Patent Grant
8590301
(Not Applicable)
This invention relates to free piston Stirling machines and more particularly relates to a free piston Stirling machine that is adapted for use in applications where its component parts that are in the region of its expansion space are subjected to extreme temperatures.
Free piston machines, including free piston engines, coolers and heat pumps, have been applied to a variety of purposes in a variety of environments. Typically they have a compression region of the machine that operates at a temperature that is nearer to their ambient temperature and an expansion region that operates at a temperature that is farther from their ambient temperature. The expansion region is usually at one end of a generally cylindrical head and is either much colder than the ambient temperature, as in the case of a cryocooler, or the expansion region is much hotter than the ambient temperature, as in the case of a engine.
These temperature extremes present difficult design problems because of the temperatures themselves and because of the temperature differential between the component parts in these regions and the parts in the remainder of the machine. Some component parts extend into both the region of extreme temperature and the region of more moderate temperature. Typical problems include selecting materials that can maintain their characteristics and function properly at the extreme temperature and selecting the dimensions of the component parts and selecting machining tolerances to accommodate thermal expansion and contraction of the materials.
The design of a free piston Stirling engine for use in interplanetary travel is an example of the need to contend with extreme temperatures. The temperature of the atmosphere on Venus is on the order of 500° C. Because heat is applied to the heater head of an engine to power the engine, for use on Venus there is a need for a heater head that can withstand on the order of 1100° C. One of the most difficult component parts to design in a manner that can accommodate the extreme temperature is the displacer of the free piston Stirling machine. The reason is that the displacer of a free piston Stirling machine not only reciprocates along an axial path between the compression space with the moderate temperature and the expansion space with the more extreme temperature but the displacer also extends essentially all the way from within a heat rejecting heat exchanger at the compression space, through a regenerator to within a heat accepting heat exchanger at the expansion space. Consequently, the reciprocating displacer is subjected to an extreme temperature differential between its opposite ends with a temperature gradient along its length.
Efficient work is done in a free piston Stirling machine by transferring heat into the working gas at the expansion space and transferring heat out of the working gas at the compression space. Heat that is instead transferred through the displacer is wasted or lost heat representing inefficiency. Therefore, displacers are designed to minimize the heat transfer through the displacer from one end to its opposite end. Consequently, a typical displacer has a thin walled dome at its expansion space end fixed on top of a more rigid supporting piston at its compression space end. Examples of such displacers are illustrated in U.S. Pat. Nos. 4,559,779 and 7,866,153. The dome typically has an axial length that is considerably longer than its rigid supporting piston and its purpose is to thermally isolate the hot and cold spaces (expansion and compression spaces). The dome is a thin walled and essentially hollow structure in order to minimize its mass and to minimize heat conduction through the metal of the displacer. The displacer usually has baffles in the interior of the displacer dome to function as radiation shields and to subdivide the space in order to limit gas convection within the displacer and thereby limit heat transfer through the displacer between the expansion space and the compression space. Typically there are 3 to 6 baffles tack welded inside the displacer. Such displacers are expensive to manufacture and subject to thermal expansion/contraction. The metal, especially of the dome, must be able to withstand the extreme temperatures of the expansion space. Furthermore, the baffles can also be a reliability problem, especially if they become detached from the interior wall of the displacer dome.
An example of a typical prior art free piston Stirling machine 8 is illustrated in
The prior art has suggested avoiding the problems of the extreme temperature at the expansion space end of a displacer by using a thermoacoustic Stirling heat engine configuration. This configuration eliminates the displacer and substitutes a tuned inertance tube. Consequently it has no moving part that extends to the extreme temperature of the expansion space end of the head. Typically the inertance tube is ¼λ long and extends through a radial port in a generally radial direction out the side of the machine at the heat rejecting, compression space end of the working gas space and returns to the compression space through another radial port.
This thermoacoustic solution, however, introduces several disadvantages. The thermoacoustic Stirling heat engine configuration has a lower efficiency than a Stirling machine using a displacer because of the less than ideal phasing of the working gas through the regenerator and the added gas volume in the inertance tube. Another disadvantage is that a thermoacoustic Stirling heat engine requires a fluid diode for preventing a detrimental, unidirectional, circulating fluid flow component of working gas. There is also the problem of attaching the inertance tube to the casing in a manner that is durable and provides proper gas communication with the compression space. The inertance tube also forms an unwieldy arm that projects out the side of the machine.
It is therefore an object and feature of the present invention to provide a free piston Stirling machine that avoids problems inherent in the presence of extreme hot or cold temperatures to which component parts in the expansion region of a free piston machine are subjected.
