EA044627B1 - HEAT EXCHANGE SYSTEM - Google Patents

Description

State of the art

Thermal power cycles typically use either a Brayton cycle with a direct combustion air-jet gas turbine or a closed indirectly heated Rankine cycle with steam as the working fluid. High efficiencies are obtained by combining the Brayton cycle with saturation in the Rankine cycle to form a combined cycle. While combined cycle power generation can achieve high productivity, combined cycle power generation is not suitable for CO2 capture, and the construction may incur high capital costs due to the large amount of equipment and piping network required. In some cases, supercritical carbon dioxide (CO2) thermodynamic Brayton cycle (SCCO2) can be used in thermal power cycles. The Brayton supercritical carbon dioxide (CO2) thermodynamic cycle (SCCO2) can beneficially reduce greenhouse gas (GHG) emissions, improve carbon capture, provide high efficiency, reduced footprint and less water consumption. However, there are some technical problems that must be resolved before the supercritical carbon dioxide (CO2) thermodynamic Brayton cycle can realize its benefits. In particular, a current area of research and development is the design and operation of recuperative heat exchangers for these supercritical carbon dioxide (CO2) thermodynamic Brayton cycles (SCCO2).

A semi-closed oxygen-fuelled Brayton cycle may be called the Allam power cycle or Allam cycle. The Allam cycle is the process of converting fossil fuels into mechanical energy, while trapping the carbon dioxide and water produced. Typically, the Allama cycle requires an economizer-heat exchanger and an additional external low-grade heat source to achieve high efficiency comparable to existing combined cycle technology, with the key added benefit of capturing CO2 for use or storage. The efficiency of the Allam cycle increases if the turbine operates at high temperatures, typically above 600°C, and at high pressures between 120 and 400 bar (12-40 MPa). These conditions lead to the attendant requirements of high pressure and high temperature and high performance of the heat exchange system. Typically, multiple individual heat exchange units are required and these must be arranged in a network to create a recuperative heat exchanger, while simultaneously recovering heat from an external low grade heat source. Examples of traditional heat exchange systems and methods can be found in such patent documents as US Patent No. 8,272,429; US Patent No. 8,596,075; US Patent No. 8,959,887; US Patent No. 10,018,115; US Patent No. 10,422,252; and US Patent Publication No. 2019/0063319. All of them are included here by reference.

Typically, heat exchange systems can be divided into high, medium and low temperature sections. While it is desirable to cool the exhaust gas in the high-temperature section to the lowest possible temperature (eg, the same temperature as the low-grade heat source), this is contrary to the mechanical requirements that dictate the design, cost, and reliability of such a system. Typically, the design temperatures and pressures in the high temperature section are set to the highest temperature and pressure, which in turn determine the mechanical requirements.

The essence of the invention

This summary provides an introduction to the selection of principles that are further described in detail below. This summary is neither intended to identify key or essential features of the claimed subject matter, nor is it intended to be used as a limitation on the scope of the claimed subject matter.

In one aspect, the embodiments disclosed herein relate to a system. The system may include a turbine and a recuperative heat exchange system. The recuperative heat exchange system is designed to receive exhaust gases from the turbine. The recuperative heat exchange system may include a pre-cooling section for cooling the exhaust gases, a main heating section for receiving the cooled exhaust gases, and an auxiliary heating section for receiving the cooled exhaust gases.

In yet another aspect, embodiments disclosed herein relate to a method. The method may include generating exhaust gas in a turbine; supplying the exhaust gas to a pre-cooling section of the recuperative heat exchange system to cool the exhaust gas; separating the cooled exhaust gas into a main flow path feeding the main heating section of the recuperative heat exchange system, and an auxiliary flow path feeding the auxiliary heating section of the recuperative heat exchange system; flowing in an auxiliary flow path of cooled exhaust gas through a first auxiliary heat exchanger of the auxiliary heating section and a second auxiliary heat exchanger of the auxiliary heating section; flowing in a main flow path of the cooled exhaust gas through a first main heat exchanger of the main heating section, a second main heat exchanger of the main heating section, and a third main heat exchanger of the main heating section; and formation

- 1 044627 combustion chamber associated with a turbine, with fluid flowing from a main flow path and an auxiliary flow path.

In yet another additional aspect, the embodiments disclosed herein relate to a pre-cooling heat exchanger. The pre-cooling heat exchanger may include a first annular shell creating a pressure boundary. The first annular shell may have an exhaust gas inlet for receiving exhaust gas from the turbine, and one or more exhaust outlets for removing the exhaust gas. The pre-cooling heat exchanger may also include a second annular shell disposed within the first annular shell. The pre-cooling heat exchanger may further include a tube bundle disposed within the second annular shell. In addition, an annular distributor device may be provided within the second annular shell, the annular distributor device being configured to control the flow of exhaust gas entering the tube bundle.

In one aspect, the embodiments disclosed herein relate to a recuperative heat exchange system. The recuperative heat exchange system may include a pre-cooling section within the first rigid frame, an auxiliary section within the third rigid frame, and a first main section within the second rigid frame. The pre-cooling section may include one or more heat exchangers for receiving and cooling the exhaust gases. The auxiliary section may include a first auxiliary heat exchanger and a second auxiliary heat exchanger. The first main section may include a first main heat exchanger, a second main heat exchanger, and a third main heat exchanger.

In yet another aspect, embodiments disclosed herein relate to a method. The method may include cooling the exhaust gases with a pre-cooling section within the first rigid frame; separating the exhaust gases by means of a manifold located outside the first rigid frame into a first main section inside the second rigid frame, a second main section inside the third rigid frame, and an auxiliary section inside the third rigid frame; flowing exhaust gases into the auxiliary section through a first auxiliary heat exchanger of the auxiliary section, and into a second auxiliary heat exchanger of the auxiliary section through one or more curved flow circuits; flowing exhaust gases into the first main section through a first main heat exchanger of the first main section and a second main heat exchanger of the first main section, and then a third main heat exchanger of the first main section, through one or more curved flow circuits; flowing exhaust gases into the second main section through a first main heat exchanger of the second main section and a second main heat exchanger of the second main section, and then a third main heat exchanger of the second main section through one or more curved flow circuits; flowing exhaust gases from the second auxiliary heat exchanger, the third main heat exchanger of the first main section and the third main heat exchanger of the second main section into the exhaust gas header through the secondary curved flow circuits.

In one aspect, the embodiments disclosed herein relate to a heat exchange system including a rigid frame. The first heat exchanger may be coupled to a first support structure on top of the rigid frame. A second heat exchanger may be placed underneath the first heat exchanger. The second heat exchanger may be coupled to a second support structure, wherein the second support structure is suspended from a rigid frame by a first set of hangers, wherein the first set of hangers may be configured to move the second support structure vertically and horizontally. A second set of hangers may be coupled to the second support structure and extend downward to suspend the support beam. A third set of hangers may be coupled to the support beam and extend downwardly to suspend the third support structure, and the third set of hangers may be configured to accommodate vertical and horizontal movement of the third support structure. The third heat exchanger may be connected to the third support structure. The vertical and horizontal movement of the second support structure may be based on thermal expansion of the second heat exchanger. The vertical and horizontal displacement of the third support structure may be based on thermal expansion of the third heat exchanger.

In yet another aspect, embodiments disclosed herein relate to a heat exchange system including a rigid frame. The first heat exchanger may be coupled to a first support structure on top of the rigid frame. A second heat exchanger may be placed underneath the first heat exchanger. The second heat exchanger may be coupled to the second support structure. The second support structure may be suspended from the rigid frame by a first set of hangers. The first set of hangers may be designed to vertically and horizontally move the second support structure. The vertical and horizontal movement of the second support structure may be based on thermal expansion of the second heat exchanger.

