WO2003069125A1 - Machine a detente - Google Patents

Machine a detente Download PDF

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Publication number
WO2003069125A1
WO2003069125A1 PCT/JP2003/000453 JP0300453W WO03069125A1 WO 2003069125 A1 WO2003069125 A1 WO 2003069125A1 JP 0300453 W JP0300453 W JP 0300453W WO 03069125 A1 WO03069125 A1 WO 03069125A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
expansion chamber
cylinder sleeve
oil
piston
Prior art date
Application number
PCT/JP2003/000453
Other languages
English (en)
Japanese (ja)
Inventor
Hiroyuki Makino
Makoto Uda
Original Assignee
Honda Giken Kogyo Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honda Giken Kogyo Kabushiki Kaisha filed Critical Honda Giken Kogyo Kabushiki Kaisha
Priority to US10/501,521 priority Critical patent/US20050158181A1/en
Publication of WO2003069125A1 publication Critical patent/WO2003069125A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block

Definitions

  • the present invention comprises: a casing; a rotor rotatably supported by the casing; and an axial piston cylinder group arranged annularly around the mouth so as to surround the axis thereof.
  • the present invention relates to an expander that rotates a rotor by supplying high-temperature, high-pressure steam to an expansion chamber defined between a piston and a cylinder sleeve via a rotary valve.
  • Such an expander has already been proposed by the applicant of the present invention in Japanese Patent Application No. 2001-61424.
  • This expander is used in a Rankine cycle device, and supplies and discharges steam to expansion chambers in a plurality of cylinder sleeves provided on a rotor via a rotary valve.
  • the cylinder sleeve is fitted and held in a bottomed cylindrical recess formed from one end face of the rotor, and the expansion chamber has an inner surface of the cylinder sleeve, a bottom surface of the recess of the rotor, and a piston fitted to the cylinder sleeve.
  • the present invention has been made in view of the above circumstances, and has as its object to minimize heat loss, that is, heat loss, from an expansion chamber of an axial piston cylinder group of an expander.
  • a casing, a mouth rotatably supported by the casing, and an annular arrangement are arranged on a rotor so as to surround the axis thereof.
  • an insulated space is provided at a position facing the expansion chamber of the rotor.
  • the expansion chamber is partitioned between the pistons and the cylinder sleeves of the axial piston cylinder group provided at the rotor of the expander, and the heat insulating space is provided at a position facing the expansion chamber of the rotor.
  • the heat of the supplied high-temperature and high-pressure steam can be minimized from escaping in the evening, and a decrease in thermal efficiency can be prevented.
  • the rotor further includes a first opening and closing body for holding a separate cylinder sleeve, and a second housing for housing a rotary valve.
  • the two rotor halves are joined in the axial direction, and the expansion chamber is sealed by interposing a metal gasket between the end surfaces of the first rotor half and the cylinder sleeve and the end surface of the second rotor half.
  • the material of the cylinder sleeve can be selected in consideration of thermal conductivity, heat resistance, strength, wear resistance, etc., without being limited by the material of the rotor. It is economical because only the damaged cylinder sleeve can be replaced.
  • the cylinder sleeve there is proposed an expander characterized in that a notch that exposes the outer peripheral surface of the is formed in the circumferential direction.
  • the heat mass of the rotor can be reduced to improve the thermal efficiency and reduce the weight.
  • Making the notch function as an insulating space thus, heat escape from the cylinder sleeve can be suppressed.
  • an expander characterized by covering the periphery of the cutout with a heat insulating cover in addition to the third aspect.
  • the sleeve support flanges 33, 34, 35 of the embodiment correspond to the first rotor half of the present invention
  • the rotor head 38 of the embodiment corresponds to the second rotor half of the present invention.
  • FIGS. 1 to 13 show an embodiment of the present invention.
  • FIG. 1 is a longitudinal sectional view of an expander
  • FIG. 2 is a sectional view taken along line 2-2 of FIG. 1
  • FIG. Fig. 4 is an enlarged view of part 4 of Fig. 1
  • Fig. 5 is an enlarged view of part five of Fig. 1
  • Fig. 6 is an exploded perspective view of the rotor
  • Fig. 7 is a sectional view taken along line 7-7 of Fig. 4
  • Fig. 8 is a sectional view taken along the line 8-8 in Fig. 4
  • Fig. 9 is an enlarged view of a part 9 in Fig. 4
  • Fig. 10 is a sectional view taken along the line 10-10 in Fig. 5
  • Fig. 11 is a sectional view taken along the line 11- 11 is a sectional view taken along line 11
  • FIG. 12 is a sectional view taken along line 12-2 of FIG. 5
  • FIG. 13 is a section
  • the expander M of this embodiment is used, for example, in a Rankine cycle device, and converts the heat energy and pressure energy of high-temperature high-pressure steam as a working medium into mechanical energy and outputs it.
  • the casing 11 of the expander M has a casing body 12, and a front cover 1 connected to a front opening of the casing body 12 by a plurality of ports 14 via a sealing member 13. 5, a rear cover 18 which is connected to a rear opening of the casing body 12 with a plurality of ports 17 via a sealing member 16 and a sealing member 19 which is connected to a lower opening of the casing body 12.
  • an oil pan 21 connected by a plurality of ports 20.
  • a rotor 22 arranged rotatably about an axis L extending in the front-rear direction at the center of the casing 11 has a front portion supported by a pole bearing 23 provided on a front cover 15 and a rear portion thereof. It is supported by a pole bearing 24 provided on the casing body 12.
  • a swash plate holder 28 fitted to the rear surface of the front cover 15 via two seal members 25, 26 and a dowel pin 27 is fixed with a plurality of ports 29.
