EP3622167B1 - Machine à gaz chaud à piston étagé - Google Patents

Machine à gaz chaud à piston étagé Download PDF

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Publication number
EP3622167B1
EP3622167B1 EP18722503.2A EP18722503A EP3622167B1 EP 3622167 B1 EP3622167 B1 EP 3622167B1 EP 18722503 A EP18722503 A EP 18722503A EP 3622167 B1 EP3622167 B1 EP 3622167B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
hot gas
gas engine
working
Prior art date
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EP18722503.2A
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German (de)
English (en)
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EP3622167C0 (fr
EP3622167A1 (fr
Inventor
Josef Frauscher
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Frauscher Holding GmbH
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Frauscher Holding GmbH
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Priority to EP23177758.2A priority Critical patent/EP4273393A3/fr
Publication of EP3622167A1 publication Critical patent/EP3622167A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • F02G2243/04—Crank-connecting-rod drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/40—Piston assemblies

Definitions

  • the present description relates to a hot gas engine with at least one double-acting displacement or working piston, for example a Stirling engine.
  • Stirling engines are probably the best known representatives of hot gas engines. If air is used as the working gas, the term hot-air machine is also used. Some such machines can be operated both as an external combustion engine and as a heat pump or chiller. Other well-known types of hot-gas engines are, for example, the Manson engine, the Ericsson engine, etc.
  • Stirling engine is used as a collective term for different hot-gas engines with a closed gas cycle (i.e. the working gas circulates exclusively inside the engine without contact with the surrounding atmosphere). used.
  • Three basic types of Stirling engines can be distinguished, which are referred to as alpha type, beta type and gamma type, whereby in turn different variants of the individual types have become known, sometimes under special names (e.g.
  • the hot-gas machine has a transmission with a connecting rod, a cylinder and a tube, which is at least partially arranged inside the cylinder.
  • One end of an at least partially hollow differential piston is positioned between the tube and the inner wall of the cylinder to form an annular cylinder space.
  • the connecting rod passes through the tube and is articulated to the differential piston inside the latter.
  • the hot-gas machine has a gear that is arranged in a gear space in which ambient pressure prevails.
  • the Stirling engine further includes a double-acting stepped piston disposed in a cylinder and having a larger diameter first section and a smaller diameter second section.
  • the stepped piston is at least partially hollow and has a piston rod inside which is mechanically coupled to the transmission.
  • the gear-facing second section of the stepped piston opens into a buffer space for the working gas of the Stirling engine, and inside the At least part of a sealing device is arranged on the stepped piston, which seals a passage of the piston rod between the buffer space and the gear space.
  • the examples described here mainly concern different types of Stirling engines.
  • the concepts described here (especially the die
  • the basic shape of the piston and its mechanical coupling to the transmission can be transferred at least in part to other types of hot-gas machines.
  • the designs of cylinder and piston explained using the various examples described here can be combined as desired in multi-cylinder machines.
  • 1 shows an example of the structure of a gamma-type Stirling machine.
  • the mode of operation of such a gamma-type Stirling engine is based on the fact that, for example, a displacement piston VK actuated by a crank mechanism (e.g.
  • crankshaft 10 and connecting rod 12 in a displacement cylinder VZ alternately transfers the working gas via a heat exchanger (heater E), regenerator R and cooler K between a "hot" side H and a "cool” side C of the displacement cylinder VZ transported back and forth.
  • the resulting pressure changes act on a working piston AK (on the right in 1 ), which transmits the resulting forces to the crankshaft 10 and generates a torque there.
  • the piston rod 13 of the displacement piston VK is led out of the displacement cylinder VZ via a passage (seal 30) and is connected to the crankshaft 10 via a short connecting rod 12.
  • the working piston AK trailing, for example, 90 degrees behind the displacement piston VK is connected via a line L to the displacement cylinder VZ.
  • Devices for guiding the connecting rod head in order to absorb the lateral force are not shown.
  • Various examples are in the publications WO 2009/082997A2 and DE 102 29 442 A1 described.
  • Both examples 1 and 2 have in common that the piston (displacement piston VK in the gamma type, cf. 1 , or the working piston AK in the double-acting alpha type, cf. 2 ) within a gas-tight cylinder filled with working gas (displacement cylinder VZ in the gamma type or working cylinder AZ in the double-acting alpha type).
  • the piston force is transmitted via a piston rod 13 attached to the piston VK or AK.
  • the piston rod 13 is guided through an opening at the cool end C of the cylinder VZ or AZ and sealed (see 1 , seal 30).
  • the outwardly guided end of the piston rod 13 can be connected to a connecting rod of a crank mechanism (for example connecting rod 12, crankshaft 10) which specifies the oscillating movements.
  • a crank mechanism for example connecting rod 12, crankshaft 10.
