JP2002544420A - Drive and rotary displacer for hot air engine - Google Patents

Abstract

(57) Abstract: A drive device (20) for use in transmitting power from a plurality of linear reciprocating power generating members (14) to a rotary output member (60). The drive device (20) comprises a drive cam member (21) having a cam follower guide profile (30) extending along the cam member (21); Operatively connected to the member (14). Each follower (31) is adapted to engage a cam follower guide profile (30) with each reciprocating motion cycle of the power generating member (14), the drive cam follower guide profile (30) comprising: Following a generally sinusoidal profile of the surface of the drive cam member (21), the profile includes a series of lobes (25, 26) forming a trough with peaks having intermediate regions (27, 28) therebetween. The peak-to-peak amplitude of the substantially sinusoidal profile of the cam follower guide profile (30) on the surface of the drive cam (21) is substantially equal to the stroke amplitude of the stroke of the reciprocating power generating member (14). Corresponding to There are at least three drive cam followers (31) spaced from one peak along the contour (30) of the adjacent trough. A rotary vane displacer for a gamma configuration Stirling engine is also disclosed.

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to a drive for use with a powered reciprocating member. One particular application of the present invention is that the drive is a Stirling engine (Stirlin engine).
g engine). However, this drive has other applications and is used in many other types of devices that have a powered reciprocating device.

[0002] The Stirling engine was designed by Robert Stirling in the early 1800s, advocating a hot-air engine capable of converting energy into useful work.
bert Stirling). Stirling engines are seen to have many advantages over normal and well-known internal combustion engines,
Much analysis and development has taken place in this century.

[0003] Stirling cycle engines operate in a closed regenerative thermodynamic cycle with periodic compression and expansion of the working fluid at different temperature levels. It typically has the following components: One or more cylinders; a displacer and a power piston moving in one or more cylinders; a working fluid control loop; a regenerator or other heat exchanger / chiller device. And a drive device. A Stirling engine connected to a drive to convert the linear motion of the piston into a rotary motion is called a motion engine. The Stirling engine has alpha, beta,
Various piston / cylinder arrangements can be employed, including what is known as a gamma arrangement. In the alpha configuration, there is a separate cylinder for expansion and compression space with each piston. In the beta configuration, the displacer and the power piston operate on the same cylinder, and in the gamma configuration, the displacer and the power piston are housed in separate cylinders. In another form of Stirling engine, the reciprocating displacer piston can be replaced by a rotating displacer, known as a rotating displacer engine.

[0004] Stirling engines, in their basic form, were earlier than internal combustion engines.
date) and has many applications, but no universal application capability has been found due to many issues, including power output. It is generally believed that when such problems are addressed, Stirling engines can gain widespread acceptance in many applications. This is due to the high thermal efficiency that can employ heat from any source, little or no emissions, and modern Stirling engine aspects, including quiet operation, that make it suitable for many applications. This is especially so in the times.

Many drives have been proposed for use in Stirling engines,
They include simple crankshafts, rhombic devices, Ross connections, and rotating swashplates. A cam drive has been proposed, see for example US Pat. No. 5,442,913 and US Pat. No. 5,533,335. In the present invention, another drive for use with a Stirling cycle is disclosed as enabling some of the advantages of a Stirling cycle to be realized.

According to one aspect of the present invention, there is provided a drive for use in transmitting power from a plurality of linear reciprocating power generating members to a rotary output member, the drive comprising a cam. A drive cam member having a cam follower guide profile extending along the member; the drive cam follower is operatively connected to each power generating member, and each follower is coupled to each of the power generating members. Suitable for engaging a cam follower guide profile by a reciprocating cycle, said drive cam follower guide profile following a substantially sinusoidal profile of the surface of the drive cam member, With a series of lobes forming a trough with a peak having an intermediate region between them, the peak-to-peak amplitude of the substantially sinusoidal profile of the cam follower guide profile on the surface of the drive cam is , Reciprocating motion Substantially corresponds to the stroke amplitude of the stroke of the over generating member comprises at least three drive cam follower spaced along the contour of the adjacent Tiger (trough) off from one peak (peak).

The term “sinusoidal” is understood to mean any suitable contour having a series of peaks and troughs joined by an intermediate region, ie, the contour is a strict geometric It is not always necessary to be a sine wave with a sense. In one form of the invention, the drive cam member has a substantially cylindrical body rotatable about a central axis, and the cam follower guide profile extends along a surface of the cylindrical body. In some arrangements, the cam follower guide profile may be on an outer surface of the cam body. In another arrangement, the cam follower guide profiles are on their inner surfaces. The cam follower guide profile may include, for example, an upright member or groove on the surface of the cam body.

[0008] The drive cam member is operatively connected to the drive shaft such that rotation of the cam member results in rotation of the drive shaft. In one embodiment, the reciprocating members are provided in a generally annular arrangement, with each cylinder assembly being equally spaced circumferentially from its respective adjacent reciprocating member. In one form, the reciprocating member has a piston provided within each cylinder for reciprocating operation therein. The drive has a main body portion and a drive cam member is provided for rotation associated therewith. The apparatus further has a carriage associated with each drive cam follower, each cam follower being operatively connected to its associated carriage. Truck
ck) is provided on the main body, and each carriage is provided for linear movement along a track. In one form, the truck has a plurality of groups of rods, each group associated with a respective carriage, each carriage being receivable on a rod for sliding movement therewith. It has a guide member. In another form, the track has a plurality of grooves in the main body, each groove being associated with a respective carriage, each carriage being receivable in each groove for movement therewith.

