HEAT EXCHANGER

Abstract

A heat exchanger comprises a plurality of cells formed by a stack of alternate planar flow-guide plates (1) and heat transfer plates (2), each heat transfer plate having at least three apertures (3, 4, 6) therethrough, each aperture defining a part of a respective one of at least three fluid flow paths in the heat exchanger. Each flow-guide plate has apertures therethrough corresponding to at least two of the flow paths and a larger aperture (5, 7, 8) therethrough configured to guide fluid in the remaining flow path across the face of the heat transfer plates between which the flow-guide plate is located, each successive flow-guide plate in the stack forming part of a different flow path from the preceding one in the stack.

Claims

1. A heat exchanger comprising a plurality of cells formed by a stack of alternate planar flow-guide plates and heat transfer plates, each heat transfer plate having at least three apertures therethrough, each aperture defining a part of a respective one of at least three fluid flow paths in the heat exchanger, each flow-guide plate having apertures therethrough corresponding to at least two of the flow paths and a larger aperture therethrough configured to guide fluid in the remaining flow path across the face of the heat transfer plates between which the flow-guide plate is located, each successive flow-guide plate in the stack forming part of a different flow path from the preceding one in the stack.

2. A heat exchanger according to claim 1, wherein at least some of the cells include a turbulence-inducing matrix therein.

3. A heat exchanger according to claim 2, wherein the matrix comprises a welded or woven mesh insert within the cell.

4. A heat exchanger according to claim 2, wherein the matrix comprises a formation on the surface of at least one of the heat transfer plates between which the cell is defined.

5. A heat exchanger according to claim 1, wherein the plates are formed from stainless steel.

6. A heat exchanger according to claim 5, wherein the plates are bonded together by copper brazing.

7. A heat exchanger according to claim 1, wherein the plates are rectangular in plan.

8. A heat exchanger according to claim 1, comprising a pair of end plates between which the stack of plates is clamped, the end plates having flow connections therethrough.

9. A heat exchanger according to claim 1, wherein the cells in the stack are not equally divided between the three flow paths.

10. A heat exchanger according to claim 4, wherein the direction of flow across the face of the heat transfer plates in each of the flow paths changes along the length of the stack.

11. A heat exchanger according to claim 1, comprising 48 to 200 cells.

12. A heat exchanger according to claim 1, having three flow paths therethrough.

13. Apparatus for separating hydrogen and oxygen from a mixed gas stream, comprising a mixed gas inlet connected to a condensing coil at least partially submerged in liquid nitrogen in an insulated container, a liquid oxygen reservoir connected to the condensing coil, a hydrogen gas outlet from the condensing coil, an oxygen flow control valve connected to the liquid oxygen reservoir, and a heat exchanger according to claim 12, wherein the mixed gas inlet is connected to a first flow path in the heat exchanger, the hydrogen gas outlet is connected to a second flow path in the heat exchanger and the oxygen flow control valve is connected to the third flow path in the heat exchanger.

14. Apparatus according to claim 13, wherein the heat exchanger is mounted within a vacuum chamber above the liquid nitrogen container.

15. Apparatus according to claim 13, wherein the mixed gas stream is generated by the decomposition of water by electrolysis.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In the drawings, which illustrate embodiments of the invention:

[0025] FIG. 1 shows one example of a sequence of plates used in a heat exchanger according to the invention;

[0026] FIG. 2 is a perspective view of the complete heat exchanger incorporating plates of the type illustrated in FIG. 1;

[0027] FIG. 3 is an exploded view of a sequence of plates according to another embodiment, prior to assembly into a heat exchanger;

[0028] FIG. 4 is a view of a gas separation apparatus embodying the heat exchanger of the invention; and

[0029] FIGS. 5 and 6 illustrate an alternative sequence of plates to that shown in FIG. 1.

DETAILED DESCRIPTION OF THE ILLUSTRATED EMBODIMENT

[0030] Referring first to FIG. 1, the heat exchanger is formed from a series of thin plates of two general types—flow guide plates 1 (typically around 1.5 mm to 2.5 mm in thickness) and heat transfer plates 2 (typically around 0.5 mm to 1.5 mm in thickness)—stacked alternately. In the embodiment illustrated in the Figure, there are three different flow guide plates 1a, 1b, and 1c and three different heat transfer plates 2a, 2b and 2c, each having apertures therethrough, each aperture forming part of one of three fluid flow paths through the heat exchanger. In the Figure, the apertures relating to the three flow paths are indicated by black, grey and white circles respectively. FIG. 1 illustrates a sequence of twelve plates in a stack, but the numbers are not limited to this; a typical heat exchanger may include 48 cells for a small flow rate and up to 200 or more cells for larger systems. Taking the plates in the sequence shown (which is for illustrative purposes, other arrangements being possible), the first flow guide plate 1a is in the form of a generally square frame with radiused corners, each of the plates having the same external form. One edge portion of the frame is widened to accommodate an aperture 3 forming part of the second path in one corner of the frame and an aperture 4 forming part of the third flow path in the other corner. The area 5 within the frame is shaped to align with a spaced-apart inlet and outlet for the first flow path, shown as black circles with the direction of flow between them indicated by an arrow, but the inlet and outlet do not actually form part of the plate 1a.