  • piston rod refers to a rod that is rigidly (not pivotably) connected to the respective piston, so that the piston rod can only move along the longitudinal axis S of the piston.
  • a connecting rod is pivoted relative to the longitudinal axis S of the piston.
  • the piston rod 13 takes off in the area of the bushing from the cylinder VZ (cf. 1 ) or AZ (cf. 2 ) those lateral forces which are caused by the inclined position of the connecting rod 12.
  • These lateral forces can be problematic with regard to the storage of the piston rod 13.
  • additional longitudinal guides for example crosshead guides—are installed in order to relieve the piston rod 13.
  • Such machine elements can lead to an increase in the overall height of the entire arrangement, which is why relatively short connecting rods 12 are usually used.
  • it can be unfavorable for the thermodynamic process of the Stirling engine if the piston movement deviates greatly from a sinusoidal curve.
  • crank mechanism is generally regarded as a mechanical functional unit which is designed to convert an oscillating translational movement of the pistons into a rotation.
  • a crank mechanism therefore does not necessarily have to be configured as in the examples according to FIG 1 or 2 , in which the connecting rods are deflected directly on a crankshaft.
  • the crank drive can have a Ross-Yoke mechanism.
  • a wobble plate may be connected to the shaft to convert the oscillating movement of the pistons into rotation.
  • Figure 1 shows an improved example of a gamma-type Stirling engine not according to the invention.
  • the example shown is essentially the same as the example below 1 , but the displacement piston VK has at its lower end (on the "cool" side C) instead of the piston rod 13 a hollow cylinder (tube) with an outside diameter d that is smaller than the outside diameter D of the upper part of the piston VK.
  • the piston VK is a differential piston designed as a (double-acting) stepped piston, which has a first section S 1 with a larger diameter D and a second section S 2 with a smaller diameter d.
  • the displacement piston VK designed as a stepped piston is at least partially hollow, and the hollow cylinder with a diameter d (section S 2 of the stepped piston) allows a passage for a sufficiently long connecting rod 12, the upper end of which is inside the stepped piston VK in the area of the larger diameter D (section S 1 of the stepped piston VK) is articulated on this.
  • the connecting rod 12 is therefore not connected to the piston VK at the lower end thereof, but extends far into the piston VK up to the section S 1 .
  • the connecting rod 12 can be made significantly longer as a result.
  • the area of the larger diameter D (section S 1 ) is clearly delimited in the non-inventive examples shown here and is (in the axial direction) above the step in the stepped piston at which the diameter widens from the smaller value d to the larger value D. If the transition from the smaller Diameter d to the larger diameter D does not take place in one step, but gradually, the area S 1 of the larger diameter is that (axial) cylinder section in which the diameter is larger than the small diameter d.
  • the pivot axis of the connecting rod 12 is denoted by A.
  • the connecting rod 12 can be articulated by means of different types of bearings in the piston.
  • a cylindrical slide bearing or roller bearing can be used.
  • a spherical joint bearing can be used. This can be arranged at the upper end of the connecting rod 12, for example.
  • the connecting rod is articulated in the first section S 1 (in which the diameter of the piston VK is larger than the small diameter d) of the stepped piston. This means that the pivot axis A of the connecting rod 12 is in the section S 1 .
  • a guide element F sliding surfaces
  • the piston force perpendicular to the piston center axis S is relatively low. Since this force is divided between the two guide surfaces F, there is an extremely low specific surface load on the sliding surfaces.
  • This arrangement allows the use of oil-free sliding elements as guide elements F, for example made of PTFE-graphite compounds with a low coefficient of friction.
  • the two sliding elements F also ensure precise linear guidance of the piston VK and prevent tilting movements that can occur with one-piece or closely spaced guide elements.
  • the diameter of the stepped piston VK can be dimensioned, for example, in such a way that the smaller diameter d of the stepped piston (outer diameter of the hollow cylinder) is about 70% of the larger diameter D of the stepped piston, corresponding to a surface division of the circular ring surface that is formed ((D 2 -d 2 ) ⁇ ⁇ /4) in relation to the circular area defined by the hollow cylinder (d 2 ⁇ /4) of around 1:1.
  • the area below the stage of the stage cylinder is therefore the "cool side" C of the stepped piston VK or the displacement cylinder VZ.
  • the cylinder volume in the displacement cylinder VZ above the stepped piston VK is filled with hot working gas during operation.
  • the area above the first section S1 of the stepped piston VK is therefore the "hot side" H.
  • a sealing ring 20 is arranged in the second section S 2 of the stepped piston VK.
  • another sealing ring 21 is arranged in the first section S 1 of the stepped piston VK.
  • the sealing ring 21 seals the hot side H against the cool side C of the displacement cylinder VZ
  • the sealing ring 20 seals the cool side C of the displacement cylinder VZ against a buffer space P below (cf. also 4 , where the stepped piston there is a working piston of a double-acting Alpha machine and piston rings are provided as sealing rings).