[0009] In one application, the device is suitable for use in a Stirling engine. The Stirling engine has a plurality of adjacent cylinder assemblies, each cylinder assembly being associated with a power piston and a displacer, a piston connecting rod extending from each power piston, and a power piston connecting rod being operated. A drive cam follower connected to them. Each follower is suitable for engaging a cam follower guide profile during each reciprocating cycle of the power piston. There is further provided control means operable such that the displacer and power piston for each assembly are in a selected phase with respect to each other. Advantageously,
The sinusoidal profile can be modified to meet the requirements of the selected engine parameters. For example, by "flattening" to change the dwell time of the displacer and power piston, the engine power output is
The lobes can be increased while maintaining the harmonics equal to a harmonic, ie, a series of waveforms. Preferably, the cylinder assemblies are provided in a generally annular arrangement, with each cylinder assembly being circumferentially equally spaced from its respective adjacent cylinder assembly.

[0010] In one form, each cylinder assembly includes a cylinder having a displacer and a power piston therein, the displacer being arranged to undergo a reciprocating operation. In this configuration, the displacer may have a central displacer connecting rod in the piston connecting rod, which may extend through the piston and be provided in the piston connecting rod. In this form of the invention, the control means comprises coupling means such that the reciprocating cycles of the assemblies and the displacer and power piston of each assembly are in a selected phase. In one form, the power piston connecting rod is formed from an at least partially tubular member into which the tip of the displacer connecting rod extends.

In another form, each displacer is provided in a spaced displacer cylinder, each power piston is provided in a power piston cylinder, and each associated displacer and power piston cylinder is They are connected by a gas conveying passage. This is a typical gamma configuration type engine. In order to control the power output, an electrically operable ball valve may be further provided in each gas transfer passage.

According to one aspect of the present invention, a displacer is provided in an associated displacer cylinder for effecting reciprocating movement therein. In this particular form of the invention, the control means comprises a displacer cam member having a displacer cam follower profile extending therealong. A displacer connecting rod has a displacer cam follower extending from each displacer and adapted to engage the displacer cam follower profile and operatively connected thereto. The drive cam member and the displacer cam member are provided such that the reciprocating cycle of the assembly is in a selected phase.

In the above aspect of the invention, each cam member is operatively connected to an output shaft. Rotation of the drive cam member is suitable to cause rotation of the output shaft, which in turn results in rotation of the displacer cam member. Preferably, the displaced sac member has, for example, a plurality of planet gears (pla
It is operatively connected to the output shaft by a gear train having a netary gear and a ring gear. According to another aspect of the invention, each displacer is provided in a cylinder associated therewith for individual rotational movement therein. In this rotating displacer of the present invention, the displacer is substantially hemispherical in cross section, extends along a cylinder, and is in the form of a vane rotatable along their longitudinal axis. Preferably, the front surface of the blade is concave. In this rotary vane displacer configuration of the invention, the control means comprises a gear train having a ring gear operatively connected to the drive shaft and a series of pinion gears associated with each displacer, the rotation of the pinion gear being selected phase. Causes rotation of the blades.

The displacer blades described above form a separate invention on their own. Thus, according to another aspect of the present invention, there is provided a displacer for a Stirling engine, the displacer having elongated vanes provided for rotation in a cylinder in use, the vanes being associated therewith. It has a body that is substantially semi-circular when viewed in cross-section having a front surface and a rear surface that are substantially similar to a curved cylinder. Preferably, the cylinder wall is articulated with ridge rings and grooves to increase the effect of the working fluid. Preferably, the front face of each blade is provided on the opposite side of the rotation axis of the blade and has a recess formed inward.

In two embodiments of the invention described below, the control means comprises an operable adjusting device for controlling the rotation direction of the drive output shaft by adjusting the displacer to the timing of the power piston with which it is associated. Have more. The adjusting device may have a planetary gear support sleeve coupled to the drive shaft for rotation therewith. This sleeve supports the planet gears thereon. The planet gear support sleeve is provided in the ring gear support sleeve that holds the ring gear. Each sleeve has an associated slot therein, the slot containing a pin therein, the pin being provided on a plug provided for linear movement within the sleeve. The movement of the pin is controlled by a screw member operated by a control actuator.

In normal operation, the cam member and the ring gear via the drive output shaft, the sleeve, the planetary gears rotate integrally. The rotation of the control actuator and the screw member allows the pin to move up or down along the longitudinal axis of the drive output shaft, thereby causing relative rotation between the two sleeves, thereby timing the reciprocation of the displacer. To adjust. As a result, the engine output cam can be driven normally in the forward or reverse direction, or can be selected in the neutral position.

