US3216190A

US3216190A - Fluid engine compensator device

Info

Publication number: US3216190A
Application number: US202285A
Authority: US
Inventors: Charles H Baker
Original assignee: Cleveland Pneumatic Industries Inc
Current assignee: Cleveland Pneumatic Industries Inc
Priority date: 1962-06-13
Filing date: 1962-06-13
Publication date: 1965-11-09
Anticipated expiration: 1982-11-09

Description

Nov. 9, 1965 c, BAKER 3,216,190

FLUID ENGINE GOMPENSATOR DEVICE Filed June 13, 1962 2 Sheets-Sheet l INVENTOR CHARLES H. BAKER wmw A TTORNE Y Nov. 9, 1965 c. H. BAKER 3,216,190

FLUID ENGINE COMPENSATOR DEVICE Filed June 15, 1962 2 Sheets-Sheet 2 X I32 F I28 I24 FIG. 3 30 I06 I ,5

36 I 34 68 INVENTOR.

28 CHARLES H. BAKER BY X ATTORNEY United States Patent Ofifice 3,216,190 Patented Nov. 9, 1965 3,216,190 FLUKE) ENGINE COMPENSATOR DEVICE Charles H. Baker, Cleveland, Ohio, assignor to Cleveland Pneumatic industries, Inc, Cleveland, Ohio, 21 corporation of Ohio Filed June 13, 1962, Ser. No. 202,285 29 Claims. (Cl. 6024) This invention relates to thermodynamic engines in which working fluids traverse a thermodynamic cycle to produce power and more particularly, pertains to novel or improved apparatus for maintaining the horsepower output of such engines constant by compensating for variations in the temperature of heating and cooling sources associated therewith and for substitution in the type of working fluid utilized in the operating cycle thereof.

In a fluid-type engine of the type disclosed herein, a working fluid, compressed and heated, is expanded against a working surface within an expansion chamber of a piston-cylinder arrangement to produce mechanical power. The working fluid, in an initial condition, is compressed then heated and subsequently directed to the expansion chamber whereat the working fluid expands against the working surface of the piston-cylinder arrangement surface. After expansion, and at a reduced temperature and pressure, the working fluid is directed to a unit whereat the working fluid is cooled to the initial (before compression) condition. In a fluid engine of this type, the above set forth thermodynamic cycle is traversed by a suitable working fluid having desirable volumetric expansion characteristics and advantageous thermal properties. In the past, fluid-type engines were specifically designed for a particular type of working fluid and wherein the temperatures of the heating and cooling sources remained constant. However, in the event a different working fluid was contemplated, the specific heating source as well as the cooling source would be inadequate to obtain the desired output from the fluid-type engine depending upon the properties of the working fluid. Further, where a particular working fluid is employed and the corresponding required heating and cooling sources are not available, an entirely new fluid-type engine redesigned for the available power sources would be necessary to compensate for any variation in operating temperatures at each site of application of the fluid-type engine.

By providing apparatus in the form of a compensator device to readily compensate for any substitution of working fluid as well as the temperature variations in the available heating and cooling sources, a single fluid-type engine design may be utilized for a multiplicity of applications in which these variables are prevalent. For example, in instances where a fluid-type engine has been designed for a particular working fluid such as carbon dioxide, requiring specific heat source and cooling source capabilities applicable to CO any change in the working fluid or temperatures of the power sources would require a corresponding change in the fluid-type engine design. However, by utilizing the inventive compensator device described, disclosed, shown and illustrated herein such compensations without complete redesign of the fluid-type engine can be readily made. Where the operating temperatures of available heat sources are below a required amount, for effective operation of the working fluid, the compensator device of the apparatus may be readily adjusted to increase the pressure of the working fluid in the compression chamber. Thus the working fluid can be transmitted to the lower temperature heat source and receive an amount of heat proportional to the increased pressure thereof resulting in the required volumetric expansion in the working fluid and accordingly maintain constant horsepower output of the fluid-type engine as though the temperature of the heat source originally specified were available. In like manner, in a substitution of working fluid having different temperature and pressure requirements for optimum volumetric expansion, a change in the thermodynamic cycle to compensate for same is readily obtained by controlled operation of the compensator device of the apparatus. The compensator device permits the fluid-type engine to function properly with a constant desired horsepower output irrespective of the working fluid utilized or the variation in the operating temperatures of the heating and cooling sources available at such locations where the fluid-type engine is being utilized.