In yet another additional aspect, the embodiments disclosed herein relate to a heat exchange system including a rigid frame. The first support structure can be suspended from

- 2 044627 rigid frame by means of a first set of hangers having one end connected to the rigid frame and another end connected to the first support structure. The first set of hangers can be designed to accommodate vertical and horizontal movement of the first support structure. The first heat exchanger may be coupled to the first support structure. A second set of hangers may be coupled to the first support structure and extend downward to suspend the support beam. The third set of hangers may be connected to the support beam and extend downward to suspend the second support structure. The third set of hangers can be designed to accommodate vertical and horizontal movement of the second support structure. The vertical and horizontal displacement of the first support structure may be based on thermal expansion of the first heat exchanger. The vertical and horizontal movement of the second support structure may be based on thermal expansion of the second heat exchanger.

Other aspects and advantages of the invention will be apparent from the following description and the appended claims.

Brief description of drawings

Figures 1A and 1B illustrate a schematic view of a power generation system in accordance with one or more embodiments of the present invention.

Fig. 2 illustrates a schematic view of a recuperative heat exchange system in accordance with one or more embodiments of the present invention.

Fig. 3 illustrates a cross-sectional view of a pre-cooling heat exchanger in accordance with one or more embodiments of the present invention.

Figures 4A and 4B illustrate a perspective view of a recuperative heat exchange system in accordance with one or more embodiments of the present invention.

Fig. 4C is a side view of the recuperative heat exchange system of Figures 4A and 4B in accordance with one or more embodiments of the present invention.

Fig. 4D is a top view of the recuperative heat exchange system of Figures 4A and 4B in accordance with one or more embodiments of the present invention.

Fig. 5A is a side view of a heat exchange system in accordance with one or more embodiments of the present invention.

Fig. 5B is a side view of the heat exchanger suspension system of FIG. 5A in accordance with one or more embodiments of the present invention.

Figures 6-9 are side views of a heat exchange system in accordance with one or more alternative embodiments to Figure 5A.

Detailed Description of the Invention

Embodiments of the present invention are described in detail below with reference to the accompanying figures. Similar elements in different figures may be designated by the same numbers for consistency. In addition, in the following detailed description, numbered specific details are set forth so as to provide a more complete understanding of the claimed subject matter. However, it will be apparent to one of ordinary skill in the art that the described embodiments can be implemented without these specific details. In other examples, well-known features have not been described in detail to avoid unnecessary complexity of the description. As used herein, the term associated or associated with, or connected or connected to, may indicate the establishment of either a direct or indirect connection, and is not limited to one of them unless specifically indicated thereto. As used herein, fluids may include suspensions, liquids, gases, and/or mixtures thereof. To the extent possible, similar or identical reference numerals are used in the figures to identify common or the same elements. The figures are not necessarily drawn to scale, and certain features and certain views in the figures may be shown exaggerated to scale for purposes of explanation.

In one aspect, embodiments disclosed herein relate to a power generation system for power generation, petrochemical plants, waste heat recovery, and other industrial applications. The power generation system may also be interchangeably referred to in the present invention as a recuperative heat exchange system in the form of a network or array of heat exchangers. In addition, the recuperative heat exchange system may include a pre-cooling section to reduce the temperature of the turbine exhaust gas. A regenerative heat exchange system can minimize the lifetime cost of heat exchangers, which are critical for efficient regenerative heat exchange at high pressures and high thermal efficiencies. In some embodiments, the recuperative heat exchange system can be used for supercritical carbon dioxide (SCCO2) thermodynamic cycles, such as the Allam cycle.

In yet another aspect, embodiments disclosed herein relate to a recuperative heat exchange system for power generation, petrochemical plants, waste heat recovery, and other industrial applications. The recuperative heat exchange system is also

- 3 044627 can be interchangeably referred to in the present invention as a network or set of heat exchangers. In addition, the recuperative heat exchange system may include a pre-cooling section to reduce the temperature of the turbine exhaust gas. A regenerative heat exchange system can minimize the lifetime cost of heat exchangers, which are critical for efficient regenerative heat exchange at high pressures and high thermal efficiencies. In some embodiments, the recuperative heat exchange system can be used for supercritical carbon dioxide (SCCO2) thermodynamic cycles, such as the Allam cycle.

In yet another additional aspect, embodiments disclosed herein relate to a heat exchange system for power generation, petrochemical plants, waste heat recovery, and other industrial applications. A heat exchange system may also be interchangeably referred to in the present invention as a network or array of heat exchangers. In addition, the heat exchange system may include a heat exchanger suspension system to minimize thermal expansion stresses resulting from thermal expansion of the heat exchangers and associated piping network. A heat exchanger suspension system can minimize the lifetime cost of heat exchangers, which are critical for efficient regenerative heat exchange at high pressures and high thermal efficiencies. In some embodiments, the heat exchanger suspension system can be used for supercritical carbon dioxide (SCCO2) thermodynamic cycles, such as the Allam cycle.

The recuperative heat exchange system, as embodied herein, may include a combination of Printed Circuit (PCHE) and Shell and Tube (STHE) heat exchangers. For example, a recuperative heat exchange system may include a pre-cooling section, a main heating section (recirculation heating), and an auxiliary heating section (oxidizer heating). In some embodiments, the heat recovery section may optionally be connected to the main heating section and/or the auxiliary heating section.

In one or more embodiments, a recuperative heat exchange system may employ a network of heat exchangers that includes parallel sections for heating a smaller portion of the high-pressure gas and a major portion of the high-pressure gas. A minor portion may consist of oxygen-containing CO2 (oxidizing agent), and the major portion may be composed of the remaining amount of recirculating CO2 (recycled CO2). Two parallel sections may have significantly different temperature profiles. In one non-limiting example, the major portion (about 75% of the total flow, in the range of 51-90%) may be heated to a lower temperature than the minor portion. A smaller portion may first be heated to an intermediate temperature of approximately 440°C (range 350-550°C) before being used to pre-cool the entire high temperature exhaust stream from a high temperature of approximately 600°C (range 550-850°C ) to a temperature low enough to avoid significant mechanical design limitations, and in particular to temperatures below 575°C. The 575°C limit may represent a mechanical design limitation when using diffusion-welded RSHE, and when fabricated from austenitic stainless steel, and in particular from alloy 316/316L. Alloy 316 RSNE blocks may require stress tolerances determined by time-dependent behavior (creep) at temperatures above 575°C. In addition, a heat recovery section may be provided in the recuperative heat exchange system. The heat recovery section can add heat at a temperature below the combustion temperature, such as low grade heat.

Traditional power generation systems in industrial applications are typically extremely large and heavy. Traditional power generation systems can involve an extensive system and arrangement of pipes that take up large amounts of space and weigh several tons each. In some situations, large heat exchangers are connected in series and may involve complex rotations or changes in orientation. In addition, large lines are required to introduce fluids into the heat exchangers and as fluids exit the heat exchangers. Such power generation systems may be both heavier in weight and may also be more expensive to manufacture due to the sheer number of parts and components. For example, expansion joints are used to accommodate the expansion of pipelines within the system. These additional pipes in the expansion joints, required to connect the various lines and heat exchangers to each other, add weight, installation costs, and overall costs to the power generation systems.

Accordingly, one or more embodiments of the present invention can be used to overcome such problems, as well as achieve additional benefits.

- 4 044627 entities in front of traditional energy generation systems, as will be obvious to a person with ordinary qualifications. In one or many embodiments, the recuperative heat exchange system may be lighter in weight and less expensive than traditional power generation systems due, in part, to minimizing the combined effects of creep and fatigue/damage, independent oxidation and regeneration sections, so that control the separation of the exhaust fluid stream through one or more low temperature valves, and the exhaust fluid leaving the turbine does not require a surge tank located between the turbine and the recuperative heat exchanger. In addition, a recuperative heat exchange system can improve reliability and performance over thousands of hours where certain components of the recuperative heat exchange system are exposed to high pressures, high temperatures and operating cycles. Overall, a recuperative heat exchange system can minimize product engineering design, flow circuit manufacturing risk, reduce assembly time, reduce equipment cost, and reduce weight and work area.

