U.S. patent number 3,579,980 [Application Number 04/875,252] was granted by the patent office on 1971-05-25 for uniflow stirling engine and frictional heating system.
Invention is credited to Donald A. Kelly.
United States Patent |
3,579,980 |
Kelly |
May 25, 1971 |
UNIFLOW STIRLING ENGINE AND FRICTIONAL HEATING SYSTEM
Abstract
The Uniflow Sterling engine consists of multiple power and
displacer sections which are arranged in in-line form. The in-line
arrangement allows for the ganging of the piston sets so that a
simple modular, easily-serviced engine is produced. Hot and cold
conduction rods within the thermal zones aid in transferring heat
within the displacer sections. Alternating one-way gas flow bores
within the displacer blocks provide a uniflow gas flow loop for
improved thermal effectiveness. A frictional heating system is
advocated as a sustaining heating means, which utilizes an electric
motor and battery system to drive a friction drum against
replaceable heat transfer elements to produce sufficient heat
energy for the hot displacer zone.
Inventors: |
Kelly; Donald A. (Maspeth,
NY) |
Family
ID: |
25365461 |
Appl.
No.: |
04/875,252 |
Filed: |
November 10, 1969 |
Current U.S.
Class: |
60/525;
60/520 |
Current CPC
Class: |
F25B
9/14 (20130101); F02G 1/044 (20130101); F25B
2309/003 (20130101); F01B 1/12 (20130101) |
Current International
Class: |
F25B
9/14 (20060101); F02G 1/00 (20060101); F02G
1/044 (20060101); F01B 1/00 (20060101); F01B
1/12 (20060101); F03g 007/06 () |
Field of
Search: |
;60/23,24,27 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Schwadron; Martin P.
Assistant Examiner: Ostrager; Allen M.
Claims
I claim:
1. A uniflow Stirling cycle engine comprising multiple rectangular
power stage housings, multiple squarish power blocks fitted with
ball bearings in rolling association with the internal surfaces of
said multiple rectangular power stage housings, rectangular sealing
strips disposed within corresponding square grooves within one end
of the said squarish power blocks, wrist pins secured inside the
squarish power blocks, connecting rods pivoting on said wrist pins,
a crankshaft assembly disposed at the lower portion of said
multiple rectangular power stage housings, bearing means for said
crankshaft assembly, sealing means associated with said crankshaft
assembly, multiple rectangular displacer stage housings disposed at
one end and coaxial with said multiple rectangular power stage
housings, communication means between the two said stage housings,
hot and cold end plates secured to each end of said multiple
rectangular displacer stage housings, insulation means disposed
between the said hot and cold end plates and said multiple
rectangular displacer stage housings, squarish displacer blocks
fitted with multiple ball bearings, in rolling association with the
internal surfaces of said rectangular displacer stage housings,
multiple uniformly disposed regenerator bores within said squarish
displacer blocks, multiple interconnected conical baffle assemblies
uniformly disposed within said regenerator bores, multiple
uniformly disposed metallic conduction rods secured to said hot and
cold end plates, electric heating means disposed within some of the
hot said metallic conduction rods, axial clearance bores uniformly
disposed within said squarish displacer blocks in association with
said metallic conduction rods, a vertical slot disposed midway on
one side of said squarish displacer block, output shafts and
bearing means secured midway in said multiple rectangular displacer
stage housings, a crankdiscs secured to said output shafts, ball
bearings secured to the ends of said crankdiscs in rolling
association with said vertical slot of said squarish displacer
blocks, multiple chain sprockets secured to said output shaft and
said crankshaft assembly, drive chains connecting said multiple
sprockets, a half-stroke phase relationship between the said
squarish power blocks and said squarish displacer blocks, pressure
tight cover assemblies disposed over said multiple chain sprockets
and drive chains, a liquid fuel burner means disposed at the said
hot end plate in association with the hot side of said multiple
rectangular displacer stage housings, a liquid cooling means and
circulating system disposed adjacent to and in contact with said
cold end plate in association with the cold side of said multiple
rectangular displacer stage housings.
2. A uniflow Stirling cycle engine according to claim 1 including a
frictional heating system comprising multiple rotating friction
drums in rubbing contact with replaceable heat transfer plates,
electric motors and an electrical power source to rotate said
rotating friction drums, gear reduction means between said rotating
friction drums and said electric motors, pivots and pivoting
brackets for said replaceable heat transfer plates in communication
with said hot end plates spring means in association with said
replaceable heat transfer plates, mounting brackets for said
rotating friction drums and electric motors in association with
said multiple rectangular displacer stage housings, speed control
means for said electric motors.