Therefore, it is the principal object of this invention to provide apparatus in the form of a device cooperable with a fluid-type engine in which a working fluid traverses a thermodynamic cycle with such device being operable to compensate for the use of more than one type of working fluid having different temperature characteristics for which the fluid-type engine was designed.

It is another object of this invention to provide apparatus in the form of a device cooperable with a fluid-type engine in which a working fluid traverses a thermodynamic cycle with such device being operable to compensate for temperature variations of available heating and cooling power sources at the respective installation site of the fluid-type engine.

A further object of this invention is to provide a compensating device cooperable with a fluid-type engine in which a working fluid traverses a thermodynamic cycle wherein the device permits the utilization of a specific working fluid in a variety of thermodynamic cycles of operation.

These and other objects and important features of the invention will be apparent from a study of the specification following taken with the drawing, which together show, illustrate, describe and disclose certain preferred embodiments and modifications of the invention and what is now considered to be the best mode of practicing the principles thereof. Other embodiments or modifications may be suggested to those having the benefit of the teaching herein, and all such embodiments or modifications are intended to be reserved as they fall within the spirit and scope of the subjoined claims.

In the drawing:

FIGURE 1 is a schematic illustration, partially in crossection, of a system having a fluid-type engine employing a thermodynamic cycle showing apparatus incorporated therewith for compensating for certain conditions and factors which may exist in a working fluid of the system.

FIGURE 2 is an enlarged, longitudinal sectional view of the apparatus associated with the fluid-type engine as illustrated in FIGURE 1 of the drawing and showing in more detail a compensator device of the apparatus, and

FIGURE 3 is an enlarged, longitudinal sectional view similar to FIGURE 2 of the drawing showing a modification or additional embodiment of the compensator device of the apparatus.

Attention is now directed to FIGURE 1 of the drawing, wherein a system ltl is illustrated in partial schematic form wherein the system 10, is in effect, closed and comprises, as a part thereof, a fluid-type engine 12 having a block 14 in which a cylinder 16 is bored and a piston 18 is reciprocably mounted. The piston 18 is secured to a connecting rod 20 and a crankshaft 22 arrangement disposed in a crankcase chamber 25 formed by a housing 26. The piston 18 comprises an enlarged base portion 28 and an extended reduced portion 30 forming a shoulder 32 therebetween. The shoulder 32 has a Working surface 34, (note FIGURES 2 and 3 of the drawing), thereon forming one wall of a compression chamber 36 and the extended reduced portion has a working surface 38 thereon forming one wall of an expansion chamber 40. The structural details of the piston 18 and the arrangement thereof with the engine block 14 are more specifically described, disclosed, shown, illustrated and claimed in the US. application Serial Number 213,401, filed July 30,1962, now Patent No. 3,174,276, filed in the name of the instant inventor and assigned to the assignee of the present invention.

The compression chamber 36 has an inlet port 42 and an outlet port 44 circumferentially spaced and suitably arranged about the engine block 14 with the

ports

42 and 44 each being communicable with the compression chamber 36. The outlet port 44 has a check valve 46 communicable therewith wherein working fluid F from the compression chamber is directed through the outlet port 44 and the check valve 46 into a conduit 48 and thence into the power heat exchanger 50. Disposed intermediate the outlet valve 46 and the power heat exchanger 50 is a valve 52 and an accumulator 54 arrangement, which functions to provide rapid starting of the fluid-type engine 12 after shutdown. A conduit 56 connects the power heat exchanger 50 to an inlet valve 58 disposed adjacent one end portion of the engine block 14 in communication with the expansion chamber 40. An outlet valve 60 is also disposed at the one end portion of the engine block adjacent the inlet valve 58 to provide communication of the working fluid F in the expansion chamber 40 with a conduit 62. The conduit 62 directs the working fluid F from the expansion chamber 40 into a cooling heat exchanger 64 and therefrom through a conduit 66 into an inlet valve 68 connected to the inlet port 42 communicable with the compression chamber 36.

