opened by the outlet valve 2105. The second sub-chamber 2103 is further communicable with the heatsink or exhaust of the engine 1005 through another controllable opening which, in a , is closed / opened by inlet valve 2106. Valves 2105, 2106 are controlled (shaded line in FIGURE 2) by a valve control mechanism 2107. Fluid pump 1007 also includes a 2008 cooling system for cooling a fluid medium in the first sub-chamber 2102.

As will be described in more detail below, the steam of the low pressure working fluid in the engine exhaust 1005 is sucked into the second sub-chamber 2103. The volume of the sub-chamber 2103 expands with the displacement movement of the partition member 2104. At the rear of the partition member 2104, the high pressure steam from the boiler 1001 has been injected into the first sub-chamber 2102. The high pressure steam injected is then isolated and condensed by the cooling system 2108, creating a suction against the partition member 2104 and, therefore, causing a low pressure suction action from the condenser or engine exhaust 1005 within the second sub-chamber 2103. When the second sub-chamber 2103 is filled with low pressure steam, the second sub-chamber 2103 is isolated then and both the low pressure steam in the second sub-chamber 2103 as the vapor condensed in the first sub-chamber 2102 are open to the high-pressure steam of the boiler 1001. The pressures on both sides of the partition member 2104 are equalized, allowing the partition member 2104 return and compress the second sub-chamber 2103. Thus, a determined volume of the low pressure steam extracted from the engine exhaust 1005 within the second sub-chamber 2103 is replaced by the same volume of the high pressure steam entering the second sub-chamber 2103 from the boiler 001. As a result, a substantial portion of the working fluid in the determined volume of the low pressure steam will be transferred into the high pressure steam side of the boiler 1001. It will be noted that the efficiency of the fluid pump 1007 is determined by = Q1 / (Q1 + Q2) where d = efficiency, Q1 = amount of heat required to raise a given mass of low pressure steam from the condenser or engine exhaust 1005 from its low pressure to the high pressure of boiler 1001, and Q2 = amount of heat required to cool an equivalent mass of the high pressure steam from the boiler 001 which is consumed by the first sub-chamber 2102. In a non-limiting illustrative mode using helium at 212 ° F and the Stirling Cycle, the efficiency is calculated as follows : Ql = fasia * »- lliao0 Q2 = (Usopsi / d-isopsDxCAkziz" - 8 = Q1 / CQH-Q2) =? 1? 212 »- 1-120 ° ÷ Ah.212- ~ lll20-] where d = efficiency, ?? 2 2 - h12o = heat required to raise a given mass helium from 150 psi to 480 psi, Ah2i2 ° -hioo ° = heat consumed to cool an equivalent helium mass from 480 psi to 100 psi, and d48oPs di50ps¡ = helium density ratio to 480 psi and helium density to 150psi . It is useful to mention a well-known characteristic of a high pressure steam, that is, when the steam is cooled, its volume decreases. Notoriously, when the steam is cooled and converted to the liquid state, its volume decreases significantly. Depending on the type of working fluid used as well as its pressure and temperature, the fluid volume of the working fluid can be as low as a few hundred of its volume of steam. A fluid pump operating cycle 1007 will now be described with reference to FIGURE 2. Assuming that the cycle starts with an opening of the outlet valve 2105 (inlet valve 2106 remains closed) which allows high pressure steam from the boiler 1001 fill the first sub-chamber 2102 and the second sub-chamber 2103. The pressures in the first sub-chamber 2102 and the second sub-chamber 2 03 are equalized and, as a result, the partition member 2104 assumes its Initial position as shown in FIGURE 2. Next, the outlet valve 2105 is closed, trapping a quantity of high pressure steam in the first sub-chamber 2102. The cooling system 2108, which functions as a condenser, it cools the steam trapped in the working fluid in order to reduce its volume and therefore the pressure. In one embodiment, the cooling system 2108 is configured to cool the trapped vapor from the working fluid to the liquid state, thereby greatly reducing its volume and hence its pressure within the first sub-chamber 2102. As a result, the partition member 2104 is moved, by means of the pressure difference between the first sub-chamber 2102 and the second sub-chamber 2103, to expand the volume of the second sub-chamber 2103 as shown by arrow A in FIGURE 2. Subsequently, the pressure of second sub-chamber 2103 is reduced due to its volume expansion. In addition, the inlet valve 2106 opens as long as the outlet valve 2 05 remains closed. Since the pressure in the second sub-chamber 2103 has been reduced, due to its volume expansion, a suction force is created in the second sub-chamber 2103 to extract the low pressure steam from the engine exhaust 1005 within the second sub-chamber 2103. It will be noted that although the steam in the exhaust of the engine 1005 is called "low pressure steam", its pressure will be even higher than that in the second sub-chamber 2103 expanded so that the fluid pump 1007 work properly When the inlet valve 2106 is subsequently closed, a quantity of the low pressure steam is trapped in the second sub-chamber 2103. The cycle will now return to the initial stage, that is, with the opening of the outlet valve 2105 as long as that the inlet valve 2106 is kept closed. Again, the high pressure steam from the boiler 1001 will enter and fill the first sub-chamber 2102 and the second sub-chamber 2103. In the second sub-chamber 2103, an exchange occurs. of equal volume, i.e., the trapped volume of the low pressure steam is replaced with the same volume of high pressure steam from the boiler 1001. As described above, said equal volume exchange will move a substantial portion of the steam at low pressure trapped towards the boiler 1001. In the first sub-chamber 2102, incoming high pressure steam will supply the first sub-chamber 2102 with a new high pressure steam charge for the next cycle. The partition member 2104 will move, as shown by arrow B, by means of pressure equalization for the initial position. It will now be understood that the volume reduction of the first sub-chamber 2102 because the working fluid is cooled from the high pressure steam state until the cooled liquid state is the suction driving force sucking the low pressure steam from the condenser heatsink 1005 into the second sub-chamber 2103, as described above. It will now be further understood that the volume sucked from the low pressure of the condenser heatsink 1005 within the second sub-chamber 2103 can be passed into the high pressure boiler by means of a volume exchange action as described above. before. It will be noted that although the high pressure steam trapped in the first sub-chamber 2102 may be, in some embodiments, cooled to the liquid state, i.e. undergoing a phase change, the low pressure steam trapped in the second sub-chamber. chamber 2103 remains substantially in its vapor state without undergoing a phase change. As a result, the working fluid is pumped from the exhaust of the engine 1005 to the boiler 1001 without a change of phase from vapor to liquid, thus saving additional heat that would otherwise be necessary to reheat the liquid cooled to steam from new. In some additional embodiments, the high pressure steam (e.g., helium) trapped in the first sub-chamber 2102 will also be cooled without undergoing a phase change, in which case the vapor cooled in the first sub-chamber 2102 will be discharged in the boiler 1001 in a manner similar to the low pressure steam trapped in the second sub-chamber 2103. In some other embodiments using R-134 as the working fluid, there will be a phase change in the first sub-chamber 2102 for to maximize the suction in the second sub-chamber 2103. It will further be noted that the valves 2105, 2106 and the valve control mechanism 2107 in the above description of the circulation system would function as the closure system of a channel closure. In particular, the high-pressure shut-off valve (outlet valve 2105) closes before the shut-off valve at low pressure (valve input 2106) open and release the load (the low pressure steam from the engine exhaust 005) into the closing chamber (second sub-chamber 2103). Subsequently, the high-pressure shut-off valve (outlet valve 2105) opens after the shut-off valve closes at low pressure (inlet valve 2106), thereby releasing the low pressure steam trapped in the shut-off chamber (second sub-chamber 2103) to the boiler 1001. As in a channel closure, the lower pressure side (engine exhaust 1005) and the high pressure side (boiler 1001) are always isolated from each other. The thermodynamic efficiency of the general thermal system 1000 using a fluid pump according to the modality described above and using the Stirling Cycle is driven considerably compared to the use of the Ranking Cycle. The efficiency of the system is C = W / Q, where the consumption of