CN110088477B - Device for compressing gas by using heat as energy source - Google Patents

Abstract

A gas compressor comprising a pressure chamber comprising a gas chamber inlet and a gas chamber outlet; a gas heating device comprising a heater chamber having a heater inlet for gas and a heater outlet for gas; gas heating apparatus comprising: a heating chamber comprising a gas heater inlet and a gas heater outlet. The gas heating means is for heating a gas present in the heating chamber to heat the pressure to a superheated pressure. A first portion of the heated gas is discharged into the pressure chamber through the heater outlet, and a second portion of the heated gas remains in the heating chamber to compress the gas present in the pressure chamber by applying pressure to the gas by the first portion of the heated gas, while the gas pressure within the heater chamber is reduced below the superheat pressure.

Description

Device for compressing gas by using heat as energy source

This application claims priority to U.S. provisional patent application serial No. 62/382,301 filed on 1/9/2016.

Technical Field

The present invention relates to the art of refrigerant compressors, and more particularly, to a refrigerant compressor without moving parts that uses thermal energy as a source of compression power.

Background

Refrigerant compressor technology the present invention relates to the art of refrigerant compressors and, more particularly, to refrigerant compressors without moving parts that use thermal energy as a source of compression power.

Background

When using a heat pump, which may be geothermal/water, geothermal/air, air/air, etc., it is common for the refrigerant to condense at a temperature between 30 ° and 60 °. If we assume a constant heat capacity, in the range of 0 ° to 50 °,49/50 performs work that is preserved in heat.

In summary, if you wisely reuse this energy, one can earn much if it can be used to compress gas and at 100% efficiency, then compressing fresh gas requires only a small amount of the original compression energy if a conventional heat engine is used, the maximum theoretical efficiency of the heat engine (not reached by any engine) being equal to the temperature difference between the hot and cold ends divided by the temperature of the hot end, both expressed as absolute temperature, and, presumably, 15% of the theoretical efficiency is obtained using the above temperatures.

In this patent, the gas is compressed by compressing a cold low pressure gas with a hot high pressure gas, using waste heat and, of course, other sources of thermal energy. It shows how it can be used to compress gas before and after the compressor. ,

referring to fig. 1, a preferred embodiment utilizes a cooled unidirectional flow as a compressor component, whereby the hot input gas exerts pressure on the cold output gas, thereby compressing the output gas.

Many inventions cool the refrigerant before the compressor to reduce the pressure or possibly increase the density of the refrigerant and thus reduce the energy consumption of the compressor.

In US5797277, the refrigerant is cooled by condensation from an evaporator in a heat exchanger which simultaneously cools the refrigerant condensed from the condenser. However, a pressure drop of the refrigerant in the process seems unavoidable. Furthermore, the gas is not superheated prior to cooling, and cooling does not seem to be controlled to recover energy, so compression is not very energy efficient.

In US4208885, a transducer is used which adopts an expansion valve position, but also compresses the refrigerant out of the evaporator. The refrigerant flowing to the compressor may then be supplied directly to the compressor or may be heat exchanged with the refrigerant flowing from the condenser.

However, none of these patents appear to intentionally overheat the gas simply to pressurize the cold gas and thereby compress it. None of the above patents show an arrangement in which the refrigerant (after the evaporator) is first heated, partially injected into the compressor section, and then cools the non-injected gas while there is no energy injected. This behavior of the invention solves the problem of having low pressure gas enter the device. Their only example also shows the cooling of the boil-off gas, where the superheating of the gas tends to be very small and therefore the pressure increase above the saturation pressure is small.

To achieve energy efficient compression we propose to recover energy and cool under pressure.

To make the compression ratio large you need a very large temperature rise or several units working in series. None of the above shows an example of such a solution. In addition, in order to operate these cells in series, you need to solve the problem of how to let low pressure gas enter each cell, as described below.

One problem with the solution described previously in section 005 is the difficulty of injecting low pressure gas into the high pressure volume (see figure 2). Suppose you have a sealed high pressure hot gas volume, exerting pressure on the cold gas pressure, compressing the cold gas volume. It may start pressurizing the cold gas volume, but when it loses its density, it will have a lower pressure than the cold high pressure destination, so that it does not inject any gas into the flow. The evaporator will not add any gas to the hot high pressure volume because it still has a rather high pressure.

Referring to fig. 2, assuming that the high pressure hot gas seals the volume, with some design, such as a spring or equivalent, keeping the pressure in the volume constant, applies pressure to the cold gas volume, compressing it. It can then continue to compress the cold gas volume even though it is losing gas because the spring keeps the pressure constant. However, when the volume has lost all gas, it must be refilled. This volume cannot be refilled by an evaporator for the gas, since the spring is then configured for the high-pressure gas.

With reference to fig. 4, one proposed solution to the aforementioned problem is to have a heat exchanger unit comprising a heating section, heating cold low pressure gas while keeping the density sufficiently high, followed by an injection device injecting high pressure gas to the compressor section. The injection component, followed by the cooling section, cools the unexjected gas until it has a sufficiently low pressure to be refilled by the evaporator,. the evaporator of the gas is refilled, which means that you can keep a fairly constant gas flow into the compressor section, while at the same time the heat exchanger unit can be injected with gas from a cold, low-pressure gas source.

Another problem with the previously described solutions is that if you try to reach a high pressure volume, it is difficult to transfer this pressure to a different target volume. For example, suppose you have 2 containers, one source and one destination, with the same capacity, the source has a starting pressure of 2bar and a destination of lbar, when you connect them, you will get something close to 1, 5bar in both containers. Therefore, in order to keep the flow pressure in the compressor section high in the previously described solutions, you can only inject a small portion of the superheated gas in the injection component to prevent its pressure from dropping. In theory, this problem could be solved, since most of the energy is still present in the non-expelled gas, which could theoretically be reused to heat the new gas. Therefore, part of the solution is an advanced heat exchange unit for the gas. In this solution, you often want to transfer energy from the refrigerant to the gas, convert the gas to the gas, and convert the gas to the refrigerant. This can be difficult because the pressure of the hot gas is higher than the cold gas, so the cold gas does not flow to the hot gas, and furthermore, you may need to heat a heat exchanger to heat the gas, which may be of greater mass than the gas. The content claimed by the patent is therefore specified in such a heat exchanger unit, and such a proposal is also provided. The preferred embodiment uses a heating device from another patent.

Another part of the solution to the aforementioned problem is that when the injection part is used, the gas is injected in several steps, injecting the gas with gradually decreasing and decreasing pressure. Rather than injecting only the highest pressure gas but injecting the gas into several different pressure streams, you can still use superheated gas at a pressure less than the maximum pressure, while still having a very high pressure destination. In addition, a greater amount of heated gas is injected, so a smaller amount of gas must be cooled and reheated.