A bypass valve 70 is disposed in the conduit 62 intermediate the outlet valve 60 and the cooling heat exchanger 64 and communicates through a suitable conduit 72 with the conduit 66 and the inlet valve 68. An oil separator 73 is connected to the conduit 62 intermediate the bypass valve 70 and the cooling heat exchanger 64. The oil separator '73 functions to separate the lubricating oil from the working fluid with which it passes through the system 10 during the operating cycle thereof. The oil separator 73 is connected to a filter 74 which is connected to the engine crankcase housing 26 by suitable conduits. The lubricating oil enters into the system by conventional pumping means which directs the oil from the crankcase into the piston and through suitable passageways (not shown). Lubricating oil as directed, is thereby disposed onto the cylinder walls and into the compression chamber becoming commingled with the working fluid. The specific details of the oil separator 73 and the filter 74 in combination with the system 10 is more fully described, disclosed, shown, illustrated and claimed in the US. application Serial Number 191,075 filed April 30, 1962., now Patent No. 3,138,918, in the name of the instant inventor and assigned to the assignee of the present invention.

In order to compensate for certain conditions or factors, such as variations in the temperature of the working fluid F resulting from the effect created thereon by the power heat exchanger 50 and the effective cooling of the working fluid F resulting from the heat exchanger 64, as well as providing for the substitution of different types of working fluid which may be employed in the system 10 to operate the fluid-type engine 12, there is provided apparatus which may take the form of a compensator or engine multiplier device 75 (FIG. 2) which comprises a housing 76 having an externally threaded portion 78 thereon cooperable with a correspondingly internally threaded portion 80 of a recess 81 formed in the engine block 14. A chamber 82 is defined by the recess 81 and the multiplier housing 76 with the multiplier device 75 being connected to the block 14 through the threaded engagement of the portions 78, 80. A freely movable piston member 84, responsive to pressures of the compression chamber 36, is reciprocably mounted in a bore 86 formed in the housing 76 and comprises a pair of cylindrical portions 88 and 90 separated by a necked down portion 91 disposed therebetween. An annular shoulder 92 is formed by the housing 76 and is engageable with cylindrical portion 88 of the piston member 84 to restrict axial movement thereof in an inwardly direction. The cylindrical portion 88 of the piston member 84 has an integrally formed extended portion 94 projecting therefrom for engagement with a surface 96 formed'on a cam member 98 disposed in a cavity 99 formed by the housing 76. The cam member 98 is suitably secured to a camshaft 100 wherein the camshaft 166) is operably connected to means (not shown) for providing the desired rotative movement in the camshaft 160 which will be effective to reciprocate the piston member 84 through the engagement of the cam member 98 therewith in the housing 76 of the multiplier device 75. 0 rings 101 and 102 are disposed on the cylindrical portions 88 and 90 respectively, and provide a fluid seal restricting the passage of the working fluid F past the piston member 84 and into the cavity 99. A projection 103 is formed on the other end of the piston member 84 integral with the cylindrical portion 90 and reciprocates therewith within a passage defining a chamber 194 formed in the correspondingly threaded portion 78 of the housing 76, responsive to the actuation of the cam member 98. A passage 106 is formed in the engine block 14 with one end 108 thereof communicable with the inlet port 42 of the compression chamber 36 and the other end 110 thereof communicable with the recess chamber 82 and the chamber 104 formed in the threaded portion 70 of the multiplier housing 76. Thus the compression chamber arrangement comprises the chamber 36 as well as the passage 106, recess chamber 82 and the chamber 104 formed in the multiplier device 75.

The fluid-type engine 12 as shown, discloses a single piston 18 and cylinder 16 arrangement, however, it is within the scope of the invention described herein to provide a multiplicity of such piston and cylinder arrangements within the engine block 14 and correspondingly provide a compensator or multiplier device 75 in communication with each compression chamber 36 of a multiple piston and cylinder embodiment.