  • the hot side H and the cool side C of the displacement cylinder VZ are connected via heater E, regenerator R and cooler K, which is why the pressure on both sides is essentially the same.
  • the sealing ring 21 essentially serves to prevent process gas from flowing through (leakage) between the stepped piston VK and the inner wall of the cylinder.
  • the sealing ring 20 must seal the interior of the displacement cylinder VZ against the buffer space P, which is why the sealing ring 20 is generally designed as a piston ring.
  • the seal 22 arranged on the working piston AK must seal the working space of the working cylinder AZ against a buffer space P located underneath, which is why the seal 22 is generally also designed as a piston ring.
  • piston guides F and piston seals 20, 21 are mounted on or in the piston as elements that move with the piston, or are arranged on the inside of the cylinder as fixed, non-moving elements are and slide along the piston skirt.
  • Exemplary 3 the piston ring 21 and the guide element F are arranged in the area of the large diameter D of the stepped piston and the elements accordingly slide on the inner wall of the cylinder VZ.
  • the guide element F and the piston ring 20 are fixedly attached to the inside of the cylinder.
  • FIG. 4 1 shows an improved example of a piston-cylinder unit, not according to the invention, of a double-acting Alpha-type Stirling engine.
  • This piston-cylinder unit e.g. four as in the example 2
  • the working pistons AK, AK ⁇ have at their lower end (on the "cool" side C) instead of the piston rods 13 each a hollow cylinder (tube) with a diameter d, which is smaller than the diameter D of the upper part of the respective piston AK, AK'.
  • the working pistons AK in the present example can be constructed essentially the same as the displacement piston VK, which is designed as a stepped piston, in the previous example 3 , and reference is made to the associated description above.
  • the functioning of the two motor types in 3 and 4 is different (see above description of the 1 and 2 ).
  • the working pistons AK designed as stepped pistons can differ from the displacement piston VK designed as stepped pistons from the previous example, however, for example in the seals.
  • the sealing rings 20 and 21 can both be designed as (pressure-loaded) piston rings, since they have to withstand the pressure difference between the hot side H (expansion space) and the cool side C (compression space) of the working cylinders AZ, AZ ⁇ .
  • oil scraper elements A oil scraper rings
  • section S 2 small piston diameter
  • a low lambda value (r K /l P ) enables an almost sinusoidal piston movement accompanied by low second-order mass forces and a favorable course of the gas mass flow through heater E, regenerator R and cooler K.
  • the working piston AK approximately in the middle position, which is why no offset is visible on the crankshaft 10.
  • FIG 12 shows another example of a gamma-type Stirling engine, not in accordance with the invention, which is constructed similarly to and as the example shown in FIG 3 .
  • the working piston AK is designed as a single-acting stepped piston.
  • the stepped piston has a first section S 1 'with a larger outside diameter D' and a second section S 2 'with a smaller outside diameter d ⁇ .
  • the working space AR of the working cylinder AZ is the annular space that is formed between the inner wall of the cylinder and the second section S 2 ′ of the stepped piston.
  • the connecting line L between the cool side C of the displacement cylinder VZ and the working cylinder consequently opens into the aforementioned annular space (cylinder space AR).
  • the working piston AK has a continuous opening along its longitudinal axis, so that a pressure equalization can take place between the buffer space P and the cylinder space P ⁇ on the end face of the working piston AK.
  • the arrows drawn in, which run through the working piston, indicate that a gas flow is possible through the opening in the working piston AK, which enables the mentioned pressure equalization.
  • the connecting rod 12 coupled to the working piston AK is—similar to the displacement piston VK—articulated inside the working piston AK in the region S 1 ′ of the larger diameter D′.
  • the sealing ring 23 seals the cylinder space AR (working space/annular space) of the working cylinder AZ toward the buffer space P.
  • the sealing ring 22 seals off the working space AR from the front cylinder space P ⁇ , in which the same pressure prevails as in the buffer space P.
  • Both seals 22, 23 can be designed as piston rings.
  • the description is applied 3 referred. Compared to the example from 3 enables the variant figure 5 a shorter line L between displacement cylinder VZ and working cylinder AZ and consequently a smaller dead space, with a comparatively long connecting rod 11.
  • Figure 12 shows another example of a gamma-type Stirling engine, not according to the invention, which differs from the previous example as far as the function and design of the pistons are concerned figure 5 is very similar.
  • the main difference between the examples from figure 5 and 6 consists in the position of the cylinders relative to each other.
  • the longitudinal axes S and S' of displacement cylinder VZ and working cylinder AZ are parallel, whereas in the previous example the longitudinal axes S and S' are essentially parallel enclose a right angle and thus form a V-engine.
  • the parallel arrangement of the cylinders enables an even shorter line connection L between displacement cylinder VZ and working cylinder AZ and consequently an even smaller dead space.
  • the description to the 3 and 5 referred.