the motor 1003 is the output of work W and the required heat input is Q. In a very specific example, helium is used as the working fluid to drive the engine 1003 and fluid pump 1007, volume reduction as it passes through the engine and is cooled from, for example, 480 psi to approximately 100 psi is 2,482 times lower. This means that approximately 2.5 times more volume must be pumped back into the boiler 001 in order to maintain a circulating equivalent mass that is consumed by the engine 1003. This means that the displacement of volume caused by the movement of the partition member 2 04 it should be about 2.5 times more than the volume consumed from the boiler 1001 for the motor 1003 in order to pump the equivalent amount of steam back into the boiler 1001. In one embodiment, the cooling medium of the condenser 2108 in the Fluid pump 1007 is water at approximately 57 ° F. The required temperature range will be from 212 ° F to about 70 ° F, representing that the pressure drop will be from about 480 psi to about 80 psi. This temperature drop it will consume 180 Btu / lbm per operation. Therefore, the total heat loss needed to pump the same mass from the exhaust sink 1005 to the boiler 1001 would be 180 Btu / lbm x 2,482 or 447 Btus / lbs plus the addition of the heat that was consumed by the 1003 engine , that is, 142 Btu. The amount of heat that must be added to replenish losses is 447 Btu / lbs plus 142 Btu or a total required heat input of 589 Btu / lbs. Note that the heat loss of the 1003 engine is 142 Btu / lbm, if the engine efficiency is 85% and the efficiency of the fluid pump is 85%, the efficiency of the system C = W / Q, will be ( 142/589) x (0.85) x (0.85) or 17.4%. However, if R-134 is used, the volume reduction as it cools from 500 psi to 200 ° F to 101 psi to 80 ° F will be 7.09 times, representing that the 1007 fluid pump will pump more than 7 times to pass the equivalent amount of the mass used by the motor 1003 during the pressure drop. The enthalpy loss of the 1003 engine is approximately 4.78 Btu / lbm. The heat loss that drives the 1007 fluid pump would be 7.09x5.97 Btu / lbm or 42,327. If the efficiency of the motor is 85% and the efficiency of the fluid pump is 85%, the efficiency of the system for R 34a, C = W / Q, will be (4.78 / 47.11) x (.85) x (. 85) or 7.33%. Even if a conventional Rankine Cycle with regeneration (ie, phase change) is used, it would be difficult to achieve such efficiency, considering that a conventional Rankine Cycle would experience at least a loss of 80 Btu due to the change of vapor state to liquid, through regeneration and heat input. If R-134a is used as the working fluid, a loss of 80 Btu of a conventional Rankine Cycle Cycle compared to a loss of 47.11 with the illustrative fluid pump could achieve an 80 / 47.11 or 170% more efficient system. FIGURE 3 is a schematic diagram of a fluid pump 1007 'according to a further embodiment. The fluid pump 1007 'is similar to the pump fluid 1007 of FIGURE 2, except that an auxiliary boiler 3001 is provided and the controllable outputs of the first sub-chamber 2102 and the second sub-chamber 2103 are now separately controlled. In particular, the common outlet valve 2105 of FIGURE 2 is replaced in the fluid pump 1007 'of FIGURE 3 with two outlet valves 21052 and 21053 for the first sub-chamber 2102 and the second sub-chamber 2103, respectively . The first sub-chamber 2102 is communicable with the auxiliary boiler 3001 through the outlet valve 21052, and the second sub-chamber 2103 is communicable with the boiler 1001 by means of the outlet valve 21053. The valves, i.e. inlet valve 2106 and outlet valves 21052 and 21053, are controlled by valve control mechanism 2107. Although shown in FIGURE 3 that auxiliary boiler 3001 is located within or as part of boiler 1001, auxiliary boiler 3001 can be a separate boiler with the same heat source 1002 or a different heat source. A fluid medium moves through the boiler coil of auxiliary boiler 3001, is heated and vaporized under pressure. Said fluid medium can be the same as or different from the working fluid that is heated by the boiler 1001 and on which the motor 1003 operates. In the particular mode shown in FIGURE 3, the auxiliary boiler 3001 is a boiler coil located within the boiler 1001 and is heated by the same heat source 1002. Therefore, the internal coil boiler 3001 will provide the working pressure for the smaller internal system (cooling system 1008 and the first sub-chamber 2102) that drives the fluid pump 1007 '. The location of this internal coil boiler 3001 within the main coil 1001 ensures that the working temperature will be the same for the working fluid of the boiler 1001 and the fluid medium of the auxiliary boiler 3001. The pressure in the internal boiler boiler 3001, which drives the smaller internal system, in one embodiment, is equal to or greater than the working fluid pressure in the main boiler 1001. However, no Other provisions are excluded. The reason for separating the fluid medium used in the first sub-chamber 2102 and the auxiliary boiler 3001 from the working fluid used in 001, the second sub-chamber 2103 and the motor 1003 is for the control flexibility of, in particular, (1) The parameters of the main working fluid that drives the motor 1003 can be configured / controlled to provide optimum power output capacity, while (2) the parameters of the fluid medium of the lower internal system that drives the fluid pump 1007 'can be configured / controlled independently to provide the optimal expansion and contraction capacity between the temperature parameters with minimum BTU losses. More specifically, the fluid medium of the auxiliary boiler 3001 can be selected or, if it is the same as the working fluid of the boiler 1001, configured to have parameters, such as temperature and / or pressure etc., different from those of the working fluid, to provide the desired volume reduction of the first sub-chamber 2102, and thus, the desired suction force for extracting the low pressure steam from the engine exhaust 1005 within the second sub-chamber 2103 During the operation of the fluid pump 1007 of FIGURE 2, if at least one of the parameters, for example, the temperature and / or pressure, of the working fluid is to be changed, the same parameter of the working fluid in the first sub-chamber 2102 it will be changed accordingly, which would not be desirable since it results in excessive or insufficient suction forces. However, in the fluid pump 1007 'of FIGURE 3, the parameter of the fluid medium in the first sub-chamber 2102 and the boiler auxiliary 3001 does not need to be changed in response to the parameter change in boiler 1001 and motor 1003, or can be controlled independently of the working fluid of the boiler 1001 and the motor 1003 to ensure that desirable and sufficient suction forces are always available in the second sub-chamber 2103. The operation of the fluid pump 1007 ' it is substantially similar to the fluid pump 1007 and will not be repeated here. It is sufficient to note that in the fluid pump 1007 of FIGURE 2, the first sub-chamber 2102 and the second sub-chamber 2103 are simultaneously communicated with the boiler 1001 at the opening of the common outlet valve 2105. However, in the fluid pump 1007 'of FIGURE 3, the outlet valves 21052 and 21053 can be controlled by the control mechanism 2107 to open with a slight delay between them, allowing adjustment of the pumping action of the second sub-unit. chamber 2103 and / or the cooling action of the first sub-chamber 2102. It is within the scope of the present invention to replace both the outlet valve of the first sub-chamber 21052 and the outlet valve of the second sub-chamber 21053 in the fluid pump 1007 'of FIGURE 3 with a common outlet valve, such as 2105 of the fluid pump 1007 of FIGURE 2. Said embodiment simplifies the pump construction, although the fluid medium of the auxiliary boiler 3001 and the fluid of 1001 will be mixed, which may not be desirable in some applications. It will be noted that in the embodiments described above, there are intervals in the operation cycles where the inlet valve 2106 closes. As a result, the low pressure steam is not removed from the engine exhaust 1005 during said intervals. This may not be desirable, especially in a multi-cylinder engine described, for example, in the aforementioned patents and applications, where one of the cylinders is always in the downward stroke and releases the low pressure steam towards the exhaust of the cylinder. 1005 engine. therefore, it is desirable to provide a fluid pump that substantially pumps the low pressure steam from the engine exhaust 1005 to the high pressure level of the boiler 1001. FIGURES 4A-4G show said fluid pump. Specifically, FIGURES 4A-4G are cross-sectional views of fluid pump 400 in operation. The fluid pump 400 includes two similar halves divided by imaginary center 401. Each half corresponds to one of the fluid pump 1007 described above in relation to FIGURE 2. In other words, the fluid pump 400 includes two pumps of 1007 similar fluid that work in tandem.

