US3141309A

US3141309A - Air conditioning apparatus

Info

Publication number: US3141309A
Application number: US208893A
Authority: US
Inventors: Carlos I Gesell
Original assignee: Individual
Current assignee: Individual
Priority date: 1962-07-10
Filing date: 1962-07-10
Publication date: 1964-07-21
Anticipated expiration: 1981-07-21

Description

July 21, 1964 c. l. GESELL 3,141,309

AIR CONDITIONING APPARATUS Filed July 10, 1962 39 I 2 la! 5 Sheets-Sheet 1 GOLD AIR AMBIENT AIR FROM BLOWER COMPRESSED HOTAIR T0 HEAT EXGHANGER COOLED com'nsssso Alli! FROM HEAT EXOHANGER INVENTOR CARLOS I. 65 55 LL ATTORNEYS July 21, 1964 c. 1. GESELL AIR counmcmmc APPARATUS 5 Sheets-Sheet 2 Filed July 10, 1962 INVENTOR CARLOS GE'SELL July 21, 1964 c. l. GESELL AIR CONDITIONING APPARATUS 5 Sheets-Sheet 3 Filed July 10, 1962 COOL FIG/0 65a. INVENTOR CARLOS 6E5ELL BY ATTORNEYS 7 FIG.

July 21, 1964 c. 1. GESELL AIR CONDITIONING APPARATUS 5 Sheets-Sheet 4 Filed July 10, 1962 July 21, 1964 c. L GESELL AIR CONDITIONING APPARATUS 5 Sheets-Sheet 5 Filed July 10, 1962 m A D L O C INVENTOR ATTORNEYS United States Patent 3,141,309 AIR CONDITIONING APPARATUS Carlos I. Geseil, Villa Geseli, via Juancho F.N.G.R., Argentina Filed July 10, 1962, Ser. No. 203,893 2 Claims. (Cl. 62-401) My invention relates to improvements in air-conditioning apparatus.

This application is a continuation-in-part of my copending application Serial No. 151,759, filed November 13, 1961.

An object of my invention is to provide a new and useful combination of means to provide an air-conditioning apparatus compact in size, economical to maufacture, efiicient in use, highly dependable, non-vibrating, and noiseless.

Another object of my invention is to provide a pair of rotary cooperating members having compression-expansion chambers, a heat exchanger associated therewith and conducting means to compress air, cool the compressed air in the heat exchanger, followed by the cham bers expanding the cooled compressed air to further cool the air and obtain some work therefrom to help in the compression of the air of the succeeding cycles and the conducting means acting to conduct either the warmed air from the heat exchanger or the further cooled air or both at atmospheric pressure to the place of use.

A further object of the invention is to provide in an air conditioner apparatus a pair of rotary members with their axes parallel but offset from each other and rotated together with cyclically operating compression and expansion chambers therebetween to compress air fed thereto, pass it through a heat exchanger to cool the same, heating thereby other air at atmospheric pressure and then reintroduce the cooled air into the expanding chambers to further cool the first mentioned air so as to provide a cooling or heating medium at atmospheric pressure in an efficient manner.

A further object of the invention is to provide in a rotary apparatus having a compression-expansion chamber disposed therebetween, two offset rotary members whose axes are offset and parallel, compression expansion chambers formed by cylinder and pistons therein with connecting rod means transmitting thrust from each piston to the surrounding rotary member.

Yet a further object of the invention is to provide in a rotary apparatus having a compression-expansion chamber disposed therebetween, two oifset rotary members whose axes are offset and parallel, compression expansion chambers formed by cylinders and pistons therein with a hollow elastic sphere transmitting thrust from the top of each piston to the surrounding rotary member.

A still further object of my invention is to provide in an air conditioner wherein air is compressed and expanded an associated heat exchanger for cooling the hot compressed air before expanding the same in the apparatus, said heat exchanger being of the counterfiow type and formed with an outer shell having a plurality of thermal conductive discs with a plurality of struck-up apertures therein forming one pass for air and another plurality of struck-up apertures therein forming another pass for other air with the two sets of apertures forming the passes separated from each other by poor-heat conductive gasket means between the spaced apart disc.

Still further objects and the entire scoope of applicability of the present invention will become apparent from the detailed description given hereinafter. It should be understood, however, that the detailed description and specific examples are given by way of illustration only and while indicating a preferred embodiment of this invention are not given by way of limitation, since various 3,1415%? Patented July 21, 1964 changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description.