With reference to FIG. 1A, fig. 1A shows a schematic view of a power generation system 100 in accordance with one or more embodiments of the present invention. In one or many embodiments, the turbine 101 may receive energy from a fuel source 102 through a combustion chamber 103 . As is known in the art, such a turbine 101 may be a structure useful for extracting energy from a fluid stream and converting the fluid stream into useful work, such as driving a generator to produce electricity, and a frequently rotating device with other components (i.e. , rotor, stator, and/or turbine blades) performing various functions related to the production or conversion of mechanical energy. It should be noted that turbine 101, in one or more embodiments, may be configured as a gas or steam turbine. The combustion chamber 103 may be a component of the turbine 101 where combustion occurs, such as a chamber. In addition, an oxygen supply 112 may be provided to supply oxygen to the combustion chamber 103. As will be known to one of ordinary skill in the art, turbine 101 may produce exhaust gases 104. Exhaust gases 104 may be routed to a recuperative heat exchange system 105 (see dotted line square) to form a turbine exhaust gas stream.

In one or many embodiments, the recuperative heat exchange system 105 may include a pre-cooling section 200, a main heating section 301, and an auxiliary heating section 302. In some embodiments, the main heating section 301 may be a recirculating heating section, and the auxiliary heating section 302 may be oxidizing heating section. The precooling section 200 may be high temperature precoolers having a shell and tube type design in which the shell may be combined with a ring distributor. Both the main section 301 and the auxiliary section 302 may include at least two heat exchangers stacked vertically on top of each other to form a vertical modular heat exchanger stack.

Still with reference to FIG. 1A, all of the exhaust gas 104 exiting the turbine may be directed to the pre-cooling section 200. Pre-cooling section 200 may cool exhaust gas 104 with a smaller portion of the heated high-pressure gas, and preferably through oxygen flow, before being redistributed to independent parallel circuits (eg, main section 301 and auxiliary section 302). In this way, the exhaust gas 104 can be directly cooled before entering the main section 301 and auxiliary section 302, with significant cost savings and increased reliability. In addition, manifold 205 may optionally be used to separate the cooled exhaust gas 104 into streams entering the main section 301 and the auxiliary section 302. The cooled exhaust gas 104 may be divided into a main flow path 131 supplied to the main section 301 and a minor path stream 130 supplied to the auxiliary section 302. Additionally, one or more valves 106 may be used to coordinate the splitting of the exhaust gas stream 104 flowing from the main section 301 and entering the auxiliary section 302. In addition, in both of the main section 301 and auxiliary section 302 may be provided with hydraulic resistances to match the flow of exhaust gas 104. In addition, flow may exit the main section 301 through pressure conduits 133, while flow may exit the main section 302 through pressure conduits 132. In some embodiments, One or more valves 106 may be located in the pressure lines 132.

In some embodiments, the heat recovery systems may be operatively coupled to the recuperative heat exchange system 105. The heat recovery systems may add heat at a temperature below the combustion temperature. Additional examples of heat recovery systems include, but are not limited to, direct or indirect addition of heat (via low grade heat source 108) to the turbine exhaust gas stream, reclaimed heat from an air separation unit

- 5 044627 (ASU) associated with the compressor (not illustrated), or reclaimed heat from the recirculation gas compressor exiting the compressor (not illustrated). In one non-limiting example, flow line 134 from pump 111 may supply to auxiliary section 302, while flow line 135 from pump 111 may supply to main section 301. In addition, separator 109 may separate liquid condensate from exhaust gas so that liquid condensates 109a be collected. In addition, the compressor 110 may be coupled to the separator 109. In addition, an outlet pressure line 138 extending from the pump 111 may be configured to remove carbon dioxide (CO2) as a product from the power generation system 100. In some embodiments, heat recovery systems may be built into the main section 301. In addition, it is provided that a series of manifolds within the heat recovery and recirculation sections may be used to redistribute the high pressure recycled carbon dioxide, and provide release points for various cooling streams. turbines that may be required. In addition, a first pressure return line 136 from the main section 301 and a second pressure return line 137 from the auxiliary section 302 may be provided to supply the combustion chamber 103 with a fluid flow from the main section 301 and the auxiliary section 302.

Referring now to FIG. 1B, another embodiment of a power generation system 100 according to the embodiments shown herein is illustrated, wherein like numerals represent like parts. The embodiment according to Fig. 1B is similar to the embodiment in FIG. 1A. However, instead of just one heat exchanger, the main section 301 and the auxiliary section 302 may in each case include two or many vertical modular heat exchanger stacks in series connection. PCHE units may have a maximum size based on the size of the plate that can be placed inside the diffusion-welded furnace, and thus may be advantageous in that they have more than one vertical modular heat exchanger stack. In some embodiments, it may be necessary to redistribute the high-pressure flow between the main section 301 and the heat recovery section, and thus it may be advantageous to have more than one vertical modular heat exchanger stack.

Fig. 2 illustrates a schematic close-up view of a recuperative heat exchange system 105 according to the embodiments shown herein, where like numbers represent like parts. As depicted by arrows 104, exhaust gas flowing from the turbine may enter the pre-cooling section 200 through one or more transfer lines. In one non-limiting example, four nominally identical transfer lines may be used to transfer off-gas (arrows 104) to pre-cooling section 200. It should be noted that any number of transfer lines may be used without departing from the scope of the present invention.

In one or many embodiments, the precooling section 200 may include one or more shell and tube heat exchangers (STHE) 201. These STHE 201 precooling sections 200 may be made of a material selected from Inconel (Inconel, e.g., alloy 625 or alloy 617) , or similar material which is not subject to change in properties with time at the highest temperature. One or more transfer conduits may be connected to STHE 201 on the shell 202 side. In one non-limiting example, each STHE 201 may have one transfer conduit connected thereto. At tube side 203 in STHE 201, STHE 201 may receive a flow of fluid (eg, oxidizer fluid) from the auxiliary section (302a, 302b). In some embodiments, the mass heat capacity (e.g., mass flow loss heat capacity) of the fluid on the tube side of STHE 201 may be less than the mass heat capacity of the exhaust gas (arrows 104) entering STHE 201 on the shell side 202. Due to the low mass heat capacity of the oxidizing fluid on On the pipe side, the change in temperature of the exhaust gas may be small (for example, by 15-50°C), while the change in temperature of the oxidizer flow can be large (for example, by 100-200°C). It is further contemplated that STHE 201 may include an outlet 204 for discharging a heated oxidizer stream. From STHE 201, off-gas may flow to manifold 205 to separate the off-gas stream.

In some embodiments, the manifold 205 may separate the exhaust gas into different flow paths. In one non-limiting example, manifold 205 separates waste gas into two flow paths, such as a minor waste gas stream 206 and a main waste gas stream 207.

In the smaller exhaust gas stream 206, the exhaust gas flows through an auxiliary section having a first auxiliary heat exchanger 302a and a second auxiliary heat exchanger 302b. Both of the first auxiliary heat exchanger 302a and the second auxiliary heat exchanger 302b may be a printed circuit type heat exchanger (PCHE), a spiral wound type heat exchanger, a microtubular heat exchanger, a diffuse welded heat exchanger using stamped plates in addition to etched plates, or a heat exchanger of any

- 6 044627 other type. In addition, both of the first auxiliary heat exchanger 302a and the second auxiliary heat exchanger 302b can be formed from a suitable material such as dual standard 316/316L stainless steel. In addition, the first auxiliary heat exchanger 302a may operate at a higher temperature than the second auxiliary heat exchanger 302b. In addition, the off-gas can be used to preheat the smaller stream 134 to 350-500°C. In some embodiments, both the first auxiliary heat exchanger 302a and the second auxiliary heat exchanger 302b may be used to heat the oxidizer.