More specifically, as shown in FIGURE 4A, the fluid pump 400 includes a chamber 402 which, in turn, includes two halves 101, 102. Each half 101, 102 is divided by a mobile partition member 103. , 104, respectively, in first sub-chamber 105, second sub-chamber 107, third sub-chamber 108, and fourth sub-chamber 106. The sub-chambers have variable volumes due to the displacement of the respective partition members 103, 104 In this embodiment, the partition members 103, 104 are diaphragms which are fixed at opposite ends 4103A, 4103B, 4004A and 4104B to the wall of the chamber 402. The partition members 103, 104 correspond to the partition member 2104 of the fluid pump 1007. A plurality of tubes 109, 110 containing water, air or any other suitable cooling means are placed on opposite sides of the chamber 402 and in thermal contact with the first sub-chamber 105 and fourth sub-chamber 106 what corr sponde to the first sub-chamber 2102 of the fluid pump 1007. The tubes 109, 110 play the role of cooling system or condenser 2108. The second sub-chamber 107 and the third sub-chamber 108 are equivalent to the second sub-chamber. - chamber 2103 of the fluid pump 1007. The upper portions of the second sub-chamber 107, third sub-chamber 108 they have controllable openings 4107, 4108 that are alternately opened / closed by a common inlet valve 111. The inlet valve 111 includes a valve body 112 slidable within a valve housing 4111 and having a reduced cross-sectional portion 113. The reduced cross-sectional portion 113, when aligned with the opening 4107 or 4108 will open the opening and will communicate the second sub-chamber 107 or third respective sub-chamber 108 with the exhaust of the motor 1005. As can be seen in FIGS. 4A-4G, at least one of the openings 4107, 4108 is in fluid communication with the exhaust of the engine 1005 at all times, thereby ensuring the substantially continuous pumping of the low pressure steam from the exhaust of the engine 1005. The inlet valve 111 plays the role of the inlet valve 2106 of the fluid pump 1007. The valve body 112 further includes through holes 118, 119 at opposite ends thereof. The holes 118, 119 will be described hereinafter with reference to other figures. The lower portions of the second sub-chamber 107, third sub-chamber 108 have controllable openings 4107 ', 4108' which are opened / closed by the outlet valves 121, 122, respectively. Each of the outlet valves 121, 122 includes a valve body 123, 124 slidable within a valve housing 4121, 4122, and having a reduced cross sectional portion 125, 126. The reduced cross section portion 125, 126, when aligned with the respective opening 4107 ', 4108' will open the opening and communicate the second sub-chamber 107 or third respective sub-chamber 108 with the boiler 1001. The outlet valves 121, 122 correspond to the outlet valve 2105 of the fluid pump 1007. The valve body 123, 124 further includes through holes 129, 130 in end portions thereof. The outlet valves 121, 122 each comprise a return spring 131, 132 to close the outlet valves shortly after opening. The holes 129, 130 and springs 131, 132 are they will describe hereinafter with reference to other figures. The upper portions of the first sub-chamber 105, fourth sub-chamber 106 are sealed by the placement of the ends 4103A, 4104A of the respective partition members 103, 104 in the wall of the chamber 402. The lower portions of the first sub-chamber 105, fourth sub-chamber 106 have controllable openings 4105, 4106 which are also open / closed by the outlet valves 121, 122, respectively. The reduced cross-sectional portion 125, 126, when aligned with the respective opening 4107 ', 4108', will also be aligned with the openings 4105, 4106 of the first sub-chamber 105, fourth sub-chamber 106 to communicate simultaneously both the first sub-chamber 105, the second sub-chamber 107 to the boiler 1001 and the fourth sub-chamber 106, the third sub-chamber 108 with the boiler 1001. Other arrangements are not excluded. Each of the partition members 103, 104 is connected to a control valve 140 by means of ropes 143, 144 to activate the control valve 140 and will be described hereinafter. The control valve 140 includes a valve body 141 slidable within a valve housing 4140, and having a reduced cross section portion 142. The reduced cross section portion 142, when located in one of the first conduit 154 and the Second duct 155 extends through valve housing 4140, will open said duct and close the other. Therefore, only one of the first duct 154 and the second duct 155 will open at the same time. Each of the first duct 154 and the second duct 155 communicates the high pressure level of the boiler 1001 to one of the opposite sides 114, 115 of the inlet valve 111 when the control valve 140 is in the respective open position, and the outlet valves 121, 122 are in the closed position that aligns the first duct 154, the second duct 155 with the respective holes 129, 130, as shown in FIGURE 4 A. The first duct 154, 155 further communicates the high pressure level of the boiler 1001 to one of the outlet valves 121, 122 through the respective orifice 118, 119 of the valve body 112 when the respective orifice is aligned, through the movement of the inlet valve 111, with the first duct 154, or second duct 155. In FIGURE 4 A, the second duct 155 is shown to communicate the high pressure level of the boiler 1001 to the outlet valve 122 through the orifice 119. The operation of the fluid pump 400 will now be described with reference to FIGS. 4A-4G. It will be noted that at least the last stage, Step 7 (FIGURE 4G), is a return to the first Stage 1 (FIGURE 4A) of the cycle.