For a more complete description reference is had to the drawings in which- FIG. 1 is a side elevational view of one form of the apparatus;

FIG. 2 is a fragmentary vertical cross-sectional view of the compressor-expander in FIG. 1 on an enlarged scale;

FIG. 3 is a view taken on line 3-3 of FIG. 2;

FIG. 4 is a fragmentary vertical sectional view of a piston and connecting rod attachment on an enlarged scale in one form of the apparatus;

FIG. 5 is a fragmentary exploded view of a piston and connecting rod attachment thereto;

FIG. 6 is a side elevational view of a counterflow heat exchanger shown in FIG. 1 but on an enlarged scale;

FIG. 7 is a cross-sectional view through the heat exchanger of FIG. 6 along line 77 on an enlarged scale showing a single disc element with the passageways therethrough;

FIG. 8 is an enlarged fragmentary view of one of the passageways in the portion of the disc shown in FIG. 10 at line 8--8 thereof;

FIG. 9 is an enlarged fragmentary view of another of the passages in the portion of the disc shown in FIG. 10;

FIG. 10 is an enlarged sectional view of a portion of the disc along line Ill-10 of FIG. 7.

FIG. 11 is an enlarged sectional side elevational view of the heat exchanger of PEG. 6 with the outer casing broken away at each end to show the disc association and flow passages of the counterfiow heat exchanger;

FIG. 12 is a side elevational view with the compressionexpander in vertical section of a modified form of apparatus;

FIG. 13 is a vertical sectional view along line 1313 of FIG. 12; and

FIG. 14 is a vertical sectional view of the manifold plate along line 14-14 of FIG. 12.

Throughout the description like reference numbers refer to similar parts.

The first form of the whole apparatus is generally indicated at 10. A suitable elongated platform or base 11 has mounted thereon a drive motor 12, here shown in the form of an electric motor, which drives a compression-expander 13 at one end and a blower 14 at the other end. In the apparatus assembly there is also included a heat exchanger 15.

The compressor-expander 13 is of the rotary type having a plurality of compressible-expansible chambers which serve to take air at pressure and ambient temperature and compress the same following which the hot compressed air is led to the heat exchanger 15 where it is cooled and then led back to the chambers in their expansible state whereupon the compressed cooled air is expanded and becomes further cooled. The expansion of the cooled compressed air tends to also supply a part of the driving force for the compressor-expander 13.

In FIG. 2 the compressor-expander 13 is made up of a first rotary member 16 driven by a shaft 12a extending from motor 12 and a second rotary member 17 cooperating therewith rotating on shaft 1% supported in a pedestal bearing stand 19 mounted on base 11. The shaft 13 has its axis offset from and parallel to the axis of shaft 12a and thus the two rotary members are eccentrically disposed.

A manifold plate member 29 is disposed at one end of the first rotary member 16 and is supported at 25111 on the platform 11 and this plate has various passages that will be described.

The first rotary member 16 driven by shaft 12a on which it is keyed by a key 21 has a concentric socket 22 in which is received a compression spring 23 that is held by a Washer 24 and a screw 25 threadedly received in the end of shaft 12a. The spring 23 urges the first rotary member 16 to the right and in sealing engagement with fixed manifold plate 20. Within the left-hand end of member 16 is a concentric recess 26 which receives the inwardly protruding eccentric shaft 18 and hub 17a of the second rotary member 17.

Formed in the first rotary member 16 which is of suitable material, of generally cylindrical shape, are a plurality of radially extending cylinder chambers 27. The inner ends 28 of each cylinder 27 recedes slightly to the center thereof and has formed in the wall portion a port 28a which has a tapered seat on the outside that communicates with the recess 26 that is at surrounding atmospheric pressure. Seating in each port 23a is a valve closure member 2 of proper weight and carried on the end of a leaf spring 30 mounted on the adjacent wall portion 26a defining the cavity 26 in member 16. These valve closure members 29 are normally held open and vent the cylinders 27 for starting purposes but close the port 23a through centrifugal action when the rotation is sufficiently up to speed. Each of the cylinders has a communication passage leading thereto adjacent its inner end such as passage 31 and adjacent the outer end such as passage 32. These passages 31 and 32 lead to the manifold end of the first rotary members 16 for communication with arcuate passages in the manifold plate as will be described.

Reciprocably received within the cylinders 27 are pistons 33 which are closed at their inner ends and have their open ends extending radially outward towards the surrounding backup or camming portion formed by the cylindrical skirt of the second rotary member 17 to which they are pivotally attached as will be described.