  • the swash plate 31 is rotatably supported by the swash plate holder 28 via an angular pole bearing 30.
  • the axis of the swash plate 31 is inclined with respect to the axis L of the rotor 22, and the angle of inclination is fixed.
  • the shaft 22 has an output shaft 32 supported on the front cover 15 by the pole bearing 23 and a notch 5 7, 5 8 (FIGS. 9) three sleeve support flanges 3 3, 3 4, 3 5 integrally formed through the, and a plurality of ports 3 7 through the metal gasket 36 to the rear sleeve support flange 35.
  • the rotor head 38 supported on the casing body 12 by the pole bearings 24 and the three sleeve supporting flanges 33, 34, 35 are fitted from the front to form a plurality of ports.
  • a heat insulating cover 40 coupled to the sleeve support flange 33 on the front side at 39.
  • Five sleeve support holes 33a, 34a ..., 35a ... are formed on the three sleeve support flanges 33, 34, 35 at intervals of 72 degrees around the axis L. And five cylinder sleeves 41 are fitted into these sleeve support holes 33, ..., 34a-, 35a ... from behind.
  • a flange 41a is formed at the rear end of each cylinder sleeve 41, and this flange 41a is formed in a sleeve support hole 35a of a rear sleeve support flange 35a. When fitted to 5b, it comes into contact with the metal gasket 36 and is positioned in the axial direction (see Fig. 9).
  • a piston 42 is slidably fitted inside each cylinder sleeve 41, and a front end of the piston 42 comes into contact with a dimple 31a formed on the swash plate 31 and a piston 42 is formed.
  • a steam expansion chamber 43 is defined between the rear end and the rotor head 38.
  • An oil passage 3 2a extending on the axis L is formed inside the output shaft 3 2 integral with the rotor 22.
  • the front end of the oil passage 3 2a is branched in the radial direction to form the output shaft 3 2. It communicates with the outer circumferential groove 32b.
  • an oil passage closing member 45 is screwed into the inner periphery of the oil passage 32 a via a seal member 44, and in the vicinity thereof.
  • a plurality of oil holes 32 c extending radially outward from the oil passage 32 a of the output shaft 32 open on the outer peripheral surface of the output shaft 32.
  • the trochoid-type oil pump 49 is provided with an outer port 50 that rotatably fits into the recess 15 a, and an inner port that is fixed to the outer periphery of the output shaft 32 and mates with the outer rotor 50. 5 1
  • the internal space of the oil pan 21 communicates with the suction port 53 of the oil pump 49 through the oil pipe 52 and the oil passage 15b of the front cover 15 and the discharge port 54 of the oil pump 49. It communicates with the annular groove 3 2b of the output shaft 32 via the oil passage 15 c of the front cover 15.
  • the piston 42 which is slidably fitted to the cylinder sleeve 41, includes an end portion 61, an intermediate portion 62, and a top portion 63.
  • the end portion 61 is a member having a spherical portion 61 a that comes into contact with the dimple 31 a of the swash plate 31, and is joined to the tip of the intermediate portion 62 by welding.
  • the intermediate portion 62 is a cylindrical member having a large-capacity hollow space 62a, and has a small-diameter portion 62b having a slightly reduced diameter on the outer peripheral portion close to the top portion 63.
  • a plurality of oil holes 6 2 c are formed so as to penetrate therethrough in the radial direction, and a plurality of spiral oil grooves 6 2 d ... are formed on the outer peripheral portion in front of the small diameter portion 6 2 b. Is formed.
  • the top portion 63 facing the expansion chamber 43 is formed integrally with the intermediate portion 62, and a partition wall 63a formed on the inner surface thereof, and a lid member 6 fitted and welded to the rear end surface thereof.
  • a heat insulating space 65 (see FIG. 9) is formed between the first and second heat exchangers.
  • Two compression rings 66, 66 and one oil ring 67 are mounted on the outer periphery of the top part 63, and the oil ring groove 63b into which the oil ring 67 fits has a plurality of rings. It communicates with the hollow space 62a of the intermediate part 62 via the oil hole 63c.
  • the piston end part 61 and the middle part 62 are made of high carbon steel, and the top part 63 is made of stainless steel, of which the end part 61 is induction hardened and the middle part 62 is hardened. You. As a result, high endurance resistance of the end part 61 that comes into contact with the swash plate 31 with a large surface pressure, wear resistance of the intermediate part 62 that slides on the cylinder sleeve 41 under severe lubrication conditions, and expansion chamber 4 3 The heat and corrosion resistance of the top part 63 exposed to high temperature and high pressure is satisfied.
  • An annular groove 41b (see FIGS. 6 and 9) is formed on the outer periphery of the intermediate portion of the cylinder sleeve 41, and a plurality of oil holes 41c are formed in the annular groove 41b. Regardless of the mounting position of the cylinder sleeve 41 in the rotation direction, the hole 32 formed in the output shaft 32 and the sleeve support flange 34 formed in the center of the rotor 22 are formed.
  • the holes 3 4 b ′ ′′ (see FIGS. 4 and 6) communicate with the annular groove 4 1 b.
  • An annular lid member 6 9 is provided on the front or expansion chamber 4 3... side of the rotor head 3 8 connected to the rear surface of the sleeve support flange 3 3 on the front side of the mouth 22 by a port 37. It is welded, and an annular heat insulating space 70 (see FIG. 9) is defined on the back surface or the rear surface of the lid member 69.
  • the rotor head 38 is positioned in the rotational direction with respect to the rear sleeve support flange 35 by the knock pin 55.
  • the five cylinder sleeves 41 and the five pistons 42 constitute an axial piston cylinder group 56 of the present invention.
  • the rotary valve 71 arranged along the axis L of the mouth 22 has a valve body 72, a fixed-side valve plate 73, and a movable-side valve plate. 7 and 4.