Step 1 As shown in FIGURE 4A, both outlet valves 121 and 122 between the chambers 101 and 102 and the boiler 1001 are closed. The reduced cross-sectional portion 113 of the inlet valve 1 1 communicates the engine exhaust 1005 and the second sub-chamber 107. The opening 4108 of the third sub-chamber 108 is closed by the inlet valve 111 to disconnect the exhaust of the motor 1005 of the third sub-chamber 108. With the left chamber 101, the diaphragm 103 is shown extended to the left. The open volume of the second sub-chamber 107 to the right of the diaphragm 103 will be filled with the low pressure steam 120 which was sucked from the exhaust of the motor dissipator 1005. The fluid medium, in this case the working fluid of the boiler 1001, in the first sub-chamber 105 on the left side of the diaphragm 103 has been cooled to its desirable lower volume using the water cooling condenser system 109 in the left wall of the left fluid pump chamber 101. It will be observed again that, in this particular modality, that each of the valves 111, 121 has a channel valve or through-hole 118, 119, 129 and 130 designed inside it which, it opens only when the respective valve 111, 121 and 122 moves to its closed position. This is true with the two outlet valves 121 and 122 which are completely independent of one another. This is also true with the upper double inlet valve 111, which is a single unit, opens and closes the openings 4107, 4108 in tandem. Following the path of each of the first duct 54 and the second duct 155 and its tube sections 152, 153, 154, 155, 116, and 117 as it flows from the boiler 1001 to the respective pneumatic valves 111, 121, 122 , it will be understood how each channel valve or through-hole 118, 119, 129 and 130 accesses the high pressure steam from the boiler 1001 to open / close the respective valves 111, 121 and 122. Returning now to FIGURE 4A, as shown in FIG. established earlier, the outlet valves 121, 122 are closed while their channel valves 129, 130 are open. The high pressure steam 138 is allowed to pass through the left channel valve 129 of the outlet valve 121 and then through the left opening of the diaphragm activated control valve 140 in the center of the device. This control valve 140 was opened earlier when the left diaphragm 103 was extended to its left.

With respect to each respective chamber 101 and 102, each outlet valve 121 and 122 must always be closed when the respective side of the upper tandem inlet valve 111 is open, due to the low pressure steam 120 which is fed from the exhaust of the motor 1005 within the respective second sub-chamber 107 and the third sub-chamber 108 must be captured therein before the captured volume can be discharged into the high-pressure boiler 1001. Again, it will be noted that the Valve system in the modalities described herein functions as the closure system of a channel closure.

In FIGURE 4A, because the left side of the upper inlet valve 11 (that is, the opening 4107) is open, the respective valve channel 118 is closed. Therefore, the section 151 of the first duct 154 leading past the inlet valve 111 can not access the pressure of the boiler 138 to open the lower left outlet valve 121 between the boiler 1001 and the second sub-chamber 107. The diaphragm 103 is fully extended to the left allowing the volume of the second sub-chamber 107 to the right to be completely filled with the low pressure vapor 120 from the exhaust of the heatsink heatsink 1005. This action of the left diaphragm 103 occurs , due to the suction caused on the left side of the diaphragm 103 (i.e., the first sub-chamber 105). In particular, the hot working fluid injected from the boiler 1001 (or as will be described hereinafter in a dual fluid pump from the internal coil boiler 237) is cooled by the water or air cooling condenser 109 Note that, in the upper tandem input valve 111, the left side is open between the exhaust of the motor heatsink 1005 and the second sub-chamber 107, allowing the low pressure steam 120 from the exhaust heatsink 005 to flow towards the second sub-chamber 107. Also note that, when the diaphragm 103 in the left chamber 101 is extended completely to the left, it opens by pulling (through the connection of the rope 143) the valve activated by diaphragm 140 in the center of the fluid pump. Because the channel opening 129 of the pneumatic outlet valve 121 is open and the first duct 154 is opened through the control valve 140, the upper inlet valve 111 is susceptible to receiving the pressurized vapor 138 from the boiler 1001 acting on the left side 114 of the upper inlet valve 111, causing the upper inlet valve 111 to slide to the right, thus closing the left side (i.e., opening 4107) of the tandem input valve 111. This leads to Step 2.

Step 2 FIGURE 4B shows that the boiler pressure 138 acting on the left side 114 of the upper inlet valve 111, forces the inlet valve 111 to slide to the right, has therefore opened the right side (i.e. the opening 4108 of the third sub-chamber 108) to communicate the exhaust of the engine 1005 with the third sub-chamber 108, insulating the second sub-chamber 107 of the left chamber 101 of the engine exhaust 1005. Meanwhile, the two lower exit valves 121 and 122 remain closed. At this point, the low pressure steam in the second sub-chamber 107 extracted from the exhaust of the motor heatsink 1005 in the Stage has been isolated. On the other hand, the third sub-chamber 108 of the right chamber 102 is now accessed for the low pressure steam 120 from the exhaust of the motor heatsink 1005. Before, the pressure in the fourth sub-chamber 106 on the right side of the diaphragm 104 was equal to or greater than the pressure in third sub-chamber 108. This allowed diaphragm 104 to return to its natural non-extended position, as shown in FIGURE 4B. The diaphragm 104 in the right chamber 102 is not shown to have moved negligibly to the right. Of course, the stretch in the right diaphragm 104 may have already started due to the high pressure steam already injected from the boiler 1001 or from the internal coil boiler 237 it would have already begun to cool. The cooling action is caused by the condensing coil 110 located on the outer wall of the right chamber 102. The lower left exit valve 121 is opened when the boiler pressure 138, accessed through the channel valve 129 located in the bottom outlet valve 121, via the first duct 154 opened by the valve driven by diaphragm 140, and through the channel valve 118 located in the upper inlet valve 111, and the tube section 151, acts on the end portion 127 of the valve exit 121. This leads to Stage 3.

