JPH0345201B2 - - Google Patents

Description

[Detailed description of the invention]

There are generally two types of devices used to do work or have work done by compression or expansion of gases. Two of these common types of devices are positive displacement devices and turbines.
Positive displacement devices include a variety of mechanically driven or driven piston or vane type rotors. A constant volume of gas is conveyed at a relatively low velocity from one volume to different volumes, which may be larger or smaller depending on the function of the compressor or engine. In another type of device, a turbine, the flow of gas past the blades occurs at approximately the speed of sound of the gas. It is well known to those who design such devices that turbines can be made more efficient than positive displacement devices. The reason for this difference in efficiency has often been unclear. With this fundamental knowledge of inefficiency, it would be possible to design positive displacement devices in such a way that inefficiencies or losses are reduced by important factors to a minimum value. Of course, it is well recognized that friction between the displacement member, piston or vane and the walls of the chamber causes additional energy losses in positive displacement devices. Although turbines avoid this inefficiency, they are subject to aerodynamic flow friction and other effects at near-sonic speeds. Heat Exchange and Total Energy Losses Frictional losses between sliding parts are important, but are usually not the major energy losses in a system. However, let us note one property of positive displacement devices that is not well understood and creates a major inefficiency.
This is a heat exchange between the compressed or expanded gas and the displacement wall. This heat exchange is usually accepted as fundamental. However, this heat exchange can be greatly reduced. Heat Exchange with the Wall Although these explanations can be equally applied to expansion engines with the terminology reversed, consider first the compressor. When a gas is compressed adiabatically, it becomes hotter as a result of the compression as well as the increase in pressure. The increase in temperature and pressure follows the well-known relationship of the adiabatic law. In some cases, as in air compressors, the additional temperature created in the gas is later dismissed as a nuisance. However, a significant portion, a major portion, of useful work is wasted in rejecting this heat. In the particular case of air compressors where this heat is rejected, it is more efficient to reject this heat as early as possible in the cycle so that less work is done to achieve the desired volume of cold compressed gas. be. (Isothermal devices are the subject of a concurrently filed patent application of the present applicant entitled “Isothermal Displacement Devices.”) Compressors are used, as in Rankine cycle heat pumps or compression cycles of various internal combustion engines. In other cases, the departure from adiabatic compression due to heat exchange of the working fluid or gas with the walls of the compressor is a major disadvantage and inefficiency of the system. The point of the invention is that by appropriate design of the input and output ports of the insulated positive displacement device this heat exchange can be reduced to small values. The mechanism for this heat loss is the turbulent movement of the working fluid in contact with the walls during compression or expansion and contraction. This heat exchange consists of two parts. (1) heat exchange between the gas and the wall if the wall is held isothermal; and (2)
This is the thermal impedance of the wall itself. It is clear that the thermal impedance of the wall is such that in the lag phase of the process the wall acts as a lag averaging reservoir with a temperature equal to the average temperature of the gas.
Both phase lag as well as magnitude of heat exchange are detrimental to adiabatic efficiency. Heat Penetration Thickness By calculating the heat penetration thickness during the thermal contact time, the thermal mass of the wall during temporary contact with the gas can be calculated. The thermal penetration thickness d of heat (or cold) penetration within a given time t is expressed mathematically as d=[(K/Cv)t] ^1/2 . Here, C _v is the specific heat of the wall material, K is the thermal conductivity, and t is the time. (K/ _Cv )
is often called the diffusion coefficient. For a typical material with a C _v of 1 calcm ^-3 deg ^-1 and a time of 10 ^-2 sec or longer (for a process at 3000 RMP), the penetration thickness is K = 10 ^-3 calcm at maximum speed. ^-3 deg ^-1 varies between 3 x 10 ^-3 cm for plastic and 3 x 10 ^-2 cm for metal and large slow pistons. Even the smallest penetration thickness has a heat mass equivalent to a few centimeters of air or Freon at atmospheric pressure.
mass). The heat mass of the wall in contact with the gas is therefore comparable to or even greater than the heat mass of the gas. It is common in engineering practice to ignore this penetration thickness factor and assume that the wall experiences a temperature that is the time average of the heat flow from the gas. The main factor in determining the heat loss in this case is the theoretical heat exchange between the virtual isothermal wall and the gas, which has little influence on the wall properties. Later, we will show the importance of time-dependent phase lag in heat flow.
First, we will show the effect of penetration thickness. Assume that the walls of the chamber are smooth and that heat loss is then dominated by turbulent exchange with the smooth walls. Description of Diffusive Heat Flow FIG. 1 shows the classical explanation of the diffusion of heat from the reservoir 1 of FIG. 1 to the second reservoir 2. 1st
The reservoir 1 is hotter at T ₁ and is a turbulent gas with an essentially unlimited ability to transfer heat to the barrier 3. Heat diffuses into and out of region 2 with a diffusivity K/C _v . The distribution of heat at temperature T as a function of depth X then follows a series of "error function" solutions below. T=T ₂ + (T ₁ −T ₂ )exp(−X ² /d ² ) or T=T ₂ +(T ₁ −T ₂ )e(−X ² /d ² )where d= as mentioned above. [(K/C _v )t].
The distance d is the center of the depth of penetration of the heat wave. _d1 ,
The three curves labeled d ₂ , d ₃ are temperature contours at times t ₁ , t ₂ , t ₃ , where the penetration depth d ₁ is less than d ₂ and d ₂ is less than d ₃ . as in a cylinder with alternating hot or cold gases
If T ₁ is time dependent, the actual temperature distribution should be a simple addition of such a solution. In this sense, “cold” or T ₁ is
Smaller than T ₂ , can penetrate into walls,
T ₁ , which is also hotter, is greater than T ₂ . The penetration depth is the average depth of each temperature change at time t.
The heat mass explained by each curve is H=
(T ₁ −T ₂ )C _v , thus the longer heat is absorbed, the more heat is transferred. Typical diffusivity and penetration depth heat masses are shown in Table 1 for various materials. A frequency of 3000 RPM is chosen as an example and the penetration depth heat mass is compared to the 8:1 compressed combustion gas of an Otto cycle engine.

【table】 Heat capacity of compressed air with 8 times more fuel =
5×10^-3calcm^-3 Turbulent heat exchange with smooth surfaces If a gas flows through a pipe with smooth walls
Then, the characteristics of turbulent fluid heat exchange are that the gas is about 50%
Diameter (American Physics Handbook, 1963)
such that it reaches thermal equilibrium with the wall after moving
be. This is also the same sticky slow length.
Yes, or at a length where kinetic energy is wasted.
be. The amount of “50 pipe diameter” is laminar flow low layer
Determined by special characteristics of (Iaminar sud−layer)
determined. This is a combination of turbulent fluid flow and smooth pie
This is the boundary layer between the wall and the wall. cylinder or other
In the case of a compressed volume of , a suitable requirement is the stroke
The fluid (or gas) moves in contact with the wall for a period of time.
This is the distance. high velocity of the gas relative to the chamber
If the gas enters through the valve, it will be compressed or expanded.
is circulated many times in the compression chamber during the expansion stroke.
circle. The number of cycles of circulation is the speed of the piston
The ratio of the velocity of gas entering through the input valve to
It can be roughly estimated by piston surface
The average ratio of valve area to product is about 20:1 (Taylor
(1966), and the gas entering the cylinder is
The speed is 10 to 20 times the ton speed. in general,
The turbulence created by the flow is transferred through the pipe.
caused by normal pipe flow of a moving fluid
The gas is compressed relative to the volume so that it is greater than the turbulence.
and invade the chamber in a non-contrastive manner. Therefore the wall
The heat exchange becomes larger when the turbulence becomes larger.
Will. A straight pipe with gas flowing through the corner
It is disturbed by the flow, so a circulation of about 10 degrees will increase the flow by about e times.
heat exchange is expected. therefore entrance was restricted
A typical piston with a valve can either compress or expand.
Approximately half the wall of the differential heat of the gas during the time of the boiling stroke
and gas to enable heat exchange. wall against gas
Since the differential temperature difference is approximately 1/2 of the total temperature difference, the heat
Roughly 1/4 is lost to the wall. Such gas handling
This large amount is a major source of inefficiency in modern equipment.
This is a good heat exchange. The only way to avoid this heat loss is
The method involves forcing the gas into the compressed volume at low velocity.
The goal is to be able to do this. The gas is stroking
The distance traveled during the arc (measured in diameter) is small.
heat exchange is small. The fluid velocity of the invading gas is
If equal to the velocity of tons or other compressed members
For example, it is a weakly turbulent boundary layer, that is, an incompletely laminar flow.
Perhaps an alternative to small turbulence is expected. turbulence
A state where almost no flow exists is called a flow close to laminar flow.
Make it. Thus the critical design is the compression or expansion sensor.
Creates a nearly laminar flow in the input gas for the cycle.
It is to give out. The flow is close to laminar at the piston speed.
If the flow is large, the inlet port area should be the entire piston.
must be close to the area of the tunnel. Similarly bloated
In a bulging engine, the inlet port is equal to the piston area.
I have to go. This also applies to rotating vane equipment.
Applies to the location. Non-reduction due to wall-to-gas heat exchange in an adiabatic cycle
efficiency Intermediate temperature T during the post-compression stage₂isothermally held at
If instead of full adiabatic compression, the maximum
Initial temperature T₁The final temperature of the gas at is T₃It will be
Assume that the data is compressed as follows. T₁is T₂smaller,
T₂is T₃smaller. gas after leaving the piston
The thermal energy of is the ratio T₂/T₃smaller than by
stomach. (The mass of the gas is retained.) Therefore, the inefficiency factor
Heat loss is the heat present in the gas (T₃−
T₁) divided by the difference (T₃−T₂).
Depends on the cooling of the cylinder walls and other factors
T₂is T₁and T₃is only half of the
The efficiency is 50% when the position is accompanied by adiabatic compression. the wall
The temperature reached T₂is a combination of heat exchange process and wall cooling.
It becomes a complicated function. In general, gas is
There is no equilibrium at all points, and this heat loss
Approaching loss actually occurs. However, theoretical
It is said that up to 50% of the maximum heat can be exchanged.
The fact that simple calculations show that this heat
Equipment to avoid short circuits and associated loss of efficiency.
This is sufficient reason to design a new location. wall is at temperature T₂on the wall if maintained isothermally at
This heat loss to the refrigeration cycle or
is actually used in compressors such as ordinary air compressors.
will be of benefit. However, against the wall
Gas heat exchange is more complex. If you care
the body losing heat to the walls during part of the cycle
If the wall is hotter than the gas, then the gas is
heat from the walls during other parts of the cycle.
I can do it. The wall is temporarily exposed to air due to the penetration thickness effect.
Hotter than my body. This method of heating gas from the wall
The penetration thickness effect is that when the wall is hotter than the inlet gas, the gas
heating occurs in the introduction section, so the efficiency of the compressor is
Particularly harmful. Then the gas is an ideal insulator.
It is compressed at higher heat than the cycle, thus doing more work.
than would be required for an idealized cycle.
required. Thus heat is exchanged by a harmful phase lag.
will be replaced. Figure 2 shows a
These ideal cycles are shown below. The gas has a constant pressure P₀along the temperature T₀Deji
Volume V during the complete introduction stroke₀up to cylinder
is absorbed into the. In an ideal cycle, pure
Volume V along the neat adiabatic curve 1₀Start compression with
Volume V₁and temperature T₁The final reservoir pressure at
P₁reach. heating the gas by the wall
There are several possibilities. (1) Only during the introduction the gas is affected by +Tdiff.
The pressure-volume relationship is the same if the
It remains the same. In other words, the gas is compressed by assumption
Heated by the entrance wall rather than between the
, the compression is adiabatic and therefore the same state V₁,
P₁However, at high temperatures T=
(Tdiff＋T₀)/T₀×T₁It is. After excessive heat
, thus releasing the same mass of gas
requires more work. (2) After the start of compression, heat can be added and air
The body follows steep curve 2 due to the purely adiabatic curve.
cormorant. Then the temperature of the gas will exceed the temperature of the wall.
The curve becomes curved, returning heat from the gas to the wall.
Bend over curve 3, which has a slope smaller than adiabatic curve 1.
Garu. The required work will become even greater. rhinoceros
The wall cooling of the compressed gas at the end of the cell creates an adiabatic field.
V at₁T in₁V below_Fourfinal energy in
Body temperature T_FourAt the point where the curve actually decreases
4 is more realistic, but the net work is in the adiabatic field.
exceed the limit. (3) The wall is completely cooled and the temperature T₀to hold in
, the gas can completely exchange heat with the wall
and then the compression is equal along curve 5
It's warm. This is the final temperature T_Five=T₀Nii
Minimum work cycle to obtain cold gas
It is le. (1) From the outside to the inside on a temporary foundation
(2) turbulent heat exchange
Partially in normal cylinders and pistons
Since it's only valid for
cannot be achieved. Heat loss and adiabatic cycle summary Heat exchange occurs due to the turbulent flow of the introduced gas.
Maximum gas mass or minimum temperature T₀If the wall
temperature T₀or the introduced gas is maintained in a laminar flow.
If the flow is close to
It will be done. The same argument applies during compression. death
However, the discussion of thermal penetration thickness is
If it is thicker than the outside, the heat flow will be averaged on the outside.
but on the inside it heats and cools alternately in thin layers.