The operational cycle of the fluid-type engine 12 will be described to best illustrate the inventive concept disclosed, described, shown and illustrated herein and accordingly the cycle will be described only to the extent necessary for a complete understanding of the present invention. Values for the temperatures and pressures experienced by the working fluid F are merely exemplary and constitute representative amounts for illustrative purposes only. In operation, a unit mass of working fluid P such as carbon dioxide at a temperature of approximately 70 F., is compressed in the compression chamber 36 to a pressure of approximately 6,000 p.s.i. and a temperature of approximately 300 F. At this temperature and pressure the carbon dioxide is directed through the outlet port 44, the outlet valve 46 and into the conduit 48. The valve 46 is actuated by suitable means (not shown) and synchronized in relationship to the cooperating elements of the cycle during engine operation. The compressed working fluid in the conduit 48 is directed through the valve 52 of the accumulator arrangement 54 and into the power heat exchanger 50 in which heat from any suitable source is applied to the working fluid F to substantially raise its temperature to approximately 500 F. while the pressure remains substantially constant. At this temperature and pressure, the carbon dioxide enters the inlet valve 58, through conduit 56 and upon synchronized opening of the inlet valve 58 by suitable means (not shown) the working fluid F is directed to the expansion chamber 40. When the working fluid enters the expansion chamber 40, the increased volume thereof enables the carbon dioxide to expand so that a given mass of working fluid F has a greater volume when it enters the expansion chamber 40 than it has as it is pumped out of the compression chamber 36. This expansion reduces the presssure and in turn reduces the temperature adiabatically. The piston 18 at this stage of operation, is in the top dead-center position but upon expansion of the carbon dioxide, is moved downwardly against the connecting rod 20 and the crankshaft 22 arrangement imparting rotative movement to the crankshaft. Upon continued rotation of the crankshaft 22, through the rotation of a flywheel (not shown) attached thereto, the piston 18 is directed upwardly and the outlet valve 60 is opened allowing the escape of the expanded carbon dioxide at a reduced temperature and pressure of approximately 200 F. and 800 p.s.i. respectively, from the expansion chamber into the conduit 62 through the bypass valve 70 arrangement and into the Cooling heat exchanger 64. The bypass valve 70 comprises means for controlling the speed of the fluid-type engine 12 and the details thereof are more specifically described, disclosed, illustrated, shown .and claimed in the U. S. application Serial Number 212,831 filed July 27, 1962, now Patent No. 3,180,081, in the name of the instant inventor and assigned to the assignee of the present invention. Upon leaving the cooling heat exchanger 64, the working fluid F is reduced to a temperature of approximately 70 F. and a pressure of 800 p.s.i. and enters the inlet valve 68 through the conduit 66. Simultaneously with the expansion stroke, the inlet valve 68 is opened to permit the carbon dioxide at the low temperature and pressure values to enter the compression chamber 36 whereupon the cycle is then repeated.

The valve 52 and the accumulator 5'4 arrangement disposed in the conduit 48 comprises means for starting the fluid-type engine 12 after it has been shutdown. A detailed description of the valve 52 and the accumulator arrangement 54 and the advantages thereof are more specifically claimed in the U. S. application Serial Number 222,729 filed Sept. 10, 1962, now Patent No. 3,200,- 581, in the name of Stanley A. Welland and assigned to the assignee of the present invention.

The object and advantages of the compensator or multiplier device 75 can best be described with reference to the operating cycle hereinabove set forth. If the power heat exchanger 50, due to the limitations in the available heat source, is incapable of supplying the desired amount of heat to raise the temperature of the compressed working fluid F and constant horsepower output must be maintained for the specified fluid-type engine application, manipulation of the camshaft 100 will cause the multiplier piston 84 to be directed inwardly towards the compression chamber 36 whereby the chamber 82 formed between the housing 76, the recess 81 and the extending portion 102 of the piston 84 will be substantially reduced in volume. The inwardly directed movement of the piston 84 and the reduction in the volume of the chamber 82 reduces the overall dimensions of the compression chamber 36 whereby the compression stroke of the piston 18 with the volumetric displacement thereof being constant will accordingly compress a unit mass of fluid F, occupying a smaller volume and accordingly being more dense, to a higher unit pressure. Upon opening the outlet valve 46, the working fluid F at a substantially higher pressure will enter the power heat exchanger and accordingly the available heat, being less than the amount required under higher pressure conditions, is applied to the carbon dioxide, resulting in the desired volumetric expansion in the expansion chamber 40 to maintain constant horsepower output of the fluid-type engine 12. In like manner; when the temperatures of the available heat source for the power heat exchanger 50 are high in comparison to the operating temperatures required for the optimum volumetric expansion of the carbon dioxide,

