WO2003069126A1 - Machine a detente - Google Patents

Machine a detente Download PDF

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Publication number
WO2003069126A1
WO2003069126A1 PCT/JP2003/000454 JP0300454W WO03069126A1 WO 2003069126 A1 WO2003069126 A1 WO 2003069126A1 JP 0300454 W JP0300454 W JP 0300454W WO 03069126 A1 WO03069126 A1 WO 03069126A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
piston
rotor
cylinder sleeve
expander
Prior art date
Application number
PCT/JP2003/000454
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 US10/501,540 priority Critical patent/US20050147507A1/en
Publication of WO2003069126A1 publication Critical patent/WO2003069126A1/fr

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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
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F01B3/0088—Piston shoe retaining means
    • 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
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0017—Component parts, details, e.g. sealings, lubrication
    • F01B3/002—Cylinders
    • 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
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • 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
    • F01B3/0082—Details
    • F01B3/0085—Pistons

Definitions

  • the present invention comprises: a casing; a rotor rotatably supported by the casing; and an axial piston cylinder group arranged in a ring shape so as to surround an axis of the casing, and a piston of the axial piston cylinder group.
  • Background Art related to an expander that drives a rotor to rotate by supplying high-temperature and high-pressure steam to an expansion chamber defined between a cylinder sleeve and a cylinder, and lubricates sliding surfaces of a piston and a cylinder sleeve with oil.
  • Such an expander has already been proposed by the present applicant in Japanese Patent Application No. 2001-61424.
  • This expander is used for a Rankine cycle device.
  • the expander is provided with a group of axial piston cylinders arranged in a ring so as to surround the axis of the rotor. It is performed by oil separate from steam (water), which is the working medium of the expander.
  • the top portion of the piston of such an expander is not only easily oxidized by being exposed to high-temperature and high-pressure steam supplied to the expansion chamber of the cylinder sleeve, but also has a possibility of being corroded by contact with the condensed water of the steam. .
  • the end of the piston may be damaged by a large load due to contact with the swash plate.
  • the middle part of the piston that slides against the cylinder sleeve is lubricated with oil.However, if the steam leaking from the expansion chamber of the cylinder sleeve becomes condensed water and adheres to the sliding surface, water is mixed into the oil. This makes it difficult to maintain the oil film and may cause abnormal wear.
  • the top, end, and middle parts of the conventional piston are integrally formed of the same material, the heat resistance, corrosion resistance, high surface pressure resistance, and wear resistance required for each part of the piston are the same. It was difficult to satisfy all of the above.
  • the present invention has been made in view of the above circumstances, and has as its object to increase the durability of a piston of an axial piston piston type expander.
  • the rotor is driven by supplying high-temperature and high-pressure steam to the expansion chamber defined between the piston and cylinder sleeve of the axial piston cylinder group, and the sliding surfaces of the piston and cylinder sleeve are oiled.
  • the piston In the expander, which is lubricated with a piston, the piston is sandwiched between a top portion exposed to high-temperature and high-pressure steam in the expansion chamber, an end portion in contact with the swash plate, and the end portion, and slides on the cylinder sleeve.
  • the top portion is made of a heat and corrosion resistant material
  • the end portion is made of a material having high surface pressure resistance.
  • the top portion exposed to the high-temperature and high-pressure steam supplied to the expansion chamber is made of a heat-resistant and corrosion-resistant material. It is possible to prevent parts from being oxidized by heat or from corroding steam by contact with liquefied water.
  • the end of the piston that comes into contact with the swash plate is made of a material having high surface pressure resistance, it is possible to prevent the end from being damaged by the strong surface pressure received from the swash plate.
  • the middle part of the piston that slides on the cylinder sleeve is made of a material with high wear resistance, abnormal wear occurs even if water condensed with steam enters the oil on the sliding surface and lubricity is reduced. Can be prevented.
  • an expander characterized by providing a heat insulating space between the top portion and the intermediate portion.
  • the heat insulating space is provided between the top part and the middle part of the piston, the heat of the high-temperature and high-pressure steam supplied to the expansion chamber is prevented from escaping from the top part to the cylinder sleeve through the middle part.