He says he will want to do so. If the gas is turbulent
If this alternating hot and cold heat pool
This will cause heating of the incoming air at the worst possible time.
the compressed gas to a hotter temperature T₃before reaching
Recorded temperature T₃, the higher average temperature of the walls transports heat
heating the gas even further until it is allowed to leave,
Requires more work etc. this is inefficient
It is a compressor. Compression as well as layers reduce turbulence
By having a flow introduction close to the flow,
It is even better to reduce the heat exchange between the body and the wall.
stomach. Temporary due to partial turbulence and thermal penetration thickness
Heat exchange is detrimental to all positive displacement devices. Yes
As a practical measurement, Taylor (1966) found that approximately 30%
Blaming the efficiency loss on heat loss within the gasoline engine
Heat loss in the diesel engine causes a loss of efficiency of 50%
blame the loss. In other words, gasoline engines are 30%
can be 45% efficient instead of
Zell engines will be at 70% rather than 35% to 40%.
I can do it. These are great advances and therefore
Justifies some degree of complexity to achieve them
become thin layer heat exchange If we assume that the volume has corners, then the fluid
Don't exchange heat with the wall in something like 10 diameter motion.
If the velocity of the incoming fluid is
of other moving boundaries of restricted volume (e.g. rotating vanes)
that the speed cannot be much greater than
means. These speeds in a typical device are
The speed of sound in the gas is usually less than 1/10, so the inlet port
The differential pressure at the point is only about 1% of the gas pressure.
It means that. This means that the piston port
It must be designed with an area roughly equal to the area of
It means something. Gas pressure like a reed valve
A valve that opens by
tens of inlet gases to reach large heat exchange losses.
inevitably cause high speeds in minutes, but
A tube-type intake valve works well. On the other hand, the exhaust port
It doesn't have to be that big; in fact, a reed-operated valve can
Something can happen. Because it leaves the cylinder
The gas creates a turbulent flow inside the cylinder during the exit process.
It doesn't start. As a result, the strip exposing sidewall area
Only with the relative complexity of a leaved inlet valve
It is possible to create a piston compressor with laminar flow ports.
It is Noh. This area is the total area of the cylinder head.
, but the substantial reduction in heat loss is
Layers with small introduction ports, e.g. cylinder head area
It brings about one-half of On the other hand, vane-type devices have vanes located outside the compressed volume.
If it does not rest on the wall, the inlet port area will be compressed.
It seems that the area is as large as the total cross-sectional area of the expanded volume.
can be designed. otherwise inlet port
is to support the vane as it passes
unless somewhat restricted by the strings required for
No. Therefore, the inlet is approximately equal to the total cross-sectional area of the compressed volume.
The gas at the inlet has the same velocity as the moving boundary of the restricted volume.
special precautions are taken to ensure that the
A specially designed ported engine is provided.
In this mode the gas flow during compression and expansion
A thin layer close to the inside of a medium-restricted volume, reducing heat loss to the wall
Loss is greatly reduced. In many heat engines,
This translates to improvements in fuel efficiency by up to two factors.
make good possible. laminar and turbulent flow Turbulence refers to fluid flow when two conditions match.
It is drawn out. (1) Kinetic energy of average flow range
Less sticky waste or flowing putter
Reynolds number is large. (2) The slope of the velocity distribution is
not constant, i.e. the distance perpendicular to the average flow
the first derivative of velocity as a function of separation.
There are limited derivatives. Therefore uniform variations within the flow
The shape is not enough to initiate turbulence. During actual turbulent flow, fluid flow in contact with a hard surface
promote friction (and heat transfer). Smooth
Because it enters the fluid from a solid surface, it comes very close to the wall.
In the flow, fluid friction caused by viscosity causes turbulent friction.
The dimensions are small so that it is larger than the scraping, so it is a thin layer.
Become. Reynolds number greater than 100 (perpendicular to the wall)
at a critical distance into the flow (measured at
So, first there is only room for a small vortex, so
A small vortex forms and then moves further into the fluid.
As the flow progresses, it gradually becomes a larger vortex and the flow becomes turbulent.
Ru. The size of the vortex as it moves from the surface into the fluid.
The length is called "logarithmic change." For example, an airplane
Turbulent contours further downstream along the wing
extends further into the fluid. This to smooth surface
The penetration depth is small, about 1/10 to 1/20 of the downstream distance.
It is a part. Thus the flow is everywhere in the fluid
can travel relatively long distances before causing turbulence.
Ru. This is because small vortices close to the wall are inside the fluid.
This is to create an even larger vortex. other
If the wall is very rough with large protrusions
The turbulence is caused very quickly and the roughness
In other words, a vortex is formed immediately due to the size of the protrusion.
Ru. Airplane wings have a ratio between 10:1 and 20:1.
Smooth so that the ratio of buoyancy to drag is achieved.
The spoiler (protruding vertically)
If you use a flap that
The turbulence is large and the ratio of buoyancy to drag is 2:1.
Or it will be 3:1. On the other hand, if the flow is completely laminar
If so, a buoyancy to drag ratio of 100 or more is possible.
It is Noh. Thus, on a relative scale, weak disturbances
A smooth wall with a flow boundary layer is prevented by a spoiler.
In order to counter the severe turbulence that occurs when
It is as if the drag characteristics were a “layer-like flow”.
It works like this. In the case of rotational flow in a cylinder, the flow
contact with a smooth wall that does not have a
The flow is close to laminar flow. Azimuthal
vortex) is a flow diverted by a sharp corner
, and thus the flow will be more turbulent. this
However, even though the azimuthal vortex is sufficiently turbulent, the axial
The reason why linear vortices are called “near laminar flow”
It is. Finally, the slope of radius and velocity is constant
Therefore (state 2), the radial action and
The deformation of the velocity distribution as follows does not cause turbulence. wall
Only contact with or friction causes turbulence.
This discussion of near-laminar flow along a smooth surface
, the flow immediately upstream from the surface is itself a layer.
It is a flow close to the flow, and from the speed along the problem surface
be of velocity and direction that are not significantly different.
Ru. General description of insulated positive displacement devices According to the invention, a positive displacement device (piston cylinder
and vane compressor, expander) efficiency is
It provides a near laminar flow of gas into the chamber and
Heat flow to and from the walls of the chamber through
shape and size that substantially reduces
through an inlet passageway (or several inlet passageways) with
to introduce gas into the compression or expansion chamber.
Substantial improvements can be made by adding fixie
In the case of a piston-cylinder device, approximately 1/1/2 of the area of the piston
an inlet passageway having an area approximately equal to from 2 to 2;
Preferably a three-way tube extending 360 degrees around the cylinder.
Inlet port opened and closed by valve
Due to the passage that opens at
achieved. The passage is the tangential velocity of the cylinder
Introducing gas into the cylinder by a substantial component of
, thereby creating an axial vortex flow.
and radial vortex formation and high turbulence, heat exchange
A plenum chamber arranged to prohibit
There should be two or more spirals. Be
In the case of installations, both the inlet and outlet passages
Both have a speed substantially compatible with the speed of the rotor vanes.
A near laminar flow is maintained at a certain degree, thereby
between the gas and the rotor vane and the equipment casing wall
cross-sectional area along its length such that it reduces the heat flow of
have. Preferably the casing of the vane device
wall to reduce heat flow within the wall and prevent wall thermal short circuits.
From materials with low thermal conductivity to minimize
able to make. 4 Stroke Otto-Cycle Engine The inlet passage is at the top of the cylinder like a plenum chamber.
It extends 360 degrees around the
operated by a musshaft or crankshaft
It is opened and closed by a sleeve valve. The fuel is
collected for combustion in an area spaced from the cylinder wall.
Introduced into the cylinder along the axis so that the
It will be done. The plenum chamber has an axial vortex within the chamber.
oriented diagonally to the tangential direction to create a flow.
It has hollowed out vanes. The axial vortex flow is
Oxygen-filled air helps support the combustion of fuel.
Remove unused fuel outward from the axis where possible.
Accelerate combustion by centrifuging the droplets.
Ru. 2 Stroke diesel engine This engine has compression ratios within the following ranges:
Supercharging piston-cylinder, combustion piston
- cylinder and exhaust piston-cylinder
have Supercharging - 3:1 to 8:1, Compression - 3:1
4:1, exhaust - 6:1 to 9:1. the air is good
Preferably through a 360 degree inlet port at the top.
is introduced into the supercharging cylinder and the inlet port is introduced into the supercharging cylinder.
The port is opened and closed by a sleeve valve, and is connected to the plenum chamber.
or receiving air from the vortex, said plenum chamber or
Vorticity creates axial vortices and laminar flow within the cylinder
velocity component in the circumferential direction to form a flow close to
give rise to The supercharged air is stored in an isolated storage channel.
The chamber is guided by a semi-stationary moving and combustion chamber.
Retains air for cleaning of baking cylinder. Savings
The volume of the storage chamber is the displacement volume of the combustion cylinder.
should be within the range of about 1 to 6 times. Burning
The firing cylinder is located at the bottom of the piston stroke.
The filter has a 360 degree inlet port, and the inlet port
receives supercharged air from the storage chamber from the vortex.
The swirl is axially located within the combustion cylinder.
Causes a vortex flow. Preferably the highest compression odor
Therefore, the radius and stroke of the combustion cylinder are
Large clearance volume to minimize losses
is approximately equal to providing combustion silicate
The head of the cylinder is smooth and the exhaust valve is
substantially coaxial with the axis. axial vortex flow
virtually unimpeded and the air is depleted of oxygen.
Combustion is carried out by centrifugation of fuel droplets in areas where there is no
As the fuel is promoted, the fuel is substantially removed from the fuel cylinder
is injected along the axis of the from the combustion cylinder
The opening of the exhaust valve is located between the axis of the cylinder and its wall.
located midway between the
provide For coaxial tubular exhaust valves, the combustion series
The head of the valve is cooled and high for valve cooling.
Provide heat conduction. Exhaust gas is inside the exhaust cylinder
A vortex that produces a vortex flow close to laminar flow in the axial direction.
Through an insulated passageway with smooth walls leading to
It is guided from the combustion cylinder to the exhaust cylinder.
The exhaust valve of the exhaust cylinder is a sleeve valve.
Located at 1/2 of the diameter, approximately the radius of the cylinder
It has a width equal to 1/2. gas compressor Air is supplied to the cylinder, which is opened and closed by a sleeve valve.
The 360° introduction port at the top of the
A plate having vanes oblique to the radial direction through the plate.
It is guided from the num chamber into the cylinder. introduced sky
Air flows in a series due to the generation of vortex flow in the axial direction, which is close to laminar flow.
exchanges only a small amount of heat with the interior wall. Articulated vane compressor or expander Introduction leading to and from the compression-expansion region, respectively.
Both the passage and discharge passage are connected to the rotor vane.
Near laminar flow at velocities that are substantially equal to
with a cross-sectional area such that flow is maintained within the passage
There is. Highly efficient Brayton cycle heat pump
The pump is a suitably sized articulated model embodying the invention.
It uses a vane device. housing and
Yaft fittings are isolated to minimize thermal short circuits
Should. turbulent flow for combustion For exhausting combustion gas in internal combustion engines
In particular, in the case of gasoline engines, internal combustion gas
and the fuel-air mixture near the cold wall.
to provide thorough mixing and promote complete combustion.
turbulence is very often deliberately induced
We should recognize that. These requirements are clear
This contradicts the near-laminar flow. On the other hand, diesel engines and Otto cycle machines
Reliable control of gas movement at both the wall and
The contacting cooled boundary layer contains only a small amount of fuel.
The device should not be leaky, i.e. very leaky.
Easel engine and fuel-injected Otto cycle
Possibility of designing a fuel injection system for the engine
I will provide a. Then the combustion area is cooled on the outside
The center and height of the hot piston are isolated from the inner wall and
exposed only to the head. Reduced unforeseen fuel problems
Do a little. compression and expansion Also the average temperature of the gas during compression and expansion
There is an additional contradiction: the large difference between pressure
The temperature of the gas during contraction is the same as the temperature during expansion due to combustion.
Very small than the degree, so the hot air during expansion
Heat loss from the body results in a higher average temperature than in the case of compression.
tends to heat up the walls. Thus compression is adiabatic
Hotter than compression and requires more energy than necessary
shall be. Some of this energy goes into the expansion
recovered in time, but the net effect is inefficient.
Ru. Efficiency to separate compression equipment from expansion equipment
This means that there is a clear benefit from the standpoint of
It's for a reason. This is the case in gas turbines.
After the blades of the expansion turbine burn
must be at equilibrium temperature with the highest temperature gas at
Due to the high required speed of the blade
Stress severely limits the peak temperature and thus
Limit no efficiency. Due to turbulent heat exchange between the wall and the gas
limiting the temperature of the blades or turbine blades;
Current devices are limited by: heat pump Layer in Brayton cycle heat pump
Special benefits of near-flow compressors and expanders
exist. There are three common types of heat pumps:
Ru. (1) Regarding the applicant's patent application filed at the same time.
The isothermal cycle or standstill described in
- ring cycle. (2) compressed like a gas,
A special refrigerant that supplies heat inside the capacitor and becomes a liquid.
Rankine cycle using. The liquid is heated
The gas is then expanded to a cold heat exchanger.
(3) Gas is compressed adiabatically and heat is extracted into the heat exchanger.
The remaining energy is then transferred to a thermal expansion engine.