In the main exhaust gas flow 207, the exhaust gas flows through a main section having a first main heat exchanger 301a, a second main heat exchanger 301b, and a third main heat exchanger 301c. Each of the main heat exchangers 301a, 301b, 301c may be a printed circuit type heat exchanger (PCHE), a wound coil type heat exchanger, a microtubular heat exchanger, a diffusion welded heat exchanger using stamped plates in addition to etched plates, or any other type of heat exchanger. In addition, the first main heat exchanger 301a may operate at the highest temperature in the main section, while the third main heat exchanger 301c may operate at the lowest temperature in the main section. The second main heat exchanger 301b may operate at a temperature between the temperatures of the first main heat exchanger 301a and the third main heat exchanger 301c. In addition, each of the main heat exchangers 301a, 301b, 301c may be made of dual standard 316/316L stainless steel material. In addition, the main exhaust gas stream 207 can be used to preheat the main stream 135 to 520-650°C. In some embodiments, each of the main heat exchangers 301a, 301b, 301c can be used to heat the recirculated CO2. In addition, a second flow line 304 may be used to supply a cooled stream to the turbine. In one non-limiting example, the cooled stream may be the exit recycle gas 107a or 301b. In some cases, the cooled stream temperature may not match the required turbine coolant temperature. To match the required turbine coolant temperature, hot gas or cold gas may be added to the cooling stream to raise or lower the temperature to match the desired turbine coolant temperature. In some embodiments, the cooling stream may be a mixture formed by mixing the outgoing recycle stream 107a or 301b and the outgoing recycle stream 301a at a higher temperature.

In some embodiments, the balance of exhaust gas flow between the auxiliary section (302a, 302b) and the main section (301a, 301b, 301c) can be adjusted by means of hydraulic resistances in the auxiliary section (302a, 302b) and in the main section (301a, 301b, 301c) ). In one non-limiting example, one or more valves at the outlet (ie, cold end) of the auxiliary section (302a, 302b) may be used to balance the flow.

In heat recovery stream 208, recirculated exhaust gas or a separate low-grade heat stream may be used to add heat at a temperature below the combustion temperature through the first recuperative heat exchanger 107a and the second recuperative heat exchanger 107b. In some embodiments, the recirculated exhaust gas may be exhaust gas that is preheated and recirculated back through the recovery sections 107a and 107b. Both of the first recuperative heat exchanger 107a and the second recuperative heat exchanger 107b may be a printed circuit type heat exchanger (PCHE), a wound coil type heat exchanger, a microtubular heat exchanger, a diffuse welded heat exchanger using stamped plates in addition to etched plates, or any other type of heat exchanger. In addition, each of the first recuperative heat exchanger 107a and the second recuperative heat exchanger 107b may be formed from a suitable material such as dual standard 316/316L stainless steel. In addition, the first recuperative heat exchanger 107a may be at a higher temperature than the second recuperative heat exchanger 107b. In some embodiments, the first recuperative heat exchanger 107a and the second recuperative heat exchanger 107b may be integrated into the second main heat exchanger 301b and the third main heat exchanger 301c, respectively.

In one or many embodiments, the pre-cooling section 200 may cool the exhaust gas. In one non-limiting example, off-gas 104 may be pre-cooled to a temperature of 575°C. By precooling the exhaust gas 104 to 575°C, the available temperature difference for the first main heat exchanger 301a can be reduced. This can be compensated for by using additional heat transfer surface area, or by increasing the overall heat transfer coefficient. The product of the overall heat transfer coefficient and the heat transfer surface area can be called UA, the value of which is equivalent to the thermal load divided by the average temperature difference LMTD, which can be calculated from those

- 7 044627 temperatures at the inlet and outlet of the hot stream and cold stream. The UA value of a heat exchanger can be related to the cost of the heat exchanger. By including a pre-cooling section 200 in the recuperative heat exchange system 105, the overall UA value can be generally increased by about 15%. However, the cost difference (e.g., cost/UA value) between high temperature sections and low temperature sections may be less than the total cost of the recuperative heat exchange system 105. In one non-limiting example, the cost/UA value of systems above 575°C may be greater than 30%, higher than the cost/UA value of systems below 575°C. The regenerative heat exchange system 105 can provide lower cost/UA by increasing equipment life expectancy and reducing material usage due to higher stress tolerance for heat exchangers at temperatures below 575°C. Although the Inconel material of the precooling section 200 may be a more expensive material, the amount of material required is relatively small due to the higher LMTD in the precooling section 200, which reduces the required UA value.

The embodiments presented herein regarding the operation of the recuperative heat exchange system 105 may be implemented using a computer system. Any combination of mobile device, desktop device, server, router, switch, embedded device, or other types of equipment may be used with the regenerative heat exchange system 105. For example, a computing system may include one or more computer processors, a random access memory (e.g., volatile memory such as random access memory (RAM), cache memory), a persistent storage device (e.g., a hard disk drive, an optical disk drive, such as a compact disc (CD) or digital versatile disc (DVD) drive, flash memory, etc.), communication interface (such as Bluetooth interface, infrared interface, network interface, optical interface, etc.) , and numerous other elements and functionality. It is further contemplated that software instructions may be stored in the form of computer readable program code for executing embodiments of the invention, in whole or in part, temporarily or permanently, on a non-volatile computer readable medium such as a CD, DVD, storage device, floppy disk, tape, flash memory, physical memory, or any other computer-readable storage medium. For example, the software instructions may correspond to a computer-readable program that, when executed by the processor(s), is configured to execute one or more embodiments of the invention.

In one or more embodiments, a pre-cooling heat exchanger may be used in the recuperative heat exchange system. The pre-cooling heat exchanger may be a shell and tube heat exchanger (STHE) for distributing exhaust gas from the turbine. In some embodiments, instead of being a STHE, the pre-cooling heat exchanger may be a printed circuit heat exchanger (PCHE), a coil-wound type heat exchanger, a microtubular heat exchanger, a diffusion-welded heat exchanger using stamped plates in addition to etched plates, or any other type of heat exchanger type. The pre-cooler heat exchanger, in turn, can supply exhaust gas directly to the heat exchangers, thereby eliminating the need for a large high-temperature exhaust manifold. In one non-limiting example, the STHE may replace a large high temperature exhaust manifold so that turbine exhaust gases can be directly cooled before entering the auxiliary (oxidizer stream) section and main (recycle stream) section of the recuperative heat exchange system. In some embodiments, the pressurized components of the pre-cooling heat exchanger may be made of a material selected from Inconel (for example, alloy 625 or alloy 617) or similar material that does not change properties over time at the highest temperature. The internal components of the pre-cooling heat exchanger 500, which are non-pressure-bearing parts, may be formed from stainless steel or similar materials.

In one or more embodiments, fluid may enter the center and split into two streams (one flowing to the right and one flowing to the left). Fluid may exit the heat exchanger through two or more separate outlets. The flows can be combined again outside the heat exchanger by means of a pipe system. In some embodiments, fluid may enter two or many points, combine, and ultimately exit through a single outlet nozzle. Large pressure changes can cause pipeline vibration, which can damage pipes and casings. As a result, splitting the flow in a heat exchanger can be beneficial in reducing the risk of damage due to vibrations, and can reduce pressure drops associated with the heat exchange system.

In some embodiments, the heat exchanger may be a dual-split heat exchanger. This means that the heat exchanger can have two zones where the flow is divided and then reconnected, as well as two support plates. When the pressure drop needs to be kept low, a split shell design can be used. Additionally, a split-shell heat exchanger design may eliminate baffle plates and mount a single support plate in the center of the shell.

With reference to FIG. 3, in one or more embodiments of FIG. 3 illustrates a pre-cooling heat exchanger 500, which may have two annular shells 501, 502 and a distribution section 513. The first annular shell 501 may be an outer shell defining a pressure boundary. In addition, the first annular shell 501 may include an exhaust gas outlet 503, which may be located on the shell side 504 for receiving exhaust gas from the turbine. A supply pipe from the turbine may be connected to the exhaust gas outlet 503. Additionally, a stationary head duct 505 may be provided at the end of the precooling heat exchanger 500 with an inlet 506 and an outlet 507. A dividing wall 508 may be provided within the stationary head duct 505 to separate flow between the inlet 506 and the outlet 507. The inlet 506 may be used to receiving oxidizer from the auxiliary section. It is further provided that one or more exhaust outlets 515 may be provided on the shell side 504 to discharge the exhaust stream.