The number of peaks of the substantially sinusoidal cam follower guide profile is set to the preferred number of cylinders of the associated Stirling engine. For example, where the guide surface has four peaks (ie, a two-cycle substantially sinusoidal configuration), the Stirling engine preferably has eight power pistons and each power piston connection The cam follower of the rod is equally spaced from its adjacent cam follower. As a result, each pair of pistons is actually provided 90 degrees out of phase when reciprocated in their respective cylinder. The angular separation of the axes of each power piston connecting rod (where there are eight power connecting rods) is 45 ° (see FIG. 29).

Further, in the case where the engine has eight power pistons, since each power piston has four strokes per revolution of the cam, the total number of power strokes of the eight power pistons is 32 strokes per rotation. As the number of peaks in the guide profile increases, the number of power pistons engaging the drive can increase. This in turn leads to an increase in the number of power strokes per revolution of the cam, as shown by Table 1 below.

[Table 1]

As the number of peaks increases, it is readily foreseen that the number of power pistons available to drive the drive will also increase linearly with the relationship described above. A particularly advantageous application of the drive according to the invention relates to its use as a component of an electric generator. In this regard, the drive cam member is configured to form an armature suitable for operating with the stator for generating electricity. The drive cam member has a plurality of permanent magnets provided along the surface of the drive cam member, such that the relative movement between the two parts produces electricity.
It is provided to operate with the stator. Preferred embodiments of the present invention will be described with reference to the accompanying drawings.

Referring to FIGS. 1 to 6 of the drawings, there is shown a Stirling engine embodying a drive according to the present invention. The Stirling engine shown is in beta (bet
a) The shape of the placement engine. The engine is indicated generally at 10 and comprises a cylinder block 18 having a drive 20 at one end. The drive device 20 includes a cylindrical rotating body 21 having a fixed base plate 22 operatively connected to a drive shaft 60. The rotating cam body 21 includes a frame 2 having an end plate 24 fixed to each other by a plurality of carriage rods 35 and 36.
3 is covered. The substantially cylindrical drive support shell 32 covers the frame 23 and the cam body 21 as shown in FIG. Engine 10 further includes a plurality of piston / cylinder assemblies, two of which are 11 and 13.
Indicated by

Each assembly comprises a cylinder 12 having two spacers or zones, each cylinder being associated with a power piston 14 in one space and a displacer 15 in the other space. Each power piston 14 is operatively connected to a connecting rod 16 and each displacer is operatively connected to a connecting rod 17. As shown in FIGS. 1 and 6, the connecting rod 17 of the displacer is provided in the piston connecting rod 16 and is movable with respect thereto. Each cylinder has a cold zone C and a hot zone H
And they are interconnected like a conventional Stirling cycle engine. The engine operates in a closed regeneration cycle with periodic compression and expansion of the working gas at different temperature levels. Since the displacer 15 is provided to move the working gas between the hot zone and the cold zone, it acts on the power piston 14 so that the working gas volume changes.

As in the prior art, in a Stirling engine, the displacer 15 and its associated power piston 14 in each cycle are provided basically 90 ° out of phase with respect to each other, as shown in FIG. The displacer guides the power piston 90 ° with respect to the direction of rotation of the output shaft, as shown in FIG.

The particular shape of the engine shown in the figure has twelve cylinders arranged in a circular arrangement. The assemblies are equally spaced by an angle θ. In this arrangement, twelve assemblies and θ = 30 °. It should be understood that other arrangements having more or fewer cylinders can be used. This is discussed in more detail below. Further, as shown, the cylinders 12 are provided in a circular or annular arrangement, however, the cylinders may be arranged in a side-by-side linear arrangement as shown in FIG. It should also be understood that other arrangements can be provided.

Each of the displacers 15 is operatively connected to a power piston of an adjacent piston / cylinder assembly. This is clearly shown in FIG.
Displacer 15 of one piston / cylinder assembly is operatively connected to power piston 14 of the other piston / cylinder assembly. The power piston 14 of the assembly 13 directs the displacer 15 of the assembly in the direction of rotation of the output shaft. Each power piston connecting rod 16 is operatively connected to an output cam member 21 that forms part of the drive and then operatively connected to an output shaft 60.

The cam member 21 has a substantially cylindrical body (see FIG. 2) having a cam guide portion 30 (see FIG. 3) thereon, and the cam body 21 (FIGS. 1 and 3) has an axis X- Rotate around X. The cam guide 30 is shown on the inner surface of the body 21, however, it is provided on either the inner or outer surface of the cylindrical body 21. As shown, the cam guide 30 also has a continuous profile with a series of lobes 25 and 26 that are the peaks or troughs of the guide with intermediate portions 27 and 28 between them. As can be seen, the outer shape of the cam guide 30 is substantially sinusoidal.

The arrangement of the various components of the cam guide 30 can be varied to maximize the operating characteristics of the engine. For example, it may be desirable to increase the piston dwell (see FIG. 29) time, since this creates a significant gain in power. To that end, the lobes 25 and 26 of the cam guide can be flattened because their tips are less pronounced. In addition, movement is facilitated by forming an intermediate portion, as they are substantially straight. The control is executed by changing the inclination of the intermediate portion.