Finally, the heat is transferred to a second or cold exchanger.
Brayton cycle added to exhaust gas in exchanger
Le. Expanding orifice in Rankine cycle
The energy (pressure x
The volume of fluid) is wasted, but the relatively high volume of fluid
Because the volume is small due to density, this wasted energy is
Energy is small. On the other hand, limitations on the properties of refrigerants are
Degree ratios cover useful extremes encountered in average climates
Relatively large compression ratio so that it is large enough to
requires that it be used. An example is the compression cycle.
For example, when included at 80% efficiency, the result is approximately 2 to
This results in an average “coefficient of operation” (COP) of 2.5. ideal
COP is T₃/(T₃−T₂). thus typical
For a temperature difference of 30℃ and an absolute temperature of 300〓, the theoretical
The maximum COP of 2.0 should be 10.
It should not be a relatively small value. this big
To get closer to the value, avoid freezing agent limitations and
It is also necessary to use a more efficient compressor.
It is said that If you don't use a Brayton cycle
If so, an expansion engine must be added, and this expansion
Institutional efficiency is critical. In a cycle like this
The compressor produces work (T₃−T₂) × (gas uni
(thermal mass), and then the heat exchanger
The total amount of heat extracted in the converter is this same value.
(T₃−T₂). This unit thermal mass of gas
is the ratio Vol₂-Vol₃=T₂/T₃Vol.₃From Vol.₂to
The volume decreases to . Smaller Vol₂is atmospheric pressure
In other words, when expanding to the same pressure ratio, almost the same
temperature difference (T₃/T₂), but the capacity is
product becomes smaller and thus the work done within the institution becomes smaller.
The thing is ratio Vol.₂/Vol₃=T₂/T₃to the compressor.
less than the work done. If this job is compressed
If supplied to the machine, it must be supplied from outside.
The net work that must be done is 1-(T₂/T₃)=(T₃
−T₂)/T₃or the opposite of the theoretical maximum COP.
In this COP10, the expander is made by a compressor.
90% of the work done by
Must be 10 times the supplied force, i.e. structural force = 10%
means. Thus compression engine and expansion engine
Both waste 5% of energy each,
That is, if the efficiency of each is 95%, the external source
additional loss energy must be supplied
double the energy that must be supplied.
Ru. Each engine has an efficiency of 95% rather than 100%
%, the theoretical maximum value of COP is 10 to 5.
or the loss in efficiency of the factor is 2. Heat pump equipment is used for compression engines and expansion engines.
It is understood how sensitive it is to efficiency. mosquito
Brayton cycle heat pump equipment
The main motivation is to achieve as high efficiency as possible.
It will be done. A loss of 10 percent is significant in an internal combustion engine.
There is no loss in efficiency for a given turbulent heat exchange rate.
The temperature difference is very large so that the loss is very large.
Hey. The resulting efficiency loss is significant.
It's big enough. Therefore, the flow is almost laminar.
less than the displacement velocity of the moving chamber boundary.
or comparable residual circulation or
Volume type where gas is guided into the displaced volume by vortex velocity
Equipment - compressors, thermal expansion engines, internal combustion engines and
Toponpu is provided. Description of exemplary embodiments One embodiment of the invention is the articulated type shown in FIG.
A vane air pump or expansion engine. joint
A vane air pump adds compressed air to the exhaust stream.
In addition, in order to reduce the amount of gas, automobile engines
Widely used in connection with for heat pump
Articulated Vane Compressor or Expander (AVC)
There are special benefits for using
This is due to the very low friction of moving parts;
Riding on a fairly large outer race
On the other hand, the vane is mounted on the bearing of the center shaft.
This is because that. A considerable amount of patent literature exists for automobiles.
Exists for articulated vane pumps such as divergence control
However, this prior art does not improve the efficiency of adiabatic compression.
Not directed. Selected key technologies
References to these references appear at the end of this specification.
There is. It has an inlet chamber 61 and an outlet chamber 62.
A set of vanes inside the housing 72
63, 64, 65 are fixed by a rotating drum 67.
It is rotated about a fixed axis 66. vane drum
, radius through seals 68, 69, 70
Concentric housing that slides in the direction and in the compression area
With the clearance 71 as well as the clearance 72,
Separate the inlet chamber 61 from the outlet chamber 62
It is sealed by a web. vane
and the compression housing 72 and the drum 67.
The clearance 71 between the web 73 and the gas
Must be kept small to prevent leakage
However, contact must still be prevented. because
If the surface is not lubricated, it should be
for they are stripped naked. Prior art connoisseur
In its usual form, the AVC entrance chamber and
The exit chamber can be of relatively arbitrary shape.
Ru. In relatively large chamber situations,
Air flow at the mouth and outlet is controlled by vanes 63,6
It is relatively fixed compared to the movement of 4.65.
From this, large turbulent vortices are generated by the vanes.
Ru. At the inlet chamber, these vortices are
The circulation in the compression chamber is controlled by heat exchange with the walls.
resulting in an increase in exchange. Corresponding in the discharge chamber
turbulent vortices cause heat and energy waste.
Ru. In this example and according to the invention:
The inlet chamber and outlet chamber are
is formed to match the rotational speed of the drum 67.
and are dimensioned (dimensions 74 and 75).
Dimensions 74 for the inlet 61 are in the compressed volume
equal to the average vane length, so that drum 6
7 and the given rotation of the vanes is the same as the drum 67.
moving the gas in chamber 61 at the same speed
let In the exit chamber 62, the width 75 is
Three blade pump as described below
divided by the compression ratio 1.336:1 in case
The width of the inlet dimension is 74. Rota vanes 63, 64, 65 are clear run
Vane 65 at outlet 62 when valve 71 is open.
is shown when the compressed volume behind the is released.
Ru. Three vane design with 120° angle between vanes
have a degree. Equal spacing such as 2, 4, 5, etc.
The vane design can be easily made.
The number of blades determines the compression ratio, which is the compression
The block from the position where it starts to the compression position after 60 degrees.
is the volume ratio captured between the rads. three blocks
The composite compression ratio for heat pumps is
The compression ratio is close to the optimum value for
The temperature ratio is 1.336:1, and the temperature ratio is 1.123:1.
That is, Tdiff=37℃, and ideal COP=
The ratio is 8:1. If the compressor and expander are 95%
In terms of efficiency, the actual COP is 4. At an angular distance of 60 degrees from
is compressed to such a pressure that it is released. with chain line
The blade position 76 shown indicates that the inlet volume is just closed.
corresponds to when Each blade at position 76
The gas in contact with eventually moves to position 77.
and comes into contact with the outer wall. In this process, compression
(If the flow reverses due to expansion)
(cools down) and heats the wall. However, the reason
In the hypothetical case, the gas and the wall
, each position corresponds to compression.
Therefore, the temperature will be the same. If the exterior wall material
In the absence of thermal conduction, heat transfer is minimal. this place
In this case, according to the invention, the outer wall is made of stainless steel or
is a sufficiently low conductivity material such as plastic-coated metal.
The walls of the housing are made of materials that provide reverse heat conduction.
It is desirable to reduce the number of lines. However, drum 6
7 and blades 63, 64, 65 are high temperature areas.
It rotates from the low temperature region to the high temperature region, etc. gas
Heat transfer from and to gases has already been discussed
The heat dissipation is due to the penetration thickness. adjacent layers of flow
The degree of gas dissipation can be reduced by
As shown in Figure 4, the temperature drop is
It occurs when Region 1 is temperature T₁The temperature is high at this temperature.
temperature is temperature T₂taller than. Average wall temperature T₃is T₂Yo
Larger T₃larger T₁is the boundary temperature of wall
Temperature drop due to dissipation into the interior (T₃−T₂) is thin
thickness d₂, and this depth is compared to the layer gas
small, where (T₁−T₃) is larger, penetration thickness
Sad₁It is. However, the density of the gas is less than that of the wall.
very small, 3×10^-Fouris the ratio of
The heat lost or exchanged is small.
is smaller than the case in Figure 1, and in this case,
The gas appears to be turbulent, with heat flux to boundary 3.
(flux) is quite large. heat pump Figure 5 shows the Brayton cycle cooling heat pump.
schematically shows the layers shown in FIG.
Utilizes a flow AVC air pump. Compressor 81
compresses and heats the air entering the inlet 83, and
At the port 84 it is evacuated. high temperature compressed air
goes to a standard heat exchanger 85 where it is cooled and
It goes to expander 86, which creates compressor 81.
However, the volumetric flow is small to the ratio (1-1/Rc) = 75%.
stomach. The actual dimensions are the cube root of the ideal compression magnitude.
That is, it is as small as 91%. The applicant is stating his ideal
Ru. This is because the efficiency loss part is due to leakage.
Therefore, the actual volumetric flow ratio is less than 75%.
Sai. Cold air from the expander engine 86 and from the outlet 87
The hot air goes directly to the air gap where it is cooled, for example
Go inside the car where there is cooling air. sleeve valve piston air compressor Standard air pressure
What is usually not very important for compressors is
It was pointed out early on that the heat of compression
is usually rejected before using it, even if it is not efficient.
Because it will be done. This means that pure adiabatic compression
During compression the gas is always cooler than when
It is considered to remain in the. On the other hand, as explained above
As shown in Figure 2, if the compressor
Cylinder walls and heads are not properly cooled.
On average, during compression the gas is
becomes hotter and compresses a given amount of gas.
The amount of work required to do so is greater. If the cylinder wall and head are not sufficiently cooled,
When the curve 2 is lower than the curve 5 in Fig. 2,
and T and P are smaller than in the adiabatic case.
Always less. This is an industrial air compressor stage.
This is similar to what happens with internal coolers between engines. this
requires a further compressor mechanism and a similar argument
is applied to each stage. Therefore, in general
is, unless the cylinder is particularly efficiently cooled.
Reduces heat exchange between any compressor wall and the gas
That is well worth it. In Figure 2
and this is the initial temperature T₀, the edge is on top
This corresponds to the isothermal compression of curve 5. The purpose of the invention is to induce an inlet gas charge
Piste to enter a state similar to laminar flow.
The aim is to reduce heat exchange with the compressor wall. Achieves flow similar to laminar flow in piston compressors
In order to, the area of the inlet port is the axis of the cylinder
Area of the piston, as symmetrical as possible to the line
are created almost equally. gas from the wall to the inner volume
induces a vortex to circulate rapidly into the wall and back against the wall.
No one wants that. The layer-like flow in this relationship is due to the piston speed
There is no air velocity in the cylinder that is sufficiently greater than
means. Therefore, the odor within one stroke
Therefore, the gas is approximately closer to the wall than the stroke length.
Do not move much more than in contact with
stomach. If the wall were smooth, this would be a fragment.
This means that the heat exchange is small. the other smell
The gas exiting through the outlet valve is then
exchange heat with plumbing and piston,
However, this
Plumbing is caused by conduction to the rest part of the cylinder.
Thermal conduction metal with too much heat transferred through
Assume that the condition is not to evangelize through the genus route. Exclusion
All air streams are at the same constant temperature, so
In this case, the exhaust plumbing can be balanced.
Ru. This means that the gas flows in a syringe with layer-like flow.
e.g. have to enter the data volume at low speed.
, but can exit more rapidly and turbulently.
can. Therefore, the suction port
Must be at least 1/2 the area
In both cases, the discharge exit port can be made small. Air operated reed valve or sprue for intake
air compressor using a pumping valve or equivalent
pneumatically actuated valves, air-operated valves are
There is a continuous pressure drop down to a fraction of the pressure
Remains open only when overcoming tension and ellipticity
Therefore, it is almost impossible to obtain laminar flow.
Ru. As a result, the input gas exceeds the slope of the valve lip.
When the gas expands, it travels at a fraction of the speed of sound.
, that is, 1/2 to 1/4 of Cs, is transferred into the cylinder.
move. Generally, this is the maximum speed of the piston
10 to 100 times the turbulence between strokes.
Guarantees high heat transfer. How to avoid this high heat transfer
The method is to install an air conditioner with an inlet at the top of the stroke.
Figures 8a and 8b where the case of Pretusa is shown.
As shown in the figure, the gas is guided around the cylinder wall.
into the cylinder through the large enclosed port area.
That's true. The port area around the cylinder is
area = 2(pi)RL, where R is the series
and L is the length of the port. Pi
The stone area is (pi)R²It is. Therefore, the port
The required port length like area is L=R/2.
be. Stroke is 2R, that is, stroke = straight
Since it is the diameter, next the length of the input port is the stroke.
It is a small fractional value (1/4) of the length, and the piston
ports do not need to overlap. direct inflow
The flow pattern, e.g. radial flow
Shown in Figure 9a. In the embodiment shown in FIGS. 6 and 7b, the piston 9
1 is located inside the cylinder 92 and is standard type (lead type).
standard type, spring-loaded type, butterfly type).
It has a pipe 93 and an exhaust valve 94. slide
The ring or sleeve input valve 95
In fact, it is open 360°, approximately half the radius of the piston.
Close the input port 96 at the minute height. In a suitable manner, together with the piston, the sleeve valve
One way to operate the 95 is to leak compressed gas.
In order to seal it properly and return it to the plenum chamber 100.
Insert the sleeve valve 95 into the small recess in the head 93.
It is to put it in. Plenum room 100 is introduced
Gas or air is guided to input valve 95. plenum room
Vane 101 at the inlet to 100 admits the introduced gas.