  • the movable-side valve plate 74 is fixed to the rear surface of the rotor 22 by a port 76 that is screwed to the oil passage closing member 45 (see FIG. 4) while being positioned in the rotational direction by the knock pin 75. .
  • the port 76 also has a function of fixing the rotor head 38 to the output shaft 32.
  • the fixed-side valve plate 73 which comes into contact with the movable-side valve plate 74 via the flat sliding surface 77, has a single plate at the center of the front surface of the valve body 72. It is fixed by a port 78 and is fixed to an outer peripheral portion of the valve body 72 by an annular fixing ring 79 and a plurality of ports 80. At this time, the stepped portion 79 a formed on the inner periphery of the fixing ring 79 is press-fitted so as to be fitted into the outer periphery of the fixed side valve plate 73, and the stepped portion formed on the outer periphery of the fixing ring 79.
  • the coaxiality of the fixed-side pulp plate 73 with respect to the valve body 72 is ensured by the inlay fitting of 79 b into the outer periphery of the valve body 72.
  • a knock pin 81 for positioning the fixed valve plate 73 in the rotation direction is disposed between the valve body 72 and the fixed valve plate 73. Therefore, when the mouth 22 rotates, the movable-side valve plate 74 and the fixed-side valve plate 73 rotate relative to each other while closely contacting each other on the sliding surface 77.
  • the fixed-side valve plate 73 and the movable-side valve plate 74 are made of a highly durable material such as carbon or ceramics, and the sliding surface 77 has heat resistance, lubricity, and corrosion resistance. The durability can be further improved by interposing or coating a material having heat resistance and wear resistance.
  • the valve body 72 made of stainless steel is a stepped cylindrical member having a large-diameter portion 72 a and a small-diameter portion 72 b, and the outer periphery of the large-diameter portion 72 a and the small-diameter portion 72 b.
  • a pin 84 implanted on the outer peripheral surface is fitted in a notch 18c formed in the rear cover 18 in the direction of the axis L to be positioned in the rotational direction.
  • a plurality of pre-opening springs 85 are supported on the rear cover 18 so as to surround the axis L, and the preload springs 85 are provided between the large-diameter portion 72a and the small-diameter portion 72b.
  • the valve body 72 which is pressed against the stepped portion 72c, is urged forward to bring the sliding surfaces 77 of the fixed valve plate 73 and the movable valve plate 74 into close contact.
  • a steam supply pipe 86 connected to the rear surface of the valve body 72 has a first steam passage P1 formed inside the valve body 72 and a second steam passage P formed in the fixed side valve plate 73. It communicates with the sliding surface 7 through 2. Further, a steam discharge chamber 88 sealed by a sealing member 87 is formed between the casing main body 12 and the rear cover 18 and the mouthpiece 22. The sliding surface 77 is formed via the sixth and seventh steam passages P 6 and P 7 formed in the valve body 72 and the fifth steam passage P 5 formed in the fixed valve plate 73. Communicate. A sealing member 89 surrounding the connection between the first and second steam passages PI and P2 and a fifth and sixth steam passage P 5 are provided on the mating surface between the valve body 72 and the fixed side valve plate 73. , And a sealing member 90 surrounding the connection portion of P6.
  • the both ends of the fourth steam passages P 4... are respectively connected to the third steam passages P 3... It communicates with the expansion chamber 43.
  • the portion of the second steam passage P2 that opens to the sliding surface 77 is circular, while the portion of the fifth steam passage P5 that opens to the sliding surface 77 is a circle centered on the axis L. It is formed in an arc shape.
  • the high-temperature and high-pressure steam generated by heating the water in the evaporator is supplied from the steam supply pipe 86 to the first steam passage P1 formed in the valve body 72 of the outlet valve 71, and the valve body 7 2 Through the second steam passage P 2 formed in the fixed-side valve plate 73 integral with the movable-side valve plate 74.
  • the second steam passage P2 opening to the sliding surface 77 is instantaneously connected to the corresponding third steam passage P3 formed in the movable valve plate 74 rotating integrally with the rotor 22 during a predetermined intake period.
  • the high-temperature and high-pressure steam is supplied from the third steam passage P3 to the expansion chamber 43 in the cylinder sleeve 41 via the fourth steam passage P4 formed in the rotor 22.
  • the oil pump 49 provided on the output shaft 32 is operated, and the oil pipe 52 from the oil pan 21, the oil passage 15 b of the front force par 15, and the suction port 5 3
  • the oil sucked through the outlet is discharged from the discharge port 54, the oil passage 15c of the front cover 15, the oil passage 3 2a of the output shaft 32, and the annular groove of the output shaft 32.
  • the hollow space 62 a communicates with the inside of the cylinder sleeve 41 via a plurality of oil holes 62 c penetrating through the intermediate portion 62 of the piston 42, and the inside of the cylinder sleeve 41 is
  • the plurality of oil holes 41c communicate with the annular groove 41b on the outer periphery of the cylinder sleeve 41.
  • the periphery of the annular groove 4 1 b is covered by the sleeve support flange 3 4 in the center of the mouth 22, but since the oil hole 3 4 b is formed in the sleeve support flange 34, the piston 4 2
  • the oil in the hollow space 62 a is urged radially outward by centrifugal force, discharged through the oil hole 34 b of the sleeve support flange 34 to the space 68 inside the heat insulating cover 40, and from there the heat insulating cover It is returned to the oil pan 21 through one 40 oil holes 40 a.
  • the oil radially outside the oil hole 34 b is It is held in the hollow space 62 a of the piston 42 by centrifugal force.