Each power piston connecting rod 16 has a cam follower 31 associated therewith suitable for following along a cam guide 30. The amplitude from peak to trough substantially corresponds to the amplitude of the stroke of the power piston 14 of the engine. As shown, the trough and the middle part from each peak of the cam guide are connected to the connecting rod 1.
6 and three associated power followers 31 and three power pistons 14 associated therewith. Each displacer 15 has an adjacent piston /
Operatively connected to the power piston 14 of the cylinder assembly. Thus, there is provided a cam guide having twelve displacers of six lobes and a power piston / cylinder assembly, in which the power piston operates in sequence, and for each 30 ° of rotation, an expansion stroke is performed. There are three power pistons that are connected and three power pistons that are undergoing a compression stroke. FIG. 9 diagrammatically illustrates the arrangement shown in FIG. 1 with the pistons and displacers shown in their positions for each assembly, with the assemblies laid out side-by-side. . It should be readily appreciated that at full rotation of the cam member in the above arrangement, the engine produces 36 expansion strokes and 36 compression strokes (ie, 72 strokes per revolution).

As previously mentioned, and as best shown in FIG. 1, for example, the displacer 15 of the assembly 11 is operatively connected to the piston 14 of the assembly 13. This is done, for example, by a connecting link 19. As disclosed, the output shaft 60 extends through the center of the engine,
It is supported by the drive support 32 having a bearing 53. As described above, the cam member 21 includes the cylindrical cam body having the groove-shaped cam guide portion 30 on the inner cylindrical surface. The cam body 21 is provided on the output shaft 60 via the fixed base plate 22, and is arranged such that rotation of the cam body 21 causes rotation of the output shaft 60.

The cam follower 31 is operatively connected to a cam follower carriage 33 operatively connected to the power piston connecting rod 16. The cam follower carriage 33 is arranged for linear movement along a track 34 having track rods 35 and 36 in the configuration shown. The coupling link 19 is operatively connected to the carriage 33. 7 and 8 show a cam follower carriage of another T-slot system, without the need for a track 34. FIG. As shown in FIGS. 7 and 8, the power piston 14 and the power piston connecting rod 16 have a carriage 41 at one end of the connecting rod 16 having a cam follower 31. A carriage 41 in the form of a slider can be accommodated in a T-slot in a part of the mechanical body.

Referring to FIGS. 10 to 17 of the drawings, there is shown a second configuration of a Stirling engine incorporating a dual cam drive according to the present invention. In this case, the Stirling engine is of the gamma type arrangement. The engine includes a cylinder block 118, indicated generally at 110, having both cylinders 112 and cylinders 114. The dual cam drive has a drive support 122 at one end. The drive support 122 includes a substantially cylindrical shell 132 having a drive output shaft 160. Cylinder 112
And 114 are provided in the cylinder block 118,
One group 112 is associated with a power piston 115 and the other group 114 is associated with a displacer 116. Each cylinder 114
Are connected to each cylinder 112 by a gas conveying passage in the form of a conduit 119. An electrically operated ball valve 120 is provided in each conduit 119 for transport of the working fluid and control of the power output.

Each cylinder 112 is suitable for housing a power piston 115 and each cylinder 114 is suitable for housing a displacer 116. Each power piston 115 is operatively connected to a connecting rod 124 so that each displacer 11
6 is operatively connected to a connecting rod 125. Each cylinder 114 has a low temperature zone C and a high temperature zone H, as in a conventional Stirling cycle engine. The engine operates in a closed regeneration cycle with periodic compression and expansion of the working gas at different temperature levels. Since the displacer 116 is provided to move the working gas between the hot zone and the cold zone, it acts on the power piston 115 so that the working gas volume changes.

In the particular configuration of the engine shown in FIGS. 10 to 17 of the drawings, groups of cylinders are provided one above the other in a circular arrangement. The assemblies are circumferentially equally spaced from each other. In an arrangement with 12 assemblies, they are 3
0 ° apart. It should be understood that other arrangements having more or fewer cylinders can be used. This is discussed in more detail below. Further, while cylinders 114 are shown as being arranged in a circular or annular arrangement, it should also be understood that they can be arranged in other arrangements, such as side-by-side linear arrangements.

As disclosed, the drive includes a drive cam member 130 having a substantially cylindrical body 133 having a cam guide 134 thereon, such that the cam member rotates with the drive shaft 160. Is provided. The cam guide 134 is shown on the inner surface of the body 133, however, it is provided on either the inner or outer surface of the cylindrical body 133. As disclosed, the cam guide 134 is a continuous profile having a series of lobes 135 and 136 that are peaks or troughs of the guide with intermediate portions 137 and 138 therebetween. As can be seen, the outer shape of the cam guide 134 is substantially sinusoidal.

The arrangement of the various components of the cam guide 134 can be varied to maximize the operating characteristics of the engine. For example, it is desirable to extend the dwell time of the piston, since this creates a significant gain in power. To that end, the lobes 135 and 136 of the cam guide can be flat because their tips are less pronounced. In addition, operation is facilitated by forming an intermediate portion, as they are substantially straight. The control is executed by changing the inclination of the intermediate portion.

Each power piston connecting rod 124 has a cam follower 141 associated therewith suitable for following along a cam guide 134. The peak to trough amplitude substantially corresponds to the amplitude of the stroke of the engine power piston 115. As shown, each peak to trough and intermediate portion of the cam guide has three power pistons 115 associated therewith via a connecting rod 124 and an associated cam follower 141. Each cam follower 141 is operatively connected to a cam follower carriage 143 operatively connected to the power piston connecting rod 124. The cam follower carriage 143 is arranged to make a linear movement along a track 144 shown as having a track rod.