I will guide you to Chikaraguchi 96. The valve is connected to the cam 102.
is opened and closed by the swing arm 103.
Rotate the valve 95 slightly. Ricardo (1954)
For gasoline and diesel engines, the sleeve
Demonstrated effective operation of the valve. During World War II
Thousands of British aircraft have sleeve valves.
Seki was manufactured. These valves are rotary as well as axial
Opening the intake and exhaust passages by directional movement,
The mechanical technology of sleeve valves for piston machines is still
exist. However, the introduction and exhaust
Close to laminar flow is not possible due to the port.
This causes turbulence similar to that of an overhead valve, but the valve
The operation is very reliable. As shown in FIG. 7A, the vane 101
is guided from the entrance to the plenum chamber 100, and the cylinder
If 92 points in the radial direction, the flowing gas
produces a large annular vortex. Input port area
If equal to the area of the piston, then the velocity of the vortex
is approximately equal to the piston speed. Simply put, approximately one revolution during each half stroke
and make two complete revolutions between inhalation and compression. high
A gas with a small Reynolds number has a diameter of 50 to 100 times its diameter.
It has to travel a distance and exchange heat with the wall,
It seems to be less in 4 rotations. Unfortunately, simple
There isn't. The vortex is the figure skater's arm while spinning.
Similar to a weight at the end of a string to shorten it.
Ru. The vortices become faster as they are compressed in the compression stroke.
It rotates quickly, and the friction with the wall is sufficiently small. heat transfer
If the d is small and the two are done together, the wall
We must reduce the friction between the radial direction
For a vortex, its velocity increases when it is compressed. vortex
When compressed in one direction, due to conservation of angular momentum,
Increase its speed as follows. V_vprtex=
V₀(S₀/S_nio)^1/2Here S_niois a compressed straw
length, S_pis the maximum stroke length
Ru. Therefore, the compression ratio, i.e., S_p/S_niois big
If it does, the velocity of the vortex increases significantly. In fact, compression
If the ratio is as large as Smin which is smaller than R, then
Next, one vortex is created as shown in Figures 8B and 8C.
The sea urchin splits into small eddies. Figure 8 shows the bottom strike.
Showing a single large annular vortex in Rourke, the 8th
In figure B it is partially compressed and in figure 8C it is completely compressed.
Compressed. The splitting of the single vortex in Figure 8A is
As a ring of four vortices in Figure 8B, as a ring of four vortices in Figure 8C.
Shown as a ring of eight vortices. The compression ratio
Assuming a 4:1 ratio, 100 psi air
It is an industrial air compressor supplying. Then the vortex
The velocity of each small vortex increases by a factor of two at maximum compression.
The size (diameter) of is r/4, and each is 1/8
Make one revolution between strokes. The result is that the vortex
Because it rotates and splits, the speed is almost turbulent.
Ru. As a result, the vortices are removed from the walls (particularly the pistons and cylinders).
heat flow to the head) occurs. Furthermore, if the input gas
This creates turbulence from the beginning, and then this turbulence is compressed.
and then the strength increases to a level similar to that of a 3D energy body.
Add. (A radial vortex is a two-dimensional gas.
act. ) Therefore, the turbulence velocity is (capacity)^-〓increased
In addition, the energy has a G value (comparative heat) of 5/3.
(capacity) for gas^-〓 is proportional to Cylinder
In the heat exchange between the wall and the head, turbulent energy is compressed.
It will increase greatly. The purpose of the present invention is to solve the problem of piston compressor and engine turbulence.
as well as a single large radial vortex heat exchange layer
flow and by introducing weak axial vortices.
It is to reduce the amount. Formation of annular vortices, their compression,
The discussion of aggregation, fragmentation, and dissipation is somewhat speculative.
Ivy, now with Doppler laser tracking and this explanation
Use the elements described to make it true.
There is sufficient evidence from the available measurement methods. Numerical settings
4 above with special emphasis on size and eddy viscosity.
shows two sequences. of an element
The size is larger than the boundary layer of the desired layer and allows circulation.
The lifetime of the vortex is truncated, but the result is consistent with experiment.
give. In addition, the main annular vortices aggregate due to compression and their
Isotope vortices are expected. The dynamics of the input flow is determined by the completeness of the vortex.
The fact that it is the source of everything has been established. S
Experimental measurements of the flow in the cylinder
It is particularly encouraged to observe whether the
Ru. Morse, Uitztrojanski (1979)
uses Doppler laser wind measurement to measure motor
Draw the flow pattern of the piston cylinder assembly
Ta. By Morse et al. (1979, p215)
The observed flow pattern is similar to that of Gosman et al.
This completely confirms the theory. So
Therefore, we believe in the analytical predictions of these trends and
and how to establish them.
Ru. As shown in Figure 7B, it leads to the input port.
The vanes 101 of the plenum chamber 100 are arranged in the radial direction.
has an angle of approximately 60° to 45° with respect to
The input gas or air has a velocity buildup perpendicular to the cylinder wall.
radial and axial vortices are established.
It will be done. Figure 9A shows the input side during half stroke.
A top view and the rotating passage of gas in cylinder 2 are shown.
ing. Figure 9B shows the piston at the bottom of the stroke.
It shows the rotating gas passage. axial vortex
Since its angular momentum does not change, it is the axis
When compressed or expanded in the direction, the velocity changes
do not. However, if the gas injected at radius
pushed axially by the following gas
When the standard vortex relation holds a Rankine-type vortex
However, the vortex curls up, i.e., the center is more concentrated than the periphery.
The vortex rotates faster. Due to conservation of angular momentum
So, V perpendicular direction = V₀(R₀/R), right angle direction
The velocity in the direction increases, where V₀is the radius R₀outside of
R is the velocity in the perpendicular direction of the cylinder wall, and R is a certain
It has a smaller radius. Standard equal to piston area
, and the vane angle is 45°.
then the average perpendicular velocity = V_naxThen, this
Kode V_naxis the maximum velocity of the piston. Radius R
= Ro/2, the rotational speed is less than the ambient speed
Twice as fast. As the gas approaches the axis, its velocity increases
A kind of centrifugal barrier is thus created. It's the atmosphere
In the tortuous flow, why does the vortex have such a stable
It is well known whether it is recognized as a structure. heavy
The key point is that a relatively weak axial vortex creates an annular vortex.
The goal is to prevent them from forming. centrifugal barrier
is a flow that exchanges fluid elements radially.
prevent. The gas, by some friction with the wall,
Losing the angular momentum caused by the centripetal barrier (i.e. angular motion
amount) tends to decrease, therefore making it easier to
You can get closer to the axis. However, the first
Radial motion toward the axis forming the vortex in Figure 8A
is prevented. Instead, it is faster near the axis
It has a rotational speed. Of course, the azimuth speed is the most
A faster head causes more friction, but here the area
is small, so overall heat exchange is low. for example,
If the radius is half, i.e. R=Ro/2
If the orthogonal velocity is 3Vmax, and the area
is the head which is 1/12 of the total area of the cylinder wall
1/4 of the area, and the head for stroke length is
The diameter is So=2Ro. Fast region of axial vortex
area has only slight contact with the wall, and therefore
than the introduction of high-speed isotropic turbulence or large vortices.
Furthermore, heat loss is small. Therefore, the cylinder wall as well as
axially to reduce heat loss on both sides of the head.
The input gas is given a rotational motion that produces a vortex.
Incorporate a pitch into the vane with a laminar flow input valve.
It is desirable to Detailed design of suction axial vortex flow In general, annular or radial flow vortices move convectively.
participate in and must therefore be avoided.
I learned. The main purpose of the axial vortex is to control the radius of the gas flow.
Its purpose is to suppress directional movement. Therefore, Sirin
The gas entering the chamber has as little radial flow as possible.
It is desirable to have an opening of the suction port.
be as large as possible so that the suction port is radial
Absolute speed, whether tangential or
Keep the degree small. Furthermore, the flow through the suction port
has constant velocity in both tangential and radial directions
This is desirable. If the truth were not so,
For example, keeping the radial flow velocity constant and tangential
If the directional velocity is reduced, the angular velocity within the cylinder
The radial gradient of induces axial circulation and the desired
This induces an undesirable annular vortex. The radial speed is (piston speed) x (piston surface
product/port area). piston
The area is constant. Then, speed = frequency ×
Rsin〓; (The projection of the crank arm has a slight sine motion.
); (Piston speed/port area = -
We want a port area proportional to this
established a cam design to open and close the annular suction port
In other words, the opening degree of the suction port is approximately (DR)sin〓
(DR = maximum suction opening degree).
To keep the annular velocity constant during suction, some
Have a choice. 1 The vanes that give radial motion to the suction air are
constant even though the opening degree of the opening changes.
can be configured to give a tangential velocity of
can. 2 Suction air can be drawn from the plenum.
and this plenum has long enough connections within it.
has a secondary vortex that causes the angular momentum of the suction gas to
remains constant during each inhalation period. This second aspect is probably easier. and
This is because secondary vortices are easily created and piston support
This is because it has a long extinction time compared to the cycle.
Ru. For a conservative design example: radial tangential velocity
The radial suction speed is (pi)/2 times the radial suction speed.
Stroke twice the radius, with degrees as the piston speed
Assume that Then, S = Stroke = 2R V_p= piston speed at mid-stroke, i.e.
Maximum speed (crank arm projection)
ignore) t_s= Stroke time = (2R/V_p)(pi)/2=
(pi)R/V_p t_cy= Cycle time (2 cycles) = 2(pi)R/
V_p V_R=V_pThe radial direction of the inlet air is assumed to be equal to
speed V_T=Tangential suction speed=(pi)V_R/2=(pi)
V_p/2 Time for one rotation of intake air = t_T=2(pi)
R/V_T=4R/V_p. Air rotation speed during cycle = t_cy/t_T= [2 (pi)
R/V_p] [4R/V_p]=(pi)/2. Therefore, as discussed earlier, the expected reduction in vortices
Attenuation or resistance is f_d= Number of revolutions/50 = should be 3%
be. The axial length of the plenum chamber surrounding the suction port.
R and radius 2R. Then, the tangential velocity; Plenum room radius 2R_pThe V plenum in V plenum = 1/2V_T= [(pi)/4]V_pbecome,
The rotation time is t plenum = 2 (pi) R plenum / V plenum =
16R/V_pand the play per stroke is
Number of rotations in the num = t_cy/t plenum = (pi)/8. This means that the vortex will move from stroke to stroke.
This means that it does not disappear significantly. I mean,
For blades, the vortex extinction time is 5 to 10 rotations.
It is. The plenum is S(pi)R²=2(pi)R³/ (per cycle)
The cylinder volume is replenished and itself is R[4(pi)
R²]=4(pi)R³Contains volume. Therefore, half of the plenum volume is placed in each cycle.
The vortex in the plenum is changed per filling time.
(pi)/4 rotations. This is also part of the plenum vortex.
sufficient to guarantee constant angular momentum or negligible annihilation.
It's small. The input to the plenum vortex is the average suction
Single or several pieces of sufficient area to match the speed.
Preferably a tangential port. The plenum vortex is
average the loading speed. The average suction speed, i.e. the average piston
Stone speed, = 2V_p/(pi). Tangential direction of plenum
The vortex velocity is half the suction tangential velocity of the cylinder, i.e.
Chi, V plenum = V_T/2=[(pi)/4]V_pbecome. The plenum inlet port area is determined by the following relationship:
determined. (plenum port area) x (plenum tangential speed
degrees) = (piston area) x (average piston speed) Or plenum port area = (pi)R²V_p/V pre
Nam = [8/(pi)]R². The plenum has an R cross section.²Therefore, this is
This means that several ports are required. If
The rational design is four pieces with width R/(pi) and length R.
It is a tangential port. Commercially available air so you can see the flow with smoke
A clear plastic sleeve valve and transparent
An experiment was carried out with a bright plastic head attached.
The angle specified in the above analysis is applied to the plenum inlet vane.
, the movie of the gas motion shows the expected vortices.
vinegar. When the blades are oriented radially, the axial vortices are
more chaotic momentum - turbulence
It was hot. Sleeve valve piston compressor operation During the suction stroke, the air flows through the oblique surrounding vanes
101 into the cylinder, axially circular
Circumferential flow vortices are formed within the plenum 100
(See Figures 6 and 7B). Air from the vortex is sucked
When it is sucked into the cylinder through the injection port 96,
The air forms an approximately laminar axial vortex inside the cylinder.
to be accomplished. The approximately laminar flow and stability of this eddy flow are
Reduces heat transfer from the air to the cylinder wall during engine downtime.
Cheating. The suction sleeve valve 95 starts opening immediately after top dead center.
fully open on half of the downward stroke. Below this
During the downward (suction) stroke, the approximately laminar suction vortex
122. Piston 91 is a straw
Near the end of the cycle, the sleeve valve 95 closes and
As the piston slows down, the
Maintain a constant suction speed. At the end of the stroke, the sleeve valve is closed and
Piston 91 begins to move upward within the cylinder
and compression begins. When compressing a gas, the gas pressure is delivered
This continues until the pressure is exceeded, and the discharge valve 94
opens until it reaches top dead center. In the meantime, the sleeve
The valve begins to descend. Suction port 128 is at top dead center
After that, a small amount of residue within the clearance at the top of the stroke
When the distillate gas expands again to the suction pressure, it opens several degrees.