Another object of the invention is to avoid the problems presented by the extreme temperatures and yet retain a displacer in the machine so that the higher efficiency of a free piston machine that has a displacer can be attained and the disadvantages of the inertance tube and fluid diode of the thermoacoustic configuration can be avoided.
The invention is a free piston Stirling machine having a displacer that is confined to reciprocation substantially within the heat rejecting heat exchanger that surrounds the displacer cylinder so that no part of the displacer is near or makes excursions near the extreme temperature region of the free piston Stirling machine. A thermal buffer tube extends between the end of the displacer when it is positioned at the boundary of its furthest excursion toward the heat accepting heat exchanger and the distal end of the heat accepting heat exchanger.
In describing the preferred embodiment of the invention which is illustrated in the drawings, specific terminology will be resorted to for the sake of clarity. However, it is not intended that the invention be limited to the specific term so selected and it is to be understood that each specific term includes all technical equivalents which operate in a similar manner to accomplish a similar purpose.
Free Piston Stirling Machine Principles
In a Stirling machine, a working gas is confined in a working space that includes an expansion space and a compression space. The working gas is alternately expanded and compressed in order to either do work or to pump heat. Each free piston Stirling machine has a pair of pistons, one referred to as a displacer and the other referred to as a power piston and often just as a piston. The reciprocating displacer cyclically shuttles a working gas between the compression space and the expansion space which are connected in fluid communication through a heat acceptor (heat accepting heat exchanger), a regenerator and a heat rejector (heat rejecting heat exchanger). The shuttling cyclically changes the relative proportion of working gas in each space. Gas that is in the expansion space, and gas that is flowing into or out of the expansion space through a heat exchanger (the acceptor) between the regenerator and the expansion space, accepts heat from surrounding surfaces. Gas that is in the compression space, and gas that is flowing into or out of the compression space through a heat exchanger (the rejector) between the regenerator and the compression space, rejects heat to surrounding surfaces. The gas pressure is nearly the same in both spaces at any instant of time because the spaces are interconnected through a path having a relatively low flow resistance. However, the pressure of the working gas in the work space as a whole varies cyclically and periodically. When most of the working gas is in the compression space, heat is rejected from the gas. When most of the working gas is in the expansion space, the gas accepts heat. This is true whether the machine is working as a heat pump or as an engine. The only requirement to differentiate between work produced or heat pumped, is the temperature at which the expansion process is carried out. If this expansion process temperature is higher than the temperature of the compression space, then the machine is inclined to produce work so it can function as an engine and if this expansion process temperature is lower than the compression space temperature, then the machine will pump heat from a cold source to a warm heat sink.
Stirling machines can therefore be designed to use the above principles to provide either: (1) an engine having a piston and displacer driven by applying an external source of heat energy to the expansion space and transferring heat away from the compression space and therefore capable of being a prime mover for a mechanical load, or (2) a heat pump having the power piston (and sometimes the displacer) cyclically driven by a prime mover for pumping heat from the expansion space to the compression space and therefore capable of pumping heat energy from a cooler mass to a warmer mass. The heat pump mode permits Stirling machines to be used for cooling an object in thermal connection to its expansion space, including to cryogenic temperatures, or heating an object, such as a home heating heat exchanger, in thermal connection to its compression space. Therefore, the term Stirling “machine” is used to generically include both Stirling engines and Stirling heat pumps.
Because free-piston Stirling machines can be constructed and operated as an engine, such engines have been linked as a prime mover to a variety of mechanical loads. These loads include linear electric alternators, compressors and fluid pumps and even Stirling heat pumps. Similarly, because free-piston Stirling machines can be operated in a heat pump mode, they have been driven as a load by a variety of prime movers, including linear motors.
The Invention
A basic concept of the invention is to form and position the displacer so that its stroke is confined to displacer reciprocation that is substantially within the heat rejecting heat exchanger in order that no part of the displacer is near or makes excursions near the extreme temperature region of the free piston Stirling machine. A further basic concept of the invention is to form a thermal buffer tube that extends from the position of the end of the displacer when the displacer is at the boundary of its furthest excursion (TDC) toward the heat accepting heat exchanger to the distal end of the heat accepting heat exchanger. The invention can eliminate the need for the thin walled dome with baffles and no part of the displacer is subjected to the extreme temperature region at the expansion space of the free piston Stirling machine.
Referring to
Therefore, a part of the central, tubular cylinder 40 forms and functions as a thermal buffer tube 44 extending from the expansion space 20 and surrounded by the heat accepting heat exchanger 24 and the regenerator 26. Another part of the central, tubular cylinder 40 forms and functions as a displacer cylinder 46 extending from the thermal buffer tube 44 to the compression space 22 and is surrounded by the heat rejecting heat exchanger 28.