The second rotary member 17 is of cylindrical shape and hasan inwardly extending center hub 17a formed integrally'with a radially extending end plate portion 17b that has an annular backup ring 170 extending transversely in the same direction as center hub 17a and surrounding in spaced relation the first rotary member 16. The center hub portion I'7a receives the hollow shaft 18 that is fixedly mounted on the pedestal 19 by a cap 1%. The hollow shaft 18 receives a packing material 1&1 which is saturated with lubricant through a removable threaded end cap 18b. Suitable apertures 180 are formed in the hollow shaft 18a within the area of center hub 17:: to adequately feed the lubricant to the hub bearing ITa.

Reference to FIGS. 2, 4 and shows the pivotal connection of the piston 33 through a connecting rod 34 to the backup portion or thrust receiving portion 170 of second rotating member 17. The piston 33 is formed with a domed shaped head 33a of like configuration to the end 28 of the cylinder. On the inside of head portion 33a is formed a lug 3312 having an aperture 330 extending transversely therethrough which receives a bushing 33d and needle bearings 35. In line with the aperture 33c are apertures 332 in the walls of the piston for assembly purposes. The inner end of the connecting rod 34 is cupshaped at 34a and is received over the lug 33b of the piston and has transversely disposed apertures Edd in line with the aperture 330 in the lug to receive a wrist pin 36 for hearing engagement with the needle bearings 35. Suitable threaded cap screws 37 are received in threaded end portions of the apertures 33c and hold wrist pin 36 in assembled position. The access apertures 33a in the skirt or wall of the piston serve to receive the pin 36 and Wrench members for the screws 37. The cup-shaped end 34:: of the piston rod has a cavity 34c therein to receive wick packing material 38 which is saturated with suitable lubricant. The outer end 34d of the connecting rod 34 reaches into a cup-shaped container attached to the second rotating member 17 as will be described. The outer end 34d has in line transversely extending apertures 34c extending therethrough. A specially formed cup or cap member 39 fits over the end 34d and has a transversely extending flange 39a that is provided with a plurality of spaced apart apertures therethrough to receive securing screws 40 that are threadedly received or riveted in the backup or thrust receiving camming portions of the second rotating member 17. The cap 39 has a central lug 39b with a transversely extending aperture 39c therethrough in alignment with the apertures 34:2 to receive needle bearings 41. Threaded apertures 39d in cap 39 are in alignment with the apertures 34a and a wrist pin 42 is received therethrough. The pin 42 is held in place by the cap screws 42 received in the threaded apertures 39d. In the end 34d at the outer end of connecting rod 34 is a cavity 34f in which is received a packing or wicking material 43 to hold a lubricant to lubricate the needle bearings. Suitable oiling leads may be made in the connecting rod 34 for replacing the lubricant of these packed bearings.

The manifold plate 20 of the first form of the apparatus shown in FIGS. 1, 2 and 3 will now be described. This fixed manifold plate is shown supported at 20a on the platform 11. However, it could equally as well be directly mounted on the housing 12b attached to the motor, as shown in FIG. 2, and the leads to the manifold could be reshaped to shorten the distance between motor 12 and compressor-expander 13 to afford a more compact unit. The manifold plate 20 is formed with apertures and passages therein and a transverse skirt portion 20!) extending in overlapping relation about the adjacent end of the skirt 17 c of the second rotary member 17.

Manifold plate 20 shown in FIGS. 2 and 3 has a first station I where cool air from the blower is supplied at ambient temperature and cold air which has been expanded in the cylinders or compressible-expansi'ble chambers is lead off cyclically as the chambers reach their largest volume. A second station II is shown where the chambers are smallest and the hot compressed air is led off to the heat exchanger 15 for cooling. The cool air from the blower 14 is led by a conduit 45 under blower pressure to an inlet opening 46 in the outer face of the manifold plate 20 which communicates with an arcuate passage 47 at station I in the inner face of the plate 29 which extends in the illustration an arcuate distance so that three chambers cyclically communicates therewith. This air supply under blower pressure serves to scavenge out the cold expanded air and to furnish a fresh supply of air. The air is compressed cyclically between station I and II and led off at station II when the chambers are smallest by the aperture 31 to an arcuate passage 48 in the inner face of plate 20 thence to aperture 49 in plate 20 and thence to conduit 50 to the heat exchanger 15. After being cooled in exchanger 15 the cold compressed air is led through conduit 51 to an aperture 52, see FIG. 3, in the outer face of plate 20 and extending on through to an arcuate passage 53 on the inner face of plate 20 where it cyclically enters the chambers through aperture 31 in the first rotary member 16. As the chambers pass cyclically from station 11 to I the cooled compressed air expands and becomes further cooled and at the same time provides a working thrust on the pistons. On the chambers reaching station I again, the expanded cold air leaves by aperture 32 which communicates with arcuate passage 54 in the inner face of plate 20. An aperture 55 in plate 20 communicates with arcuate passage 54 and leads off the cold air through a conduit 56 to place of use.