3. A uniflow Stirling cycle engine according to claim 1, wherein
the said sealing means associated with said crankshaft assembly is
comprised of multiple rotor discs equally spaced and sealed to said
crankshaft assembly, multiple stator discs equally interspaced
between said multiple rotor discs and sealed to a stationary disc
housing sealed in association with said multiple rectangular
displacer stage housings, multiple tiny air flow vanes uniformly
arrayed on said multiple rotor discs disposed to cause an outward
air flow when said uniflow Stirling cycle engine is in normal
operation.
4. A uniflow Stirling cycle engine according to claim 1, wherein
the total number of said multiple interconnected conical baffle
assemblies are equally divided into hot and cold gas flow
directions, half said multiple interconnected conical baffle
assemblies have the apex of the cones pointing toward the cold end
of said multiple rectangular displacer stage housings, the
remaining half of said multiple interconnected conical baffle
assemblies have the apex of the cones pointing toward the hot end
of said multiple rectangular displacer stage housings, the said
half multiple interconnected conical baffle assemblies having their
cone apex pointing toward the cold end of said multiple rectangular
displacer stage housings are uniformly arrayed around the
cross-sectional periphery of said squarish displacer blocks, the
remaining half of said multiple interconnected conical baffle
assemblies having their cone apex pointing toward the hot end of
said multiple rectangular displacer stage housings are uniformly
arrayed on and near the cross-sectional center of said squarish
displacer blocks.
5. A uniflow Stirling cycle engine according to claim 1, wherein
dry film lubrication is uniformly applied to all internal working
surfaces and bearings of both said multiple rectangular power and
displacer stages and said squarish displacer blocks.
6. A uniflow Stirling cycle engine according to claim 1, wherein a
gas fuel burner means is applied in place of said liquid fuel
burner means disposed at at the said hot end plate in association
with the hot side of said multiple rectangular displacer stage
housings.
7. A uniflow Stirling cycle engine according to claim 1, wherein
said liquid cooling means consists of a liquid containing jacket in
close maximum surface area contact with said cold end plate
associated with the cold side of said multiple rectangular
displacer stage housings, multiple connecting tubes from said
liquid containing jacket to multiple air-cooling radiators forming
a circulating cooling loop system, pumping means driven directly
from said uniflow Stirling cycle engine.
8. A uniflow Stirling cycle engine according to claim 1, wherein
said output shaft and crankshaft assembly are fitted with large
spur gears in place of said chains and sprockets, an idler gear is
interposed and meshes with said large spur gears, said large spur
gears are of equal size so that a one-to-one ratio is provided.
Description
The invention relates to improved reciprocating, multiple piston
Stirling engines with an auxiliary frictional heating arrangement.
The principal features of this in-line engine is that a generally
circular gas flow loop is established with effective heat transfer
provided by both hot and cold multiple conduction rods. A unique
feature provided for the operating pistons is the addition of
special ball bearings which significantly reduce the operating
friction level in both sections.
This in-line engine design is generally similar to a Stirling T
engine described in patent application, Ser. No. 760,256, now U.S.
Pat. No. 3,508,383. It will be recognized that this form of
Stirling engine is similar to existing Stirling cycle machines, but
with the addition of effective thermal transfer means for both hot
and cold zones. The adoption of effective thermal transfer means
aids in producing a compact closed cycle engine and makes high
operating efficiency and fuel economy possible.
The multiple conduction rod technique is only applicable to
reciprocating machines since the reciprocating displacer is
provided with corresponding clearance bores, so that the displacer
may freely pass over the conduction rods.
The adoption of the uniflow gas flow loop is necessary to avoid
passing the hot expanding gas near the cold displacer walls.
One-way hot gas flow bores near the center of the block displacer
allows the hot gas to act directly on the power piston. On the
reverse stroke the gases are directed along the cold walls, through
the displacer block and thereby away from the hot central displacer
zone, so that a generally circular gas flow loop is established.
The uniflow gas flow is accomplished by placing multiple
interconnected conical baffles within the designated hot and cold
bores. The hot conical baffles will be placed with the cone apex
pointing toward the hot displacer volume, while the cold conical
baffles will have their cone apex pointing toward the cold
displacer volume.
By arranging the hot uniflow bores near the center of the displacer
block and the cold uniflow bores around the outer portion of the
block, a separation is made between the thermal flows and a series
of circular gas flow loops is established.
Regeneration of the gas flow is obtained through the
interconnection of the conical baffles which take on and give up
heat to the opposite gas flow. The interconnected conical baffles
act in the same manner as any suitable filament or other
regenerative material within the uniflow gas bores.
This form of Stirling engine requires that the two operating
sections, the power and displacer pistons be chained or geared
together with each section independently dyna-balanced and made as
lightweight as possible. Since the displacer block must nearly half
fill the displacer volume, the counterbalance arrangement must be
externally placed within an adjacent pressurized drive section. The
chain or gear drive connecting the two sections drive shafts will
be enclosed within the pressurized volume so that only a single
pressure seal is required at the output shaft.