Ku. Furthermore, during the downward stroke, the suction air undergoes a vortex motion.
Through the sleeve valve suction port from the plenum
It is sucked in. this is the beginning of a new cycle
be. Almost laminar flow of axial vortices and reduced stability
The turbulent flow combines with the cylinder wall, head and piston.
Draws greatly reduced heat transfer to the tank crown.
cause. internal combustion engine “Theory and Practice of Internal Combustion Engines” Charles, F.T.
Iller (1966) or “High-Speed Internal Combustion Engine” Sir, Ha.
Internal combustion, such as by Ri, R., and Ricardo (1953)
A typical reference book on engines is the concept of heat penetration thickness.
The transient effect of the heat penetration thickness heat exchange discussed earlier for
doesn't say anything about it. Instead, relate
The runs are averaged over the amount to account for this major
Rate factors are ignored. The gas temperature at the end of compression is
The observation that it is close to the expected adiabatic temperature is a topic.
However, as shown in Figure 2 and its
As shown in the later discussion, the heat loss in compression, i.e.
Energy losses are significant and still
Sometimes the situation differs little from ideal insulation.
have a final pressure or temperature that is not The result
As a result, the source of heat loss from the gas to the wall is handled within the turbulence limit.
be managed. There is a turbulence assumption for this. turbulence
The necessary condition for is a large Reynolds number.
In fact, this condition is satisfied. However, Sirin
The condition of turbulent flow that uniformly fills the cross section of the volume is not treated.
Not possible. the gas has a large velocity comparable to the piston velocity
If the area of the inlet valve is configured to enter in degrees
For example, a high-velocity gas is nearly adiabatic within the cylinder volume.
There is plenty of time to cause uniform turbulence, and this
This is what usually happens. Instead,
Capable of inhaling gas in a smooth, almost laminar flow.
It was found that this greatly reduces turbulence.
Ta. Moreover, it gives a rotation of the gas around the axis
It can suppress unwanted heat exchange vortices. other
On the other hand, many books and recent designs of internal heat engines are
by the generation of turbulence, especially by “pushing”.
Emphasis is placed on achieving complete combustion.
Ru. Turbulent flow increases the mixing of combusted and unburned gases,
There is an opinion that this will further promote combustion.
This reduces turbulence to reduce heat transfer
This is contrary to the purpose of the present invention. There are two types of displacement internal combustion engines. Otstocycle
involves mixing fuel and air before suction;
Therefore, the fuel close to the cold wall is hotter, inside the
Requires turbulent mixing to transport to the combustion zone. No.
The second type of internal combustion engine is a diesel, and in this case
After the air is compressed to a high temperature, the fuel is formed into droplets.
It is injected as. In this case, the axial vortices are
It has certain advantages. Dense solid or liquid particles move outward in a gas vortex.
is subjected to centrifugal force. Typical fuel injectors
The jet velocity of a particle the size of Ron is 1 cm.
After driving at torque and decelerating, radius of Ro/2 to Ro/4
The expected vortex velocity at (10³cm seconds^-1(several times)
do. Therefore, the diesel fuel injector is
If you spray drops in a fan shape with the center of the axis
The linear vortex moves the droplet in a radius until it evaporates and burns.
It has the ideal property of transporting it outward. drop size
Droplets by adjusting the distribution and spray angle
automatically directs them to the area that burns them most effectively.
be transferred. The drops burn in one radial band.
If not, the drops will be filled with air, which increases combustion.
It is then blown outward by centrifugal force to an area with little fuel.
Ru. By injecting fuel near the axis of the vortex
Further beneficial effects occur. Burned near the axis of the vortex
The fuel is most
This is a hot area. However, this region is
The area that is shielded from the wall by the outer layer. last
The characteristic of thermally stabilized vortices is that the hot flow
The inner region is stable. (hot
Air is light and "floats" toward the axis. rotating vortex
In the centrifugal field of , the axis is the "high" point of gravity.
Ru. ) This effect affects the walls that are in contact with the hottest gas.
greatly reduces the area and as a result, from the combustion gases.
Reduce heat flow to walls. Therefore, the aim of this invention is
The target is Otsut engines and diesel cycle engines.
During both compression and combustion for both gases and
The purpose is to greatly reduce the flow of heat to and from the wall.
Ru. In diesel cycle engines, the cylinder wall
This maintains combustion that is slightly removed from heat loss, thereby reducing heat loss.
with the aim of further reducing loss and divergence.
There is. Heat loss in the Carnot cycle The theoretical maximum of a compression engine from the second law of thermodynamics
Efficiency is high, Efficiency = (T₂−T₁)/T₂It is. Here, T₁is the initial temperature of the gas, T₂is ideal
This is the temperature of the gas after adiabatic compression. The ratio of temperatures is T₂/T₁=R^(1-G) _cTherefore, the ideal effect is
Rate is 1-R^(1-G) _cIt is. R here_cis the compression ratio, G is the ratio of specific heat, and G
=1.4. Therefore, a typical example with a compression ratio of 8:1
Otsutocycle engine gives 56% efficiency, 16:1
A diesel with a compression of 67% gives an efficiency of 67%.
In reality, the efficiency may be 1/2 of these values.
Not possible. Heat loss to the wall is a large loss of about 30%
It is well recognized that (Taylor,
(1968); the remaining loss is (1) for the maximum compression time.
“Time” loss (15%), which is the delay in fuel combustion,
and (2) due to friction of moving parts. Discuss on duty
Thermal penetration thickness loss is not mentioned in the agency's literature.
not present. In fact, on average, depending on the wall time,
heating is the heat loss measured in the cooling water (or air).
cause loss. However, the thermal penetration thickness phenomenon is also excluded.
Exhaust gas is greater than that of the ideal cycle.
causes the temperature of the gas to rise. how does that happen
Show that. exhaust heat loss Measurements at general testing institutes are carried out on exhaust gas ducts.
Because unknown heat exchange takes place inside the engine, the exhaust gas
There is no comparison of the temperature to the expected value. we
is an ideal but unfeasible heat penetration thickness cycle.
The effect of the exhaust gas temperature on the exhaust gas temperature was considered. surrounding sky
Chi is temperature T₁enters, adiabatically T₂compressed into
Heat is added by burning the fuel and the temperature is T₃to
and this hot gas adiabatically T_Fourinflated to
Ru. The relationship between pressure, volume, compression ratio, temperature and specific heat is
It is expressed as follows. Vol.₁/Vol₂=R_c T₂/T₁=R^(1-G) _c P₂/P₁=R^G _c The heat H added by the combustion of fuel is
temperature T₃bring about. H=T₃−T₂ Moreover, the peak pressure is as follows. P₃=P₂(T₃/T₂) The expansion rate is usually (with the exception of exhaust turbines) the pressure
Reduction ratio R_cTherefore, the exhaust gas temperature T_Fouris the following
Piece temperature T₃related to. T₃/T_Four=T₂/T₁=R^(G-1) _c Heat penetration thickness loss temperature T₃40% of the heat is transferred to the cylindrical piston during combustion.
Suppose it is stored on the wall of Stone. T₃=0.6T₃Tona
Therefore, the new values of P, T, P′ and T′ are as follows.
I'm going to growl. P′₃= (0.6T₃/T₂)P₂ The exhaust temperature is as follows. T′_Four=0.6T₃R^(1-G) _c 40% heat loss due to walls, 1/2 during inhalation
Assume that it is returned to gas and 1/2 is lost to cooling water.
That is, the heat wave of the heat penetration thickness is the heat wave between the inflow and outflow.
divided equally into streams. Part of the heating of the incoming gas is
Occurs after compression begins, and also due to the previously mentioned mechanical
We acknowledge that it also causes losses, but this heating
Before closing the inlet valve and beginning the compression stroke
We can easily suggest that it is smaller than the initial heating.
Set. Therefore, compression begins with the following conditions: T′₁=T₁+0.2T₃ P′₁=P₁ The conditions after compression are as follows. T′₂＝T′₁R^(G-1) _c =(T₁+0.2T₃) R^(G-1) _c The same amount of fuel is burned as before, T′₃＝T′₂+(T₃−T₂) as well as P′₃=P₂(T′₃/T′₂) becomes. Here, T′₃is T₃larger, so again
A 40% loss occurs, further heating the wall. Continuous
In the cycle, T′₃is T₃Bigger, T″₃is T′₃
bigger. This chain of temperature increases is an auxiliary effect.
must be limited by. R_c=16,T₃=2T₂Typical of a diesel engine
Calculate the value. The heat added is H=T₂It is.
This is 26% of the stoichiometric amount of mixed fuel.
corresponds to T₂=T₁R^(G-1) _c=3T₁ T′₁+0.2T₃=T₁+0.4T₂=2.2T₁ From the above T′₂=2.2T₂ as well as T′₃＝T′₂+T₂=3.2T₂=1.6T₃ Therefore, the exhaust temperature is as follows. T′_Four=0.6T′₃R^(1-G) _c=0.96T_Four This is an estimate of the exhaust temperature excluding the 40% heat loss
value, but in reality there is less work to be done.
be done. In other words, the temperature is
The peak pressure increases with a ratio of 1.6, and the peak pressure is given by: P′₃= (1.6/2.2)P₃=0.73P₃ It decreases by 0.73 per cycle. Therefore, other regulations
more each cycle until a limiting effect occurs.
Heat loss occurs and less useful work is done.
Ru. One such effect is the compressed inlet air
body temperature T′₂is 0.6T₃, i.e. combustion air cooled by the wall
The temperature is higher than the body temperature. In this case, compression
Heat loss during the stroke is the wall preheated?
to limit the heat loss of the continuously occurring combustion gases.
Ru. If T₃are the same, hypothetically 1.6T₃Heat penetration thickness
The heat loss for T₃change to 20% of (the other 20
% is T₂), then the exhaust gas
T_Fouris 1.2T_Four20 of the available energy rises to
% is lost in the exhaust rather than through the cooling water
It will be. Naturally, these relationships are extremely complex.
In order to make accurate predictions, very thin gauges are used.
Arithmetic analysis has to be done, but the above
The analysis is about how to compensate for these losses.
Enough to give a needle. compensate for these losses
The policy is to increase the compression ratio of diesel engines.
Even if I raise it to 16 to 20, for example, why?
Explanation of the inability to increase efficiency
to assist. Useful performance at compression ratios of 16 and above.
That is, efficiency remains constant as a function of compression ratio.
This was revealed by Taylor in 1966.
It was done. The reason for this is that as the compression ratio increases, heat loss
This means that the
At the end of the locus, the clearance volume becomes smaller.
As a result, the surface relative to the volume
The product ratio is larger, and the heat loss is also larger.
I hear it. diesel engine design We have significantly reduced the following:
We propose the structure of this institution. (1) Heat loss through walls (2) Time loss in compression ratio during combustion (3) Mass of moving parts The above configuration consists of supercharging, combustion, and
and combination of expansion cylinder (2 cycles) configuration
are doing. We chose an overall compression ratio of 20:1. first
The supercharged cylinder has a volume ratio of 5:1. Therefore,
The combustion cylinder has a volume ratio of 4:1, resulting in
The final compression ratio is 20:1. Inside the combustion cylinder
The first expansion of has the same volume ratio of 4:1. if
When combustion doubles the temperature and subsequent pressure, expansion occurs.
tension cylinder 5×2^1/G=8.2:1 Therefore, the exhaust pressure must have a ratio of
atmospheric pressure. The advantages of this are as follows. 1 The cylinder and piston with additional charge are 1/(2×
Four^G) = 1/14 = 7% less than the peak combustion pressure
The pressure will be low. This is much lighter and
short piston skirt, short stroke and
It can be made to have a larger diameter. 2 Combustion cylinders with equal length strokes have a diameter of
Five^-1/2= 1/2.24 = 45% smaller, or
It will reduce the piston area by 1/5. subordinate
Therefore, the maximum output of the piston and head are the same.
Standard diesel cylinder for power and stroke.
will be smaller by the same ratio, i.e. 1/5.
Therefore, weight and friction are reduced by the same ratio
right. 3 The compression ratio of the combustion cylinder is only 4:1,
We have a long stroke of 4r, or twice the diameter.
Assume that If the length of the bottom port is 0.5r (2
stroke), then the compression or expansion stroke
The stroke is 3.5r. This is the peak compression
Provides a large crank angle. As an example, we
Compression ratio from 16:1 to 20:1, then 16:1, etc.
In other words, the utilization efficiency increased from 67% to 70%, and further to 67%.
Assume that combustion occurs after a long period of time. This is a fire
The compression ratio of the fired cylinder increased from 3.2 to 4 and then to 3.2.
show what will happen. All the displacements correspond to these displacements.
The rank angle is 54 degrees or about 1/6 of one cycle
It is. This is an equivalent single cylinder 2 stroke
diesel engine, i.e. R_c=16.1→20:1
→16:1 change is 24 degrees or 1/2.25 shorter
larger than its diesel counterpart. Therefore, burning
Compression losses during baking time are significantly reduced. 4 Peak compression and combustion period (16:1→20:1→
Combustion piston-cylinder configuration between 16:1)
is approximately one time the length of the radius. This is a strike
During combustion with a compression ratio of 3.5 and a radius of 3.5
Average head clearance. Therefore, volume
The surface area ratio is for a compression ratio of 20:1.
A mark with an average head clearance of 1/9 of the radius.