The dual cam gun master ring further comprises a connection control means 150 having a displacer member 152 operatively connected to the drive shaft 160 and rotating therewith. The cam member 152 has the shape of a cylindrical body having a cam guide 155 on its outer surface. The cam guide 155 is suitable for receiving a cam follower 158 operatively connected to each displacer connecting rod 125.
A cam follower 158 is provided on the carriage and track assembly, similar to that described above in connection with the drive cam. In the particular embodiment shown, drive output shaft 160 and cam member 152 are operatively linked by a gear train having a series of planetary gears 153 and ring gear 154 on the inner surface of the cam member. The reason for this method of operative connection will become apparent from the following description of the adjacent mechanism. However, it should be understood that cam member 152 can be directly coupled to drive output shaft 160. This rotation of the drive output shaft causes rotation of cam member 152, which in turn causes reciprocation of displacer 116.

In the particular embodiment disclosed and best shown in FIGS. 11 and 15, the coupling control means 150 includes an adjustment device 170. This adjusting device 17
0 is operable to control the direction of rotation of the drive output shaft 160 by adjusting the timing of the displacer 116 with respect to the power piston 115 associated therewith. The adjusting device 170 has a planetary gear support sleeve 173 surrounding the drive shaft 160 and supporting the planetary gear 153 on its flange-shaped base. The planet gear support sleeve 173 has a ring gear 156 near its base.
Is provided in a ring gear support sleeve 176 that holds Each sleeve 17
3 and 176 have operating slots 174 and 175 therein for receiving pins 172 therein, the pins 172 being arranged for linear movement within the hollow portion of the drive shaft 160. Plug 179.

In normal operation, the drive output shaft 160, the sleeves 173 and 176, and the cam member 152 rotate integrally via the planetary gear 153 and the ring gears 154, 156. The rotation of the control actuator 180 and the screw member 171 allows the pin 172 to move up or down along the longitudinal axis of the drive output shaft 160, thereby causing relative rotation of the two sleeves, The timing of the relative reciprocation of the displacer 116 with the power piston is adjusted. The rotating displacer gamma configuration of a Stirling engine incorporating a drive according to the present invention is shown in FIGS. Referring to the specific engine embodiment shown in FIGS. 18 and 19, the arrangement is somewhat similar to the gamma arrangement shown in FIGS. The major difference is that in this particular embodiment,
The displacer rotates rather than reciprocates, so that the coupling control means is different and the engine employs a single cam member.

As shown in FIGS. 18 and 19, there is a Stirling engine, indicated generally at 210, which includes a displacer cylinder block 218, shown in detail in FIG. 21, and a drive at one end thereof. And a support plate 217. The drive support plate supports the drive output shaft 260. The engine is also 2
One group 212 having two groups of cylinders 212 and 214
Is associated with a power piston 215 and the other group 214 is associated with a displacer 216. Each displacer cylinder 214 is connected to each power piston cylinder 212 by a gas carrying passage in the form of a conduit 219. Each conduit 219 has an electrically operated ball valve 120 for delivery of working fluid and control of power output.

Each cylinder 212 is suitable for housing a power piston 215, and each cylinder 214 is suitable for housing a displacer 216. Each power piston 215 is operatively connected to a connecting rod 224, and each displacer 21
6 is operatively connected to the connecting rod 225. Each displacer cylinder 2
24 has a low temperature zone C and a high temperature zone H like a conventional Stirling cycle engine. The engine operates in a closed regeneration cycle with periodic compression and expansion of the working fluid at different temperature levels. Displacer 216 is
As it is provided to move the working gas between the hot and cold zones, it acts on the power piston 215 so that the working fluid volume changes.

In this particular embodiment, displacer 216 is provided for rotation within cylinder 214 of shaft 225, which is the center of the displacer.
The displacer 216 has the shape of a vane 227 that is substantially semi-circular when viewed in the cross-section shown in FIGS. The front face 229 of each vane is formed so that they are recessed inward, and the rear face approximately matches the curvature of the cylinder in which it is mounted. The blade 227 is configured such that it extends along substantially the entire length of the cylinder 214. It should be understood that the rotational displacer power output of the engine increases.

The high temperature zone H and low temperature zone C of the cylinder are arranged as opposing halves of the cylinder as shown in the plan view of FIG. To that end, the part of the cylinder defining the cold zone C has cooling fins 222 thereon. The section of the cylinder defining the high temperature zone H is configured such that the cylinder wall is heated by a suitably shaped heating member. The inner surface of each displacer cylinder 214 is a preferred shape, not shown in FIGS. 20 and 21, articulated with ridge rings and grooves to increase the effect of the working fluid.

The drive includes a drive cam member 230 having a substantially cylindrical body 232 having a cam guide 234 thereon, wherein the cam body 232 having a fixed base plate 270 is adapted to rotate the cam body with an output shaft. It is arranged to produce a rotation of 260. As disclosed, the cam guide 234 is a substantially sinusoidal continuous profile. Each power piston connecting rod 224 has an associated cam follower suitable for following along a cam guide 234. The peak to trough amplitude substantially corresponds to the amplitude of the stroke of the engine power piston 215. As shown in FIG. 19, the trough and the intermediate portion from each peak of the cam guide portion are connected to the connecting rod 2.
It has three power pistons 215 associated therewith via a cam follower 241 associated therewith.