The improvements of the above solution in the range of (014) to (016) are:

the target volume with low activation pressure absorbs gas from different flows/volumes in reverse order compared to the flow/volume filling approach.

This means that the flow from the stream with the lowest pressure among the different pressure streams is injected first into the target volume, then the one with a slightly higher pressure, then the one slightly more, and so on, thereby transferring the pressure from the injection section into the destination volume more efficiently. Another benefit of this is that the target volume is compressed and increasing the pressure is more energy efficient. For example, if a large amount of high pressure gas (from 2Bar) is discharged into a small amount of low pressure gas (from 1Bar), the work performed can be represented by Graaff in FIG. 16, even if the work required is represented by FIG. 15 only. By compressing the target volume in 4 steps, the work shown in fig. 17 can be achieved, which is an improvement compared to fig. 16.

The present invention will solve the above problems.

Abstract

In this patent, a device for compressing gas using a different source of thermal energy (e.g., internal waste heat from a heat pump). It shows how it can be used to compress the gas before and after the compressor, why you can reduce the amount of work required by the compressor.

It is an object of the present invention to provide a compressor for compressing gas using thermal energy as an energy source.

In some embodiments, the compressor member includes a unidirectional flow. The unidirectional flow cools in the flow direction, while the hot gas simultaneously exerts a pressure on the cold gas, whereby the density increases in the cooling direction.

In a preferred embodiment, the invention proposes a two-part device, a compressor part, in which hot gas exerts pressure on cold gas, and a second part comprising a heat exchanger unit for the gas, in which the gas is heated to a high pressure and then injected into the compressor part, and then the thermal energy from the unexjected gas is recovered as described.

In some embodiments, the heat exchanger unit comprises means for heating the cold gas while keeping its density fairly constant, wherein the gas is heated to a high pressure and then injected into said compressor section, after which the thermal energy from the non-injected gas is recycled upon cooling. The unexprayed gas moves forward and into the cooler, thereby reducing the pressure of the gas, so when connected to a new external gas having substantially the same temperature but a higher external density, the external gas can be absorbed into the volume. Alternatively, the volume of the cooled unexjected gas is reduced so that fresh external gas having substantially the same temperature and density can be injected in parallel into the volume. In this way, a constant injection of hot gas to the compressor section is possible.

In a preferred embodiment the heat exchanger unit comprises as heat exchanger unit for gas the device from another patent PCT000033 cited in this patent.

In one embodiment, the heat exchanger unit includes the apparatus described more fully in this patent.

Thus, according to the invention, the compressor section and the heat exchanger unit are combined to form a compressor, called "cooling compressor", which receives cold gas at low pressure and then emits a slightly hotter and more pressurized gas. The output of one cooling compressor may be injected into a second cooling compressor. The cooling of the compressor can advantageously be carried out in several steps to become a compressor which together can perform a large compression. Since it is recommended to recover as much heat energy as possible, the energy recycled from one cooling compressor can be used as energy for the other cooling compressor, both in the first and in the second section, so that a considerable compression can be obtained. It requires a small amount of energy.

How to heat the gas effectively and recover the heat is solved in another patent, better described in PCT000033, which is used to describe the preferred embodiment. For the purposes of this description, another device is also used, which can be more easily understood.

Furthermore, to solve this problem, why heating the gas usually takes longer than the fluid. In addition, this patent describes other methods of improving the basic required performance:

for example, it may be difficult to transfer pressure from one plenum to another because it just becomes the average pressure of the two separate pressure chambers. This patent describes how to transfer gas pressure from one chamber to another in an energy efficient manner.

Brief description of the drawings

The present invention will now be described in more detail, by way of example, and with reference to the accompanying drawings,

figure 1 is a stand alone refrigeration compressor with an embodiment of 2 vessels.

Problem 1 of fig. 2 uses a separate cooling compressor without a heat exchanger unit.

Figure 3 problem 2 uses a separate cooling compressor without a heat exchanger unit.

FIG. 4 is a depiction of a fictitious optimized heat exchanger with a cooling compressor

Fig. 5 is a fictive heat exchanger for gas if the gas is a fluid.

Fig. 6 alternative heat exchange unit: fixing some bottom Vyl

FIG. 7 alternative to the heat exchange unit 1) fixing some of the bottoms, 2) rotating part 3) fixing part of the cover

Fig. 8 "heat exchange unit": from the top "swivel part", diagonally from the side

FIG. 92 containers not interconnected, with poor pressure equalization

FIG. 10 shows poor pressure equalization between two containers connected to each other

FIG. 11 optimal pressure equalization between two vessels, each with a means for controlling pressure

FIG. 12 counter-current pressure equalization without control pressure device-step 1

Figure 13 does not have counter-current pressure equalization-step 2-of the controlled pressure device process.

Figure 14 is a table illustrating why heating with many chambers is faster.

FIG. 15 work required for compression

FIG. 16 unnecessary compression work using maximum pressure directly

FIG. 17 improves compression work using incremental compression

FIG. 18 compressor embodiment

FIG. 19 two compressor embodiments connected in series with a cross-connect

FIG. 20 embodiment with a cooling compressor connected to the compressor output

Figure 21 compares the effect of the embodiments of the cooled and non-cooled compressors.

FIG. 22 apparatus for heating gas

FIG. 23 is a view of a particular pump that can be used in the preferred embodiment

FIG. 24 preferred embodiment, in series in a heat pump, process step 1

FIG. 25 preferred embodiment, in series in a heat pump, process step 2

FIG. 26 preferred embodiment, in series in a heat pump, Process step 3

FIG. 27 preferred embodiment, in series in a heat pump, process step 4

FIG. 28 preferred embodiment, in series in a heat pump, Process step 5

FIG. 29 preferred embodiment, in series in a heat pump, process step 6

Detailed Description

All illustrations in the drawings are for the purpose of describing selected versions of the invention and are not intended to limit the scope of the invention. The present invention will be described in detail and provided in a manner that establishes a thorough understanding of the invention. Aspects of the invention may be practiced or utilized without some of the features described. It should be understood that some of the details have not been described in detail in order not to unnecessarily obscure the present invention.

The invention disclosed herein is a "compressor using heat as an energy source". Although the device can be used as a stand-alone compressor, the main object of the present invention is to reduce the work performed by conventional compressors. The present invention aims to provide a solution to this problem. Generally, the solution proposed by the present invention uses superheated high-pressure hot gas to pressurize the cold gas. This can be achieved using a double acting compressor having cold gas on one side and compressing the cold gas by repeatedly injecting hot gas on the other side.