(1+r/z)= compared to quasi-single cylinder
Reduces heat loss through walls by a factor of 5
This is desirable. 5 Make the expansion cylinder larger than the supercharging cylinder
As a result, the exhaust works effectively.
“Overinflation”, actually a proper
Expansion is made. So-called overexpansion of exhaust gas
The exhaust gas is expanded to the atmospheric pressure.
means. Normally, the exhaust pressure is 2 at the time of introduction.
The gas energy is 2.5 times higher than that of the exhaust turbine.
Used with 50% efficiency in engine and turbocharging
or completely wasted. Separate exhaust system
The cylinder is small with small dimensions of the combustion cylinder
As well as the advantages of compression ratio, it also provides adequate overexpansion.
It is growing. 6. By carefully designing ports, we
is the flow direction of the near-laminar flow in each cylinder.
Normal large turbulence caused by walls by creating vortices
Flow heat exchange can be reduced. This is for each
The movement of gas from the volume is nearly stationary and therefore the pressure
Requires that the force drop transverse valve be very small
will do. Separate cylinders for charging, combustion and exhaust First reason for three separate cylinder design
is the compression ratio of the combustion cylinder,
The piston configuration is roughly “right” series.
be limited to a sufficiently small value such that
It is. The length of the above light cylinder is radius
, resulting in an approximately laminar flow direction
Directional vortex effectively reduces heat flow to the wall
I can do it. Reduced combustion time, compression losses and heat
Reduction in heat mass is an ancillary benefit.
On the other hand, two additional cylinders and a compound valve are added.
There must be. Many useful functions are exhaust gas.
It is recovered within the country. This mechanical energy
(8.2)^(G-1)From (3.5)^(G-1)The temperature ratio up to, i.e.
2.32/1.65 = 1.41 times larger than the combustion cylinder
Become. Therefore, heat loss in the combustion cylinder is eliminated.
Less important than air cylinder design. subordinate
Therefore, we can improve combustion by weakening laminar flow conditions.
Design the cylinder. Combustion cylinder design The ideal laminar compression or combustion cylinder is
stated. Introductory port on top of cylinder wall
The length is r/2, and the flow is slow and laminar.
allows azimuthal and radial flow. child
The wall slide valve has a maximum combustion temperature of 1500℃ and a pressure of 1800psi.
It is difficult to close and cool the
Ru. However, Ricardo
A slip valve diesel can be made to work well.
It was made clear in 1953 that it could be done.
However, in this case, the introduced air was 300℃ higher than that.
It's getting expensive. In addition, the scavenging of the cylinder is
Axial flow from the top through the cylinder to the top
This is very conveniently done. therefore we
The fuel cylinder is a 2-stroke diesel
I suggest that it be made similar. Here, 2-
Stroke diesel has an introduction at the bottom of the stroke
The supercharging gas (compressed) in the normal annular port in
5:1 and pressure 10:1).
Ru. These ports are r/2 long and 83 degrees
It will be the same as the sleeve port that allows the introduction of
cormorant. The exhaust is centered in the axial direction within the head.
It exits through the matched valve. Exhaust cylinder design The exhaust gas pressure leaving the combustion cylinder is equal to that of the introduced air.
Since the pressure is about twice as high, the stroke duration at the bottom
Part of this is to reduce this high pressure to the value of the supercharging inlet pressure.
must be used to lower the other
On the other hand, the incoming gas is transferred to the combustion cylinder and the exhaust gas
The air must be purged. we open at the same time
arranging the inlet port and outlet port
This is due to the almost laminar flow created by
We propose to achieve the following. Therefore, all pressure
It becomes uniform. The volume changes while the exhaust piston is descending.
Since the inlet air and exhaust gas are transferred,
Expand. Compression is from the exhaust pressure of the combustion stroke
It begins. Therefore the introduced air is
when the excess pressure is higher than the average boost pressure value.
Must be compressed. combustion cylinder gas
The combined volume of the storage volume and the supercharged storage volume is the exhaust
As the piston descends, it expands adiabatically and is ejected.
The new gas expands to the supercharging design value during introduction.
It will be replaced by fresh introduced air. We describe two ways to make this reduction.
Bell. The first one is too short and doesn't work.
Dew. This drop is due to the adiabatic expansion in the exhaust cylinder.
The exhaust pressure must be 2:1.
The crank angle of the exhaust cylinder for expansion is low
The time will be below. The time for this drop is the exhaust cylinder
The volume is small (1/8.2) from the top of the stroke.
This is the time required to change to (1/2)=0.0743.
Exhaust piston stroke length same as combustion cylinder
To make it easier, this is the cos^-1[1-2 (0.0743)] =
Match the crank angle of 32 degrees. Next, the exhaust system
Linda is at constant pressure i.e. cos^-1[1-4
(0.0743)]=Pressure of supercharging air at an angle of 45 degrees
must accept a volume equal to the exhaust gas in
No. of the timing between these two angles.
The difference is 13 degrees. This means that the supercharged air is in the combustion cylinder.
It's time to eliminate da exhaust. this time
is too short and the exclusion time required for a supercharged cylinder
All that charge is reduced at a constant pressure.
request that the entire amount be distributed. SUPERCHARGE holding volume
HOLDING VOLUME） Instead, to avoid this problem,
- Percharger maintains air at twice the introduction pressure.
Can be supplied to the required volume. Then while the exhaust decreases,
Combined volume of super charge holding volume, combustion silicon
cylinder, and within the first stroke of the exhaust cylinder.
double the pressure drop occurs. At the same time, completely filled
The supercharged air is introduced into the combustion cylinder.
The supercharger cylinder has a holding volume of
Refill fractionally, with the original pressure equal to twice the inlet pressure
Return to pressure. Therefore, the holding volume is [1/2^1/G1] = 1.56 x combustion cylinder volume becomes. At this time, air is introduced into the exhaust piston
The crank angle of arc cos [1-2 (1.56/Rc exhaust)
](1/2)P^1/G=40° Occurs when At this time, the introduction point is
83° burn so that the gate is almost fully open (88%).
Successfully done in the center of the inlet port opening of the firing cylinder
be called. Second, lower inlet air velocity and therefore lower heat
Inlet port to combustion cylinder to obtain losses
Attention must be paid to the thickness of the introduction port
If it is 20% of the microweb thickness, the effective introduction area
teeth, [1-0.2] [0.80] [(Pi)r²
]=0.7(Pi)r² becomes. The average density of the introduced gas is approximately [1-1/2
(1-2^-1/G)], which is 0.8 of its final density.
becomes. Also, the effective area is approximately the area of the combustion piston.
That's 87%. Smaller introduction compared to 1/2 stroke
The period is [2/(Pi)] [40/180], so the derived
The radial velocity of the incoming gas is [2/(Pi)] [1/effective area] [180
/40〕=3.3×piston speed It will be. Azimuthal velocity of axial vortex
velocity) is selected to be 1.5 times the radial introduction velocity.
Ru. This ratio is the angle of the web that acts as a vane.
Determined by degree. In this case, the gas is being compressed
To, (Speed x Stroke time) / Circumference = Approx. 4 times It works, and it works as well during inflation. then,
Mass fraction of fuel inside 25% of axial vortex
(mass fraction), the heat
Replacement should be 10-15% (25% equivalent fuel
(as stochiametric burn). SCAVENGING The inlet supercharging air is far away from the combustion products.
It acts strongly (“heavy”) in the direction of the mind. this thing
, the inlet air is cooler and larger than the exhaust gas.
It means that it has a large angular moment. Guidance
The incoming air is cold because it has not yet been combusted.
and the introduced air comes into contact with the wall and spins down.
Since the angular moment is large because it is not
Ru. Therefore, the introduced air comes into contact with the cylinder wall
It tends to flow in as a thin layer and into a small radius.
towards the exhaust valve at 1/2 radius
Push away hot gas. Inner part of exhaust gas core 1/
The mass of part 8 (1/4 volume, 1/2 density) is the fuel
A weak vortex is created by the moment of the fuel injection.
There is a tendency to This thing has a cold inflow
Convenient for interaction with introduced gas and exhaust gas
It is also convenient for scavenging air from the valve. Moshi Exhaust
When the remaining amount of gas is very large, i.e. scavenging
If the exhaust valve is insufficient, reduce the size of the exhaust valve by 1/3.
diameter so that only 5% of the exhaust mass remains.
It's easy to do. Axial vortex flow controlled exhaust
Valve control provides effective scavenging.
Ricardo (1954) raised the issue of scavenging.
The concept of “swirl” in the introduced gas, i.e.
Introduced rotational angular moment. This means that
Cardo's exhaust port is also provided on the peripheral wall of the cylinder.
This is because it is not installed near the axis.
Ru. Next, the introduced gas and exhaust gas are connected to ports on the peripheral wall.
The air is pushed away from the air towards the axis, resulting in scavenging air.
was insufficient. diesel engine design As shown in Figure 10, three pistons or
The supercharging piston 201, the combustion piston 202 and
and exhaust piston 203 are connected to each cylinder 20
8, 209 and 210, the crankshaft
Yaft 204 and crank 205, 206, 2
Driven by 07. super charger
The cylinder 208 is a cam of the crankshaft 204.
Cylinder wall sleeve valve driven by 212
It has 211. These cams 212
The annular port 21 by driving the wall sleeve valve 211
3 opening and closing, vortex inflow with straight vanes 215
The introduced air is introduced by the rotating circulation flow generated by the mouth.
Suction is coming from the annular Blenheim chamber. This rotational circulation
inside the supercharger cylinder due to the flow.
An axial vortex 216 of the introduced air is generated (first
(See Figure 11). The introduction port area 213 is large.
and the axial vortex flow 216 causes the cylinder to
The heat exchange with the da wall 208 is reduced, and the
The air in Yajia is compressed fractionally and leaves
Exhaust from the cylinder through the spring exhaust valve 217.
Served. The leaf spring exhaust valve 217 is
It is provided in a semicircular shape inside the head 218.
Therefore, the vortex flow in the axial direction is mostly at about 1/2 of the radius.
is discharged from the cylinder in the direction of the rotating flow. supercharging
Air is compressed 82 times to approximately 280PSI (approximately 19.69Kg/
cm²) and passes through the duct 219 into the room 220.
carried to. This chamber 220 is filled with compressed air (supercharged air).
The volume of air) is 1.56 times the volume of combustion cylinder 209.
to hold. The walls of the duct 219 and this chamber 22
0 is insulated to reduce heat loss
Or with ceramic lining 221.
be. In operation, cylinder 208 and reservoir
The pressure of the supercharged air in the chamber 220 is
Almost equal to the pressure inside the combustion cylinder 209 just before
Also, the pressure inside the exhaust cylinder 210 at the same time
is equal to, so the pressure at all three points is
be equal. The combustion piston 202 is a combustion cylinder.
The bottom port 222 of the cylinder 209 and the combustion cylinder
directly exposed to the exhaust valve 223 of the head 224.
Ru. The gas then flows at almost constant pressure and
from the storage chamber 220 through the transfer duct 226
It is transferred to the Blenheim chamber 225 at the entrance of the compression chamber.
Therefore, very slight turbulence occurs. exhaust cylinder
Due to the expansion of exhaust piston 203 within 210
The pressure is 280PSI (approximately 19.69Kg/cm²) to 140PSI
(approx. 9.89Kg/cm²) is reduced by a factor of 2 to
When the combustion cylinder is filled with fresh supercharged air
Then, the exhaust valve 223 is closed. Then supercharged air
The toggling of the combustion piston 202 is at the inlet port.
Combustion cylinder 20 by covering port 222
It can be kept within 9. Inlet port 222 is cylindrical
It has many vanes inclined at approximately 60° with respect to the radius of the blade.
The cylinder has a 360° opening. supercharging
The gas pressure ratio is 5:1, and this ratio
Area of supercharged cylinder 208 relative to cylinder 209
equal to ratio. of the supercharged air in the combustion cylinder 209
Further compression is 4:1 before fuel injection, following
Therefore, the total compression ratio is 20:1. fuel engine
Standard driven by the crankshaft 204 of
driven by a standard fuel pump (not shown)
into the combustion chamber by a standard fuel injector 228.
Injected. The fuel is injected as fine droplets 227 (see Figure 12).
vortices around the axis of the combustion injector 228
When it comes to flow 229, the fine droplets that expand into a conical shape become silica.
until it is subjected to a radial centrifugal force towards the radial wall.
It is kept within the axial region. flaming fuel
Burning remains in the central region of the vortex, leaving unburned fine droplets
Only the fuel moves towards the pre-combustion region where available oxygen exists.
It has a tendency to escape in the radial direction. Therefore, the fuel
Burning gradually radially outward until burnout
Proceed to. The high temperature combustion products are transferred to the cylinder wall 20
9 and remains separate from the piston 202 and
Only the tube 223 is exposed to hot gas in a restricted area.
be forced to Another object of the present invention is to create a nearly laminar vortex flow.
Combustion takes advantage of the central axial area of the cylinder volume
and the working gas and
The purpose is to reduce the heat flow between the cylinder wall and the cylinder wall. An example of the tubular exhaust valve 223 is shown in FIG.
As another example is shown in Figure 12, a special circle
It has a cylindrical design. As shown in Figure 10
The valve 223 is connected to the overhead cam 230 and the
The shaft 231 is driven by the shaft 231.
central cylindrical head section supported by 31
It is placed on top of 232 and is water-cooled in passage 233.