Still with reference to FIG. 3, the second annular casing 502 may be an inner casing or casing around the tube bundle 509 with two or multiple passages on the tube side. The tube bundle 509 may be a U-shaped tube bundle. The support plate 511 is designed to support the weight of the tube bundle 509 and prevent excessive tube load on the tube sheet and connection of the channel assembly 505. In some embodiments, the large difference between the flow velocities at shell side 504 and tube side 509 means that multiple passes may be used to maintain proper tube side 509 velocity and heat transfer coefficient. In addition, the ring distributor 513 may replace the function of the exhaust manifold by gradually slowing the flow of exhaust gas and creating a controlled entry into the tube bundle 509. The ring distribution device may be provided with slots that are rectangular or oval, and with an open area that decreases the further away from the inlet 503. Additionally, the tube bundle 509 may have rod or grid type baffles to support the tubes and placed rather on a damping ring. 514 than on standard segmented partitions. It is further contemplated that within the pre-cooling heat exchanger 500, insulation 517 may be provided between the various internal components.

Now with reference to FIG. 4A, in one or more embodiments of FIG. 4A illustrates a perspective view of the recuperative heat exchange system 105. The various components of the recuperative heat exchange system 105 may be mounted in a top-down configuration within one or more rigid frames (120, 121, 122, 123). A downward configuration may be arranged such that the components of the recuperative heat exchange system 105 that operate at the highest temperature are located in the highest vertical position, while the components of the recuperative heat exchange system 105 that operate at the lowest temperature are located in the lowest vertical position. position In one non-limiting example, pre-cooling section 200 may be within a first rigid frame 120, a first main section 301 may be within a second rigid frame 121, a second main section 305 may be within a third rigid frame 122, and an auxiliary section 302 may be within a fourth rigid frame. 123. Each of the rigid frames 120, 121, 122, 123 may be made of multiple vertically oriented structural members 124 and multiple horizontally oriented structural members 125. In one non-limiting example, multiple vertically oriented structural members 124 and multiple horizontally oriented structural members 125 may be interconnected with each other to form a rectangular frame around the various components of the recuperative heat exchange system 105. It is further contemplated that the plurality of vertically oriented structural members 124 and the plurality of horizontally oriented structural members 125 may be inclined to any degree without departing from the scope of the present invention. The plurality of vertically oriented structural members 124 and the plurality of horizontally oriented structural members 125 may be formed from a metallic material such as steel, stainless steel, cast iron, or any other type of metal.

In some embodiments, the precooling section 200 may include one or more shell-and-tube heat exchangers (STHEs) 201a, 201b, 201c, 201d within the first rigid frame 120. In one non-limiting example, a first STHE 201a, a second STHE 201b, a third STHE 201c, and a fourth STHE 201d can be placed in parallel. In addition, all four STHEs 201a, 201b, 201c, 201d may operate at substantially the same temperature. Additionally, it should be noted that, while in FIG. 4A shows four STHEs 201a, 201b, 201c, 201d, this is provided as an example only, and any number of STHEs may be used without departing from the scope of the present invention. All four STHE 201a, 201b, 201c, 201d may be made of a material selected from Inconel (for example, Alloy 625 or Alloy 617), or a similar material that does not change properties with time at the highest design service temperature. In addition, each of the STHEs 201a, 201b, 201c, 201d may be provided with pre-cooling section inlets 209 to receive exhaust gases from the turbine. Each precooling section inlet 209 may have a transfer line connected to the turbine such that the number of transfer lines matches the number of STHE. In addition, outlets 204 may be provided at each STHE 201a, 201b, 201c, 201d to allow heated oxidizer to be discharged from the precooling section 200.

Each STHE 201a, 201b, 201c, 201d may be provided with inlets 212 to allow heated oxidizer to enter the precooling section 200 from the auxiliary section 302. In one non-limiting example, an oxidizer manifold 211 may be provided between the auxiliary section 301 and the precooling section 200 . The oxidizer supply lines 212 may be connected to the inlets 210 of each STHE 201a, 201b, 201c, 201d from the oxidizer manifold 211 and the auxiliary section 302. In addition, the oxidizer inlet 306 may be located in the fourth rigid frame 123 to allow the oxidizer to flow through connection to the auxiliary section 302. In addition, on the pipe side, exhaust gas exits each STHE 201a, 201b, 201c, 201d to enter the manifold 205 through the supply pipes 213. The manifold 205 may be located outside one or more rigid frames (120, 121 , 122, 123) and downstream of the pre-cooling section 200 in the direction of the outflow.

In some embodiments, manifold 205 may be used to separate a waste gas stream into an auxiliary section 302, a first main section 301, and a second main section 305. Flow circuits 214 may be used as a conduit for waste gas flowing from manifold 205 to an auxiliary section 302 , a first main section 301 and a second main section 305. In one non-limiting example, the flow circuits 214 may extend from the manifold 205 to individual heat exchangers (301a, 302a, 305a) at each of the auxiliary section 302, the first main section 301 and the second main section 305 .

In auxiliary section 302, exhaust gas flows through flow circuits 214 into first heat exchanger 302a, and then into second heat exchanger 302b. In one non-limiting example, one or more curved flow paths 214 may be used as a conduit for exhaust gas to flow from the first heat exchanger 302a to the second heat exchanger 302b. In addition, the secondary curved flow paths 216 may be used to flow exhaust gas from the second heat exchanger 302b to the exhaust gas manifold 217 of the recuperative heat exchange system 105. In addition, the secondary curved flow paths 216 may be provided with one or more flow equalization valves 218. In a downward configuration, the first heat exchanger 302a may operate at a higher temperature than the second heat exchanger 302b. In one or many embodiments, the uppermost heat exchanger may be exposed to higher temperatures, and therefore it is critical that the uppermost heat exchanger be accessible for maintenance and inspection. In addition, the uppermost heat exchanger may not experience expansion as much as possible without being constrained by connections to other heat exchangers.

With reference to FIG. 4B, in one or more embodiments, illustrates a perspective view of the recuperative heat exchange system 105 obtained by rotating FIG. 2A 90 degrees counterclockwise. In the first main section 301, exhaust gas flows through flow circuits 214 into a first heat exchanger 301a to then flow into a second heat exchanger 301b, and then into a third recirculation heat exchanger 301c. In one non-limiting example, one or more curved flow paths 306 may be used as a conduit for exhaust gas to flow from first heat exchanger 301a to second heat exchanger 301b. In addition, secondary curved flow paths may be used to flow exhaust gas from the second heat exchanger 301b to the third heat exchanger 301c. In addition, the supply lines 308 may be used to flow exhaust gas into the exhaust gas manifold 217 from the third recirculation heat exchanger 301c. In a downward configuration, the first heat exchanger 301a may operate at the highest temperature, while the third heat exchanger 301c may operate at the lowest temperature. The second heat exchanger 301b may operate at a temperature between the temperatures of the first heat exchanger 301a and the third heat exchanger 301c.

In one or many embodiments, the second main section 305 may have an identical configuration to the first main section 302. For example, exhaust gas flows through the flow circuits 214 into the first heat exchanger 305a to then flow into the second heat exchanger 305b, and then into the third heat exchanger 305c. In addition, one or more curved flow paths 309 may be used as conduits for exhaust gas to flow from the first heat exchanger 305a to the second heat exchanger 305b. In addition, secondary curved flow circuits (see

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310 in fig. 4C) may be used to flow exhaust gas from the second heat exchanger 305b to the third heat exchanger 305c. In addition, the supply lines 311 may be used to flow exhaust gas into the exhaust gas manifold 217 from the third heat exchanger 305c. In a downward configuration, the first heat exchanger 305a may operate at the highest temperature, while the third heat exchanger 305c may operate at the lowest temperature. The second heat exchanger 305b may operate at a temperature between the temperatures of the first heat exchanger 305a and the third heat exchanger 305c.