As seen in
The thermal buffer tube separates the heat acceptor and the heat rejector heat exchangers. The purpose of a thermal buffer tube is to pass acoustic energy while minimizing heat transport. The mass of gas in the thermal buffer tube reciprocates in the thermal buffer tube relatively uniformly with minimum turbulence. Typically the thermal buffer tube has a slight taper to help keep the gas from mixing. The taper is not absolutely necessary but is desirable.
With the invention, the thermal buffer tube, instead of a displacer dome, is now the separation between hot and cold spaces (expansion space and compression space) within the machine. The thermal buffer tube has nothing mechanical running inside it so the designer is not concerned with clearances or thermally induced changes of clearance which are problems to be concerned with when there is a displacer dome. With a displacer dome it is difficult to avoid rubbing of the displacer against its cylinder wall, especially in the extreme temperature region of the machine.
Because the function of the displacer cylinder and the thermal buffer tube are different, they can have different shapes and contours as well as different diameters. Because the displacer does not enter the thermal buffer tube, only the displacer cylinder needs to be machined in the precision manner typically required to provide a clearance seal for properly sealing the displacer to its cylinder. The displacer cylinder and the thermal buffer tube can also be two different separate pieces arranged end to end, one a cylinder in which the displacer reciprocates and the other a tubular structures functioning as the thermal buffer tube. Of course the displacer cylinder can extend axially somewhat beyond the opposite excursion limits of the displacer to assure that the displacer does not collide with the thermal buffer tube. When the displacer cylinder and the thermal buffer tube are two different separate pieces, they can also be fabricated from different materials. For example, there are advantages in forming the thermal buffer tube of ceramic material, including the lower thermal conductivity of ceramic which reduces heat conduction through the thermal buffer tube. Although the displacer cylinder can also be formed of ceramic and machined, a metallic displacer cylinder is preferred for reasons later described below.
The thermal buffer tube 60 is tapered from a narrower diameter nearest the displacer 62 to a wider diameter where the thermal buffer tube 60 opens into the expansion space 68. The mean diameter of the displacer cylinder 58 is different from the diameter of the displacer 62 and its cylinder 58. In the embodiment of
An alternative thermal buffer tube, that may be substituted for the thermal buffer tube 60 that is illustrated in
When designing a displacer, one design goal is to thermally isolate the expansion space from the compression space in order to maximize the temperature differential between the expansion and compression spaces and to minimize heat transfer that occurs other than as a result of expansion and compression of the working gas because such other heat transfer does not represent useful work. As explained above, in the prior art one manner of accomplishing that is by minimizing heat flow through the displacer by forming the displacer with a thin walled dome having spaces and baffles.
However, with the invention, it is desirable to design the displacer to encourage heat transfer through the displacer and therefore a highly conductive displacer is desirable. In order to maintain thermal isolation and the temperature differential between the expansion space and the compression space, it is desirable to remove heat that is transferred through the working gas in the thermal buffer tube between the expansion space and the displacer. Designing the displacer to have a high thermal conductivity through the displacer from its end face that faces the thermal buffer tube to its cylindrical wall facilitates the transfer of that heat to the displacer cylinder for conduction through the displacer cylinder to the heat rejecting heat exchanger and away from the machine. Consequently, there are advantages to forming the displacer so that it is a solid heat conducting metal, such as aluminum, with no thermally isolating cavities. Alternatively, the displacer may be formed with thicker than conventional walls to facilitate heat conduction but still have one or more open cavities. Desirably, the displacer cylinder is formed of the same metal as the displacer so that they have the same coefficient of thermal expansion.
Boundaries of Displacer Excursion
As stated above, an important principle of the present invention is that the displacer is confined substantially within the axial length of the heat rejecting heat exchanger during its reciprocation, although some minor extensions beyond those limits still provides advantages and improvements.
The design criteria for confining the displacer stroke are as follows. It is desirable to make the displacer axial length as long as possible because a longer axial length allows a better clearance seal between the displacer and the displacer cylinder. The axial length of the heat rejecting heat exchanger defines to coolest temperature part of the working space. Therefore the optimum design is that the axial length of the displacer is equal to the axial length of the heat rejecting heat exchanger—(less) the displacer stroke. As is often the case with engineering design and engineering tradeoffs, some departure from this optimum can be adopted in order to accomplish some additional purpose.
The reasons for confining displacer excursions to substantially the axial length of the heat rejecting heat exchanger are that the expansion space has the most extreme temperature (the hot end in an engine and the cold end in a heat pump such as a cryocooler) and there is a temperature gradient axially along the length of the thermal buffer tube from the most extreme temperature at the heat acceptor to the more moderate temperature of the heat rejector. Preferably, the displacer of the invention does not enter any part of the machine with a temperature that is elevated above the heat rejector temperature. The typical prior art displacer reciprocates in a cylinder that is surrounded by the regenerator so there is a temperature gradient along that cylinder because of the temperature gradient through the regenerator. The typical prior art displacer also makes excursions into the expansion space and adjacent the heat accepting heat exchanger. Because the displacer of the invention avoids those regions, it doesn't encounter the extreme temperature.