In FIGS. 6-11 there is shown the heat exchanger 15 which is of the counterflow type.

The cooling air for this heat exchanger is supplied by the blower 14 under blower pressure through a conduit 60 to the right-hand end of the exchanger 15. The exchanger is of elongated cylindrical shape and has an outer cylindrical shell 61 closed by right and left-hand

circular end plates

62 and 63 held by through bolts 64.

3,1a1,soa

Within each end of the exchanger are relatively short

cylindrical spacer members

65 and 66 of materially smaller diameter than the outer shell 61 and in-between these

spacers

65 and 66 are stacked transversely extending specially formed disc members 67 of good thermal conductivity such as copper.

The discs 67 are circular and fit within the shell 61. Each disc, see FIGS. 7, 8, 9 and 10, has an outer annular row of spaced apart rectangular apertures 68 formed by punchings which extend from right to left and have struck-up portions 68a and 68b, see FIGS. 8 and 10. An inner annular row of rectangular apertures 69 is also formed in each disc and these are formed by punchings which extend from left to right and have punched portions 69a and 69b. The

rectangular apertures

68 and 69 extend radially and the outer annular row is spaced radially from the inner annular row so as to form a gasket bearing space to receive an annular gasket 75 which is of a thickness when compressed by the through bolts 64 in assembled condition to maintain a spacing between adjacent struck-in portions in each disc. Thus, there is formed an annular passage by the apertures 68 of the outer annular row to conduct the cooling air from conduit 60 to the space surrounding the right-hand spacer 65 through the exchanger from right to left to the space about the annular spacer 66 at the left-hand end and out through an aperture in end plate 63 to a lead off conduit 71. The warm air led off through the conduit 71 may be conducted to a place of use.

The hot compressed air coming to the exchanger through conduit 50 passes through an aperture in the outer shell and through an aperture in the spacer 66 at the left-hand end. This hot compressed air passes from left to right through the circular inner passage formed by the apertures 69 where in contact with the disc surface and punchings becomes cooled and passes out the conduit 51 which connects with an aperture in the right-hand spacer 65. Any condensate from the center flow section is led off by a drain 65a that may have a suitable drain-off valve placed therein.

There is here provided in this heat exchanger a relatively large heat exchange surface area between metal and fluid, in relation to the heat transmitting section of the metal through the stacked apertured discs for the size of the exchanger.

Modified Form of Air-Conditioning Apparatus In FIGS. 12, 13 and 14 there is shown a modified form of the apparatus which is compact and differs in the compressor-expander. The heat-exchanger used with this apparatus is the same as shown in FIGS. 611 previously described.

The apparatus is compactly mounted on a base 90 and comprises the drive motor 91. Shown here as an electric motor, a blower 92 of the rotary type, a compressor-expander 93 and a heat exchanger of the type shown in FIGS. 6-11.

The compressor-expander 93 comprises a first rotary member 94 and a second rotary member 95, both similar to those shown in the first form. The main difference in this modified form is the substitution of hollow metal spheres of some elasticity for the connecting rods to transmit thrust from the pistons to the backup or camming ring portion of the second rotary member 95.

The first rotary member 94 is mounted on drive shaft 91a in a similar fashion to that in the first form. The second rotary member 93 is mounted on a shaft 18 carried by pedestal 19 and secured by a cap 19a.

In the first rotary member 93 there is formed radially extending cylinders 96, here shown as six in number. Each of the cylinders have in their inner ends ports 28a and valves 29 on the leaf springs 30 as in the first form described to provide venting for bringing the apparatus up to speed whereupon the valves 29 are held closed by centrifugal force.

In each of the cylinder walls there are ports 31 and 32 as in the first described construction for feeding to a fixed manifold to be described.

Received in each of the cylinders 96 is a piston 97 having a closed inner end and a skirted outer end at 97a formed with a transversely and outwardly extending flange portion 97b. Suitable piston ring grooves and rings are provided in each piston as at 970 to provide for sealing and good compression.