Step 3 FIGURE 4C shows that the lower left exit valve 121 is newly opened. The lower outlet valve 121 will open only a few moments, just long enough to allow pressures on both sides of the diaphragm 103, i.e., in the first sub-chamber 105 and the second sub-chamber 107, to equalize that the diaphragm 103 can be retracted into its natural position, and so that the low pressure vapor 120 previously collected from the exhaust of the motor 1005 that was collected in the second sub-chamber 107 is mixed with the high pressure steam of the boiler 1001, thus forcing almost all the mass of the working fluid out of the second sub-chamber 107 into the boiler 1001. The channel port or hole 129 of the lower left outlet valve 121 is immediately closed when it is opened the outlet valve 121. This action will cut the boiler pressure 138 which is keeping the lower left outlet valve 121 in its open position. As the high pressure 138 captured in the first duct 154 cools, it will decrease in volume, allowing the return spring 131 in the lower left outlet valve 121 to close the outlet valve 121. As the pressures on both sides of the diaphragm 103, that is, in the first sub-chamber 105 and the second sub-chamber 107, are equalized by allowing the diaphragm 103 to return to its natural non-extended position, the third sub-chamber 108 of the right chamber 102 is filled with the low pressure steam 120 from the exhaust of the motor sink 1005 through the suction action as the boiler steam, which was injected into and trapped in the fourth sub-chamber 106 in Step 2, is cooled by the condenser 110.

Step 4 In FIGURE 4D, the diaphragm 104 in the right chamber 102 pulls the valve operated by diaphragm 140 to open the second duct 155, which initiates the same action in the right chamber 102 that has occurred in the left chamber 101 as shown in FIG. described earlier.

Step 5 In FIGURE 4E, the high pressure boiler 139 is now accessed through the channel 130 of the outlet valve 122, the second duct 155 opened by the control valve activated by diaphragm 140, to the right side 115 of the upper inlet valve 111, pushing the inlet valve 111 to the left, thereby closing the right side (i.e., opening 4108) and opening the left side (i.e., opening 4107) of the upper inlet valve 111 between the exhaust of the motor heatsink 1005 and the second sub-chamber 107. The outlet valve 122 is opened when the boiler pressure 139, accessed through the channel valve 130 located in the lower outlet valve 122, via the second duct 155 is opened by diaphragm-operated valve 140, and through channel valve 119 located in upper inlet valve 111, and tube section 150, acts on end portion 128 of the outlet valve 122. This leads to Stage 6.

Step 6 In FIGURE 4F, the outlet valve 122 has recently opened, so that the third sub-chamber 108 can discharge its captured low pressure vapor, which comes from the exhaust of the engine sink 1005 in Stage 4 and was caught in Step 5, within the boiler 1001. The right diaphragm 104 moves back to its natural position as the pressure on each side of the diaphragm 104, that is, in the fourth sub-chamber 106 and the third sub-chamber. Camera 108, be nice. As the diaphragm 104 returns to its natural position, the low pressure steam collected in the third sub-chamber 108 is mixed with the high pressure steam from the boiler 1001 and discharged into the boiler 1001. The outlet valve 122 It will open only temporarily as described in relation to Stage 3..

Step 7: Step 7 is a return to Step 1. In FIGURE 4G, the lower right outlet valve 122 closes as the steam boiler 139 trapped in the second duct 155, which is closed by the control valve 140 activated. by the diaphragm 103, it cools and condenses, allowing the spring 132 to push the outlet valve 122 to the left and to the closed position. The fluid pump 400 is now back in its position from Step 1, as shown in FIGURE 4A. In summary, the low pressure steam 120 from the exhaust of the continuous flow motor 1005 is pumped by the fluid pump 400 into the high pressure boiler 1001 without a phase change. This pump 400 uses suction means driven by the cooling of a hot steam from a fluid medium to create a smaller volume. This fluid medium is located in the first external sub-chamber 105 and the fourth sub-chamber 106 behind the two diaphragms 103, 104 and next to the cooling coils 109, 10. A displacement of volume in the fluid medium cooled in the first sub-chamber 105, fourth sub-chamber 106 behind the diaphragms 103 and 104 will cause the suction of the low pressure steam 120 from the exhaust 1005 of the engine 1003 inside. of the respective second sub-chamber 107, third sub-chamber 108, the fluid pump 400. This suction is caused when the fluid medium (such as helium, or R134a) cools and contracts in a smaller volume, which in an embodiment it can be a liquid volume, which must be passed after returning to the boiler 1001. After the second sub-chamber 107 or third sub-chamber 108 is filled with the low pressure steam 120, the low pressure steam is isolated and discharged into the boiler 1001. It will be noted that the fluid pump 400 of FIGURES 4A-4G corresponds to the individual working fluid mode described with respect to FIGURE 2. It is within the scope of the present invention to provide a A further fluid pump that is similar to the fluid pump 400 and corresponds to the double working fluid motor described with respect to FIGURE 3. An example of said additional fluid pump is illustrated in FIGURE 5. Specifically, the FIGURE 5 is a cross-sectional view of fluid pump 500 in a state similar to Step 6 of the fluid pump 400 shown in FIGURE 4F. The fluid pump 500 is similar to the fluid pump 400 and similar reference numbers denote similar elements. The main differences between the fluid pump 400 and the fluid pump 500 include the internal winder reel 237 and the configuration of the reduced cross section portion of the outlet valves 121, 122. In particular, the inner winder reel 237 performs the role of the auxiliary boiler 3001 of FIGURE 3. The fluid medium of the internal winder coil 237 may be the same as or different from the working fluid of the boiler 1001. The internal structure of the chamber 402 now includes extension walls 581 and 582 that isolate the fluid medium from the inner winder reel 237 from the working fluid of the boiler 1001. The openings 233, 234 are formed in the extension walls 581, 582 to communicate the internal winder reel 237 only with the first sub-chamber 105, the fourth sub-chamber 106, and not with the second sub-chamber 107 or the third sub-chamber 108. The extension walls also insulate the boiler 1001 from the first sub-chamber 105 and fourth sub-chamber 106, ensuring that the fluid medium of the internal coiler coil 237 and the working fluid of 1001 will not mix, upon entering the "incorrect" sub-chambers. In addition, the individual reduced cross section portion 125, 126 of the outlet valves 121, 122 of the fluid pump 400 has been changed to each include two reduced cross section potions 225 a, 225 b and 226 a, 226 b. The reduced cross-sectional portions 225a, 226a, when aligned with the respective lower openings of the first sub-chamber 105, fourth sub-chamber 106 will allow the fluid medium to enter the first sub-chamber 105, fourth sub-chamber 106 from the coil of the internal coiler 237, as indicated by the double-headed arrow Z in FIGURE 5. Similarly, the reduced cross-sectional portions 225b, 226b, when aligned with the respective lower openings of the second sub-chamber 107, third sub-chamber 108, will allow the working fluid to enter the second sub-chamber 107. , the third sub-chamber 108 from the boiler 1001, as indicated by the individual head arrow W in FIGURE 5. The reduced cross section portions 225a, 226a now play the role of the valve 21052 of FIGURE 3 , while the reduced cross section portions 225b, 226b correspond to the valve 2 053. The operation of the fluid pump 500 is similar to the fluid pump 400 and is not will repeat here. Suffice it to note that in the stages similar to Steps 3 and 6 of the fluid pump 400 (FIGURES 4C and 4F) instead of the working fluid of the boiler 1001 as described with respect to the fluid pump 400, the medium Fluid from the inner winder coil 237 will enter the first sub-chamber 105, fourth sub-chamber 106 to provide the sub-chambers with new high-pressure steam loads, and equalize the pressures between the first sub-chamber 105, second sub-chamber 107 adjacent and between the fourth sub-chamber 106, third sub-chamber 108 adjacent. In one embodiment, the new high pressure vapor from the fluid medium entering the first sub-chamber 105, fourth sub-chamber 106 from the internal coiler coil 237 may be at a higher pressure than the working fluid entering the second. sub-chamber 107, third sub-chamber 108 from the boiler 1001. As a result the diaphragms 103, 104 will move back towards and beyond the neutral position, as the first sub-chamber 105, fourth sub-chamber 106 expands and the second sub-chamber 107, third sub-chamber 108 contracts. This volume contraction of the second sub-chamber 107, third sub-chamber 108, will move a larger mass of the high-pressure steam trapped from the second sub-chamber 107, third sub-chamber 108 to the boiler 1001. In addition, the greater Pressure of the fluid medium supplied by the internal winder reel 237 will ensure that, upon adequate cooling, a greater suction force will be supplied to extract a greater quantity of the low pressure steam from the exhaust of the engine 1005 within the second sub-chamber 107 , third sub-chamber 108.