[0031] The next plate 2a in the stack is a heat-transfer plate, provided with three apertures 3, 4 and 6 therethrough adjacent to one edge of the plate apertures 3 and 4 aligning with apertures 3 and 4 in the flow guide plate 1a, when the plates are stacked, and the other aperture 6 opening on one side into the area 5 of the first flow guide plate 1a and thus forming part of the first flow path through the heat exchanger.

[0032] Flow guide plate 1b is the third plate in the stack and takes the form of a frame with an edge portion widened to accommodate apertures 3 and 6 aligning with the apertures 3 and 6 in the preceding heat transfer plate 2a. The open area 7 encompassed by the frame communicates with the aperture 4 in the heat transfer plate 2a, allowing gas to flow across the face of the plate to an aperture 4 in the next heat transfer plate 2b, located adjacent the opposite corner of the square shape from the aperture 4 in the preceding heat transfer plate.

[0033] The third flow guide plate 1c is in the form of a frame having an aperture 6 located centrally of one side of the frame within an intrusion into the frame, and an aperture 4 at a corner of the opposite side of the frame, which is widened accordingly to accommodate it. The open area 8 of the frame communicates with the aperture 3 of the preceding heat transfer plate 2b and with an aperture 3 in the opposite corner of the third heat transfer plate 2c, which has an aperture 6 corresponding to that in the third flow guide plate 1c and apertures 3 and 4 in the two corners opposite to it.

[0034] The same sequence of flow guide and heat transfer plates 1 and 2 is then repeated in the next six plates, but the plates are flipped so that the flow directions across the faces of the heat transfer plates are reversed with respect to the first six plates. The next six plates revert to the pattern of the first six and this pattern is repeated throughout the stack. It will be seen, therefore, that in this particular configuration only three different designs of flow guide plates and three different designs of heat transfer plates need to be manufactured.

[0035] Dependent upon the flow-rates of the gases, the number of cells in a heat exchanger stack could vary substantially.

[0036] FIG. 2 shows the stack of plates assembled between two end plates 20 and 21 with alignment pins 22 extending between them to hold the plates in alignment and threaded tie rods 23 and nuts 24 to clamp the assembly. Connecting spigots 25, 26 and 27 are provided on each end plate 20 and 21, for connecting the three flow paths within the exchanger to external gas flow pipes.

[0037] The heat exchanger of this design makes use of materials which have very similar coefficients of linear thermal expansion in order to avoid stresses which would otherwise build up during thermal cycling and gradients through the length of the heat exchanger. In order to achieve this, the heat exchanger is constructed with 316L stainless steel components throughout, with a high-temperature copper-brazed bond between each component in the construction. Both 316L stainless steel and copper have a coefficient of linear thermal expansion of around 16×10.sup.−6 mm/° C., rendering them ideal for cooperative use in these applications.

[0038] In order for the unit to operate at the pressures which may be required of the hydrogen production system, the heat exchanger must be constructed of a suitable wall-thickness. This requirement is made even greater by the need to withstand an explosion at any point within the gas-transportation system in order to resist the associated radially outward forces.

[0039] Similarly, the unit must be designed to withstand the linear cell-to-cell separation forces under such conditions. This requires a substantial area of high-integrity braze interface at each joint in the unit, aided by end-plates of substantial thickness and tie-rods. Placed between each flow-guide plate and each heat transfer plate are pre-formed copper foils which form high-strength joints between the stainless steel plates in the high-temperature vacuum brazing operation in which the unit is finally bonded.

[0040] Connectors at each end of each gas pathway are required to withstand the above described pressures and pressure spikes without failure. This, in turn, requires a joint between the heat exchanger end-plate and each connector to be of similarly high integrity. Such connectors may be threaded or tubular in construction, dependent upon mating technologies.

[0041] For improved heat transfer, cells may have a matrix of metal past which the gas can freely flow, while giving rise to greater turbulence. This could be in welded or woven mesh form or directly imposed on the profile of the cell plate. As illustrated in FIG. 3, the formed inserts 30 are made from stainless steel mesh which could be of welded or woven construction. Alternatively, the heat transfer plates could have a form imposed by pressing or stamping to obtain the same result.

[0042] The function of these inserts is three-fold: [0043] a. They create turbulent flow of the gases passing across their profile, thereby increasing the potential for transfer of thermal energy [0044] b. They provide additional surface area to the gases in order to improve heat transfer, and [0045] c. They offer resistance to the deformation of heat transfer plates in the event of a significant differential pressure between cells.

[0046] Orientation of flow manifolds in the stack can be varied to accommodate assembly in specific environments, should this be a requirement. An additional benefit of this arrangement is that the number of cells in a given gas stream can be varied to accommodate differential thermal transfer rates from fluid-to-fluid, whether or not the fluid is gaseous or liquid.