Instead of the connecting rods 34 in the first form of the apparatus to transmit thrust from the piston 97 to the surrounding camming ring portion c on the second rotary member, there are provided hollow spheres 98 which are rolling means. These rolling spheres thus eliminate all of the bearing means necessary with connecting rods and act without limit to the to-and-fromovement caused by the eccentricity of the two rotary members disposed about parallel spaced apart axles. These spheres 98 have a diameter somewhat greater than the eccentricity, i.e., the spacing between the axes of the first and second

rotary members

94 and 95. These hollow spheres of steel or plastic material are provided with a certain amount of elasticity in the event the piston should become stuck and the spheres should move with great impetus toward the surrounding camming ring portion 950. To avoid damage in this event the camming ring portion 950 may be made of steel with a certain amount of inherent elasticity. The size of the spheres 98 and the length of the skirt portion 97a of the piston is so proportioned that the spheres will not become dislodged when the apparatus is at rest.

The manifold plate 100 shown in FIGS. 12 and 14 of the modified construction is similar to the fixed manifold plate in FIGS. 1 and 2, but is here shown providing for close mounting on the motor 91 and with the similar arcuate passages 47 and 54 at station I and arcuate passages 48 and 53 at station II and the conduit leads thereto. Manifold plate 100 is held directly against the adjacent end of motor 91 by a plurality of spaced apart screws 101. As in the first mentioned construction, compression springs 23 urge the first rotary member 94 into sealing engagement with the manifold plate 100.

In both forms of the apparatus it is to be noted that compression and expansion takes place within the same chamber in succession; i.e., the chamber is alternately warmed on compression and cooled on expansion, and that the working means takes on average temperature, somewhat above freezing, so that trouble on account of freezing of condensed moisture does not occur.

While air has been accentuated as the medium compressed and used in the compression-expansion chambers, suitable gases could also be used and the interpretation of the claims is to be so understood.

This apparatus and system provides a highly efficient and very useful manner of providing an air conditioning means, cooling as well as heating in a reliable manner as it excludes the secondary fluid generally utilized in this apparatus with all of its complications and cost.

I claim as my invention:

1. A compression and expansion device for working on gases comprising in combination a blower means, a thermal chamber, an exhaust, a rotor means rotatable about an axis and provided with a plurality of compressionexpansion chambers and having a polished surface extending transversely to said axis, each of said chambers having a pair of ducts leading to said surface, one of each pair of ducts being at a determined shorter distance from said axis of rotation, the other duct being at a longer distance from said axis of rotation, a fixed wall transversely located to said axis and having a polished surface closely abutting said first mentioned surface and means to press these surfaces to one another for tightness, forming thus a sliding valve; said fixed wall having a pair of ducts in the region where the compressionexpansion chambers cyclically have their greatest volume, these ducts being separated equally from said axis as those from the compression-expansion clhambers, one duct of the last mentioned being connected to the blower means, the other duct of the last mentioned being connected to said exhaust; another pair of ducts in said rotor means in the region where the compression-expansion chambers are cyclically smallest, both of these ducts leading to the compression-expansion chambers, one of these ducts being where these compression-expansion chambers are cyclically reducing to their smaller volume, the other duct being where these compressionexpansion chambers are cyclically enlarging again following their reduction, both of said last mentioned ducts being connected to the thermal chamber, said gases flowing from the blower means, cyclically through the sliding valve to the compression-expansion chamber where the chambers are greatest and in which their volume is reduced, thence to the thermal chamber and back again to the compression-expansion chambers Where these are cyclically enlarging again and after expansion to the exhaust where the volume of these compression-expansion chambers is largest.

2. A compression and expansion device for working on gases comprising in combination a blower means, a thermal chamber, an exhaust, a rotor means rotatable about an axis and provided with a plurality of compression-expansion chambers and having a polished surface extending transversely to said axis, each of said chambers having a pair of ducts leading to said surface, one of each pair of ducts being at a determined shorter distance from said axis of rotation, the other duct being at a longer distance from said axis of rotation, a fixed wall transversely located to said axis and having a polished surface closely abutting said first mentioned surface and means to press these surfaces to one another :for tightness, forming thus a sliding valve; said fixed wall having a pair of ducts in the region where the compression-expansion chambers cyclically have their greatest volume, these ducts being separated equally from said axis as those from the compression-expansion chambers,