However, it is within the scope of the present invention to provide the fluid medium with a lower working pressure than the working fluid of the boiler 1001, depending on the application. FIGURE 6 is a cross-sectional view showing a fluid pump 600 in accordance with an additional embodiment. The fluid pump 600 is similar to many aspects to the fluid pumps 400 and 500, except that the diaphragms 103, 104 are now replaced by the pistons 303, 304, diversion springs 601, 602 are added, and the condenser coils now operate within the first sub-assembly. chamber 105, fourth sub-chamber 106 instead of the wall of chamber 402. it is within the scope of the present invention to provide fluid pumps that include less than three of the changes listed above. The piston rings 661, 662 are provided to hermetically isolate the first sub-chamber 105 of the second sub-chamber 107, and the fourth sub-chamber 106 of the third sub-chamber 108. The pistons 303, 304 may be free pistons. , which represents that their movements are determined only by the pressure difference between the adjacent sub-chambers, i.e., 105, 107 and 106, 108. In this arrangement, the pistons operate in a manner similar to the diaphragms 103, 104. However, the pistons 303, 304 may also be urged or biased by the biasing springs 601, 602. The biasing springs 601, 602 deflect the respective pistons 303, 304 towards the center of the device, i.e. they comprise the second sub-chamber 107, and the third sub-chamber 108. This arrangement will have an effect similar to the effect of the overpressured fluid medium described above with respect to the fluid pump 500, ie the pistons Deviated will further comprise the second sub-chamber 107, third sub-chamber 108 respectively in the stages similar to Steps 3 and 6 of the fluid pump 400 (FIGURES 4C, 4F) to move a larger mass of the vapor at high pressure trapped from the second sub-chamber 107, third sub-chamber 108 respectively towards the boiler 1001. In a mode shown illustratively in FIGURE 6, the volume of the third sub-chamber 108 is maximally compressed by the spring 602, ejected from the forced way a substantial portion, if not all, the working fluid vapor out of the third sub-chamber 108 and within the boiler 1001. As a result, any residual pressure left in the third sub-chamber 108 after the closing of the outlet valve 122 will be minimal, and the probability that the vapor will be significantly reduced residual flow back into the condenser or motor exhaust 1005 to the opening of the upper opening 4108 of the third sub-chamber 108 by means of the inlet valve 111. Finally, the arrangement of the capacitor coils 309, 310 within the first sub-chamber 105, fourth sub-chamber 106 will improve the cooling effect. The presence of the divert springs 601, 602 will also prevent the pistons 303, 304 from colliding and subsequently damaging the capacitor coils 309, 310. The operation of the fluid pump 600 is similar to the fluid pumps 400, 500 and not it will be repeated here. It will be noted that the fluid pump 600 can be modified to use separate working fluids for cooling the sub-chambers, ie, the first sub-chamber 105, the fourth sub-chamber 106, and for pumping the sub-chambers, that is, the second sub-chamber 107, and the third sub-chamber 108. FIGURE 7 is a schematic cross-sectional view of a fluid pump 700 in accordance with an additional embodiment, In the fluid pump 700, the valves pneumatically activated actuators described above, such as 111, 121, 122, are replaced by electrically activated valves 71, 721, 722. Further, the control valve 140 and the first duct 154, second associated duct 155 are omitted and the mechanism function valve control 2107 is executed by an electronic controller 799 which is programmed wired to suitably control the closing / opening of the valves 711, 721, 722. In particular, each of the valves 711, 721, 722 now includes an element magnetically attractable, for example, 781, attached to its valve body, for example, 112. Each valve further has an electro-magnetic coil, for example, 782 for interaction with the magnetically attractable element 781. The current flowing into the coil 782 is controlled by the 799 controller through suitable cables. The coil 782 can attract and repel the magnetically attractable element 781, in which case the return springs, for example 4122, 4121, can be omitted. However, if the coil 72 can only attract (or repel) the magnetically attractable element 781, said return springs will be required to return the respective valve to the original position. Although the valves 711, 721, 722 in the fluid pump 700 were described above as being magnetically driven, other arrangements in which the valves are driven mechanically and / or electrically, for example by means of motors, are not excluded. The channel closure control principles described above for controlling the valves are also applicable to the controller 799. In particular, the controller 799 is programmed or wired so as not to open both inlet and outlet valves of each of the second sub-chamber 107 , and the third sub-camera 108 at the same time. In addition, the timing for the opening of each valve is synchronized with the positions of the respective partition member or piston 303, 304. For example, the leftmost position of the piston 303, which corresponds to the activation of the control valve 140 and the subsequent closure of the upper opening of the second sub-chamber 107 in the fluid pump 400 (FIGURES 4A, 4B), is used in the fluid pump 700 to activate the controller 799 in order to move the inlet valve 711 accordingly, thereby closing the upper opening of the second sub-chamber 107. For this purpose, an electrical contact switch 792 is provided. and a corresponding probe 191 on the wall of the chamber 402 and the piston 303, respectively. When the probe 791 contacts the respective electrical contact switch 792 in the far left position of the piston 303, the electrical contact switch 792 is activated and the signal controller 799, which is the time, is caused to close the upper opening 4107 of the second sub-chamber 107. In additional embodiments, a position sensor that is magnetic and / or optical and / or mechanically activatable and located outside the leftmost position of the piston 303 can be used as an alternative for the switch / probe arrangement. In the pneumatic valves 121, 122, closing of the valves is effected by means of the return springs 4121, 4122 which overcome the high pressure of the working fluid which is trapped in the first duct 154, second duct 155 respectively and starts to cool down The closing timing of the valve therefore depends on the parameters of the high pressure steam of the working fluid and on how fast the trapped working fluid vapor cools down. This introduces some uncertainty in the operation of pneumatic valves. In contrast, the controller 799 can synchronize the exact time during which the outlet valves 121, 122 can be opened, using an internal or external synchronizer that will start counting to the opening of the respective outlet valves. As described above, the outlet valves of the first sub-chamber 105 and the second sub-chamber 107, as well as the outlet valves of the fourth sub-chamber 106 and the third sub-chamber 108, can be controlled and activated. independently. This can be done in a fluid pump similar to the fluid pump 700 with each of the outlet valves 721, 722 which closes only the outputs of the second sub-chamber 107, third sub-chamber 08, and the additional outputs that are added to be controlled by the 799 controller and close only the outputs of the first sub-camera 105, fourth sub-camera 106. Thus, the outputs of, for example, the first sub-camera 105 and the second sub-camera 107, can be opened in different synchronizations, instead of simultaneously. For example, the outlet valve 721 of the second sub-chamber 107 can be opened first to discharge most of the mass of the low pressure steam trapped towards the boiler 1001, and then the output valve controlled independently (not shown) of the first sub-chamber 105 is opened to push, by pressure action of the high-pressure steam of the boiler 1001 or the inner winder coil 237 plus the spring action of the bypass springs 601, the respective piston 303 to its rightmost position, thus ejecting all the working fluid from the second sub-chamber 107 into the boiler 1001. The delay between the opening of the outlet valves of the first sub-chamber 105 and the second sub-chamber 107 can be easily configured / controlled / adjusted by controller 799. It is within the scope of the present invention to provide a fluid pump with more than two pump arrangements. a associated (such as 101, 102, described above with respect to the fluid pump 400) each corresponding to one of the configurations shown in FIGURES 2-3. In a multi-pump arrangement configuration, controller 799 can be programmed or wired to regulate the closing and opening of valves of all arrangements as a centralized valve control. FIGURE 8 is a schematic cross-sectional view showing a compact configuration of a fluid pump 800 according to a further embodiment. The fluid pump 800 of FIGURE 8 is similar to the fluid pump 600 of FIGURE 6, and shows the inlet and outlet valves 111, 121, 122 as viewed along its axial direction. As you can see in FIGURE 8, the valves are located adjacent to the respective openings of the respective sub-chambers, thus resulting in a compact configuration. It is within the scope of the present invention to place the valves of the fluid pump 700 of FIGURE 7 in the manner shown in FIGURE 8 in order to provide a compact fluid pump (not shown) using an electronic controller. While the foregoing description shows illustrative modalities, it will be appreciated that various changes and modifications may be made herein without departing from the scope of the described embodiments as defined in the appended claims. In addition, although the elements of the modalities described can be described or claimed in the singular, the plural is considered unless the limitation to the singular is explicitly established.