  • the oil held in the hollow space 62 a inside the piston 42 and the oil held in the small diameter portion 62 b on the outer periphery of the piston 42 increase the volume of the expansion chamber 43. Is supplied from the small diameter portion 62 b to the top portion 63 side during the expansion stroke, and is supplied from the small diameter portion 62 b to the end portion 61 side during the compression stroke in which the volume of the expansion chamber 43 decreases.
  • the entire area of the piston 42 in the axial direction can be reliably lubricated.
  • the oil flows inside the hollow space 6 2 a of the piston 42, so that the heat of the top part 63 exposed to high-temperature and high-pressure steam is transmitted to the low-temperature end part 61, and the temperature of the biston 42 is locally controlled. Can be avoided.
  • an insulating space 65 is provided between the top part 63 of the piston 42 facing the expansion chamber 43 and the intermediate part 62.
  • a heat insulating space 70 is also formed in the opening head 3 8 facing the expansion chamber 43, the piston 42 and the opening head 3 from the expansion chamber 43 are formed. This can contribute to improving the performance of the expander M by minimizing the heat escape to the expansion machine M.
  • a large volume hollow space 62a is formed inside the biston 42, not only can the weight of the piston 42 be reduced, but also the heat mass of the piston 42 is reduced to allow the piston 42 to move out of the expansion chamber 43. Can be more effectively reduced.
  • the expansion chamber 43 is sealed with a metal gasket 36 interposed between the rear sleeve support flange 35 and the rotor head 38, so that the expansion chamber 4 is interposed via a thick-walled annular sealing member.
  • wasteful polymer around the seal can be reduced, whereby a large volume ratio (expansion ratio) of the expander M can be secured, the thermal efficiency can be increased, and the output can be improved.
  • the cylinder sleeve 41 is constructed separately from the rotor 22, the cylinder sleeve 4 1 is not limited by the material of the mouth 22, but is considered in consideration of thermal conductivity, heat resistance, strength, wear resistance, etc. The material can be selected, and it is economical because only the worn / damaged cylinder sleeve 41 can be replaced.
  • the outer peripheral surface of the cylinder sleeve 41 is exposed from two notches 5 7, 58 formed in the outer peripheral surface of the rotor 22 in the circumferential direction, not only can the weight of the mouth 22 be reduced, but also the low The heat mass in the evening 22 can be reduced to improve the thermal efficiency, and the notches 5 7, 58 can function as heat insulating spaces to make the cylinder sleeve 4 1 From the heat. Further, since the outer peripheral portion of the mouth 22 is covered with the heat insulating cover 40, the heat escape from the cylinder sleeve 41 can be more effectively suppressed.
  • the steam valve 7 1 supplies steam to the axial piston cylinder group 56 through a flat sliding surface 7 7 between the fixed valve plate 7 3 and the movable valve plate 7 4, and discharges steam. Can be effectively prevented. This is because the flat sliding surface 77 can be easily processed with high precision, so that the clearance can be easily managed as compared with the cylindrical sliding surface. In addition, since a plurality of preload springs 85 apply a preset load to the valve body 72 to generate a surface pressure on the sliding surfaces 7 7 of the fixed valve plate 73 and the movable valve plate 74, the sliding is performed. Leakage of steam from the moving surface 77 can be more effectively suppressed.
  • the valve body 72 of the rotary valve 71 is made of stainless steel having a large coefficient of thermal expansion
  • the fixed valve plate 73 fixed to the valve body 72 is made of carbon or ceramic having a small coefficient of thermal expansion. Therefore, the centering between the two may deviate due to the difference in the coefficient of thermal expansion.
  • the stepped portion 79 a of the inner circumference of the fixed ring 79 is press-fitted into the outer circumference of the fixed side valve plate 73 to form an in-row fit.
  • the fixing ring 79 is attached to the valve body 72 with a plurality of ports 80 in a state where the stepped portion 79b on the outer periphery of the fixing ring 79 is fitted in the outer periphery of the valve body 72.
  • the fixed side valve plate 73 is precisely centered with respect to the valve body 72 by the centering action of the in-row fitting. Performance degradation It is possible to stop.
  • the contact surface between the fixed side valve plate 73 and the valve body 72 can be uniformly adhered by the fastening force of the port 80-, and the leakage of steam from the contact surface can be suppressed.
  • the rotary valve 71 can be attached to and detached from the casing main body 12 simply by removing the rear force par 18 from the casing main body 12, so that maintenance work such as repair, cleaning, and replacement is greatly facilitated. To improve.
  • the high temperature and high pressure steam passes through the outlet valve 71 at high temperatures, the swash plate 3 1 and the output shaft 3 2 that require lubrication with oil are located on the opposite side of the rotary pulp 7 1 with the rotor 22 interposed therebetween.
  • the oil is heated by the heat of the rotary valve 71, which becomes hot, and the swash plate 31 and the output shaft 32 are heated.
  • the lubrication performance can be prevented from lowering.
  • the oil also has a function of cooling the rotary valve 71 to prevent overheating.
  • the expander M of the Rankine cycle device is illustrated, but the expander M of the present invention can be applied to any other applications.
  • the expander of the present invention can be suitably applied to a Rankine cycle device.
  • any expander that converts heat energy and pressure energy of a high-temperature and high-pressure working medium into mechanical energy and outputs the mechanical energy can be used for any purpose. Can be applied to expander