one duct of the last mentioned being connected to the blower means, the other duct of the last mentioned being connected to said exhaust; another pair of ducts in said rotor means leading to said surface thereon in the region where the compression-expansion chambers are cyclically smallest, both of these ducts leading to the compression-expansion chambers, one of these ducts being where these compression-expansion chambers are cyclically reducing to their smaller volume, the other duct being Where these compression-expansion chambers are cyclically enlarging again following their reduction, said fixed Wall having a second pair of ducts leading to said wall surface thereon in said region where the compressionexpansion chambers are cyclically smallest and in respective alignment with said ducts in said rotor means References Cited in the file of this patent UNITED STATES PATENTS 982,632 Prather Jan. 24, 1911 1,431,593 Oswald Oct. 10, 1922 1,939,057 Kerdher Dec. 12, 1933 2,020,923 Von Seggern Nov. 12, 1935 2,150,347 Sorensen Mar. 14, 1939 2,287,202 Smith June 23, 1942 2,328,439 Esnault-Pelterie .d Aug. 31, 1943 2,509,256 Sorensen May 30, 1950 2,678,155 Durham May 11, 1954 2,972,311

Baugh Feb, .21, 1961

Claims

1. A COMPRESSION AND EXPANSION DEVICE FOR WORKING ON GASES COMPRISING IN COMBINATION A BLOWER MEANS, A THERMAL CHAMBER, AN EXHAUST, A ROTOR MEANS ROTATABLE ABOUT AN AXIS AND PROVIDED WITH A PLURALITY OF COMPRESSIONEXPANSION CHAMBERS AND HAVING A POLISHED SURFACE EXTENDING TRANSVERSELY TO SAID AXIS, EACH OF SAID CHAMBERS HAVING A PAIR OF DUCTS LEADING TO SAID SURFACE, ONE OF EACH PAIR OF DUCTS BEING AT A DETERMINED SHORTER DISTANCE FROM SAID AXIS OF ROTATION, THE OTHER DUCT BEING AT A LONGER DISTANCE FROM SAID AXIS OF ROTATION, A FIXED WALL TRANSVERSELY LOCATED TO SAID AXIS AND HAVING A POLISHED SURFACE CLOSELY ABUTTING SAID FIRST MENTIONED SURFACE AND MEANS TO PRESS THESE SURFACES TO ONE ANOTHER FOR TIGHTNESS, FORMING THUS A SLIDING VALVE; SAID FIXED WALL HAVING A PAIR OF DUCTS IN THE REGION WHERE THE COMPRESSIONEXPANSION CHAMBERS CYCLICALLY HAVE THEIR GREATEST VOLUME, THESE DUCTS BEING SEPARATED EQUALLY FROM SAID AXIS AS THOSE FROM THE COMPRESSION-EXPANSION CHAMBERS, ONE DUCT OF THE LAST MENTIONED BEING CONNECTED TO THE BLOWER MEANS, THE OTHER DUCT OF THE LAST MENTIONED BEING CONNECTED TO SAID EXHAUST; ANOTHER PAIR OF DUCTS IN SAID ROTOR MEANS IN THE REGION WHERE THE COMPRESSION-EXPANSION CHAMBERS ARE CYCLICALLY SMALLEST, BOTH OF THESE DUCTS LEADING TO THE COMPRESSION-EXPANSION CHAMBERS, ONE OF THESE DUCTS BEING WHERE THESE COMPRESSION-EXPANSION CHAMBERS ARE CYCLICALLY REDUCING TO THEIR SMALLER VOLUME, THE OTHER DUCT BEING WHERE THESE COMPRESSIONEXPANSION CHAMBERS ARE CYCLICALLY ENLARGING AGAIN FOLLOWING THEIR REDUCTION, BOTH OF SAID LAST MENTIONED DUCTS BEING CONNECTED TO THE THERMAL CHAMBER, SAID GASES FLOWING FROM THE BLOWER MEANS, CYCLICALLY THROUGH THE SLIDING VALVE TO THE COMPRESSION-EXPANSION CHAMBER WHERE THE CHAMBERS ARE GREATEST AND IN WHICH THEIR VOLUME IS REDUCED, THENCE TO THE THERMAL CHAMBER AND BACK AGAIN TO THE COMPRESSION-EXPANSION CHAMBERS WHERE THESE ARE CYCLICALLY ENLARGING AGAIN AND AFTER EXPANSION TO THE EXHAUST WHERE THE VOLUME OF THESE COMPRESSION-EXPANSION CHAMBERS IS LARGEST.