Claims (26)

1. A fluid pump for moving a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the fluid pump characterized in that it comprises: a chamber; a partition member movable in the chamber and dividing the chamber into first and second sub-chambers of variable volumes; the first sub-chamber having an opening controllably communicable with the second fluid source or a third fluid source; the second sub-chamber having inlet and outlet openings controllably communicable with the first and second source of fluids, respectively; and a cooling element for cooling a fluid in the first sub-chamber.

2. The fluid pump according to claim 1, further characterized in that the pump is a steam pump that uses the Stirling Cycle to forcefully move the vapor at low pressure of said fluid from the first fluid source to the second. fluid source without a vapor-liquid phase change.

3. The fluid pump according to claim 1, further characterized in that the cooling element operatively cools the fluid in the first sub-chamber, thereby reducing the fluid pressure in the first sub-chamber and causing the partition member moves to the first sub-chamber and to create a suction in the second sub-chamber to extract the low pressure fluid from the first fluid source into the second sub-chamber when the inlet opening of the second sub-chamber is operationally open; and when the entry opening of the second sub-chamber is operatively closed, the outlet opening of the second sub-chamber is operatively open to move the low pressure fluid from the second sub-chamber within the second fluid source.

4. The fluid pump according to claim 1, further characterized in that the partition member is a moving diaphragm by means of a pressure difference between the sub-chambers.

5. The fluid pump according to claim 1, further characterized in that the partition member is a free piston that moves only by means of a pressure difference between the sub-chambers or a piston diverted to the second sub-chamber. .

6. The fluid pump according to claim 1, further characterized in that the opening of the first sub-chamber is communicable with the second fluid source; and when the opening of the first sub-chamber and the exit opening of the second sub-chamber are operatively open and the entrance opening of the second sub-chamber is operatively closed, the fluid pressures in the sub-chambers are equalized with the fluid pressure of the second fluid source, thereby moving the partition member to the second sub-chamber.

The fluid pump according to claim 1, further characterized in that the opening of the first sub-chamber is communicable with a third source of fluid isolated from the second fluid source; and when the opening of the first sub-chamber and the outlet opening of the second sub-chamber are operatively open and the entrance opening of the second sub-chamber is The chamber is operatively closed, a difference in fluid pressure in the sub-chambers is such that the partition member is moved towards the second sub-chamber.

The fluid pump according to claim 1, characterized in that it further comprises valves for controllably closing and opening the inlet and outlet openings of the second sub-chamber and the opening of the first sub-chamber.

9. The fluid pump according to claim 8, further characterized in that at least one of the valves is driven by the fluid pressure of at least one of said fluid sources.

10. The fluid pump according to claim 8, further characterized in that at least one of the valves is driven independently of the fluid pressures of said fluid sources, and in at least one of the dielectric, magnetic, and mechanical ways.

11. A fluid pump for moving a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the fluid pump comprising: first and second cameras; a first partition member movable in the first chamber and dividing the first chamber into first and second sub-chambers of variable volumes; a second partition member movable in the second chamber and dividing the second chamber into third and fourth sub-chambers of variable volumes; each of the first and fourth sub-chambers having an aperture controllably communicable with the second fluid source or a third fluid source; each of the second and third sub-chambers having inlet and outlet openings controllably communicable with the first and second source of fluids, respectively; and a cooling element for cooling a fluid in the first and fourth sub-chambers, thereby reducing fluid pressures in the first and fourth sub-chambers and creating suctions in the second and third sub-chambers, respectively, to extract the low pressure fluid from the first fluid source within the second and third sub-chambers, respectively; characterized in that the first fluid source is at all times in fluid communication with at least one of the second and third sub-chambers through the respective inlet openings, whereby the low pressure fluid is extracted in a manner substantially continues outside the first fluid source.

The fluid pump according to claim 11, characterized in that it further comprises an inlet valve for alternately closing the inlet openings of the second and third sub-chambers; the inlet valve which is movable between a first position, in which the inlet valve opens the inlet opening of the second sub-chamber and closes the inlet opening of the third sub-chamber, and a second position, in the which the inlet valve closes the inlet opening of the second sub-chamber and opens the inlet opening of the third sub-chamber.