In some embodiments, this is achieved by unidirectional flow, cooling in the direction of flow while preventing mixing between the hot and cold gases, and inductive heat exchange within the flow while maintaining the pressure substantially constant. One advantage of this solution is that, compared to a solution using a double-acting compressor, it is simple, you can obtain a constant flow without the need to empty the filling compressor. Another benefit is energy efficiency, you can use the counter flow heat exchange to easily cool the single flow, thus can recover a large amount of energy at high temperature, at the same time, through the single flow compressed gas, for heating the fresh gas.

Referring to fig. 1, generally speaking, the present invention comprises a graded heat transfer element 1 comprising a unidirectional flow of temperature ramp rate, followed by a graded heat transfer element 1 between a cold end 10 and a hot end 11. It is noted that the present invention may include more graduated heat transfer elements in various examples and configurations.

Referring to fig. 1, in some embodiments, the gradual heat transfer element (cooling compressor) is a single device.

Referring to fig. 20, in some embodiments, a gradual heat transfer element (cooling compressor) is positioned in the heat pump between the input of the condenser and the output of a conventional compressor configured to achieve a particular output pressure resulting from increased density and superheated gas, in other words, not just because of the output density. The cooling compressor then converts the additional pressure generated by the superheated gas to the additional pressure generated by the gas having the higher density.

Referring to FIG. 18, in some embodiments, the staged heat transfer element (cooling compressor) is preceded by a gas heating device (AFHG).

AFHG has a heating section whose purpose is to heat the gas until its pressure is significantly higher than the input gas, in other words, while trying to keep the density fairly constant.

After the exhaust part is a cooling section, the purpose of which is to cool the non-injected gas, which still has a rather high temperature, after the exhaust gas. This solves the problem of how to absorb fresh gas into the device. How the low pressure gas enters the AFHG is described in more detail in the appendix.

In some examples, from (037), the heating section preferentially heats the cold air, with other warm refrigerants, in an energy efficient manner, meaning that the closer the temperature of the gas is to the highest temperature of the other warm refrigerants, the better, the less energy is stolen from the other warm refrigerants, while keeping the higher the density of the heated gas, the better.

In some embodiments, starting from section (028), it is preferred that other cooler refrigerants have been used in other sub-sections of the heated gas. In an energy-saving manner, it is meant that the other colder refrigerants are as close as possible to the warm gas maximum temperature, while as little energy as possible is subtracted from the warm gas, resulting in as cold a low output pressure natural gas as possible.

Referring to fig. 18, in an embodiment, starting from section [037], there is an input section, preferably after the cooling section, where the input section directs low pressure and low temperature fresh outside air plus cool air to AFHG.

The cool gas enters the heating part from the cooling part. The return gas has been cooled to a cool, lower pressure than the outside gas, which will be equalized by the incoming outside gas pressure, or included in a smaller return portion during cooling. Thus, external gas can be added to a small volume parallel to the return volume. A combination of the two solutions is also possible.

Referring to figure 19, in some embodiments, the array of devices according to the description in section [037] are connected in series, characterized in that the output from each arbitrary cooling compressor is connected to the subsequent device input section except the last one. According to the description in section [028], the compression ratios of each device are multiplied by each other.

Referring to fig. 19, some embodiments include an evacuation/injection unit further comprising at least one source volume and at least one target volume characterized by releasing the source volume by interchangeably connecting to an intermediate volume for pressure equalization, a pressing force level connection, from highest to lowest, thereby gradually reducing the source volume pressure.

Further features are: the target volume absorbs gas by being interchangeably connected to each intermediate volume for pressure equalization, connected in reverse pressure order, from lowest to highest.

By doing this, you transfer pressure from the source volume to the target volume.

As shown in graph 19, in some preferred examples, the conclusion from section (042) completes the use of a series of source volumes and a series of target volumes, the feature showing that each source volume is connected in a sequential periodic manner, from a single target volume to a series of target volumes, in order of the target pressure from highest to lowest. Another characterization is shown where the characterization shows that each target volume is connected in a sequential periodic manner, in order of lowest to highest source volume pressure, from lowest source volume to the series of source volumes.

Referring to fig. 11, some embodiments include a spray/injection unit further comprising at least one source volume and at least one target volume characterized by releasing the source volume by interchangeably connecting to an intermediate volume for pressure equalization, a pressing force level connection, from highest to lowest, thereby gradually reducing the source volume pressure.

Further features are: the target volume absorbs gas by being interchangeably connected to each intermediate volume for pressure equalization, connected in reverse pressure order, from lowest to highest.

By doing this, you transfer pressure from the source volume to the target volume very efficiently.

Referring to fig. 1, a less desirable embodiment is shown in which the gradual heat transfer element (the cooling compressor) is a single device. The principle of cooling the compressor is as follows. You have two gas volumes, a colder target volume (2) and a hotter source (1). The heat is superheated, temperature-temperature (Tw), and therefore very hot, and it produces a pressure significantly higher than a gas with the same density and saturation temperature.

Then connected thereto by a cryogenic stream (4), comprising one or more heat exchangers (3) and possibly a rectifier. A rectifier may not be necessary but may prevent cold air from flowing backwards and reheating and/or mixing with warmer air. This may be acceptable if you can prevent flow backwards by other means. It is important that the gas flow (4) should flow freely in the direction towards the cooler part with little or no pressure drop, but that the gas flow is prevented as far as possible from flowing backwards. If the gas is cooled with a liquid refrigerant, a larger volume of liquid per volume of gas should be found in the colder parts, because of the higher density of the gas there. These steps will gradually cool the gas to a temperature tcold (tc). If cooling is performed using the above-described technique, most of the dissipated energy can be recovered from the cooling, presumably by means of a one-to-many step heat exchanger (3), for use at a later stage.

In any case, the gas from the last step is cold. Preferably, the gas has been cooled to near the saturation temperature (Ts). However, due to the pressure equalization, the gas can flow freely in the flow (4), so the pressure does not drop much, the pressure in the cold gas tank being at least as much as the warm gas (provided that the rectifier cold gas may in some aspects have even higher pressure). Due to the cooling, each depressurization in one step will be pressure equalized by the higher pressure in the previous step, which in turn will be equalized by the pressures in its previous steps.

In summary: the input gas has a high pressure, a high temperature and a low density. The output gas has a high pressure, a low temperature and a high density. We use the pressure of the input heat to produce compressed gas.

A large amount of energy to heat the gas from the start temperature (Ts) to Tw can be recycled. Note that Ts represents the temperature that the gas in the large chamber (3) had before being heated to Tw. It is this energy that has been used for compression and unless a significant portion of it is recovered, the system is not effective. In theory, most of the energy discharged to the heat exchanger can be recycled.