Still with reference to FIG. 4B, the heat recovery section 107 may be connected to the first main section 301 and the second main section 305 via heat recovery conduits 312. Heat recovery lines 312 may be provided between the first heat exchanger 301a, 305a, and the second heat exchanger 301b, 305b, and between the second heat exchanger 301b, 305b and the third heat exchanger 301c, 305c of the first main section 301 and the second main section 305. Moreover, it is provided that a recycle CO2 inlet 313 may be located at the bottom of the first main section 301 and a second main section 305. From the recycle CO2 inlet 313, recycle CO2 may pass through a recycle CO2 manifold (see 315 in FIG. 2C) to be distributed to the third heat exchanger 301c, 305c, second heat exchanger 301b, 305b, and heating the first heat exchanger 301a, 305a, and then exits through the hot recycle CO2 manifold 314.

Now with reference to FIG. 4C illustrates a side view of the recuperative heat exchange system 105 of Figures 4A and 4B, in accordance with one or more embodiments of the invention. As shown in FIG. 4C, the first rigid frame 120 for the pre-cooling section 200 may be positioned at a distance D from the second rigid frame (see 121 in Figures 4A and 4B) for the first main section (see 301 in Figures 4A and 4B), the third rigid frame (see 122 in figures 4A and 4B) for the second main section 305, and the fourth rigid frame 123 for the auxiliary section 302. In one non-limiting example, the manifold 205 can be located in the space created by the distance D between the first rigid frame 120 and the other rigid frames (121, 122 , 123). In addition, the height H of the first rigid frame 120 may be less than the height H' of the other rigid frames (121, 122, 123).

In one or more embodiments, the curved flow paths 215, 309 and the secondary curved flow paths 216, 310 in each of the auxiliary section 302, the first main section (301) and the second main section 305 may have a portion that extends from the respective rigid frames ( 121, 122, 123). In this configuration, curved flow loops and secondary curved flow loops are more flexible than linear connections and can expand with minimal restriction.

Now with reference to FIG. 4D illustrates a top view of the recuperative heat exchange system 105 of Figures 4A and 4B, in accordance with one or more embodiments of the invention. As shown in FIG. 4D, the width W of the first rigid frame 120 may be equal to the width W' of the second rigid frame 121, the third rigid frame 122, and the fourth rigid frame 123. The second rigid frame 121 may be spaced a distance D' from the third rigid frame 122. The third rigid frame 122 may be a distance D from the fourth rigid frame 123. In one non-limiting example, the distance D' may be greater than the distance D. Figures 4C and 4D illustrate examples of how each of the rigid frames (120, 121, 122, 123) may have different dimensions (height and width) so that components of the recuperative heat exchange system 105 can be easily placed adjacent to each other to allow fluid connections.

As shown in Figures 4A-4D, in one or more embodiments, various components (pre-cooling section 200, auxiliary section 302, first main section 301, and second main section 305) of the downstream recuperative heat exchange system 105 may provide a modular and compact system. When forming a downward configuration, the supporting surface area of the recuperative heat exchange system 105 can be much smaller than for a traditional linear system assembled at one level. In one non-limiting example, the footprint of the entire recuperative heat exchange system 105 may be about 11 feet by 14 feet (3.4 m by 4.3 m). It is further contemplated that the base area may be of any overall size without departing from the scope of the present invention. In addition, the footprint may be based on operational and transportation requirements, such as consideration of special road conditions regarding bridge heights and dimensional restrictions associated with truck, rail, and vessel lengths.

In addition, the recuperative heat exchange system 105 may eliminate the need for high temperature piping to and from the turbine on an incline. In addition, each of the pre-cooling section 200, the auxiliary section 302, the first main section 301, and the second main section 305 can be formed in a modular and compact structure to facilitate fabrication and transportation to the assembly site with a minimum number of parts.

- 11 044627 tazh connections. In one or more embodiments, each of the pre-cooling section 200, the auxiliary section 302, the first main section 301, and the second main section 305 is supported within respective rigid frames (120, 121, 122, 123), and is capable of independent expansion within the respective rigid frames. frames (120, 121, 122, 123). Since the respective rigid frames (120, 121, 122, 123) do not limit the expansion of the pre-cooling section 200, the auxiliary section 302, the first main section 301, and the second main section 305 under thermal load, the routing of the connecting pipes can be greatly simplified to provide sufficient flexibility . This is especially important for heat exchangers when moving from a rigid block to a flexible line and nozzle assembly. It is further contemplated that since high temperature heat exchangers, which experience the greatest thermal expansion stress, can be placed in the highest position where the modules will have the greatest flexibility, high temperature heat exchangers can be most accessible for inspection or repair. Additionally, condensate from high temperature heat exchangers or other sections may naturally drain downward from the recuperative heat exchange system 105.

Local or remote control systems may be provided to operate the recuperative heat exchange system 105. The embodiments shown herein of the operation of the recuperative heat exchange system 105 may be implemented on a computerized system. Any combination of mobile device, desktop device, server, router, switch, embedded device, or other types of equipment may be used with the regenerative heat exchange system 105. For example, a computing system may include one or more computer processors, a random access memory (e.g., volatile memory such as random access memory (RAM), cache memory), a persistent storage device (e.g., a hard disk drive, an optical disk drive, such such as Compact Disc (CD) drive or Digital Versatile Disc (DVD) drive, flash memory, etc.), communication interface (such as Bluetooth interface, infrared interface, network interface, optical interface, etc. .), and numerous other elements and functionality. It is further contemplated that software instructions may be stored in the form of computer readable program code for executing embodiments of the invention, in whole or in part, temporarily or permanently, on a non-volatile computer readable medium such as a CD, DVD, storage device, floppy disk, tape, flash memory, physical memory, or any other computer-readable storage medium. For example, the software instructions may correspond to a computer-readable program that, when executed by the processor(s), is configured to execute one or more embodiments of the invention.

With reference to FIG. 5A, fig. 5A shows an example of a heat exchanger suspension system in accordance with one or more embodiments. The following example is presented for purposes of explanation only, and is not intended to limit the scope of the invention. Heat exchange system 400, as shown in FIG. 5A can be used in any industrial application such as power generation. In some embodiments, the heat exchange system 400 can be used in any industrial application where heat exchangers are required.

In one or many embodiments, the heat exchange system 400 may be configured in a downward configuration to allow for easier field installation. The rigid frame may include two posts 401, 402 spaced apart by a distance D'. The two posts 401, 402 may be made of a metallic material and extend upward to a height H. The first end 401a, 402a of each post may be removably secured to the floor of a work station. In addition, the two posts 401, 402 may be rigid to allow the heat exchange system 400 to be lifted by cranes, trailers, or forklifts using the two posts 401a, 402a as anchor points. One or more heat exchangers 403, 404, 405 may be located between the two posts 401, 402 in the heat exchange system 400. While it is noted that in FIG. 5A shows three heat exchangers 403, 404, 405, this is for exemplary purposes only and any number of heat exchangers may be used without departing from the scope of the invention. For example, the auxiliary (oxidizer stream) section may have two heat exchangers, while the main (recycle stream) section may have three heat exchangers. The heat exchangers 403, 404, 405 may be a printed circuit type heat exchanger (PCHE), a wound coil type heat exchanger, a microtubular heat exchanger, a diffuse welded heat exchanger using stamped plates in addition to etched plates, or any other type of heat exchanger. In addition, it is provided that the heat exchangers 403, 404, 405 can be replaced by cryogenic or boiler type heat exchangers.

In the configuration according to FIG. 5A, in one or more embodiments, heat exchangers 403, 404, 405 may be arranged in series and vertically aligned. The first heat exchanger 403 may be located in the heat exchange system 400 in the highest vertical position. In one non-limiting example, the first heat exchanger 403 may be coupled to the first support structure 406. The first support structure 406 may be a rigid metal plate coupled to the second end 401b, 402b of each post 401, 402. In addition, at the second end

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401b, 402b of each post 401, 402, a plate or cover 407 for the first support structure 406 may be placed in movable connection therewith. In addition, part of the first heat exchanger

403 may extend beyond the height H of the two posts 401, 402.