6 actuation of the camshaft in the opposite direction will displace the surface 96 of the cam 98 such as to allow the piston 84 to move outwardly responsive to pressures of the carbon dioxide in the compression chamber 36. Movement of the multiplier piston 84 in this direction increases the overall volume of the compression chamber 36 and accordingly the working fluid F within the compression chamber 36 for a unit mass of carbon dioxide will occupy a larger volume and accordingly be less dense due to the increased volume of the compression chamber 36. Therefore, a lower unit pressure will be obtained upon compression. Upon opening of the outlet valve 46, the working fluid F directed therethrough into the conduit 48 and into the power heat exchanger 50 will require receiving a greater amount of heat to compensate for the reduced pressure in order to maintain the desired volumetric expansion during the piston power stroke to maintain constant horsepower output. The capabilities of the power heat exchanger 50 being such in this example that the necessary heat is available and accordingly raise the temperature of the working fluid F by a proportional amount to oflset the lower pressures.

It can be readily seen from the above set forth description of the operation of the multiplier device 75, that a specific working fluid can be made to traverse a variety of thermodynamic cycles by manipulation of the multiplier device 75 and further the substitution of a different working fluid having different characteristics and properties can be readily compensated for by the use of the multiplier device 75.

The fluid-type engine 12 having the apparatus comprising the multiplier or compensating device 75, may be actuated either by mechanical means or a manual type control mechanism such as disclosed in a modification or other embodiment thereof which is illustrated in FIGURE 3 of the drawing. A manually adjustable multiplier device 112 comprising a housing having a body member 114 provided with an externally threaded portion 116 thereon and a passage defining a chamber 118 formed therein extending throughout the axial length of the body member 114. A shoulder 120 is formed intermediate the engine block 14 and the externally threaded portion 116 of the body member 114 and is adaptable to engage the engine block. One end of the body member 114 has an externally threaded portion 122 thereon cooperating with a corresponding internally threaded portion 124 in the recess chamber 82 of the engine block 14. The housing of the multiplier device 112 also has a sleeve 126 provided with an internally threaded portion 128 thereon for engagement with the threaded portion 116 of the body member 114. A handle or wheel member 130 is fixed to the sleeve 126 and upon rotation thereof, the sleeve 126 will move axially inwardly or outwardly depending upon the direction of rotation of the handle member 130. A freely movable piston member 132 is disposed within the passage defining a chamber 118 of the body member 114 and is reciprocable therein responsive to the pressure of the carbon dioxide developed in the compression chamber 36. The handle member 130 has a V shaped groove or recess 134 formed therein engagable with a stem portion 136 of the piston member 132 and acts as an abutting means restricting the axial movement of the piston member 132 within the chamber 118. An 0 ring 138 is disposed on one end 140 of the piston member 132 and prevents passage of fluid thereabout into a cavity 142 formed between the sleeve 126 and the body member 114. The O ring 138 so disposed, maintains the pressurized working fluid F within the recess chamber 82 formed by the engine block 14 and the multiplier body 114 and the chamber 118 formed by the multiplier body 114, thereby controlling the effective volume of the compression chamber 36 through the communication of passage 106 with the recess chamber 82 and chamber 118. It can be readily seen that in 7 situations Where manual control may be maintained con stant through manipulation of the handle member 130 and accordingly the sleeve 136 to enlarge or reduce the chamber 118.

While the invention has been described, disclosed, illustrated and shown in terms of certain embodiments or modifications, which it has assumed in practice, the scope of the invention should not be deemed to be limited by the precise certain embodiments and modifications herein described, disclosed, illustrated and shown, since other embodiments and modifications are intended to be reserved where they fall within the scope of the claims herein appended.

I claim as my invention:

1. Apparatus for controlling output of a fluid-type engine in which a working fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling stages, said apparatus comprising;

a housing defining a chamber, said chamber being disposed to receive a portion of said working fluid therein with said working fluid being communicable with said chamber during the compression stage of said cycle, and

means for effecting pressure variation in said working fluid within said chamber.