In fig. 20, a heat pump, is an embodiment in which a graduated heat transfer element (a cooling compressor) is located between the output of the condenser and the conventional compressor. According to the unidirectional flow of the compressor element, it is placed after the compressor (5), possibly in combination with means (1) for maintaining a preferred pressure. For example, it may comprise a piston chamber with a spring to generate uniform pressure, or a large chamber to maintain relatively uniform pressure due to its size. When the gas is compressed, it is almost inevitable that the gas is overheated, increasing the pressure beyond what is necessary, thereby increasing the work that the compressor must perform. By placing a back pressure device at the compressor output that provides a corresponding pressure of gas with the correct compression ratio and saturation temperature, the compressor will not need to operate at a pressure higher than the optimum pressure. For this reason, the gas at the output (1) of the compressor will have a high pressure partly due to the density increase and due to the excessive temperature increase, and the compressor member will convert this hot high pressure gas with lower density into a slightly cooled gas with the same pressure but higher density. In theory, the compressor need not actually compress to the desired compression ratio. Theoretically only compression to bring the pressure (in combination with the unwanted temperature) to correspond to the desired pressure requires a compression ratio after which the device converts the hot gas into a gas with a higher density. In conventional heat pumps, cooling is used during compression to address the problem of overheating during compression of the gas. This may be more efficient from an energy point of view, but simply placing the device on the output (1) of the compressor should be easier to apply.

Fig. 21 corresponds to a non-limiting solution with a refrigeration compressor: the dotted line indicates the operation of the compressor without a cooling or refrigeration compressor. The dashed line corresponds to a non-limiting solution with a refrigeration compressor. The solid line represents the operation of the compressor, with perfect continuous cooling, allowing the gas to maintain the saturation temperature at each given pressure. The first two charts are up to the optimum pressure (about.2.2 in the figure), then the plant with cooling compression will not be increased more because it has a maximum of 2.2 high pressure plant. However, a device that is not cooled or that is compressed by cooling must continue to compress the gas until it receives the correct density, why it also increases temperature and pressure, and the work becomes greater. After the optimum pressure is reached, the plant with the refrigeration compressor will have a stable reaction force.

After the target pressure is reached, even other devices will perform a stable operation, since then the operation consists in pushing the gas into the flow, but for compressors that are not cooled or are compressed by cooling, the resistance becomes large. The device performs the least work with perfect cooling as it will eventually reach the maximum pressure. However, it is difficult to cool the gas during compression because you have to cool the compressor itself, and you have to cool different amounts at different compression ratios. In this case, therefore, the gas will be cooled too much,

where the gas may condense long before it is expected. Alternatively, the compressor is compressed to a desired compression ratio and further compressed using excess heat. Of course you can use the heat generated by cooling in the cooling compressor and then use this energy.

Referring to fig. 18, the apparatus includes a compressor section (42) and an AFHG (51). Description of the heated gas unit (AFHG) see FIG. 6, which is the base unit of the present invention. Referring to fig. 7, is an exploded view of the AFHG: a chamber (1) with a rotating part (2), which rotating part (2) is to be sealingly covered by a cover (3). Fig. 8 is an exploded view of the rotating part (2) of the AFHG. The rotating member (2) divides the sealed chamber created by the chamber (1) and the lid (3) into several abruptly sealed wedge-shaped subvolumes (wcsv.) while the rotating member moves the subvolumes through the chamber walls of different temperatures. The rotating portion will dwell in stages such that all wcsv are separated from each other.

In this embodiment, the heat exchange is described as a generally static cylindrical cavity separated by various cyclical (and gas-insulating and heat-insulating) walls, which are described as impinging a pointer on the image. The circulating walls isolate the cylindrical cavity from wedges having outer walls of different temperatures for each slice temporary volume. The circular wall moves the gas in a clockwise direction, preferably with a recess so that the cake does not fall longer between the two temperatures, in this way, and the temperature walls are placed so that the gas passes through the hotter and hotter walls until the maximum temperature is reached, and then its overpressure is released. Thereafter, they pass through cooler, colder walls, releasing excess energy.

Referring to fig. 7: the wall portions are set to different specific temperatures. In other words, each wcsv generated by the various elements is completely surrounded by walls with suitable temperature, except for the rotating part (2), i.e. no other part of AFHG is heated and cooled. The rotating part (2) can be heated and cooled by gas or surrounding walls and should therefore be as light as possible, as insulating material as possible, in order not to steal energy. It must also be sealingly and slidably connected to the surrounding walls so that gas does not migrate to adjacent chambers.

Referring to fig. 7: the lid (3) may also conduct heat to the container. The task of the heat exchanger is to deliver the correct temperature to the correct location. On the bottom and the lid, each specific grey part has its specific temperature. The bottom and the lid are identical when belonging to the same wedge-shaped part. . I.e. the higher the temperature near the top of the graph. You can see the gas inlet through the lid in the figure, which is of course not necessary, it can also be accessed from the side or the bottom.

Referring to fig. 6, the left and right gray rectangles are the containers for the refrigerant and heat exchangers. How to design these in detail is quite uninteresting. It is important that the fluid still gradually goes from the hottest to the coldest (darker being warmer and lighter being cooler). The refrigerant should be routed only when cooling (by gas inside the circle) or heating (by gas flowing through the heat exchanger). In other words, the temperature will remain constant in every part of the tank, why you do not have to heat the heat exchanger in order to heat up to the gas.

The refrigerant reservoir (42,50) has a controlled supply of refrigerant and the hot refrigerant should not mix with the cold refrigerant. How to control is omitted from the solution. From each temperature range in the reservoir, different heating pipes (41,45) lead to various individual temperature levels highlighted with grey areas in the figures (43, 44). The conduits are depicted as lines in the figure. The grey colour indicates the heat transfer to the individual temperature in the vessel. White between the two represents isolation.

The middle circle is the cavity. The grey triangles (9-16 and 25-32) represent the fixed areas of the heat conducting walls of the vessel. Each triangle has a fixed temperature.

The small circles (17-24) in the upper right corner represent the gas output that will be formed in the circular lumen.

The gas volume inside the various wedges (1-32) is made up of a bottom part, a rotating part (2) and a top part.

The rotating part should move as a clock within the erosion.

Thus, each gas volume will be heated in the left part (9-16) of the great circle.

As the gas volume leaves the upper chamber (16), it is at its hottest and has the greatest pressure.

Thereafter, the gas volume will gradually discharge gas into the output in the chambers (17-24).

When passing through the outlet chambers (17-24),

each gas volume will be connected to a continuous lower pressure outer vessel.

Thereafter, the gas volume is cooled in the chambers 25-32.

Flow path

We have now described various elements, let us describe the functionality of the device.

Referring to FIG. 18, the gas enters the AFHG, perhaps starting from the previous step, at several parallel flows, with different pressures, in the figure, the left input (i1) contains the highest pressure, which decreases as you go to the right, i.e. (i8) has the lowest pressure.