Even when exposed to high-temperature exhaust gas of up to 1100℃,
I'm learning not to overheat the bar. Furthermore, the radius
The axial vortex flow 22 is caused by the annular opening 1/2 of the
7 is caused by the turbulent flow induced in the exhaust gas duct 234.
It will be possible to discharge air from the room to the minimum.
ing. This duct reduces heat transfer
Laminated with ceramic coating or other heat-resistant insulation material.
It has been inning. The exhaust gas duct 234 is short.
Thus, several percent of the volume 210 of the exhaust cylinder
It is formed with a small volume so as to
Only the valve between the firing cylinder and the exhaust cylinder exhausts the air.
It is adapted to serve as a gas valve 223. Exhaust gas makes an angle of approximately 60° to the radius
from the duct 234 through the inlet port 236.
Air enters the cylinder 210 and forms an axial vortex 237
is beginning to form. Exhaust valve 223
The exhaust piston 203 is 1/5 stroke after top dead center.
is closed when it is in the archive. This is exhaust gas
is 280PSI (approximately 16.69Kg/cm²) to 140PSI (approximately 9.89
kg/cm²) when it expands to a pressure of exhaust piste
The engine then moves at 2/5 of its maximum speed and
The area 236 of the inlet port is the area where the incoming gas reaches the maximum piston.
To move at 4 times the speed, 1/10 of the piston area
It is designed to be. azimuth
gives a port area of 1/10 of the piston area around
To do so. [(Pi)/2] or 1/4 turn (turn)
Ru. The exhaust piston 230 then has a total volume ratio of
Expand the exhaust gas until it becomes 8.2:1. child
This allows the pressure to reach atmospheric pressure at the end of the stroke.
Descend. The exhaust valve 238 is connected to the combustion cylinder 209
It is designed similarly to the exhaust valve 224 of
Camshaft 231 as well as cylinder exhaust port
It is opened by a cam 239 driven by.
The exhaust valve 238 is opened when the exhaust piston 203 is at top dead center.
It remains open until just before reaching the end. exhaust port
The lead angle of the inlet port 222 and exhaust port
Inside the combustion cylinder 209 just before the port 224 is opened
280PSI (approximately 16.69Kg/cm²) was captured up to the pressure of
The angle is such that the gas is compressed. The exhaust gas is
Exhausted via vortex 241 and exhaust port 242
It will be done. As shown in Figure 12, similar to the exhaust chamber
The head portion 250 of the combustion chamber is a slot in the valve.
A lug 254 extending through a
valve 252, the valve can be supported within the valve 252;
The swinging arm 258 passes through the tapepet head 260.
It is then activated. The timing chart in Figure 14 shows the piston and valve.
It shows the relative timing of supercharging piston
Starting from the top dead center of the engine 201, the introduction three
The valve 211 is located 90 degrees ahead and should be opened just now.
I'm trying to The combustion piston 202 is a combustion exhaust gas.
At the 138° position just before valve 224 is opened, the combustion
The firing piston 202 opens the introduction bottom port 222.
It's on. The exhaust piston 203 is also at top dead center.
Ru. At a later time of 82°, the bottom port
222 is closed and the supercharging introduction port 21 is at the 180° position.
3 closes. Supercharged cylinder 208 and combustion cylinder
Compression takes place in both cylinders of the cylinder 209.
Approximately 20 degrees in front of the top dead center of the combustion cylinder 202
Then, fuel injection begins, followed by an expansion process followed by combustion.
The process begins. otsuto cycle organization As mentioned above, the Otsuto Cycle Engine
However, it uses gasoline as fuel and uses a carburetor.
) are usually designed for maximum turbulence.
It will be done. The crown or head of the piston is small.
When designed with a diameter of
and the gap between the outer diameter of the piston and the head is small.
The gas is packed into the re-inflow volume.
will be included. This is called squish.
Ru. This is because the gas in the small interstitial volume reflows.
“squish” or packed into the volume
This is because turbulence is generated at the end of the stroke.
As explained earlier, the purpose of creating turbulence is to
The mixture of air and fuel in contact with the cylinder wall is
Completed by continuously mixing with the gas that burns at a high temperature in the center.
Complete combustion and unburned gas that causes air pollution
This is to prevent this from happening. however,
Turbulence will increase heat loss. As described above, the fuel is introduced along the axis of the laminar vortex flow,
burns by cutting off the fuel from the cylinder wall.
Describes a diesel engine with improved combustion efficiency.
It's here. For diesel engines, the fuel
It is injected immediately after it is requested to fire. Otsutosai
In a cruise engine, fuel and air are mixed in advance.
In this case, there is always a fuel-air mixture.
Aiki comes into contact with the cylinder wall, but on the contrary, the fuel injection type
In engines, laminar (“stratified”) filling is performed.
can become. If there is a laminar vortex before top dead center,
When fuel is injected along the axis of the flow,
Depending on droplet size, overflow rate and evaporation rate
Fuel mixes with air only outside a defined radius.
Ru. The resulting layer allows the air-fuel mixture to
The coalescence is sufficiently prevented from reaching the cylinder wall.
It will be done. In this case, the fuel-air mixture is
There is little or no contact with the
Therefore, it is necessary to provide turbulence to achieve complete combustion.
Not required. Otsuto cycle fuel injection type engine
In engines, depending on the shape of the head valve,
A “swirl” of some degree sometimes occurs and the axial
Creates a vortex but from a restricted port area
The gas introduction speed is very large and the flow becomes non-uniform.
Ru. Despite the perfect mixture of fuel and air
goes towards the cylinder wall, so for complete combustion
is required to create turbulence. obey
As a result, combustion continues where the fuel is concentrated at the center of the vortex.
I get kicked. Head and piston at the center of the vortex
Air-fuel mixture in contact with the crown of the ton
is not cooled by the sliding of the oil film.
in contact with surfaces maintained at high temperatures. obey
Therefore, a laminar vortex flow direction in which some heat-induced loss can be expected.
Fuel-injected 4-stroke Otto cycle
Since the engine can be designed using a laminar vortex flow system, heat can be reduced.
Losses and combustion losses are negligible and therefore the
Contaminants from the cylinder walls are also reduced. This operating cycle is standard 4-stroke size
compression and explosion are performed by the above three cylinders.
compared to the diesel engine
Ru. Otsutosa with a small compression ratio (e.g. 8:1)
The system is able to successfully fulfill this request.
Wear. If a supercharger is installed, the final compression capacity can be increased.
The product becomes more favorable in proportion to the supercharging ratio.
(because the head clearance becomes larger), it becomes more efficient.
Although it is possible to create effective designs,
Even if a cylinder is not installed, the cylinder will not be activated during combustion.
Because of the laminar axial vortex flow away from the peripheral wall of the
Therefore, heat loss will be significantly reduced. 4-stroke Otto cycle engine In FIGS. 15 and 16, cylinder 3
The piston 301 in 02 is the crank arm 303
and wrist pin 304, the 4-straw
driven by the crankshaft in crank mode.
Ru. The piston has a smooth piston head and head.
With clearance 305 between 306 and
Shown at top dead center when combustion occurs.
has been done. Head clearance 305 is due to dimensions.
R/4 (R is the piston diameter), and the piston diameter is
For an equal representative stroke table (2R),
R/4 clearance 305 is typical of 8:1
Compatible with Ootcycle compression ratio. The compressed volume is
Lower cylinder clearance and head 306
Due to the sleeve valve 307 within the clearance of
limited. As Ricardo argues, this
The clearance between them allows for perfect sliding against the external wall.
until contact is made to extract heat and limit expansion.
, so that the sleeve 307 expands due to heat.
automatically adjusted. The sleeve valve 307
Notched volume in the cylinder wall extending beyond the cylinder
It is in section 310. This notch volume is zero.
It may also work as a valve seat, or if
If it is large, the captured gas will not be compressed.
It is. Sleeve valve 407 is spring loaded to open
and is actuated by two cams 311. vinegar
That is, the sleeve valve 307 is as shown in FIG.
can be actuated by a Rotzker arm.
Wear. The head portion 312 within the sleeve valve is a camshaft.
It is supported by Yaft, but as shown in Figure 13.
I can support the sea urchin too. At the top dead center at the beginning of the suction stroke
The sleeve valve then retracts and opens the spiral air inlet 32.
Inflow straightened by vane 316 in 0
The axial vortex formed by the moment of air and
Port low in plenum chamber 315 for air suction
The area 314 is opened. The head 306 has a fuel injector 317, a spark
Includes plug 318 and exhaust valve 319. fuel injection
The gun is a completely standard type, but it is equipped with a fuel spray gun.
is axially symmetrical and has a vortex layer load.
It is mounted in the axial direction. ignition blug
318 has as little oscillation as possible against the rotating flow.
A strip in the same plane as the head 306 so as to
Has a park ignition surface. such ignition plug
is representative of an aircraft ignition plug.
Ru. Similarly, the bottom surface of exhaust valve 319 drives the vortex.
It's smooth so it doesn't shake. The exhaust valve 319
Driven by cam 321. FIG. 16 shows the piston 301, head 306 and
and two spiral-shaped blenheim chambers 315. Be
The tube 316 has a suction vortex 324 and an internal axial vortex.
325 is generated. The swirl in the vane 316
The suction area is where the suction vortex is located in the small diameter of the piston.
The speed of the piston is approximately four times that of the piston.
is 1/3 of the suction area of the piston. the result,
Radial suction speed of twice the piston speed is axial
It is even smaller than the vortex in the direction (about 1/2), so the axis
Directional vortices dominate the flow and annular vortices, i.e. radius
This prevents directional vortices from forming. The timing diagram can be any 4-stroke
It is the same as a 4-stroke engine, and is similar to a 4-stroke engine.
Since ming is well known, it is not shown here. Only
The small difference is that for opening and closing the suction sleeve valve 307
It has a cam shape. The port area is the opening of the sleeve valve.
It is determined by the degree of This area has a radius
The ratio of directional velocity to azimuthal velocity remains constant during suction.
As shown, it is proportional to the speed of the piston. Therefore, the valve opening is the sine of the crank speed.
Proportional. This is the easiest thing to manufacture.
It is a cam with an off-center circle. in this way
Therefore, only the radial moment of the axial vortex
The angular moment remains constant during the suction stroke.
, resulting in meridional circulation or radial circulation.
Circulation in the direction is minimized. This minimizes heat loss.
Make it. conclusion Heat flow from the working gas and its interfaces
are the volumes to which there is decisive control over the flow of heat
A shape machine is designed. As a result, such machines
This is a major improvement in thermal efficiency. Control method
is the generation of static laminar flow, and more specifically,
Laminar flow in a stable vortex that takes advantage of the symmetry of the constrained volume.
It is to deny turbulent heat transfer by generation. Achieving extremely low heat transfer when sucked at any time
The turbulence velocity is small compared to the displacement velocity and the wall
The total displacement of the working gas in contact is approximately 50
requires a small distance compared to the
Ru. This is necessary to induce complete turbulence.
contacting a smooth wall at a large Reynolds number
is the distance of fluid displacement. suitable suction port
design and small displacement guarantee laminar flow. Examples exist within this principle, including (1) vehicle dimensions;
Articulated vane compressor compatible with heat pumps
Expander (2) Adiabatic air compressor, (3) Diesel engine
((a) precompression, (b) postcompression, combustion and preexpansion,
(c) After-exhaust expansion is carried out in three separate cylinders.
(2) and (4) preferably with fuel injection.
It is a 4-stroke automatic cycle engine. The thermal efficiency of these designs in some cases is
It's less than twice as much as it is. This has been the case until now.
Thermal expansion transfer from the gas to the wall is the level of turbulence sucked in.
It has not been sufficiently handled as it is sensitive to
It depends. Ricardo (1954) and Taylor
(1966), most of the old textbooks are
It does not even take into account the turbulence patterns within the engine. recent years
The model and measurement of
I'm just showing it now. This style putter
thermal losses, efficiency obtained and accurate measurements required.
The relationship between is the basis of the invention. Reference materials (One “American Physics Handbook” 1963 Brentay
Published by Schall, New York, pp. 256 and 257. Lucardo. Etsuchi. Earl (1954) “High
Speed Internal Combustion Engine” published by Bradsky Mandosan, Russia
London, England Taylor. C. F. Author “Theory and Practice”
Internal Combustion Engine” 1966, Volume 1, Chapter 2 (2) Article Gosman. A. Day. Johns. Jiyu
stomach. R. Watkins. A. Written by Pea
(1978) “In-cylinder in reciprocating engines
“Development of predictive methods for processes” block,
General Motors Symposium, Detro
It. Michigan. Page 103 (Figure 16) Morse. Youpi. White law. J.A.
Etsuchi. Ianeskies. Written by M (June 1979)
Month) “In the motor piston-cylinder assembly,
Turbulence measurement using laser Dobbler wind measurement”
Journal of Fluid Engineering, ASME Proceedings, Volume 101, p.
215 (Figure 17) (3) Patent U.S. Pat. No. 3,343,782 to Breuwer et al.
(Published on September 26, 1967) (Sealing “Watushi”)
Rotor end sealing and rotor end sealing using
(relationship with the tar axis, etc.) Ezotubu US Patent No. 3346176
(Published October 10, 1967) (Rotor and strip
Sealing and storage between tree landings
Molybdenum disulfide coating on Ritzper Landing
(using cover) U.S. Pat. No. 3,356,292 to Breuwer et al.