Although it is most desirable to confine the displacer to the more moderate temperature zone of the free piston Stirling machine, as stated above and practically speaking the displacer could travel as much as 10% or even 20% of the distance into the regenerator region and still have advantageous operation. As is often true of the application of technical principles to a practical design, a slight excursion into the regenerator would make only a slight difference and the greater the excursions into the regenerator, the less effective and advantageous the invention. If the machine is designed to permit the displacer to make excursions into the regenerator, at some amount of entry it would be desirable to add a small thermally insulating dome to the displacer or provide a secondary rejector (described below).
It is also preferable to avoid displacer excursions that go toward the compression space much beyond the heat rejecting heat exchanger. The displacer should not interfere with working gas flowing to and from the ports (e.g. 70) that open between the heat rejecting heat exchanger and the compression space. Any such interference that would increase flow resistance or cause added turbulence would reduce the efficiency of the machine.
Secondary Heat Rejector
In the event that the free piston Stirling machine is designed to include the invention but have a displacer that makes short excursions into the more extreme temperatures beyond the heat rejector, it can be desirable to provide a secondary heat rejector. Referring to
It is highly desirable that the secondary heat rejector be connected to a thermally conductive metal part of the thermal buffer tube so that the heat is readily conducted from the secondary heat rejector 80 to the heat rejecting heat exchanger 28. However, the secondary heat exchanger 80 must be positioned axially beyond the boundaries of displacer reciprocation so that the displacer does not collide with it. If the thermal buffer tube and the displacer cylinder comprise a two part system, the secondary heat rejector 80 is advantageously connected to an extension of a metal displacer cylinder for maximum heat conduction. However, it is believed that the secondary heat exchanger is not needed if the displacer is sufficiently conductive and is sufficiently confined in its boundaries of reciprocation to within the heat rejector.
Some Advantages of the Invention
The invention makes the free piston Stirling machine less costly to manufacture, even if extreme temperatures are not a design concern, because the invention eliminates the need both to design and to build a displacer dome and baffles in the displacer dome. Only the part of the displacer cylinder in which the displacer reciprocates needs to be machined and, because the displacer of the invention is considerably shorter than a prior art displacer, the axial length of the displacer cylinder that must be machined is shorter. Machining and clearances are only critical in the region of the more moderate temperature compression space and only along the relatively short range to which reciprocation is confined. Beyond the range to which reciprocation is confined, there is nothing to have a clearance and therefore no critical machining is necessary.
Because a thermoacoustic free-piston Stirling engine has on the order of 70% of the efficiency of a free-piston Stirling engine that has a conventional displacer, the invention provides better efficiency than a thermoacoustic free-piston Stirling engine. A free piston Stirling machine using the displacer arrangement of the invention has been computed to get 85% of the efficiency of a free-piston Stirling engine that has a conventional displacer but it avoids the problem of designing a displacer cylinder and a displacer that extends into the extreme temperature regions of the machine.
This detailed description in connection with the drawings is intended principally as a description of the presently preferred embodiments of the invention, and is not intended to represent the only form in which the present invention may be constructed or utilized. The description sets forth the designs, functions, means, and methods of implementing the invention in connection with the illustrated embodiments. It is to be understood, however, that the same or equivalent functions and features may be accomplished by different embodiments that are also intended to be encompassed within the spirit and scope of the invention and that various modifications may be adopted without departing from the invention or scope of the following claims.
This application claims the benefit of U.S. Provisional Application No. 61/422,689 filed 14 Dec. 2010. The above prior application is hereby incorporated by reference.
This invention was made with Government support under contract NNC07CA11C awarded by NASA. The Government has certain rights in the invention.
| Number | Name | Date | Kind |
|---|---|---|---|
| 4559779 | Brown | Dec 1985 | A |
| 5095699 | Blackshear | Mar 1992 | A |
| 7000390 | Wood | Feb 2006 | B2 |
| 7866153 | Sollie et al. | Jan 2011 | B2 |
| 20060179833 | Qiu et al. | Aug 2006 | A1 |
| 20090094977 | Hill | Apr 2009 | A1 |
| Number | Date | Country | |
|---|---|---|---|
| 20120144821 A1 | Jun 2012 | US |
| Number | Date | Country | |
|---|---|---|---|
| 61422689 | Dec 2010 | US |