Other input pressures vary, ranging from i8 to i 1.

They are all discharged into separate chambers defined by three sections.

Each gas cell will pass through 1-8 positions and then be compressed by the input gas from inputs i8-i1, receiving higher and higher pressure gases.

Each time gas before AFHG is entered, the rotating part moves one step.

The chamber at the last position (32) is then moved to position 1 and filled to the lowest pressure (via i 8). It is then moved one step to fill with gas (i7) having the next lowest pressure. The following steps are carried out: the rotating part will move further and will then fill the same chamber from the flow with the next lowest pressure so it will continue until no higher pressure input is available.

Incremental compression is achieved in the above-described manner, i.e. the gas volume starting at low pressure is not directly compressed with the gas at maximum pressure, but in turn the low-pressure gas volume is compressed by a gas volume with gradually increasing high pressure, preferably only slightly above the temporary pressure of the low-pressure gas volume. Less work is done by higher pressure volumes, which means similar work as described in the graf in FIG. 17

The more increments that are used are,

the closer each incremental input pressure is to the destination,

the closer the compression work is to "fig. 15".

When the gas reaches the input area i1, the gas has reached the maximum pressure that may be generated by the previous step. The thermal conductors are not connected to the sub-volume and no heat transfer to the gas volume occurs. The only heat added comes from the compression. When then going to the next step (9) to start warming. Steps 9 to 16 involve only heating. When the throttle valve is moved between two steps, in this range it will be heated by the hotter and hotter walls. In this way it achieves something comparable to a counter-flow heat exchange. Just as it leaves the location 16, it has passed the highest temperature wall, so by then it is at maximum pressure.

In a later step the rotating member moves the gas volume to position 17. At position 17 the plenums are connected to the flow at the highest pressure so they are pressure balanced.

It then moves to position 18, connecting to the flow of the next highest pressure, so they are also pressure balanced,

thereafter, the chamber continues to achieve pressure equalization by being continuously connected to a decompression destination.

This continues until 24. The gas is ejected through holes (pre-hooked rings) in the figure. You can choose whether to heat/cool or not heat in this range. However, heating may be a waste of energy.

From the upper outlet at the point 17-24, the gas is introduced into the compressor section, connected to a lower pressure at each step.

In fig. 33, they are introduced into multiple parallel cooling compressors, from the highest pressure (o8) to the next highest pressure (o7) to the lowest pressure (o 1). It was observed that the higher the output pressure, the higher the output temperature, since higher pressures require higher temperatures to avoid condensation.

As the gas enters location 24, it may leave a significant amount of heat in the gas. You have a good heat exchanger with well insulated rotating parts with very little weight and many temperature steps (corresponding positions 25-32 in fig. 18). Most of the thermal energy used for heating remains in the gas. Steps 25 to 32 comprise only cooling. When the throttle valve is moved between the two steps, it will heat up to the colder and colder walls in this range. In this way it achieves an apparatus comparable to a counter-current heat exchange, providing energy to the refrigerant at high temperatures.

This energy can be transferred to the gas in the heated sub-volumes (9-16) to the highest possible temperature. However, the gas at location 24 has lost mass and temperature, so it cannot even ideally reverse the temperature to Tmax.

When the sub-volume moves away from location 32, it has the lowest pressure, lowest temperature, because it is most cooled, and has the lowest density since it has passed through the last jet outlet in location 24, and therefore its lowest pressure. Thus, low pressure gas is likely to be injected from the external fluid of position 1, where it will move in the next step.

In a second preferred embodiment, see fig. 19, the apparatus comprises at least two cooling compressors connected in series. In fig. 19, there are only 2, but more may be connected. In this way, the compression ratio of the entire plant may be the product of each cooling compressor ratio multiplied by each other. This opens up a larger ratio. Furthermore, the recirculated refrigerant from one unit (less than maximum heating) can be reused in another unit with a lower maximum temperature, which opens up for better utilization of the thermal energy.

In addition, this embodiment utilizes counter-current pressure exchange. To explain fig. 2, attempts are made to connect chambers of the same size, but at different pressures, such as 1 and 2. Ignoring the temperature, they have a pressure relative to each other as shown in fig. 9. After joining, if cooling is neglected, they will have a pressure similar to that of fig. 10. This is a similar problem that we face when the gas volume is superheated to a certain pressure and is to be delivered to the destination.

Referring to fig. 11, when the distributor chamber has its highest pressure, it is connected to an intermediate channel with a substantially constant pressure, slightly lower and discharged to said channel, after which said chambers are connected to the channels sequentially, in order decreasing from the highest to the lowest pressure, preferably always at a lower pressure.

On the other hand, when the receiving chamber has its lowest pressure, the receiving chamber is connected to an intermediate passage, which has a substantially constant pressure, slightly higher than the receiving chamber, and then the passage is discharged to the receiving chamber, and then the chambers are sequentially connected to the receiving chamber. In order from lowest, to higher and higher, to highest pressure, to the receiving chamber, preferably always to a channel having only a slightly higher pressure.

Each subvolume from the preceding unit is observed to be connected to the subsequent unit in increasing pressure in order from lowest to highest, but the subvolume of the process set is connected to each compressor section of the process set in decreasing pressure of the compressor sections in order from highest to lowest. In other words, the intermediate channel in compressor section [071] to [073 ]. By these methods, a larger amount of gas is transferred between the two volumes, with a higher maximum pressure at the destination.

In a third preferred embodiment, another heat exchange unit "gas heating device" of patent PCT000033 is used. The heat exchange unit performs substantially the same operation as the heat exchange unit described in this patent, referred to as the heating unit, but may be slightly better. Patent PCT000033 does not need to be so many and large and does not have multiple chambers, as required by the heating unit. In the embodiment to be described, you can still connect the heating chamber to a large number of destinations without the need for many chambers in other heating units. It should be noted that in the following description, only one embodiment of the above-mentioned patent is described, even though substantially any embodiment may be used. The pump used in patent PCT000033 comes from yet another patent PCT 000031. The patent may also be read for a more complete understanding. Nevertheless, some minor modifications have been made to the pump.

Compared to patent PCT000031, additional features in the pump include an alternative solution for connecting the outlet chamber of the container to an array of openings, as shown in fig. 23, where the outlet chamber has a hole (601) in the top part, close to the right side of the piston wall (251) in the plane of the drawing. The top member is sealingly connected to a subset of said array openings (603) at said apertures (601) by a sleeve comprising array openings (603). The array opening (603) has a suitable shape so that it follows the movement of the aperture (601), in which case the aperture (601) means a circle, periodically connecting the output chambers to the subset, opening (604). The array openings may be further connected to other destinations or sources through rectifiers. In the figure, it is assumed that the aperture is connected to the source in the lower half of the array circle, thus the connection has an ejection prevention rectifier, and the upper half of the array circle has an injection prevention rectifier, since it is assumed to be coupled to the destination. The preferred embodiment of patent PCT000033 can be described with reference to fig. 22, where transparent in the additional cover only the array openings (603) are shown, and the top part cover only the wells (601) and the piston walls (251). More importantly, the input vessel is seen to comprise a plurality of sub-chambers, with separate inputs, but with outputs connected to the same input of the heat exchanger. The benefits of the recovery process will be apparent when the process is described below.