  • crank mechanism according to 7 has a so-called Ross-Yoke mechanism.
  • the connecting rods 11 and 12 do not directly connect the pistons to the crankshaft 10, but the ends of the connecting rods 11 and 12 facing away from the pistons are articulated on a rocker 14 (yoke, yoke ), which the oscillating movement of the pistons on the Crankshaft 10 transmits.
  • the rocker 14 is additionally mounted on the transmission housing via a further connecting rod 13 .
  • Such a Ross-Yoke mechanism is known per se and is therefore not explained in more detail.
  • the example is off 7 practically the same structure as the example 6 and reference is made to the above explanations.
  • FIG. 8 shows a variant of the example 4 , wherein four or more cylinder units (working cylinder AZ; working cylinder AZ ⁇ ) drive an output shaft 10 via a swash plate gear.
  • the sectional view shown shows two (in relation to the transmission) oppositely arranged cylinder units.
  • the "crank" of the shaft 10 is formed by the slanted swash plate, on which the connecting rods 11 and 12 are articulated (eg by means of spherical bearings).
  • Swash plate gears are known per se and are therefore not explained further here.
  • FIG. 12 is a schematic plan view showing how such a motor can be constructed.
  • Two cylinders AZ and AZ ⁇ each are arranged in planes E 1 and E 2 , with the cylinder longitudinal axes lying in planes E 1 and E 2 , which are perpendicular to one another (which does not necessarily have to be the case).
  • a cylinder AZ in the first level E 1 is connected (via heater E, regenerator R and cooler K) to a corresponding cylinder AZ in the second level E 2 .
  • This in turn is connected to the second cylinder AZ ⁇ in the first level, etc.
  • a formed four-cylinder engine In this way, a formed four-cylinder engine.
  • constructions with more than four cylinders are also possible.
  • a stepped piston as described in the above examples of a gamma-type and (double-acting) alpha-type Stirling engine can also be used in a beta-type Stirling engine.
  • An example of a beta machine is in 9 shown. Similar to a gamma machine (cf. 3 ) a beta machine has a displacement piston VK and a working piston AK. Unlike in the example 3 However, the displacement piston VK and the working piston AK move in the same cylinder Z. The displacement piston VK is as in the gamma machine (cf.
  • the working piston AK is designed as a ring-shaped piston (annular piston) and moves coaxially to the displacement piston VK.
  • the outer diameter of the annular piston AK is denoted by D A and the inner diameter of the annular piston corresponds (apart from the piston clearance) to the small diameter d of the stepped piston VK.
  • the section S 2 of the stepped piston VK with the smaller diameter d is passed through the annular piston AK.
  • the sealing rings can be arranged on the annular piston AK, one sealing on the outside (seal 22a) and one sealing on the inside (seal 22b).
  • the guide sliding surfaces F can be arranged on the annular piston AK (inside and outside).
  • other designs are also possible in this regard, for example the arrangement of the piston ring 22b on the stepped piston VK in section S 2 or the arrangement of the guide sliding surfaces F on the cylinder Z.
  • the working piston AK designed as an annular piston, is shown coupled to the crankshaft 10 via two connecting rods 11a, 11b arranged symmetrically to the central axis S.
  • the cylinder Z has a stepped design, which allows a larger outside diameter D A of the annular piston AK compared to the outside diameter D of section S 1 of the stepped piston VK.
  • the piston surface annular surface (D A 2 ⁇ d 2 ) ⁇ /4) gained by the larger outside diameter D A can be used to correspondingly reduce the piston stroke of the working piston.
  • a similarly favorable lambda can be achieved as with the connecting rod 12 of the displacement piston VK.
  • the piston areas (annular areas) of stepped pistons (displacement pistons VK) and ring pistons (working pistons AK) and the associated piston strokes can be selected in such a way that the ratio of the stroke volumes is approx. 1:1.
  • the displacement piston VK approximately halfway, which is why no offset is visible on the crankshaft 10.
  • the displacement piston VK leads the working piston AK by about 90 degrees (in relation to the angular position of the crankshaft 10).
  • the crankshaft 10 is as per the example 3 located in the buffer space P.
  • FIG. 10 shows a variant of the example not according to the invention 3 .
  • the examples from 3 and 10 are functionally and kinematically equivalent.
  • the two examples differ only in the structure of the displacement cylinder VZ and the displacement piston VK arranged therein, with the piston stroke and cylinder volume being able to be the same in both variants.
  • a slightly differently designed differential piston is used instead of a stepped piston.
  • the differential piston is guided coaxially to a tube R, which protrudes into the interior of the displacement cylinder VZ (and into the differential piston).
  • the differential piston is (at least partially) hollow and arranged between the tube R and the inner wall of the cylinder, so that an annular cylinder space (annular space) is created below the differential piston between the lateral surface of the tube R and the inner surface of the cylinder, as is also the case when using a stepped piston of the case would be.
  • guide can be arranged on the outside of the differential piston or on the inner wall of the cylinder.
  • the tube R is rigidly connected to the motor housing (e.g. screwed) and the seal 20 seals the annular space (i.e.