To change the dwell time of the power piston, a series of lobe waveforms are harmonically adjusted by “flattening” the peaks and troughs of the sinusoidal cam guide.
c) By leaving the engine power output increased, especially since the rotating displacer can be operated independently at or near constant full power (see FIG. 29). The cam follower 241 is operably connected to a cam follower carriage 243 operably connected to the power piston connecting rod 224. The cam follower carriage 243 is provided for linear movement along a track 244 of the illustrated shape including a track rod 245.

In certain embodiments, coupling control means 250 has a ring gear 253 operatively coupled to drive shaft 260 for rotating therewith. The ring gear 253 is provided with a pinion 2 provided on the displacer connecting shaft 225.
As it meshes with 54, rotation of the pinion attached to the displacer shaft causes rotation of ring gear 253 and drive shaft 260. On the contrary, FIG.
7, according to the gear control mechanism employed, the ring gear 253
Causes rotation of pinion 254, thereby controlling the timed rotation of the displacer.

In one exemplary embodiment, the engine has 20 power pistons driving 10 lobe cams that provide 100 power strokes per revolution, with 5 pulses every 18 degrees. Thus, there are 5 20 vibrations per revolution. The rotating blade displacer device is driven by a gear train at a 5: 1 gear ratio from the main drive shaft. The main gear drives twenty small gears, each one controlling a rotary vane displacer device. The rotating vane displacer must rotate one full revolution between the peaks on one side of the cam (except 5), and looks like two strokes of the piston between the peaks. See FIG. 24 in this regard. An electrically operated ball valve between the displacer and the power cylinder along each transport pipe controls the power output. The device is air-cooled and battery activated to overheat the cylinder walls, after which it is electrically heated by means of a dynamo operated cam drive. While the cam drive is generating electricity by means of a generator attachment coaxial with the shaft, the cam tube as in FIG. 3 acts as a generator with an attached permanent magnet and a surrounding stator. . The particular shape of this embodiment is shown in FIG. Heat is applied to a captured area of the displacer cylinder adjacent to the central shaft of the engine.

Table 2 below shows the various arrangements for the number of power pistons relative to the cam lobes and the relevance of their activity per cycle.

[Table 2]

With reference to FIG. 25, the drive is shown in a configuration that can be used as a generator.
The drive cam member 330 is shown. The drive is of the type described in connection with any of the previously described embodiments. As disclosed, the drive cam member 330 has a series of permanent magnets 332 provided thereon. The portion of the outer body 335 of the mechanism has a series of windings or stators 337 provided thereon. Thus, the driving cam member 330
Forms the armature of the generator, and body 335 houses a series of stators.

Another specific application of the engine described in connection with FIGS. 18 to 24 relates to its use in a cooled aero engine, which is shown in FIG. ing. The disclosed engine is substantially identical to the engine described in connection with FIGS. 18-24, and like reference numerals have been used for like parts. The engine is housed in cowling 291 and propeller 271 is operatively connected to the output shaft.

Yet another specific application of the engine described in connection with FIGS. 18 to 24 relates to a sealed capsule of a cooled atmospheric engine, which is FIG.
Is shown in The components of the engine described in connection with FIGS. 18 to 24 are similarly numbered. In this application, the refrigeration element 280 surrounds the displacer cylinder block 281 and supplies cool air.

In a specific embodiment, the timing device 282 includes a rotary vane displacer 216 and a power piston 215 to control the direction of rotation of the drive shaft 260.
Change the timing sequence between the two, and fine-tune the sequence at high speed. The device is controlled by a stepping motor worm and wheels 283 that control a slug running in a drive shaft 260 with a drive pin running in a slot parallel to the drive shaft. The drive pin protrudes through the slot to pick up another lot of the sleeve connected to the main drive gear, which is an 8 ° parallel slot in the drive shaft. The pin moves a maximum value in either direction to control if a rotational direction of the drive shaft is required, and also to control any progress for high speed rotation.

The heating is electric heating, and the cooling is refrigeration cooling, which is performed by
Means that it can be sealed as a unit or capsule 285 having a drive shaft with one end protruding and an electrical loom located or concentrated in the device controlling the electrically operated ball valve for power. And the stepper motor controls the timing device. Preferably, the interior of capsule 285 is maintained under fluid pressure.

Finally, it can be appreciated that various changes, modifications, and / or additions can be incorporated into the various arrangements and arrangements of the components without departing from the spirit and purpose of the invention.

[Brief description of the drawings]

FIG. 1 is a schematic perspective view of a partially cut Stirling engine according to one embodiment of the present invention.

FIG. 2 is a partial cutaway view of another portion of the engine shown in FIG.

FIG. 3 is a schematic view of a cam member of the engine shown in FIG. 1;

FIG. 4 is a schematic view of one piston and displacer of the engine shown in FIG. 1;

FIG. 5 is a cutaway view of a cylinder block of the engine shown in FIG. 1;

FIG. 6 is a cutaway view of another portion of the engine shown in FIG. 1;

FIG. 7 is a schematic view of a T-slot shape of a cam follower carriage.