2. Apparatus for controlling output of a fluid-type engine in which a working fluid traverses a thermodynamic cycle according to claim 1 wherein said means comprise a piston and cylinder arrangement operably disposed within the housing.

3. Apparatus for controlling output of a fluid-type engine in which a working fluid traverses a thermodynamic cycle according to claim 2 wherein said piston is disposed in said cylinder and is operable to reciprocate therein.

4. Apparatus for controlling output of a fluid-type engine in which a working fluid traverses a thermodynamic cycle according to claim 3 wherein said piston is freely movable in said cylinder in one direction responsive to pressure of such fluid in said cylinder and movable in an opposite direction responsive to means engageable with said piston.

5. Apparatus for controlling output of a fluid-type engine in which a working fluid traverses a thermodynamic cycle according to claim 4 wherein said means engageable with said piston comprises: a cam member, actuation means cooperable with said cam member eflfective upon actuation to move said piston in said cylinder in one direction and to restrict movement of said piston in said cylinder in an opposite direction.

6. In combination with a fluid-type engine in which a Working fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling and having a piston and cylinder arrangement defining an expansion and compression chamber, apparatus LfOI controlling the output of said engine comprising:

a housing defining a recess chamber, said recess chamber being disposed in communication with said compression chamber of said engine and operable to receive a portion of said working fluid therein; and

means cooperable with said recess chamber effective to vary the pressure of said working fluid in said compression chamber.

7. In combination with a fluid-type engine in which a fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling having a piston and cylinder arrangement defining an expansion and compression chamber, apparatus for controlling said engine output comprising:

a housing defining a recess chamber, said recess chamber being disposed in communication with said compression chamber to receive a portion of said working fluid therein from said compression chamber;

a piston member cooperable with said housing and re ciprocable within said recess chamber,

cam means engageable with said piston member and operable upon actuation to impart movement to said piston member in one direction to reduce the volume of said recess chamber and to increase the volume of said recess chamber in an opposite direction, said piston member being effective upon movement thereof to vary the pressure of said working fluid in said compression chamber.

8. In combination with a fluid-type engine in which a fluid transverses a thermodynamic cycle of compression, heating, expansion and cooling and having a piston and cylinder arrangement defining an expansion and compres-. sion chamber, apparatus for controlling said engine output according to claim 7, wherein said'cam means is automatically actuated.

9. In combination with a fluid-type engine in which a fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling, and having a piston and cylinder arrangement defining an expansion and compression chamber therebetween, apparatus for controlling said engine output comprising;

a housing defining a recess chamber disposed in communication with said compression chamber to receive a portion of said Working fluid therein from said compression chamber,

a piston member reciprocable in said housing; and

a manually controlled movable sleeve member engageable with said piston member and operable upo-n actuation to impart movement to said piston member in one direction and restrict movement thereof in an opposite direction and effective to vary the pressure of said working fluid in said compression chamber.

10. In combination with a fluid-type engine in which a fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling and having a piston and cylinder arrangement defining an expansion and compression chamber therebetween, apparatus for controlling said engine output according to claim 9 wherein said housing comprises a body member, a chamber formed by said body member and a piston member reciprocable in said body member and a movable sleeve member engageable with said body member.

11. In combination with a fluid-type engine in which a fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling and having a piston and cylinder arrangement defining an expansion and compression chamber therebetween, apparatus for controlling said engine output according to claim 10 wherein said movable sleeve member has a threaded portion thereon engageable with a correspondingly threaded portion on said body member.

12. In combination with a fluid-type engine in which a fluid traverses a thermodynamic cycle of compression, heating, expansion and cooling and having a piston and cylinder arrangement defining an expansion and compression chamber therebetween, apparatus for controlling said engine output according to claim 10, wherein said movable sleeve member is mounted for rotation on said body member and has a gripping portion to effect axial movement in said sleeve with respect to said body member to increase the volume of said recess chamber in one direction of rotation and to decrease the volume of said recess chamber in an opposite direction of rotation thereof.