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne une machine à détente caractérisée en ce qu'un flux à température élevée et haute pression est alimenté dans une chambre à détente (43) formée entre des pistons (42) et une chemise de cylindre (41), de manière que les pistons (42) pressent un plateau incliné (31), aux fins d'entraînement en rotation d'un rotor (22), en ce qu'un espace isolant annulaire (70) est formé dans une tête du rotor (38) faisant face à la chambre à détente (43), de manière à supprimer l'échappement de chaleur du flux à température élevée et haute pression alimenté dans la chambre à détente (43) dans le rotor, afin d'empêcher une baisse d'un rendement thermique, et en ce qu'un joint métallique (36) est installé entre la surface terminale de la chemise du cylindre (41) et la surface terminale de la tête du rotor (38), de manière à sceller la chambre à détente (43) ; étant donné qu'un volume inutile autour du joint peut être réduit, comparativement à un boîtier dans lequel la chambre à détente (43) est scellée par l'intermédiaire d'un élément de joint annulaire à paroi épaisse, le rapport volumique (taux de détente) de la machine à détente permet de garantir une augmentation d'un rendement thermique, de manière à accroître une sortie.
PCT/JP2003/000453 2002-02-13 2003-01-21 Machine a detente WO2003069125A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US10/501,521 US20050158181A1 (en) 2002-02-13 2003-01-21 Expansion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002/35613 2002-02-13
JP2002035613A JP2003239701A (ja) 2002-02-13 2002-02-13 膨張機