[0047] Referring now to FIG. 4, one configuration of a cryogenics system using the heat exchanger of the invention comprises a Dewar flask 40 containing liquid nitrogen. The flask 40 is provided with a cold head 41 to maintain the low temperature in the flask in conventional manner. A condensing coil 42 has at least the major portion thereof submerged in the liquid nitrogen and leads into a reservoir 43 for the liquid oxygen. The hydrogen, which remains gaseous, is led direct to a first of the inputs to the heat exchanger 44, which is mounted in a vacuum chamber 45 located above the Dewar flask 40. The liquid oxygen reservoir 43 communicates through a pipe 46 with a flow control valve 47 within the vacuum chamber 45 and the gaseous oxygen emerging therefrom is conducted to a second of the inputs to the heat exchanger. A mixed gas stream from an electrolyser is input to the third flow path of the exchanger at the opposite end thereof.

[0048] By housing a unit of this design in a vacuum chamber, efficient exchange of thermal energy can be achieved, with one end of the unit being at close to ambient temperature, while the other end is at cryogenic temperatures of around 70K to 90K (−203.15° C. to −183.15° C.). One example of a system in which there is a heat exchanger according to the invention is shown in FIG. 4, in which a Dewar of liquid nitrogen is kept cool with a cold-head. Submerged in the liquid nitrogen (LN) is a reservoir for collection of the oxygen. As the oxygen takes cooling power from the LN, the cold-head maintains the temperature.

[0049] The heat exchanger as described above sits in a vacuum chamber above the Dewar, taking the hydrogen and oxygen streams In at the base, and the mixed-gas stream in at the top. As the streams pass from cell-to-cell, the thermal energy is transferred, with the incoming stream cooled to around 70K to 90K and the outgoing streams warmed to around ambient temperature, thereby reducing to an absolute minimum the power required to maintain the temperature of the LN in the Dewar. This helps optimise the efficiency of the end-to-end process of hydrogen and oxygen production by electrolytic water decomposition.

[0050] Other designs and arrangements for a three-stream heat exchanger may be derived from the unit described above. Critically, this application covers the use in combination with a cryogenics system of a heat exchanger which performs to the aforementioned criteria.

[0051] In the graphic below, the mixed gas stream enters the heat exchanger from the top and travels down through it, cooling as it passes from cell-to-cell. A condensing coil which sits in the LN finally cools the gas stream, ensuring distillation of 99%+ of the oxygen which collects in the oxygen reservoir near the bottom of the Dewar.

[0052] From the O.sub.2 reservoir, the liquid oxygen is forced back out by differential pressure between the incoming and outgoing gas streams to pass through the liquid O.sub.2 flow control valve after which it enters the bottom of the heat exchanger.

[0053] Similarly, the hydrogen stream leaves the top of the O.sub.2 reservoir to pass through the heat exchanger. Other designs of cryogenics system may be used for the liquefaction process which will require a 3-stream heat exchanger in order to optimise efficiency.

[0054] In the arrangement of cells shown in FIGS. 5 and 6, four different internally formed flow guide plates 50a, 50b, 50c, and 50d and three heat transfer plates 51a, 51b and 51c (one of which is used twice in each 4-cell group) are employed. The mixed gas stream is represented by black ports and arrows, the oxygen flow by grey ports and arrows and the hydrogen by white ports. FIG. 6 illustrates the sequence of plates forming a group of cells, with heat transfer plates 51 being placed over the flow guide plates 50 immediately to their left in the Figure, with the first in the next row being placed directly on the last in the preceding row. Each flow guide plate is in the form of a frame with a woven mesh insert 52 within the frame and an apertures 53, 54, 55 through the frame defining separate flow paths. Thus, flow guide plate 50a has an aperture 53 forming part of the oxygen flow path and an aperture 54 forming part of the hydrogen flow path, while the area within the frame guides the flow of the mixed gas stream across the face of the adjacent heat transfer plate 51a. The heat transfer plate 50a has three apertures 53, 54 and 55 therethrough, the central aperture 55 receiving the mixed gas stream, which is passed through aligned apertures 55 in the next two plates 50b and 51b before entering the space defined by the next flow guide plate 50a in the sequence, rotated through 90° relative to the first so that the mixed stream flows across it in the reverse direction. Similarly, the oxygen stream flows across the cell defined by the flow guide plate 50b and then flows across the flow guide plate 50d in the opposite direction. It will be seen from FIG. 6 that, in the sequence of eight cells so defined, the oxygen flow exchanges heat with the mixed gas flow, while the hydrogen simply flows through the apertures 54 without transferring its thermal energy. Groups of cells can thus be configured so that in the overall heat exchanger there are fewer cells through which the hydrogen passes than for those through which oxygen passes, so that heat exchange from the oxygen flow, which has a lower thermal conductivity than hydrogen, balances that of the hydrogen.