The in-line engine is in modular form so that the adoption of
square or rectangular displacer or power blocks facilitates the use
of special ball bearings in order to lower the operating friction
level within the engine. The ball bearings were not subjected to
unreasonable temperature levels within the engine, so that their
life will not be adversely affected. A controlled airgap between
the reciprocating power block and the internal housing walls is
desirable to that excessive side loads and wear on the sealing
strips are minimized. The sealing strips which provide the pressure
sealing means for the power block are made from filled-Teflon and
are half-lapped at the ends to achieve a continuous sealing
surface. The sealing strips are provided with thin, wave springs
behind them so that constant sealing contact with the sidewalls is
assured.
The multiple conduction rods are uniformly spaced within the hot
and cold volumes and secured to the hot and cold end plates,
respectively, which are insulated from the main housing. The
multiple conduction rods provide a means of thorough internal
thermal transfer without excessive heating or cooling of the
external housings and avoids the necessity of splitting the
housings into hot and cold halves.
Some of the conduction rods are fitted with electric heating rods
for rapid heating and starting of the engine. The electric leads
from the heating rods are fully insulated and shielded where they
exit the housings. A battery assembly and switch control means is
provided for the heating rods.
A conventional cooling system is utilized for the engine with a
liquid cooling jacket secured to a maximum area of the engine cold
side. A large radiator, or multiple radiators, and pumping
arrangement would be connected to the cooling jackets through
incoming and outgoing fluid lines. The total radiator cooling area
would have to be two to three times that of conventional I.C.
engines in cars, because of the greater cooling requirement of
Stirling engines.
A frictional heating system would be provided as an auxiliary or
sustaining heating means, when the primary heat source is not
operating. The frictional heating arrangement would consist of a
friction drum revolving at moderate speed against a replaceable
heat transfer plate, which is in direct contact with the hot side
of the displacer housings. The friction drum or drums would be
driven by an electric motor or motors and a battery assembly. The
replaceable heat transfer plate or plates must be pivoted and
spring loaded against the drum to insure proper contact as the
transfer plate and drum wears. The drum should outlast the transfer
plate since the plate is easily replaced and would cost less. A
suitable gear reduction assembly must be provided from the
high-speed electric motors to the drums for the necessary
mechanical disadvantage.
A multiple-disc labrinth type of shaft seal must be provided at the
output shaft to retain the internal working pressure at a minimum
friction level. Several of the discs contain multiple
unidirectional vanes to create a dynamic back pressure in order to
aid in the retention of the working gas.
It is expected that the uniflow engine will be capable of operating
at pressure levels around 100 atmospheres so that a high high
power-to-weight ratio will be realized. Although advocated as an
in-line engine the modular design lends itself to a radial form
arrangement. The preferred in-line design has the advantage of
allowing a compact heating and cooling means within a minimum sized
engine package. The radial design may have some advantage in
providing a relatively flat package with the possibility of
gyroscopic stability and a vertical drive shaft.
It is an object of the invention to create an improved Stirling
engine which operates at high thermal efficiency.
It is an object of the invention to provide a Stirling engine which
is relatively inexpensive to manufacture and repair.
It is an object of the invention to create a Stirling engine which
operates with a minimum of lubrication and requires a minimum of
maintenance effort.
It is an object of the invention to provide a quick-starting
Stirling type engine.
It is a final object of the invention to provide an auxiliary
frictional heating means as a backup for the primary heat
source.
The above objects and general aims will be apparent from the
detailed description to follow when taken in conjunction with the
drawings.
It should be understood that variations may be made in the detail
design of the engine without departing from the spirit and scope of
the invention.
Referring to the drawings:
FIG. 1 is a top sectional view through the uniflow engine.
FIG. 2 is a side elevational section through the engine.
FIG. 3 is an elevation view of the auxiliary frictional heating
arrangement.
FIG. 4 is a front elevational section through the engine.
FIG. 5 is a front elevation view of the Uniflow Stirling Cycle
diagram.
FIG. 6 is the Stirling cycle diagram, showing pressure vrs.
volume.
Referring to the drawing in detail:
The power stage housings 1 are built up of steel or aluminum plates
to form a rectangular chamber which is pressure tight, with the
internal surfaces 1a made flat and smooth to minimize seal wear.
The machine screws 1b join the plates together. The power blocks 2
are built-up of aluminum and fiberglas in a rectangular form, and
fitted with 12 ball bearings 3. The ball bearings 3 are supported
by 12 small shafts 4, with the bearings revolving in the slots 5.
The machine screws 6 join the plates of the power block together.
The power blocks 2 are provided with sealing grooves 7, into which
the sealing strips 8 are closely fitted. The sealing 8 are
half-lapped at the ends so that a continuous perimeter sealing is
maintained.