(Published December 5, 1967) (Reduces rapid pressure changes)
cutout on the internal wall of the housing for shaft
Receiving and sealing shoes. Also, the vane
special materials and combinations) U.S. Pat. No. 3,370,785 to Pasek et al.
(Published on February 27, 1968) (Attached to the pulley)
"Impeller" disk near filter). Adsit U.S. Patent No. 3401827
(Published September 17, 1968) (Preserve the sealing show)
Brass molded in place to hold
Cloter lining and bearing shoes are lined.
molded with ) U.S. Pat. No. 3,419,208 to Breuwer et al.
(Published December 31, 1968) ((1) Sealing and bearing system
Spot weld to hold dowels and align dowels.
Metal rotor liner (2) for easy lifting
Curved to allow assembly. (3) Fishing
Heat-reinforced vanes (4) molded into the hub of the overlap
Vanes molded in hardenable plastic (5)
Various organizations in vane plastic (6) Housing
Molded ball bearing (7) facilitates assembly during assembly
Ball bearings for smaller pulleys
hub) Rohde U.S. Pat. No. 3,437,264 (1969)
(Published on April 8, 2016) ((1) Hazards in rotor and recesses)
Coat to seal at the end of the housing.
Rotor with Teing (2) Strituparande
Relationship between coating and coating (3) Coating
MoS₂including) Rohde U.S. Pat. No. 3,437,265 (1969)
Published on April 8, 2017) (The base of the shoe and those
(wedge-shaped space between retaining strips) U.S. Pat. No. 3,844,696 to Stiles et al.
(Published October 29, 1974) (Two balanced
Rotor unit with extending vanes: Inlet port
cover to reduce noise on the route) Zeal U.S. Pat. No. 3,954,357 (1976)
Published on May 4, 2017) (For pins to which vanes are pivoted)
Holds the pilot sleeve during the guided track of the
standard 2-vane unit).

[Brief explanation of drawings]

Figure 1 is a diagram showing heat transfer across a barrier, Figure 2 is a PV diagram showing various thermal cycles, and Figure 3 is an end cross-sectional view of an articulated vane compressor-expander. 4 is a diagram showing the temperature drop of the gas in the machine of FIG. 3, FIG. 5 is a schematic diagram of a Brayton cycle heat pump using the vane of FIG. 3, and FIG. FIG. 7A is a cross-sectional side view of the compressor, FIG. 7A is a cross-sectional plan view through the guide passage showing radial vanes, which can be used but are not preferred; FIG. 7B is a cross-sectional side view of the compressor; is a cross-sectional plan view through the guide passage in the compressor shown in FIG. 6, the vanes being oblique to the radial direction;
Figures 8A, 8B, and 8C induce a desirable axial vortex flow that suppresses the formation of annular vortices, with little or no circumferential component of velocity and When the gas is guided, it exhibits annular vortices forming and persisting in the bottom stroke, middle stroke and top stroke, respectively, which is the case with radial vanes similar to that shown in FIG. 7A; Figures 9A and 9B schematically illustrate the formation and expansion as a guided progression of an axial vortex flow as the cylinder expands; such flow is induced by the diagonal vanes shown in Figure 7B. 10 is a sectional view of a two-stroke diesel engine implementing the present invention, and FIG. 11 is a sectional view of a two-stroke diesel engine implementing the present invention.
12 is a plan view in generally schematic form showing the path of gas flow through the engine shown in FIG.
13 is a cutaway sectional view of the head of a combustion cylinder that can be used in place of the head shown in FIG. 10, FIG. 13 taken along line 13--13 of FIG. 12 and viewed in the direction of the arrow; 14 is a diagram showing the timing of the engine shown in FIGS. 10 and 11; FIG. 15 is an end sectional view of a four-stroke automatic cycle engine embodying the present invention; FIG. Fig. 16
15 is a cross-sectional plan view of the engine shown in FIG. 15 taken in the guideway as indicated by line 16--16 in FIG. 15.

Claims (1)

[Scope of Claims] 1. Means for forming a variable volume chamber for compression or expansion, and for substantially the entire time that gas is introduced into said variable volume chamber, said variable volume chamber being substantially equal to the pressure within said chamber. a gas displacement volume having means for maintaining the volume as a confined volume at different pressures and inaccessible to any gas; and inlet passageway and port means for introducing gas into the variable volume chamber. In an apparatus for compressing or expanding a fluid, the channel and port means 74; 96, 100;
214, 225, 236, 315 are moving boundaries 63, 64, 65; 201; 202;
03; supplying said variable volume chamber at a velocity equal to that of 301 and along the main direction of movement of said gas to reduce heat flow to and from the walls forming said variable volume chamber; A device featuring: 2. The device according to claim 1, wherein the variable volume chamber has a piston 9 in the cylinder.
1,201,202,203,301,401 in a movable manner, and is characterized in that the area of the inlet port ranges from about half the area of the piston to almost the entire area. Device. 3. A device according to claim 2, in which the inlet passage extends over 360° around the cylinder as a plenum area and further includes a sleeve 9.
5,211,307, wherein the sleeve valve is movable across the inlet port between its closed and open positions. 4. The device according to claim 3, in which the plenum chamber is adapted to convey gas into the chamber with a velocity component tangential to the cylinder, so that an axial vortex is obtained and a radial A device characterized in that the formation of eddy currents and the associated heat exchange are prevented. 5. The device according to claim 2, wherein the device is an Otto cycle engine and further comprises means 317 for introducing fuel into the chamber approximately in the direction of the axis of the chamber, so that the fuel and Combustion is at least partially localized in a region remote from the cylinder wall and combustion is enhanced by centrifugally directing unburned fuel droplets outward from the axis of the cylinder, thereby A device characterized in that oxygen-free air is obtained for maintaining fuel combustion. 6. The device according to claim 4 or 5 further includes a crankshaft 102, 204, 311 connected to the piston to move the piston within the cylinder, and a crankshaft 102, 204, 311 that causes the piston to perform reciprocating motion A device comprising coupling means for coupling a sleeve valve to a crankshaft for driving the crankshaft in a timed relationship. 7. The device according to claim 6, characterized in that the coupling means comprises an overhead camshaft 311. 8. In the device according to claim 1,
A supercharging piston-cylinder device 201 for supercharging gas, and a combustion piston for receiving gas from the supercharging cylinder and combusting it.
It consists of a cylinder device 202 and an exhaust piston-cylinder device 203 for receiving exhaust gas from a combustion chamber, and the compression ratio in the supercharging cylinder is larger than the compression ratio in the combustion cylinder, and is approximately 3: 1 to about 8:1, and the compression ratio in the combustion cylinder is about 16:1 to about 20:1.
It is on the order of about 3:1 to about 4:1 for a total compression ratio on the order of A device characterized in that it has a volumetric expansion ratio. 9. In the device according to claim 8, the supercharging cylinder 201 has a 360° angle at its head end.
an inlet port 2 that extends over the area and has an area that is approximately half to approximately the same as the cross-sectional area of the supercharging cylinder;
13, a sleeve valve 211 movable across the inlet port, and a sleeve valve 211 that imparts a circumferential velocity component to the gas to create a near-laminar axial turbulence in the supercharging cylinder. a plenum chamber 214 adapted to supply an inlet port. 10. The apparatus according to claim 9, further comprising an insulated transfer duct 219 and an insulated storage chamber 220 for holding supercharged heated air for introduction into and exhaust from the combustion cylinder, Apparatus characterized in that the volume of the storage chamber is on the order of about 1 to about 6 times the displacement capacity of the combustion cylinder. 11. In the device according to any one of claims 8, 9, and 10, the combustion cylinder 209 has an inlet port 222 near the bottom dead center of the stroke, and the inlet port is located within the combustion cylinder. A device characterized in that it also communicates with the supercharging cylinder by means of a volute 225 adapted to create an axial vortex flow. 12. In the device according to any one of claims 8, 9, 10, and 11, during combustion, the radius of the combustion cylinder 209 and the clearance length of the central head are approximately equal. , for which the ratio of the clearance volume to the surface area of the combustion chamber during combustion is dimensioned to reduce heat losses. 13. The apparatus according to claim 11, wherein the head of the combustion cylinder is substantially smooth and is disposed on the combustion cylinder so as to be substantially coaxial with the axis of the combustion cylinder. exhaust valve 2
23 and means 228 for injecting fuel substantially along the axis of the combustion cylinder, so that the axial turbulence is substantially undisturbed and the combustion action is controlled by the oxygen content of the air. A device characterized in that it is enhanced by centrifugally directing the fuel droplets to an area that is not depleted. 14. The apparatus of claim 12, wherein the head of the combustion cylinder is substantially dropwise flat and smooth, and further comprising means 228 for injecting fuel generally along the axis of the combustion cylinder.
It consists of an exhaust valve 223 for exhausting air from the combustion cylinder, and the exhaust valve is arranged at the head approximately midway between the axis of the combustion cylinder and its wall for more complete exhaustion. A device characterized by: 15. The device according to any one of claims 12 and 13, wherein the exhaust valve 223 of the combustion cylinder has a cylindrical sleeve, and the sleeve has a cooled inner surface at the head of the combustion cylinder. A device, characterized in that it is adapted to slide along an outer guiding surface 240, thereby providing a large heat transfer for cooling the exhaust valve. 16. The apparatus according to claim 8, further comprising an exhaust channel 234 for communicating the combustion cylinder 209 with the exhaust cylinder 210, the exhaust channel being thermally insulated and having a smooth wall. The exhaust channel is designed to guide the exhaust gas from the combustion cylinder into the exhaust cylinder so as to create an axial turbulent flow close to laminar flow in the exhaust cylinder. Featured device. 17. In the device according to claim 16, the exhaust cylinder 210 has an annular exhaust opening 2.
36, characterized in that the exhaust opening is located approximately half the radius of the combustion cylinder and has a width equal to approximately half the radius. 18. The device according to claim 1, wherein the device is a four-stroke automatic cycle engine, and the piston-cylinder device 301/
302 and the inlet port to the cylinder,
The inlet port 314 extends all the way around the head of the cylinder and has a height that is less than about half the radius of the cylinder and whose height is approximately equal to the stroke length divided by the compression ratio. , further comprising a sleeve 107 movable across the inlet port between an open position and a closed position. 19. The apparatus according to claim 18, further comprising passage means 320 for imparting a circumferential velocity component to the air and supplying the air to the inlet port, the velocity component imparting a radial velocity component to the inlet port. An ottocycle engine characterized in that it is of the order of one to two times the speed and that an axial vortex is therefore created in the cylinder. 20. The device according to claim 19, further comprising means for injecting fuel into the cylinder in close proximity to its axis for laminar charging, thereby reducing heat flow. 1. An Otto cycle engine characterized in that at the same time the amount of contamination from relatively cold unused gas that has come into contact with the cylinder wall is reduced. 21. The device according to any one of claims 18, 19, and 20, further comprising a spark plug 318 disposed close to the fuel injection point, the spark plug being in contact with the head surface. An automatic cycle engine characterized in that it has electrode surfaces that are substantially coplanar, thereby reducing axial overflow and surface friction with the head surface. 22. The device according to any one of claims 18, 19 and 20, further comprising an exhaust valve 319 having a combustion side surface, the combustion side surface being smooth and having a head surface. are substantially coplanar, thereby minimizing friction with the gas flow within the cylinder, and the exhaust valve is located approximately half the radius of the cylinder;
Therefore, the Otsuto cycle engine is characterized in that the outflow of exhaust gas is promoted. 23. The device according to claim 1, wherein the device is a gas compressor for supplying adiabatically compressed air or gas, comprising a piston-cylinder device 91 and a cylinder. It consists of an inlet port 96 extending 360° around the upper end, a sleeve valve 95 movable across the inlet port, and means 101 for introducing air into the inlet port. Upon introduction, the air is given a large velocity component in the circumferential direction of the cylinder, creating a nearly laminar axial turbulence in the injected air or gas, which reduces the interaction between the air or gas and the cylinder wall. at least one reed valve 194 located at the head of the cylinder to remove gas or air in the direction of overflow;
A device consisting of a passage 94 in the head of the cylinder for delivering insulated compressed air or gas. 24. The device according to claim 1, wherein the device is an articulated vane device for substantially completely adiabatic compression or substantially completely adiabatic expansion of a gas, the device comprising a casing 72 and an articulated vane. a rotor 67 that supports 63, 64, and 65;
Compression formed by rotor and casing -
Consisting of an injection passage 74 leading to the expansion region and a discharge passage 75 leading from the compression-expansion region, the longitudinal cross-sectional areas of the injection and discharge passages are approximately equal to the speed of the vanes of the rotor. a near laminar flow at a velocity of A device that does this. 25. The device according to claim 24, in which the casing wall in contact with the gas is made of a material of low thermal conductivity, which reduces the heat flow in the casing wall and reduces the heat flow in the wall. Articulating vane device characterized in that thermal short circuits of the are minimized. 26. The apparatus according to claim 24, wherein the apparatus is a Brayton cycle heat pump, and the compressor and expander are
26. A device characterized in that it consists of an articulated vane device according to paragraphs 1 or 25. 27. The apparatus of claim 25, further comprising means including an insulated shaft joint and a housing insulator for thermally insulating the compressor and the expander; A device characterized in that thermal short circuits with the expander are minimized.