The fluid pump according to claim 12, further characterized in that the first and second partition members are operatively coupled to control the inlet valve, thereby closing the inlet openings of the second and third sub-chambers, respectively, when the second and third sub-chambers have expanded to a predetermined volume defined by the displacement of the first and second partition members, respectively, to the first and fourth sub-chambers, respectively.

14. The fluid pump according to claim 13, further characterized in that the inlet valve is operatively coupled to control the outlet valves in the outlet opening of the second and third sub-chambers, thereby opening the respective outlet valves of the second and third sub-chambers after closing the respective inlet openings of the second and third sub-chambers.

15. The fluid pump according to claim 14, characterized in that it further comprises a control valve for alternately closing the first and second ducts communicating the second fluid source to opposite sides of the inlet valve; the control valve that is operatively coupled to the partition members; when the second sub-chamber has expanded to the predetermined volume, the control valve is moved by means of the first partition member to a third position in which the control valve opens the first duct and closes the second duct, accessing in this way the fluid pressure from the second fluid source only towards one of the opposite sides of the inlet valve and, therefore, moving the inlet valve from the first position to the second position to close the inlet opening of the inlet valve. the second sub-chamber and opening the entrance opening of the third sub-chamber; and when the third sub-chamber has expanded to the predetermined volume, said control valve is movable by means of the second partition member to a fourth position in which the control valve opens the second pipe and closes the first pipe, accessing in this way the fluid pressure from the second fluid source only towards the other of the opposite sides of the inlet valve and, therefore, moving the inlet valve from the second position to the first position for closing the entrance opening of the third sub-chamber and opening the entrance opening of the second sub-chamber.

16. The fluid pump according to claim 15, further characterized in that when the inlet valve is in the second position, the inlet valve communicates the first duct to a third duct leading to the outlet valve of the second sub-chamber, thereby accessing the fluid pressure of the second fluid source through the control valve, towards the first duct and the third duct to open the outlet valve of the second sub-chamber which, in turn, causes the low pressure fluid trapped in the second sub-chamber to be moved to the second source of fluid; and when the inlet valve is in the first position, the inlet valve communicates with the second duct to a fourth duct leading to the outlet valve of the third sub-chamber, thereby accessing the fluid pressure of the second one. fluid source through the control valve, the second duct and the fourth duct to open the outlet valve of the third sub-chamber which, in turn, causes the low pressure fluid trapped in the third sub-chamber camera is moved to the second source of fluid.

17. The fluid pump according to claim 16, further characterized in that when the outlet valve of the second sub-chamber is opened, the opening of the first sub-chamber is also opened, thereby replacing the cooled fluid in the first sub-chamber with a new fluid load at a higher temperature and / or pressure and causing the first partition member to move into the second sub-chamber; Y when the outlet valve of the third sub-chamber is opened, the opening of the fourth sub-chamber is also opened, thus replacing the cooled fluid in the fourth sub-chamber with a new fluid load at a higher temperature and / or pressure and causing the second partition member to move into the third sub-chamber.

18. The fluid pump according to claim 17, characterized in that it further comprises return mechanisms for closing the outlet openings of the second and third sub-chambers and the openings of the first and fourth sub-chambers after a predetermined time.

19. The fluid pump according to claim 18, further characterized in that the control valve is connected to the partition members by cords, the return mechanisms comprise cords, and the inlet and outlet valves comprise pneumatically activated valves.

20. The fluid pump according to claim 9, further characterized in that the first and second partition members are deflected pistons for compressing the second and third sub-chambers, respectively.

21. The fluid pump according to claim 14, characterized in that it further comprises at least one sensor for alternatingly generating an electrical signal upon sensing that the second and third sub-chambers have expanded to the predetermined volume; an electronic controller coupled to control the inlet valve and the outlet valves, and which operatively responds to the signal to alternately close the inlet openings of the second and third sub-chambers to trap the low pressure fluid withdrawn from the first fluid source in the second and third sub-chambers; Y a synchronizer for causing the controller to alternately open the exit openings of the second or third sub-chambers after a predetermined time, the time that has elapsed since the closing of the respective inlet openings, thereby moving the fluid low pressure trapped to the second fluid source;

22. The fluid pump according to claim 21, further characterized in that the controller is further operable to alternately open the openings of the first and fourth sub-chambers to replace the cooled fluid in the first and fourth sub-chambers with new fluid loads at a higher temperature and / or pressure and causing the first and second partition members to return to compress the second and third sub-chambers, respectively.

23. A fluid pump for moving a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the fluid pump characterized in that it comprises: a chamber controllably communicable with the first and second source of fluids; closing means for communicating the camera only with one of the first and second fluid source at the same time; and suction means for generating a suction in the chamber and withdrawing the fluid at low pressure from the first fluid source within the chamber when the closure means communicates the chamber with the first fluid source and isolates the chamber from the second source of fluid; the closing means which are furthermore for isolating the extracted low pressure fluid trapped in the chamber of the first fluid source, and then communicating the chamber with the second fluid source, thereby moving the trapped low pressure fluid to the second source of fluid.

24. A system, comprising: a boiler to supply a high pressure fluid; an engine coupled to the boiler, which operates on the high pressure fluid, and discharging the fluid in a low pressure state; and a fluid pump for returning the low pressure fluid from the engine exhaust to the boiler, the fluid pump characterized in that it comprises: a chamber; a partition member movable in the chamber and dividing the chamber into first and second sub-chambers of variable volumes; the first sub-chamber having a controllably communicable opening with the boiler or an additional fluid source; the second sub-chamber having inlet and outlet openings controllably communicable with the exhaust of the engine and the boiler, respectively; and a cooling element for cooling a fluid in the first sub-chamber, thereby reducing the fluid pressure in the first sub-chamber and creating a suction in the second sub-chamber to extract the low pressure fluid from the exhaust of the motor inside the second sub-chamber from which the low pressure fluid is moved additionally towards the boiler at the opening of the outlet opening.

25. A method for pumping a fluid from a first fluid source of said fluid in a low pressure state to a second fluid source of said fluid in a high pressure state, the method characterized in that it comprises: providing a chamber having a partition member movable therein and dividing the chamber into first and second sub-chambers of variable volumes; cooling a fluid medium in the first sub-chamber to reduce a pressure in the first chamber, causing the partition member to move to expand the second sub-chamber thereby generating a suction in the second sub-chamber; communicating the second sub-chamber with the first fluid source, thereby extracting the low pressure fluid within the second sub-chamber by means of the suction generated; isolating the second sub-chamber of the first fluid source and then communicating the second sub-chamber with the second fluid source, thereby causing the extracted low-pressure fluid to move to the second fluid source without a change of phase.

26. The method according to claim 25, further characterized in that it further comprises replacing the cooled fluid medium in the first sub-chamber with a new charge of said fluid medium at a higher temperature and / or pressure, caused in this way that the partition member is moved to compress the second sub-chamber and ready for a subsequent pumping cycle.