The wrist pins 9 connect the power blocks 2 with the connecting
rods 10. The crankshaft assembly 11 is built up of several shaft
sections 11a and multiple counterbalance discs 12 with the
crankpins 13 connecting each pair of counterbalance discs 12. The
crankend of each connecting rod 10 is connected to the crankpin 13
which revolves in the roller bearing 14. The crankshaft assembly 11
is thereby made up of shaft sections 11a, counterbalance discs 12
and crankpins 13, to form a continuous integral unit. The built-up
construction allows the placement of roller bearings 14 on the
crankpins before the bearing caps 10a of the connecting rods 10 are
clamped into place.
The crankshaft assembly is supported within the engine housing by
the bearings 15 and sealed where it exits the housing 1, by the
labyrinth disc seal 16, housing.
The displacer stage housings 18 are constructed in rectangular form
and sealed pressure tight. The displacer housings 18 are mounted
coaxially in line with the power stage housings 1. The assembled
power stage housings 1 and the displacer stage housings 18 are a
unit engine module, with four or more modules assembled to form the
complete in-line uniflow engine. The displacer stage housings 18
are secured to the power stage housings 1 with the screws 19.
The displacer block 20 is built up of aluminum and fiberglass sheet
and fitted with 12 ball bearings 3. The ball bearings 3 are
supported by 12 small shafts 4, with the bearings free to, revolve
within the slots 21. The machine screws 6 join the plates of the
displacer block 20 together. Multiple uniflow regenerator bores 23
are uniformly located through the displacer block 20, parallel to
the axis of motion.
The multiple regenerator bores 23, are evenly divided between hot
and cold bores with the conical baffle assemblies 24 place
uniformly within each bore 22 and 23. The conical baffle assemblies
24 within the hot bores 22 are placed with the apex of each cone
pointing toward the hot displacer volume, and the baffles 24 within
the cold bores 23 placed with the apex of each cone pointing toward
the cold displacer volume. The cold bores 23 are arrayed around the
periphery of the displacer block 20, and the hot bores 22 arrayed
on and near the center of the displacer block to provide the
uniflow gas flow loop. The displacer block 20 is also provided with
multiple clearance bores 25, which provide operating clearance over
the multiple conduction rods 26. Some of the hot conduction rods
26a are fitted with electric heating rods 26b, with the electrical
leads 26c connected to a controlled power source 26d.
A horizontal drive slot 27 is located at midlength of the displacer
block 20 side into which the drive ball bearing 28, of the
crankdisc 29 closely fits.
The crankdiscs 29 are secured to the displacer drive shafts 30 and
supported by the bearings 31. Chain sprockets 32 are secured to the
displacer drive shafts 30 between the bearings 31. Identical
sprockets 32 are secured to each of the shaft sections 11a, with
the sprocket chains 33 provided to couple the two operating
stages.
Keying the cycle
The piston sets must be phased in each module, so that the
displacer blocks 20 lead the power blocks 2 by one-half stroke or
approximately 90.degree. shaft position.
Drive section plate assemblies 34, are secured and sealed to both
the power stage housings 1, and the displacer stage housings 18,
which seal the sprocket and chain drive. The drive section
assemblies 34, provide bearing support for the crank shaft assembly
11 and the displacer drive shafts 30.
The multidisc shaft seal assembly 35 is made up of stator discs 36
and spacers 38, with the rotor discs 37 sealed to the shaft. The
rotor discs 37 are provided with airflow vanes 37a to aid in the
retention of the internal working gas during operation. The stator
discs 36 are sealed to the disc housing, 16.
The cooling system for the engine consists of a liquid coolant
jacket 39, secured to the cold side of the displacer housings 18,
with a maximum of engine surface area in contact with the coolant
jacket 39. Inlet tubes 40 and outlet tubes 41 connected to the
coolant jacket 39, circulate the coolant to the radiators 42. The
coolant pumps 43 provide the circulation means for the coolant
through the cooling system. The pump 43 would be engine driven as
is the usual engine practice.
The heating system would normally consist of an oil or propane
burner 51 as is the usual arrangement for Stirling cycle
engines.
The auxiliary heating system would consist of fraction drums 44,
revolving against replaceable heat transfer plates 45, which are in
direct contact with the hot sides of the displacer housings 18. The
friction drums 44 would be driven by an electric motor 46 and
battery assembly 47. A gear reduction unit 48 would be provided
between the electric motor 46 and the friction drums 44. The heat
transfer plates 45 must be pivoted on the pins 49 and spring-loaded
against the friction drums 44 by the springs 50. A transfer bracket
52 secures the pins 49 to the side of the displacer housings 18. A
bracket 53, mounts the friction drums to the side of displacer
housings 18.
* * * * *