FIG. 8 is a schematic view of the T-slot carriage of FIG. 7 in a recessed sleeve.

FIG. 9 is a schematic diagram of an engine that has been flattened for purposes of disclosure.

FIG. 10 is a schematic perspective view of a Stirling engine according to another embodiment of the present invention.

FIG. 11 is a schematic side elevational view of the embodiment shown in FIG.

FIG. 12 is a schematic plan view of a portion of the engine shown in FIGS. 10 and 11;

FIG. 13 shows an arrangement of adjacent pistons of the engine shown in FIGS. 10 to 12;

FIG. 14 is a schematic diagram of the engine shown in FIGS. 10 to 12 with many components removed or cut away for disclosure.

FIG. 15 is a schematic diagram of the engine shown in FIGS. 10 to 12 with many parts removed or cut away for disclosure.

FIG. 16 is a schematic view of the engine shown in FIGS. 10 to 12 with many parts removed or cut away for disclosure.

FIG. 17 is a schematic view of the engine shown in FIGS. 10 to 12 with many parts removed or cut away for disclosure.

FIG. 18 is a schematic side elevation view of a third embodiment of the present invention.

FIG. 19 is a partially cutaway schematic view of the engine shown in FIG. 18;

FIG. 20 is a schematic diagram of an exemplary cylinder block for an engine of the type shown in FIG.

FIG. 21 is a schematic plan view of a portion of a cylinder block showing a high temperature zone and a low temperature zone.

FIG. 22 is a schematic view of a displacer blade for use in an engine of the type shown in FIG.

FIG. 23 is a plan view showing a timing sequence of a displacer for use in an engine of the type shown in FIG.

FIG. 24 is a plan view showing a timing sequence of a displacer for use in an engine of the type shown in FIG.

FIG. 25 is a schematic diagram showing a drive in a particular application used as a generator.

FIG. 26 is a schematic diagram of another particular application of an engine of the type shown in FIG.

FIG. 27 is a schematic diagram of yet another specific application of an engine of the type shown in FIG.

FIG. 28 is a diagram showing a crank cycle of a conventional Stirling engine.

FIG. 29 is a diagram of a cam layout for a drive device according to the present invention, simulating the crank cycle in FIG.

[Procedural Amendment] Submission of translation of Article 34 Amendment

[Submission date] May 14, 2001 (2001.5.14)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Contents of correction]

[Claims]

──────────────────────────────────────────────────続 き Continued on the front page (31) Priority claim number PQ3219 (32) Priority date September 30, 1999 (September 30, 1999) (33) Priority claim country Australia (AU) (81) Designated country EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, IT, LU, MC, NL, PT, SE), OA (BF, BJ, CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, GM, KE, LS, MW, SD, SL, SZ, TZ, UG, ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AG, AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, CA, CH CN, CR, CU, CZ, DE, DK, DM, DZ, EE, ES, FI, GB, GD, GE, GH, GM, HR, HU, ID, IL, IN, IS, JP, KE, KG , KP, KR, KZ, LC, LK, LR, LS, LT, LU, LV, MA, MD, MG, MK, MN, MW, MX, NO, NZ, PL, PT, RO, RU, SD, SE, SG, SI, SK, SL, TJ, TM, TR, TT, TZ, UA, UG, US, UZ, VN, YU, ZA, ZW. It has been disclosed.

Claims (31)