The recovery process is described with reference to fig. 22; dynamically connecting an input to a defined output by connecting the array of openings (603) to a coupling means (439). According to the above description, as unheated gas pressure enters the system, having half the pressure compared to the gas energizing the heat exchanger, it can be assumed that the opening (603) is preferably moved by the piston half way to the right of the chamber and connected to an external destination (410) where the pressure is reduced to said unheated gas pressure. The following array of pistons passing on their way to the right side wall should preferably be connected to a large chamber (440) in the sense that the amount of gas added or subtracted in the container (262) changes pressure negligibly. The reason for this is that the gas is injected asynchronously, but injected synchronously into the chamber (440). The chamber (440) is then connected to a cooling device (420). There are not much reasons for making the cooling device as advanced as the heating device (200), even though it may, and thus is shown in the figure as a conventional counter-flow heat exchanger. The heat emitted by the gas in the cooling device is preferably used to heat the gas in the heating device (200). After the gas has cooled down, it is again led to the coupling means, from where it is again coupled to the heating means (200), since the gas returning to the heating means is less than the gas leaving, the gas having the same pressure and temperature as the input gas in the whole gas chamber, the returning gas should be led to a volume smaller than the total volume of the output container, in this case about half the volume. This can be achieved by several smaller containers, but in the figure one input container with six sub-volumes is used and the return volume can be adjusted dynamically. The six sub-volumes are in practice quite small in number, but it is used for descriptive purposes only. In the case of a halved recovery, three of the six subvolumes should be used. The other three sub-volumes should be supplied by fresh external gas having approximately the same pressure and temperature as the cooled return gas.

This cycle then creates a pumping effect without any valves that must be opened or closed. The connecting piece is automatically opened/closed by the movement of the frame bottom and the piston itself. By having an array of outlets from the output chambers of the output container, which are exposed to specific locations of the rolling piston movement in a certain way at specific locations and connecting these locations to the target volume (at specific pressures and temperatures), you can control the output of the instrument so that the pressure in the output chambers of the output container is gradually reduced to a pressure suitable for the output chambers of the input container.

The connections shown in the coupling means (439) are merely exemplary couplings, as the coupling means in this embodiment is dynamic. Also in 439, for explanatory reasons, only the connection of the uppermost chamber is shown in the figure. In this example, the remaining outlet chambers of the outlet container should be connected in the same way, even though not shown in the figure. For the described embodiments, it is believed that the external outputs (410) should be as many as the number of outlets in the array of outlets per output chamber. Furthermore, the number of internal outputs (441) should be similar, so for each input from the output chamber it can be decided whether to connect it to an external output or one of the internal inputs.

Referring to fig. 22, as with the heating unit, the other heating units recover energy from the unexprayed portion of the gas in each cycle. In this embodiment, other heating units may be used to cool and heat the gas in unlimited steps, as it uses a special type of counter-current heating as the gas. It is very dynamic in that it has a coupling device 439 at the output of the heating section 200, which can be adjusted according to different temperature ranges and choice of output pressure. The coupling arrangement may be configured to cycle a greater output using the coupling arrangement 439 and return gas at a higher pressure through the connecting coupling 432. Due to the asynchronous discharge generated from the heating section 200, there is a large chamber 440 behind the coupling arrangement, without pressure drop. The cooling device 420 cools the non-burst portion of the gas, and the output of the cooling device 420, under pressure, is compressed so that the gas returns to the input portion 430, which is also a coupling device, which will constrict and cause a separate flow, parallel to the external input 612. From the input section 430, the external inflow and the circular inflow are collectively returned to the heating section. It can be seen from the data sheet 22 that the left pump 205 and the right pump 206 have horizontally disposed chambers, such as 437. This may be valuable in some compression environments where the target volume is smaller than the source volume, but it is omitted for reasons of simplicity in the examples described below. The pump pushes the gas forward through the heat exchanger 400 by connecting multiple pistons rolling motion to move synchronously. At the top of each chamber, the output container position, where the input container can also be placed, has an aperture 601, connected to the chamber by a subset of a large number of array channels (520,521,522), depending on the position of the aperture 601 in the rolling motion. The array channels may be connected or disconnected to other destinations by coupling means.

Using this embodiment, and some of the profits of the present invention, is described herein as a process with reference to the six steps of the graphs shown in fig. 24-29. For the purposes of this example, it is assumed that the temperature increase is very large, meaning that the output absolute temperature is about twice the absolute temperature of the input temperature of the heat exchanger. Therefore, the maximum output pressure of the heat exchanger is also assumed to be about twice the heat exchanger input pressure. The figures depict two units according to a third preferred embodiment. They all have a main gas input (612) from a common source, meaning that their input pressures are the same, but the second set of input vessels is filled with the remaining compressed gas of the first set, and the compressors (599) are cooled in steps by the array of the first set, meaning that said input vessels are assumed to have a maximum starting pressure twice the input pressure. Ideally the temperature is closer to the pressure saturation temperature.

To explain the profit of the invention, a compressor is added at the end. This example is intended to explain the value of connecting the devices in series. In this example, only two devices are coupled in series for illustrative reasons, but more devices may be used. It also gives an example of how to increase the starting pressure in the compressor. The compressor is incorporated into a heat pump, showing the benefits of doing so.

The numbers used in the description are from another patent. To separate the units, prefix 1 is added to the front of the part when referring to the first unit (1000), prefix 2 is added to the front of the part when referring to the second unit (2000), prefix 3 is added to the front of the part when referring to the compressor (3000) at the end of the flow, no prefix is added when the description refers to both cases at the same time.

Figure (a). FIG. 21 shows a first process step of the preferred embodiment, where the piston 570(576 in the output reservoir) is near the leftmost position of the left sidewall 537 (557 in the output reservoir). This applies to both units.

In this regard, assuming a ratio of 2 for each compressor (1000,2000), the expected relative starting pressure, and the input device (612) for comparison, the ratio of the output plenum (1434) of the first input vessel (1205) may be 1, the ratio of the relative starting pressure of the first output plenum of the second input vessel (1205) may be 2, and the ratio of the relative starting pressure of the output plenum (3434) of the target compressor (3000) may be 4. This is due to the fact that when the pistons (2570) of the input containers of the second group (2000) are stroked back, they are filled with gas, which is generated by the array of cooling compressors (599) in the process group in order of the increment of the pressure of each cooling compressor.