Publications (1)

Publication Number Publication Date
WO2003069125A1 true WO2003069125A1 (fr) 2003-08-21

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PCT/JP2003/000453 WO2003069125A1 (fr) 2002-02-13 2003-01-21 Machine a detente

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Country Link
US (1) US20050158181A1 (fr)
JP (1) JP2003239701A (fr)
WO (1) WO2003069125A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008047275C5 (de) 2007-12-13 2013-07-11 Renate Geipel Expansionsmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5331103U (fr) * 1976-08-23 1978-03-17
JPS5657901U (fr) * 1979-10-08 1981-05-19
US4805516A (en) * 1986-09-12 1989-02-21 Ckd Corporation Axial air motor
JPH02215975A (ja) * 1989-02-16 1990-08-28 Ngk Insulators Ltd セラミックスと金属との複合ケーシング
JPH08218816A (ja) * 1995-02-16 1996-08-27 Mitsubishi Heavy Ind Ltd 低温発電装置
JPH11294182A (ja) * 1998-04-13 1999-10-26 Mitsubishi Motors Corp エンジン

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1082968B (it) * 1977-04-05 1985-05-21 Gherner Lidio Motore idraulico a pistoni assiali
US5950425A (en) * 1996-03-11 1999-09-14 Sanshin Kogyo Kabushiki Kaisha Exhaust manifold cooling
JPH109136A (ja) * 1996-06-24 1998-01-13 Toyota Autom Loom Works Ltd 圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5331103U (fr) * 1976-08-23 1978-03-17
JPS5657901U (fr) * 1979-10-08 1981-05-19
US4805516A (en) * 1986-09-12 1989-02-21 Ckd Corporation Axial air motor
JPH02215975A (ja) * 1989-02-16 1990-08-28 Ngk Insulators Ltd セラミックスと金属との複合ケーシング
JPH08218816A (ja) * 1995-02-16 1996-08-27 Mitsubishi Heavy Ind Ltd 低温発電装置
JPH11294182A (ja) * 1998-04-13 1999-10-26 Mitsubishi Motors Corp エンジン

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US20050158181A1 (en) 2005-07-21
JP2003239701A (ja) 2003-08-27

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