A second heat exchanger 404 may be positioned below the first heat exchanger 403. A second heat exchanger 404 may be coupled to a second support structure 408. A second support structure 408 may be a rigid metal plate for a second heat exchanger 404 coupled thereto. A first set of hangers 409 may support the second support structure 408 suspended from two posts 401, 402. The first set of hangers 409 may include two or more hangers. In one non-limiting example, the first set of hangers 409 may be inclined at an angle to the center of the second support structure 408 between two posts 401, 402. The first set of hangers 409 may be a tensile member, a steel rod, chain links, wire rope, or any rod or rack type to support the weight and displacement of the second heat exchanger 404. In addition, the ends 410 of the first set of hangers 409 may be connection points for the first set of hangers 409 on the two posts 401, 402 and the second support structure 408. In some embodiments, the connection point may be variable position by means of a rack and pinion or pinion with a driving pawl to allow the first set of hangers 409 to be repositioned. By means of a rack and pinion or pinion with a driving pawl, the coupling point may be adjusted to enable active control of direct displacement of the second heat exchanger 404 and the third heat exchanger 405.

A second set of hangers 411 may hang vertically downward from the second support structure 408 to suspend the support beam 412. The second set of hangers 411 may include two or more hangers. The ends 413 of the second set of hangers 411 may constitute a connection point for a second set of hangers 411 on the second support structure 408 and support beam 412. In some embodiments, the connection point may be variably positioned by means of a rack and pinion or pinion with a driving pawl to allow the second set to be repositioned. a set of hangers 409. By means of a rack and pinion or a pinion with a driving pawl, the connection point can be adjusted to enable active control of the immediate displacement of the third heat exchanger 405. The second set of hangers 411 can be a tensile member, a steel rod, chain links, wire rope, or a rod or rail of any type to support the weight and displacement of the support beam 412.

In one or many embodiments, the third heat exchanger 405 may be located proximate the first ends 401a, 402a of the two posts 401, 402, and below the second heat exchanger 404. The third heat exchanger 405 may be coupled to the third support structure 415. The third support structure 415 may be a rigid structure. a metal plate for a third heat exchanger 405 associated with it.

From the support beam 412, a third set of hangers 414 may extend downwardly to suspend a third support structure 415. The third set of hangers 414 may include two or more hangers. In one non-limiting example, the third set of hangers 414 may be inclined at an angle to the center of the third support structure 415 between two posts 401, 402. In some embodiments, the ends 416 of the third set of hangers 414 may be connection points for the third set of hangers 414 on the support beam 412 and third support structure 415. In one non-limiting example, the connection point may be in a variable position by means of a rack and pinion or pinion with a driving pawl to allow the third set of hangers 414 to be interchanged. By means of a rack and pinion or pinion with a driving dog, the connection point may be adjusted to enable active control of direct displacement of the third heat exchanger 405. The third set of hangers 414 may be a tensile member, a steel rod, a chain link, a wire rope, or any type of rod or rail to support the weight and displacement of the third heat exchanger 405.

Still with reference to FIG. 5A, the first heat exchanger 403 may operate at the highest temperature of the three heat exchangers 403, 404, 405 in the heat exchange system 400. The third heat exchanger 405 may operate at the lowest temperature of the three heat exchangers 403, 404, 405 in the heat exchange system 400. The second heat exchanger 404 may operate at a temperature between the temperatures of the first heat exchanger 403 and the third heat exchanger 405. By placing the first heat exchanger 403 at the highest level in the heat exchange system 400, the first heat exchanger 403 can expand without any displacement limitation from the fact that the second heat exchanger 404 and the third heat exchanger 405 can also move. In addition, since the second heat exchanger 404 and the third heat exchanger 405 operate at a lower temperature than the first heat exchanger 403, the second heat exchanger 404 and the third heat exchanger 405 may experience a higher stress rating than the first heat exchanger 403. Therefore, the mobility of the second heat exchanger 404 and the third heat exchanger 405 can be provided more easily than the mobility of the first heat exchanger 403. In addition, any thermal expansion of the pipe system 417 forming the connections between the three heat exchangers 403, 404, 405 can be compensated by a set of hangers 409, 411, 414.

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In one or many embodiments, three heat exchangers 403, 404, 405 are thermally decoupled from each other within the heat exchange system 400. By having the first heat exchanger 403 coupled to the first support structure 406 in the highest position, the first heat exchanger 403 can undergo thermal expansion independently without affecting a second heat exchanger 404 and a third heat exchanger 405. In addition, the first set of hangers 409 may allow the second heat exchanger 404 to be thermally isolated from the first heat exchanger 403. When thermal expansion of the second heat exchanger 404 occurs, the first set of hangers 409 may vertically displace the second support structure 408 such that the second heat exchanger 404 is thermally independent from the first heat exchanger 403 and the third heat exchanger 405. Additionally, by having a support beam 412 suspended from a second set of hangers 411, the support beam 412 can thermally decouple the second heat exchanger 404 and the third heat exchanger 405 from each other.

Now with reference to FIG. 5B, FIG. 5B shows an example of a heat exchanger suspension system 420 for the heat exchange system (see 400) of FIG. 1A in accordance with one or more embodiments. The following example is presented for purposes of explanation only, and is not intended to limit the scope of the invention. The heat exchanger hanger system 420 may include a first set of hangers 409, a second set of hangers 411, and a third set of hangers 414 coupled to a second support structure 408, a support beam 412, and a third support structure 415.

In one or many embodiments, a first heat exchanger (see 403) may be vertically coupled, while a second heat exchanger (see 404) and a third heat exchanger (see 405) may be supported by a second support structure 408 and a third support structure 415, respectively. Therefore, the second heat exchanger (see 404) and the third heat exchanger (see 405) may experience vertical displacement as a result of thermal expansion of heat exchanger 403 as well as their own thermal expansion during operation.

As shown in FIG. 5B, arrows 421 represent the vertical displacement of the second heat exchanger (see 404) and the third heat exchanger (see 405). In addition, arrows 422a, 422b represent horizontal thermal expansion of the second heat exchanger (see 404) and the third heat exchanger (see 405). In one non-limiting example, when the second heat exchanger (see 404) experiences thermal expansion in the horizontal direction (Arrow 422a), the first set of hangers 409 may be displaced by a distance Th in the horizontal plane. The offset distance Th further changes the angle of the first set of hangers 409 to then lower the second heat exchanger (see 404) by a distance Tv due to the change in angle. When the second heat exchanger (see 404) is lowered by distance Tv, the third heat exchanger (see 405) can also be lowered by distance Tv. However, when the third heat exchanger (see 405) experiences thermal expansion in the horizontal direction (Arrow 422b), the second set of hangers 411 may move by a distance Th' in the horizontal plane by changing the angle of the second set of hangers 411. When the angle of the second set of hangers 411 changes, the third heat exchanger (see 405) is further shifted by an amount lower so that the distance Tv' of the vertically displaced third heat exchanger (see 405) can be the sum of the distance Tv and the additional downward shift amount.

In the heat exchanger hanger system 420, both horizontal and vertical thermal expansion in various components of the heat exchange system (see 400) may change or adjust the angles of the hanger array 409, 411, 414 to compensate for thermal expansion. By compensating for thermal expansion, the heat exchanger suspension system 420 can manage thermal imbalances among various components being cooled and heated at different rates. In addition, the heat exchanger suspension system 420 minimizes thermal expansion stresses in the heat exchangers and associated piping in the heat exchange system (see 400). It is further contemplated that insulation may be applied in conjunction with the heat exchanger suspension system 420 to further assist in eliminating thermal imbalances. Insulation can be used to prevent heat loss, and to improve system efficiency, which can also be beneficial in helping to regulate thermal balance, and result in more accurate predictions of displacements due to thermal expansion.