In the input container of the two units, opening 533 is now located between connections 502 and 510, and 534 is located between connections 503 and 509; thus, there is no connection within the cavity. Thus, the bottom of the frame blocks connections 502,510,503 and 509. In addition, the piston 570 blocks the left outlet openings 502 and 510. This applies to both units.

In the output container, opening 543 is between 515 and 514, and 544 is not connected to 517 or 519; for example, frame bottom barrier connection 515,514,517 or 519. In addition, the piston 576 blocks the left side outlet openings 515 and 514. In this position, the aperture 601 does not connect the output chamber of the input container with a row of openings (520,521, 522). However, it begins to move to the right, and the holes 601 will connect through the array of openings to a series of cooling compressors, connecting the output chambers of the output container (206) to a subset of the cooling array. Compressors (599) in descending order of pressure to cool the compressors. I.e. it will start to be connected to a cooling compressor with high pressure, just slightly smaller than the inlet chamber of the outlet container (206). Thus, in this example, the pressure in the output chamber is gradually reduced from unity maximum pressure to a minimum pressure, representing the input (612) pressure. The cooling compressor (599) has means for maintaining a stable pressure even if the injection and injection of the cooling compressor are slightly synchronized. This applies to both units.

In this position, the aperture 601 does not connect the output chamber of the input container with a row of openings (520,521, 522). However, it begins moving to the right, with holes 601 connecting the array of openings to a series of cooling compressors, connecting the output chambers of the output reservoir (206) to a subset of the cooling arrays. And compressors (599) arranged in descending order of the outlet chamber pressure. I.e. it will start to be connected to a cooling compressor with high pressure, just slightly smaller than the inlet chamber of the outlet container (206). Thus, in this example, the pressure in the output chamber is gradually reduced from unity maximum pressure to a minimum pressure, representing the input (612) pressure. The cooling compressor (599) has means for maintaining a steady pressure even if the injection and injection to the cooling compressor are slightly out of phase. This applies to both units.

Fig. 25 shows a second process step of the preferred embodiment, in which piston 590 is moved to the right from its leftmost position (beside left sidewall 580) and slightly upward based on the previous position. Adapted for two units

In the input container, the frame blocks the two lower connections, while the two upper connections are located in contact with the openings in the bottom of the frame and are thus connected. The piston moves to the right and then draws fluid into the left half of the chamber through inlet 501 and attempts to move fluid from the right half of the chamber into the heat exchanger, but only when the output chamber reaches the same pressure as the heat exchanger because a rectifier is connected to the heat exchanger. So that the pressure in the outlet chamber of the inlet container increases.

If we assume that the piston has moved three distances to the right 1/4, the estimated relative pressure may be 1, 33, compared to the first input device (612) of the output chamber (1434) of the first input container (1205), the relative activation pressure of the output chamber (1434) of the second input container (1205) may be 2,66, and the relative activation pressure of the output chamber (3434) of the target compressor (3000) may be 5, 3.

In this configuration and in this position, the aperture 601 connects the input container with a row of openings (520,521,522) the array of openings is connected to the array of cooling compressors. The output chambers of the output container (206) are sequentially connected to a subset of the array of cooling compressors (599). The output chamber (206, connected to each cooling compressor in sequence, in descending order, in an order determined by the cooling compressor pressure.

In this example, the minimum pressure is equal to the input pressure.

The cooling compressor should have a means of maintaining a stable pressure even if the discharge/injection of the cooling compressor is not uniform. This applies to each unit.

It is proposed to configure the connections such that the holes 601 and the array of openings (520,521,522) connect the output chamber of the output container to the target cooling compressor at only slightly lower pressure.

All output arrays (520,521, and 522) of this embodiment are connected by rectifiers (524) so that the vias (577) and the array of openings (548) can be so wide as to cover multiple outlets simultaneously.

Thus, there is no risk that the high pressure target volume is discharged to the low pressure target volume. This increases the speed at which the pressure in the output chamber can be reduced.

Fig. 26 shows a third process step of the preferred embodiment, in which the piston 570(576) has moved further to the right and until its top position. This applies to each unit.

In the input container the lower connection is still blocked and the upper connection is connected to the frame bottom opening in the same way as in the previous figures, so that fluid is sucked in through the upper inlet. Thus, since at the beginning of this example the output pressure of the heat exchanger is assumed to be twice the initial input pressure of the input vessel, and since the volume of the output chamber of the input vessel should now be approximately the same. In the heat exchanger, the gas may enter the heat exchanger through an upper outlet. This applies to both the unit (1000,2000) and the compressor (3000).

The estimated pressure at this time, assuming the piston has moved half way to the right, ignores the pressure increase due to the temperature rise, and outputs the relative pressure of the chamber (1434) compared to the device input (612). The first input vessel pressure (1205) is 2. The relative starting pressure of the output chamber (2434) of the second input vessel (2205) is 4, the output chamber of the target compressor (3000)

(3434) 3000) would be 8.

In this configuration and in this position, for both units, the aperture 601 still connects the output chamber of the output container with the array of openings (520,521 and 522), leading to the coupling means (439). But since it is assumed that the pressure of the heated gas is twice the pressure of the cell input (612) and due to the position of the piston, the pressure of the output chamber of the input reservoir and the input chamber of the output reservoir should be approximately the same. Therefore, the pressure of the output chamber of the output container should be approximately the same as the cell input (612). Meaning that the subsequent coupling device (439) should direct the incoming gas recycle (432) rather than directing it to the cooling compressor array (599).

Fig. 27 shows a fourth process step of the preferred embodiment, in which the piston 570(576) has moved further to the right from its top position and slightly downward. This applies to each unit.

The output chamber pressure of the input vessel should be about the same as the heat exchanger from the last process step, and since the gas can move into the heat exchanger, the pressure in all output chambers will remain the same (434 of the input vessel (205)), as in the last process step.

In the input container, the lower connection is still blocked,

the upper connection is connected to the frame bottom opening as in the last step. Thereby drawing fluid through the upper inlet and gas through the upper outlet into the heat exchanger.

In this configuration and in this position, the aperture 601 will still output the output chamber of the container with the array of openings (520,521 and 522) for both units. The subsequent coupling device (439) should direct the incoming gas recycle (432) rather than directing it to the cooling compressor array (599).

When the cell piston wall (1576,2576) moves further down the right to its neutral position, only the injected gas circulates within the device, not the external flow or external volume.

In fig. 28, the piston 570(576 in the output container) is in close proximity to the right sidewall 538 (or 558 in the output container) at its rightmost position and in its neutral vertical position.