[Claims] 1. A driving device for use in transmitting power from a plurality of linear reciprocating power generating members to a rotary output member, the driving device comprising a cam follower extending along a cam member. A drive cam member having a guide profile; a drive cam follower operatively connected to each power generating member, wherein each follower is driven by each reciprocating cycle of the power generating member. Wherein the drive cam follower guide profile follows a generally sinusoidal profile of the surface of the drive cam member, which profile defines a peak and a trough having an intermediate region therebetween. With a series of lobes forming, the peak-to-peak amplitude of the substantially sinusoidal profile of the cam follower guide profile on the surface of the drive cam being substantially equal to the stroke amplitude of the stroke of the reciprocating power generating member. A drive device comprising at least three drive cam followers spaced from one peak along the contour of an adjacent trough. 2. The drive cam member has a substantially cylindrical body rotatable about its central axis, and the cam follower guide profile extends along the surface of the cylindrical body. The drive device according to claim 1, wherein 3. The drive device according to claim 2, wherein the cam follower guide outer shape is provided on an outer surface of the cam body. 4. The drive according to claim 2, wherein the cam follower guide outer shapes are on their inner surfaces. 5. The drive device according to claim 3, wherein the cam follower guide outer shape has an upright member or a groove on the surface of the cam body. 6. The driving member according to claim 1, wherein each cylinder assembly is provided in a substantially annular arrangement with each cylinder assembly being equally spaced circumferentially from each adjacent cylinder assembly. The driving device according to claim 1. 7. The drive cam member according to claim 1, wherein the drive cam member is operatively connected to the drive shaft such that rotation of the cam member causes rotation of the drive shaft. Drive. 8. The reciprocating member according to claim 1, wherein each of said reciprocating members is provided in a substantially annular arrangement, each of which is equally spaced circumferentially from each adjacent reciprocating member. The driving device according to claim 1. 9. The driving device according to claim 1, wherein the reciprocating member has a piston provided in each cylinder for performing a reciprocating operation therein. 10. A main body portion, said drive cam member being provided for rotation associated therewith, having a carriage associated with each drive cam follower, each cam follower being associated with its associated carriage. 10. The vehicle of claim 1, further comprising a track on the main body, wherein each of the carriages is provided for linear movement along the track. The driving device according to claim 1. 11. The truck has a plurality of groups of rods,
11. A drive according to claim 10, wherein each group is associated with a respective carriage, each carriage having a guide member receivable on a rod for sliding movement therewith. 12. The track has a plurality of grooves in the main body, each groove being associated with a respective carriage, each carriage being receivable in each groove for movement therewith. The drive device according to claim 10, wherein: 13. A Stirling engine suitable for use in a Stirling engine, the Stirling engine having a plurality of adjacent cylinder assemblies, each cylinder assembly being associated with a power piston and a displacer, wherein the piston connecting rod is The drive cam followers extending from and operatively connected to each power piston, each follower engaging a cam follower guide profile during each reciprocating cycle of the power piston. 2. The method of claim 1 wherein the piston and displacer for each assembly are in a selected phase with respect to each other.
13. The drive device according to any one of claims 12 to 12. 14. The drive of claim 13, wherein the cylinder assemblies are provided in a substantially annular arrangement with each cylinder assembly being equally spaced circumferentially from each adjacent cylinder assembly. . 15. The apparatus of claim 13, wherein each cylinder assembly comprises a cylinder having a power piston and a displacer therein, wherein the displacer is arranged to undergo reciprocating motion. Drive. 16. The displacer having a central displacer connecting rod within a piston connecting rod, wherein the displacer connecting rod extends through the piston and is provided within the piston connecting rod. Item 15
The driving device as described. 17. A reciprocating motion cycle of the assembly having a connecting member operatively connecting the displacer of one assembly to the displacer of the other assembly such that the reciprocating cycle of the assembly is in a selected phase. The drive device according to claim 16. 18. The drive device according to claim 17, wherein the power piston connecting rod is formed at least partially from a tubular member into which the tip of the displacer connecting rod extends. 19. Each power piston is provided within a power piston cylinder, each associated displacer is provided within a displacer cylinder, and each associated power piston and cylinder of the displacer are connected by a gas carrying passage. 14. The driving device according to claim 13, wherein the driving device is connected. 20. The drive device according to claim 13, wherein the drive cam member is connected to the drive shaft such that rotation of the cam member causes rotation of the drive shaft. 21. The drive device according to claim 19, wherein the connection control means is operatively connected to the drive shaft. 22. The driving device according to claim 19, further comprising an electrically operable ball valve in each of the gas transfer passages for controlling the power output. 23. A displacer cam is provided within an associated displacer cylinder for effecting reciprocating movement therein, and the coupling control means includes a displacer cam having a displacer cam follower profile extending therealong. A displacer connecting rod having a member, the displacer connecting rod having a displacer cam follower extending from each displacer, adapted to engage the displacer cam follower profile and operatively connected thereto; 20. The drive of claim 19, wherein each cam member is operatively connected such that a reciprocating cycle of the assembly is in a selected phase. 24. A displacer is provided in an associated cylinder for effecting a rotational movement therein, said displacer having a substantially hemispherical cross-section, extending along the cylinder and extending along their length. The blades are rotatable along a directional axis, the front surface of the blades is recessed, and the coupling control means includes a ring gear operatively coupled to the drive shaft and a series of pinion gears each associated with a respective displacer. 20. The drive device according to claim 19, further comprising a gear train, wherein rotation of the pinion gear causes rotation of the blade. 25. A coupling control means having an adjustable device operable to control the direction of rotation of the drive output shaft by relating the timing of the displacer to a piston associated therewith, the adjustable device coupled to the drive shaft. 20. The drive device according to claim 19, further comprising a planetary gear support sleeve which rotates together with the planetary gear support sleeve. 26. The drive cam member having a series of permanent magnets defined thereon by a stationary part of the device and defining an armature associated with the stator for generating electricity. The drive device according to any one of claims 1 to 25. 27. An electricity generating device, wherein electricity is provided for collective electricity to provide heat for activation to the engine, for electricity of the control actuator, and for charging of the starting battery. 27. The driving device according to claim 26, wherein the driving device is used for electricity. 28. A displacer having, in use, elongate vanes provided for rotation in a cylinder, the vanes having a front surface which, when viewed in cross section, is substantially the same as the curvature of the associated cylinder. A displacer comprising a substantially semicircular body having a rear surface. 29. The displacer according to claim 28, wherein the cylinder wall is articulated with ridge rings and grooves to increase the effect of the working fluid. 30. The displacer according to claim 28, wherein the front surface of each blade has a concave portion formed on an opposite side of the rotation axis of the blade and formed inward. 31. The substantially sinusoidal profile of the cam guide of the drive cam operatively connected to the output shaft and the power piston follower has a lobe peak that is flattened to increase dwell. 31. A displacer according to any of the preceding claims, having a trough so as to keep the lobes equal to a harmonic or a series of waveforms.