13. In combination with a fluid type engine in whlch a working fluid traverses a thermodynamic cycle comprising the stages of compression, heating, expansion and cooling, and having:

engine block structure defining a bore therewithin;

piston structure disposed within said bore for longitudinal reciprocal movements relative thereto between a plurality of positions therewithin; and

compression chamber structure disposed within said engine block structure, said chamber structure comprising:

a plurality of variable volume chambers;

one of said variable volume chambers being defined by and between said engine block structure and said piston structure; compensator apparatus particularly adapted to be structurally operatively associated with said engine block structure, enabling the compensation for variations in temperatures and Working fluids utilized in said thermodynamic cycle, and further enabling said engine to maintain and present a substantially constant output, said compensator comprising: a housing structurally operatively associated with said engine block structure; said housing and block structure defining another of said variable volume chambers; and pressure responsive structure disposed in said housing responsive to the pressures within said compression chamber structure. 14. In the combination as defined in claim 13, wheresaid pressure responsive structure comprises: a plurality of portions; and a projection extending from one of said portions in a direction generally towards the one of said plurality of variable volume chambers; the diametral dimensional extent of said projection being less than that of said portions, enabling the pressures within said one chamber to be directed against the one of said plurality of portions. 15. In the combination as defined in claim 14, wheresaid pressure responsive structure is reciprocal within said housing between a plurality of positions; said housing is provided with a shoulder for defining one of said plurality of positions, and wherein there is provided: adjustable structure for defining the other of said plurality of positions. 16. In the combination as defined in claim 15, wheresaid adjustable structure comprises: a rotatable cam disposed within said housing; and said pressure responsive structure comprises further: an other projection extending from the other of said plurality of portions generally in a direction towards said cam; said other projection being particularly adapted to be mutually cooperatively engageable with a surface on said cam. 17. In the combination as defined in claim 13, wheresaid pressure responsive structure is reciprocal within said housing; and wherein there is provided: adjustable structure for defining at least one position of the pressure responsive structure within said housing, and adjustable structure comprising:

a sleeve disposed in threaded mutual cooperative engagement with said housing; and

a handle structurally operatively associated with said sleeve;

said pressure responsive structure being mutually cooperatively engageable with said handle.

18. Compensator apparatus particularly adapted to be structurally operatively associated with a fluid type engine in which a working fluid traverses a thermodynamic cycle comprising the stages of compression, heating, expansion and cooling, and comprising:

a housing particularly adapted to be structurally operatively associated with the engine block structure of said engine;

pressure responsive structure disposed in said housing, said pressure responsive structure being particularly adapted to be reponsive to the pressures within compression chamber structure in said engine, and being reciprocally movable in said housing between a plurality of positions therewithin and with respect thereto; and

adjustable structure for defining one of said plurality of positions.

19. The compensator apparatus as defined in claim 18,

wherein:

said pressure responsive structure comprises:

a plurality of portions; and

a projection extending from one of said portions;

the diametral dimensional extent of said projection being less than that of said portions, enabling the pressures within said compression chamber structure to be directed against the one of said plurality of portions.

20. The compensator apparatus as defined in claim 19,

wherein:

said adjustable structure comprises:

a rotatable cam disposed within said housing; and

said pressure responsive structure comprises further:

an other projection extending from the other of said plurality of portions generally in a direction towards said cam;

said other projection being particularly adapted to be mutually cooperatively engageable with a surface on said cam.

References Cited by the Examiner UNITED STATES PATENTS 7/52 Rinia et a1. -24 5/56 Dros et a1. 60--24

Claims

1. APPARATUS FOR CONTROLLING OUTPUT OF A FLUID-FYPE ENGINE IN WHICH WORKING FLUID TRANSVERSES A THERMODYNAMIC CYCLE OF COMPRESSION, HEATING, EXPANSION AND COOLING STAGES, SAID APPARATUS COMPRISING; A HOUSING DEFINING A CHAMBER, SAID CHAMBER BEING DISPOSED TO RECEIVE A PORTION OF SAID WORKING FLUID THEREIN WITH SAID WORKING FLUID BEING COMMUNICABLE WITH SAID CHAMBER DURING THE COMPRESSION STAGE OF SAID CYCLE, AND MEANS FOR EFFECTIVE PRESSURE VARIATION IN SAID WORKING FLUID WITHIN SAID CHAMBER.