  • the example from 11 is a modification of the example figure 5 . Both examples are functionally and kinematically equivalent.
  • displacement cylinder VZ and displacement piston VK have the same structure as in the previous example 10 .
  • This design replaces the stepped piston figure 5 .
  • the working piston AK is according to 11 designed as a ring piston, which is also arranged between a tube R', which protrudes into the working piston AK, and is sealed towards the lateral surface of a tube R' (see, for example, piston ring 23).
  • the tube R ⁇ is - analogously to the tube R in the displacement cylinder VZ - rigidly connected to the motor housing and, as mentioned, protrudes into the working cylinder AZ.
  • the working piston AK is hollow and allows pressure equalization between the buffer space P and the cylinder space P ⁇ on the front side of the working piston AK.
  • the sealing ring 22 is essentially the same as in figure 5 .
  • the sealing ring 23 seals between the working piston AK and the pipe R ⁇ .
  • the example from 12 is a modification of the example 4 , where the stepped piston from 4 was replaced by a differential piston.
  • Working cylinder AZ and working piston AK are essentially constructed in the same way as displacement piston VK and displacement cylinder in 11 and reference is made to the above explanations.
  • FIG. 13 shows an example of a hot gas engine which has become known as the Manson engine. Since the working gas does not circulate in a closed circuit (there is a connection to the buffer chamber or the atmosphere via a valve), the Manson engine shown is not, strictly speaking, a Stirling engine.
  • the stepped piston functions equally as a displacement and working piston and is denoted by AK in the present example.
  • a valve V is opened for a short time, for example via a mechanical valve control, which connects the annular cylinder space (between the narrower section of the stepped piston and the inner wall of the cylinder AZ) with the ambient pressure in the buffer space P.
  • the mechanical valve control can, for example, comprise a lever 41 which is pivotably mounted about a pivot point 40 and which is tilted by means of cams 44a and 44b arranged on the shaft 10.
  • the lever 41 transmits this tilting movement to the valve tappet of the valve V against the restoring force of a spring 42.
  • a roller 43 which rolls on the shaft 10 can be attached to the lower end of the lever 41.
  • the structure and function of a Manson engine are known per se (e.g. from the publications DE 199 04 269 A1 and GB 2554458A ) and are therefore not explained further here.
  • the gear (cf. 14 , gear room G) is not used as a buffer room, but works under atmospheric pressure.
  • the buffer space (which is under the pressure of the working gas) must be sealed off from the gear space, which is done with a piston rod, for example, using special sealing elements.
  • a sealing element is known per se.
  • Such an example is in 14 shown.
  • 14 shows a piston-cylinder unit of a double-acting Alpha-type Stirling engine.
  • Several of these piston-cylinder units e.g. four as in the example from 2
  • a double-acting stepped piston is provided as the working piston AK according to the example shown.
  • the stepped piston AK has a first section S 1 with a larger diameter D and a second section S 2 with a smaller diameter d, the stepped piston AK being at least partially (at least in the area of the second section S 2 with a diameter d ) is hollow.
  • the stepped piston AK is not directly connected to a connecting rod of a crank mechanism, but has (as shown in the example 2 ) a piston rod 13 on.
  • the guiding and sealing elements of the piston rod 13 can be arranged within the piston shaft of the stepped piston facing the crank mechanism (section S 2 with external diameter d).
  • the piston rod 13 can be connected to a crankshaft, for example via a connecting rod, in the same or similar manner as in the example from FIG 2 (with the associated disadvantages).
  • the crank mechanism (e.g. crankshaft 10, cf. Eg 2 ) facing second section S 2 of the stepped piston AK opens into a buffer space P for the working gas of the Stirling engine.
  • a partition wall 33 separates the crankcase between the buffer space P and the transmission space G, in which the transmission is located (in 14 not shown, cf. 7 and 8th ).
  • the piston rod 13 connected to the stepped piston AK is guided through an opening in the partition wall 33 .
  • the seal comprises a sleeve 31 which is rigidly connected to the partition wall 33 and through which the piston rod 13 runs.
  • An annular sealing element 35 is arranged inside the sleeve 31 around the piston rod 13 .
  • the sealing element 35 is clamped between two conical disks 34 along the longitudinal axis S of the piston rod 13 (cylinder axis S).
  • the prestressing force required for this is generated by a spring 32 which can be arranged inside the sleeve 31 around the piston rod 13 (e.g. in the case of a spiral spring) and which exerts a force on the discs 34 along the longitudinal axis S of the piston rod 13.
  • a spring 32 which can be arranged inside the sleeve 31 around the piston rod 13 (e.g. in the case of a spiral spring) and which exerts a force on the discs 34 along the longitudinal axis S of the piston rod 13.
  • the crank mechanism is arranged in the buffer space.
  • the present example allows a separation of buffer space P and gear space G, so that the gear can work under ambient pressure.
  • a construction according to 2 theoretically would not require buffer space.
  • a separate buffer space P can be advantageous, since otherwise the lower piston section S 2 would generate excessive pressure fluctuations and consequently excessive forces