With reference now to FIG. 6 illustrates another embodiment of a heat exchange system according to the embodiments herein, where like numbers represent like parts. The embodiment according to Fig. 6 is similar to the embodiment according to FIG. 5A. However, the heat exchange system 400 may have only a first heat exchanger 403 and a second heat exchanger 404 without a third heat exchanger (see 405 in FIG. 5A).

With reference now to FIG. 7 illustrates yet another embodiment of a heat exchange system according to the embodiments herein, where like numbers represent like parts. The embodiment according to Fig. 7 is similar to the embodiment according to FIG. 5A. However, the heat exchange system 400 may have only two heat exchangers, both of which are suspended in a heat exchanger suspension system (see 420 in FIG. 5B). In one non-limiting example, the first heat exchanger 403 may be removed so that the second heat exchanger 404 and the third heat exchanger remain

-

Claims (17)

405, suspended from their respective sets of hangers (409, 414). With reference now to FIG. 8 illustrates yet another embodiment of a heat exchange system according to the embodiments herein, where like numbers represent like parts. The embodiment according to Fig. 8 is similar to the embodiment according to FIG. 5A. However, instead of the first set of hangers 409 and the third set of hangers 414 being angled outward (see FIG. 5A), the first set of hangers 409 may be angled inward. In one non-limiting example, one or more projections 430 may protrude inwardly from a rigid frame (two posts 401, 402) such that one end 410 of the first set of hangers 409 may be a connection point on one or more of the projections 430. When the first set of hangers 409 is tilted inward thermal expansion of the second heat exchanger 404 may cause the second support structure 408 to rise vertically. In addition, the third set of hangers 414 may also be inclined inwardly, causing the third support structure 415 to rise vertically upward due to thermal expansion of the third heat exchanger 405. With reference now to FIG. 9 illustrates yet another embodiment of a heat exchange system according to the embodiments herein, where like numbers represent like parts. The embodiment according to Fig. 9 is similar to the embodiment according to FIG. 5A. However, the two rigid frame posts 401, 402 can be moved closer to each other so that the distance D between the two posts 401, 402 is less than the distance D'. By moving the two posts 401, 402 closer together, the first set of hangers 409 may be tilted inward. By tilting the first set of hangers 409 inward, thermal expansion of the second heat exchanger 404 may cause the second support structure 408 to rise vertically upward. In addition, the third set of hangers 414 may also be inclined inwardly, causing the third support structure 415 to rise vertically upward due to thermal expansion of the third heat exchanger 405. As described in Figures 5A-9, heat exchange systems 400 combine a series of independently moving parts. The heat exchange systems 400 described herein enable a series of independently moving parts to remain connected while still allowing for independent displacement and providing benefits to the overall system, including low stress on the heat exchangers (404, 405), such as the piping to the nozzles (417). For the heat exchange systems 400 in Figures 5A-9, the heat exchanger suspension system (420) may have a suspension system 409, 411, 414 that may be configured to adjust the position (i.e., neutral, boost, decline) of the lower heat exchangers (404, 405). In one or many embodiments, the configuration of the hangers 409, 411, 414 may be based on the expected thermal expansion or contraction of the components during startup, operation, and shutdown of the heat exchange systems 400. In addition, the angle of the hangers may be selected based on the expected thermal expansion or compression. In addition, each suspension angle can be adjusted independently. In heat exchange systems 400, support rod 412 may enhance independent displacement of heat exchangers (404, 405). When the support rod 412 is engaged, the second heat exchanger 404 does not affect the ability of the third heat exchanger 405 to move independently. Thus, the support rod 412 provides various degrees of freedom to accommodate piping movement and expansion within the heat exchange systems 400. The support rod 412 provides the ability to isolate and utilize expansion methods to favorably separate the thermal expansion of each of the heat exchangers to minimize nozzle loads, and may provide the ability to reduce extension of pipelines in length. By minimizing the load and creating shorter pipes, the overall weight of the installation can be reduced. In addition, the stresses associated with the heat exchanger suspension system (420) allow the length of the pipes to be reduced and the overall system to be more compact. While the present invention has been described with respect to a limited number of embodiments, those skilled in the art having the opportunity to become familiar with the invention will appreciate that other embodiments may be developed that are within the scope of the invention. as described here. Accordingly, the scope of the invention should be limited only by the claims contained in the appended claims. CLAIM 1. Heat exchange system containing: rigid frame; a first heat exchanger coupled to a first support structure on top of the rigid frame; a second heat exchanger located below the first heat exchanger, wherein the second heat exchanger is connected to a second support structure, wherein the second support structure is suspended from a rigid frame by a first set of hangers, wherein the first set of hangers is configured to move the second support structure vertically and horizontally; a second set of hangers coupled to the second support structure and extending downwardly to suspend the support beam; - 15 044627 a third set of hangers connected to the support beam and extending downward to suspend the third support structure, the third set of hangers being configured to move the third support structure vertically and horizontally; and a third heat exchanger coupled to the third support structure, wherein vertical and horizontal movement of the second support structure is based on thermal expansion of the second heat exchanger, and wherein vertical and horizontal movement of the third support structure is based on thermal expansion of the third heat exchanger. 2. The heat exchange system of claim 1, wherein the first heat exchanger is configured to operate at a higher temperature than the second heat exchanger, and the second heat exchanger is configured to operate at a higher temperature than the third heat exchanger. 3. The heat exchange system of claim 1, wherein the first set of hangers, the second set of hangers and the third set of hangers are selected from a structural tensile member, a steel rod, chain links or wire rope. 4. The heat exchange system according to claim 1, wherein the first set of hangers and the third set of hangers are inclined. 5. Heat exchange system according to claim 1, in which the rigid frame contains two racks spaced apart from each other. 6. The heat exchange system according to claim 5, wherein the first heat exchanger, the second heat exchanger and the third heat exchanger are located between two racks. 7. Heat exchange system according to claim 5, in which the first end of each of the two racks is removably fixed to the floor. 8. The heat exchange system of claim 7, wherein the first support structure is movably connected to a second end of each of the two struts remote from the first end. 9. The heat exchange system of claim 1, further comprising one or more protrusions extending from the rigid frame, wherein an end of the first set of hangers is connected to the one or more protrusions. 10. The heat exchange system of claim 1, wherein the first heat exchanger is thermally disconnected from the second heat exchanger, and the second heat exchanger is thermally disconnected from the third heat exchanger. 11. Heat exchange system containing: rigid frame; a first heat exchanger coupled to a first support structure on top of the rigid frame; and a second heat exchanger located below the first heat exchanger, wherein the second heat exchanger is connected to a second support structure, wherein the second support structure is suspended from a rigid frame by a first set of hangers, wherein the first set of hangers is movable vertically and horizontally of the second support structure; wherein the vertical and horizontal movement of the second support structure is based on thermal expansion of the second heat exchanger. 12. The heat exchange system according to claim 11, wherein the first heat exchanger is thermally disconnected from the second heat exchanger. 13. Heat exchange system according to claim 11, in which the first set of hangers is inclined. 14. The heat exchange system of claim 13, wherein the ends of the first set of hangers are connected to the rigid frame and the second support structure by means of a rack and pinion or pinion with a driving pawl. 15. The heat exchange system of claim 13, wherein the angle of the first set of hangers is selected based on a predetermined thermal expansion or contraction. 16. The heat exchange system according to claim 11, wherein the first heat exchanger is configured to operate at a higher temperature than the second heat exchanger. 17. Heat exchange system containing: rigid frame; a first support structure suspended from a rigid frame by a first set of hangers having one end connected to the rigid frame and another end connected to the first support structure, the first set of hangers being configured to move the first support structure vertically and horizontally; a first heat exchanger coupled to the first support structure; a second set of hangers coupled to the first support structure and extending downwardly to suspend the support beam; a third set of hangers connected to the support beam and extending downwardly to suspend the second support structure, the third set of hangers being configured to move the second support structure vertically and horizontally; and a second heat exchanger coupled to the second support structure, wherein vertical and horizontal movement of the first support structure is based on thermal expansion of the first heat exchanger, and -