In the input container, in this position, the piston blocks the right opening (509,503) and blocks all connections (510,509,502,503).

In the output container, the frame bottom blocks all connections (514,515,519,544).

Fig. 29 shows a sixth process step of a preferred embodiment, in which the piston 570 (and 576 in the output reservoir) is centered between the right and left side walls, but here at its lowest position.

In this position in the configuration, applicable only to the second unit and the compressor (3000), below the middle vertical position of the scroll cycle, i.e. when the piston moves from right to left, the holes 601 are connected to the output chamber of the input container (205) through the array opening (580) and further to the previous array of cooling compressor units, sequentially connecting the output chambers of the input container (205) in parallel to a subset (599) of said array of cooling compressors, in ascending order of the pressure of the cooling compressors. Thereby gradually increasing the pressure in the output chamber from a minimum to a maximum. The minimum pressure in this example represents the input (612) pressure of the device. The process coupling (439) should direct the output gas to its cooling compressor (599) at residual pressure while above the mid-vertical position of the scroll cycle. This applies to the subsequent units and the compressor.

In the input container, the frame bottom still blocks the upper connections (502,503), while the two lower connections (10,509) are exposed through openings 533 and 534, respectively. This will allow liquid to pass from the left side of the piston wall to the right side via internal cross-connects 506. Thus, any pressure increase will be achieved throughout the vessel.

In the output container, the frame bottom still blocks the upper connection (517,515), while the two lower connections (514,519) are exposed through openings 543 and 544, respectively. This will allow fluid to pass from the left to the right side of the piston wall through the internal cross-connect 523.

In the next processing step, the stage shown in fig. 24 is reached and a cycle is completed.

The benefits of the present invention should be apparent. The compressor only needs to compress the gas at the end of the process at a relative pressure of 4 to 8 instead of 1 to 8. It should be noted that this example uses rather extreme temperatures to achieve a 2-fold pressure increase. On the other hand, only two steps are used. With the present invention, such compression is easily performed in many steps, with the highest temperature having a lower temperature when recycled. This lower temperature can then be used in another step and so on.

In this example we use this solution in a heat pump, you can get from fig. 24-29. The device ends with a compressor, followed by a rectifier (3001), a condenser (3002), an expansion valve (3004) and an evaporator (3004), meaning a heat pump or an AC system. All three compressors (1000,2000,3000) take gas from the evaporator, then the second compressor and the conventional compressor compress the internal gas by the previous step. Although not depicted, we can use waste heat from inside or outside the heat pump. If you can reduce the compressor operation by half, you will increase the COP of the heat pump by a factor of two. Although the present invention has been described in connection with preferred embodiments thereof, it should be understood that many other possible modifications and variations could be made thereto without departing from the spirit and scope of the invention as set forth above.

Claims (12)

1. A gas compressor, comprising:

a pressure chamber comprising:

a gas chamber inlet; and

an outlet of the gas chamber;

gas heating apparatus comprising:

a heating chamber comprising a gas heater inlet and a gas heater outlet;

the gas heating means for heating a gas present in the heating chamber to raise the pressure of the gas to a heating pressure, a first portion of the heated gas being discharged into the pressure chamber through the heater outlet, a second portion of the heated gas remaining in the heating chamber; to compress the gas present in the pressure chamber by applying pressure to the gas by the first portion of heated gas, while the pressure of the gas within the heater chamber is reduced below the heating pressure.

2. A gas compressor according to claim 1 wherein the gas heating means further comprises a cooling element for receiving at least a portion of the second portion of heated gas from the heating chamber and for re-using thermal energy of at least a portion of the second portion to heat gas present in the heating chamber.

3. The gas compressor of claim 2, wherein the cooling element comprises a refrigerant for absorbing heat from at least a portion of the second portion of heated gas, the refrigerant also for heating gas entering the heating chamber.

4. A gas compressor according to any one of claims 1 to 3, comprising first and second heating chambers having respective first and second heater inlets and respective first and second heater outlets, wherein the heating chamber inlets are for alternate connection with the first and second heater outlets and the heating chamber outlets are for alternate connection.

5. The gas compressor according to claim 1, comprising,

a high pressure gas chamber;

an array pressurized gas chamber; said array plenum having a series of sub-arrays of pressures lower than the starting pressure of said high pressure plenum and connecting said high pressure plenum and said array plenum;

for releasing gas from the plenum into the array of plenums, sequentially connecting the plenum to the subarrays of the array of plenums in descending order of pressure of the plenums.

6. The gas compressor according to claim 1, comprising,

a low pressure gas chamber;

an array pressurized gas chamber; said array of plenums having a series of pressures above the starting pressure of said low-pressure plenum and connecting said low-pressure plenum and said sub-array of array plenums; for releasing gas from the low pressure plenum into the array of pressurized plenums to sequentially connect the low pressure plenum to the subarrays of the array of pressurized plenums to rank the pressurized plenums in ascending order of pressure.

7. The gas compressor of claim 1, comprising:

the array pressurizes the air chamber of the distributor,

an array receiver plenum having a series of maximum pressures below the array pressurized distributor plenum and connecting the plenum of the array pressurized distributor plenum to the plenum of the array receiver plenum;

a receiver plenum for sequentially connecting a distributor plenum of the array pressurized distributor plenum to the array receiver plenum, wherein the receiver plenum is closest to the pressure of the distributor plenum, having a pressure in the array receiver plenum that is lower than or equal to the pressure of the distributor plenum.

8. A method for compressing gas by using heat energy comprises

a, heating the gas in the heating chamber to a heating temperature to raise the gas pressure thereof to a heating pressure;

b, transferring a first portion of the heated gas in the heating chamber to a pressure chamber having an inlet and an outlet, and compressing the gas at a temperature below the heating temperature to increase the temperature and pressure in the pressure chamber with the transfer of thermal energy, while leaving a second portion of the heated gas in the heating chamber to reduce the gas pressure in the heating chamber to below the heating pressure.

9. A method according to claim 8, wherein the gas in the pressure chamber flows unidirectionally from the pressure chamber inlet to the pressure chamber outlet while controlling the pressure with the gas flow to compensate for a pressure drop caused by the decreasing temperature with the gas flow.

10. The method of claim 8 or 9, further comprising the step of reusing the thermal energy heat to the second portion to heat at least a portion of the gas and to heat new gas entering the heating chamber.

11. The method of claim 10, wherein the step of reusing thermal energy to heat at least a portion of the second portion of heated gas comprises a cooling element in a heater absorbing thermal energy of gas derived from a condensing agent and heating the fresh gas with the condensing agent.

12. A heat pump comprising as a overconventive compressor, a gas compressor according to any of the preceding claims 1-7, wherein said gas compressor uses thermal energy to additionally compress gas before or after it passes through said overconventive compressor.

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