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Fluid-Damping Devices (AREA)

Claims (11)

  1. Machine à gaz chaud comprenant :
    une transmission (10) avec une bielle (12) ;
    un cylindre (VZ ; AZ ; Z) ; et
    un piston différentiel (VK ; AK) agencé dans le cylindre (VZ ; AZ ; Z), dans laquelle le cylindre (VZ ; AZ ; Z) et le piston différentiel (VK ; AK) sont conçus de telle sorte qu'une chambre de cylindre annulaire est formée dans le cylindre, dans laquelle le piston différentiel (VK ; AK) est au moins partiellement creux, et la bielle (12) est articulée à l'intérieur du piston différentiel (VK ; AK) en une position telle que la chambre de cylindre annulaire s'étend autour de la bielle (12) ; et
    un tube (R, R') qui fait saillie dans le cylindre (VZ ; AZ), dans laquelle une extrémité du piston différentiel (VK ; AK) est agencée entre le tube (R, R') et une paroi intérieure du cylindre (VZ ; AZ), caractérisée en ce qu'une première bague d'étanchéité (20) est agencée entre le tube (R, R') et une paroi intérieure du piston différentiel (VK ; AK).
  2. Machine à gaz chaud selon la revendication 1,
    dans laquelle le tube (R, R') fait saillie dans le cylindre (VZ ; AZ) au point de faire également saillie à l'intérieur du piston différentiel (VK ; AK) lorsque celui-ci est à son point mort haut.
  3. Machine à gaz chaud selon la revendication 1 ou 2,
    dans laquelle le tube (R, R'), le piston différentiel (VK ; AK) et le cylindre (VZ ; AZ) sont agencés coaxialement les uns par rapport aux autres.
  4. Machine à gaz chaud selon l'une des revendications 1 à 3, dans laquelle le tube (R, R') est immobile par rapport au cylindre (VZ ; AZ).
  5. Machine à gaz chaud selon l'une des revendications 1 à 4, dans laquelle une seconde bague d'étanchéité (21) est agencée entre le piston différentiel (VK ; AK) et la paroi intérieure du cylindre (VZ ; AZ ; Z), et dans laquelle la chambre de cylindre annulaire est étanchéifiée par rapport à un espace tampon (P) situé sous le cylindre (VZ ; AZ ; Z) au moyen de la première bague d'étanchéité (20).
  6. Machine à gaz chaud selon l'une des revendications 1 à 5, comprenant en outre :
    un autre piston (AK) agencé dans un autre cylindre (AZ), qui est couplé à la transmission au moyen d'une autre bielle (11).
  7. Machine à gaz chaud selon la revendication 6,
    dans laquelle une chambre de cylindre annulaire est formée à la fois dans le cylindre (VZ) et dans l'autre cylindre (AZ), et dans laquelle la chambre de cylindre annulaire du cylindre (VZ) et la chambre de cylindre annulaire de l'autre cylindre (AZ) sont reliées par une conduite (L).
  8. Machine à gaz chaud selon l'une des revendications 1 à 7, dans laquelle la bielle (12) est articulée à l'intérieur du piston différentiel (VK ; AK) au moyen d'un palier lisse ou d'un palier à roulement ou au moyen d'un palier d'articulation sphérique.
  9. Machine à gaz chaud selon l'une des revendications 1 à 8, dans la mesure où elles se rapportent à la revendication 5, dans laquelle le tuyau (R) débouche dans un espace tampon (P) pour un gaz process de la machine à gaz chaud.
  10. Machine à gaz chaud selon la revendication 9,
    dans laquelle la transmission (10) est agencée dans l'espace tampon (P) .
  11. Machine à gaz chaud selon l'une des revendications 1 à 10, dans laquelle la machine à gaz chaud est un moteur Stirling.
EP18722503.2A 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé Active EP3622167B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP23177758.2A EP4273393A3 (fr) 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017109967.0A DE102017109967B9 (de) 2017-05-09 2017-05-09 Stirlingmaschine mit stufenkolben
PCT/EP2018/061441 WO2018206412A1 (fr) 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP23177758.2A Division EP4273393A3 (fr) 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé

Publications (3)

Publication Number Publication Date
EP3622167A1 EP3622167A1 (fr) 2020-03-18
EP3622167B1 true EP3622167B1 (fr) 2023-06-07
EP3622167C0 EP3622167C0 (fr) 2023-06-07

Family

ID=62116448

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EP18722503.2A Active EP3622167B1 (fr) 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé
EP23177758.2A Pending EP4273393A3 (fr) 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP23177758.2A Pending EP4273393A3 (fr) 2017-05-09 2018-05-03 Machine à gaz chaud à piston étagé

Country Status (8)

Country Link
US (2) US11215139B2 (fr)
EP (2) EP3622167B1 (fr)
JP (1) JP7202365B2 (fr)
CA (1) CA3096716C (fr)
DE (1) DE102017109967B9 (fr)
ES (1) ES2951904T3 (fr)
PL (1) PL3622167T3 (fr)
WO (1) WO2018206412A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017109967B9 (de) * 2017-05-09 2020-05-07 Frauscher Holding Gmbh Stirlingmaschine mit stufenkolben

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Also Published As

Publication number Publication date
JP7202365B2 (ja) 2023-01-11
EP3622167C0 (fr) 2023-06-07
PL3622167T3 (pl) 2023-08-21
WO2018206412A1 (fr) 2018-11-15
US20220106926A1 (en) 2022-04-07
DE102017109967A1 (de) 2018-11-15
EP3622167A1 (fr) 2020-03-18
US20200408168A1 (en) 2020-12-31
ES2951904T3 (es) 2023-10-25
EP4273393A3 (fr) 2024-01-10
JP2020519813A (ja) 2020-07-02
CA3096716A1 (fr) 2018-11-15
EP4273393A2 (fr) 2023-11-08
DE102017109967B9 (de) 2020-05-07
DE102017109967B4 (de) 2018-11-29
US11725607B2 (en) 2023-08-15
CA3096716C (fr) 2023-12-19
US11215139B2 (en) 2022-01-04

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