  • a decrease in the thermal efficiency of the expander can be minimized.
  • a hollow space is formed in the intermediate portion, and an oil ring groove formed in an outer peripheral surface of the top portion is formed in the first portion. Communicating with the hollow space through an oil hole, and an outer periphery of the intermediate portion An expander is proposed, wherein a small-diameter portion formed on the surface is communicated with the hollow space via a second oil hole.
  • the hollow space is formed in the middle of the piston, not only can the piston be reduced in weight, but also the hollow space functions as a heat insulating layer to prevent heat from escaping from the piston to the cylinder sleeve, The decrease in thermal efficiency can be minimized.
  • the bottom of the oil ring groove formed at the top is communicated with the hollow space of the piston through the first oil hole, and the small diameter part formed at the middle is communicated through the second oil hole.
  • the oil holes 63c and 62c of the embodiment correspond to the first oil hole and the second oil hole of the present invention, respectively.
  • 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. 3 is 3-3 of 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 mouth
  • Fig. 7 is a cross section taken along line 7-7 of Fig. 4.
  • Fig. 8, 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, and
  • FIG. 12 is a sectional view taken along line 12-2 in FIG. 5
  • FIG. 13 is a sectional view taken along line 13-13 in
  • the expander M of this embodiment is used, for example, in a Rankine cycle device, and converts heat energy and pressure energy of a high-temperature high-pressure steam as a working medium into mechanical energy. Output.
  • the casing 11 of the expander M has a casing body 12, a front cover 15 connected to a front opening of the casing body 12 by a plurality of bolts 14 via a sealing member 13, and a casing.
  • the rear cover 18 is connected to the rear opening of the main body 12 by a plurality of ports 17 via a sealing member 16 via a sealing member 16.
  • the rear cover 18 is connected to the lower opening of the casing main body 12 via a sealing member 19.
  • an oil pan 21 connected by several 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. 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 and 26 and a dowel pin 27 is fixed with a plurality of ports 29.
  • the swash plate 31 is rotatably supported on the 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 rotor 22 has an output shaft 32 supported on the front cover 15 by the pole bearing 23, and cutouts 57, 58 having predetermined widths at the rear of the output shaft 32 (FIGS. 4 and 5). 9) and the three sleeve support flanges 3 3, 3 4, 3 5 formed integrally with each other and the rear sleeve support flange 35 through metal gaskets 36 through a plurality of ports 3.
  • the rotor head 38 supported on the casing body 12 by the pole bearings 24 and the three sleeve support flanges 33, 34, 35 are fitted from the front by a plurality of pole bearings 24.
  • a heat insulating cover 40 coupled to the front sleeve support flange 33 with the port 39.
  • the three sleeve support flanges 3 3, 3 4, 35 each have five sleeve support holes 33 a, 34 a, 35 a... formed at an interval of 72 ° around the axis L.
  • the five cylinder sleeves 41 are fitted into the sleeve support holes 33a-, 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 step portion 35b formed in the sleeve support hole 35a of the rear sleeve support flange 35.
  • 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 32 a extending along the axis L is formed inside the output shaft 32 integral with the rotor 22, and the front end of the oil passage 32 a radially branches off to the outside of the output shaft 32. It communicates with the peripheral annular groove 32b.
  • Lowe 2 2 center sleeve support flange 3 4 At a radially inner position, an oil passage closing member 45 is screwed into an inner periphery of the oil passage 32 a via a seal member 44, and extends radially outward from the oil passage 32 a in the vicinity thereof.
  • a plurality of oil holes 3 2 c open on the outer peripheral surface of the output shaft 32.
  • the trochoid-type oil pump 49 disposed in the outer rotor 50 is rotatably fitted in the concave portion 15a, and the inner rotor 50 is fixed to the outer periphery of the output shaft 32 and is engaged with the outer rotor 50.
  • the internal space of the oil pan 21 communicates with the suction port 53 of the oil pump 49 via the oil pipe 52 and the oil passage 15b of the front cover 15 and the discharge port 54 of the oil pump 49. Communicates with the annular groove 32 b 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.
  • Force S 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 is formed by a plurality of oil rings. It communicates with the hollow space 62a of the intermediate part 62 via the oil hole 63c.
  • the end 61 and the middle 62 of the piston are made of high carbon steel, the top 63 is made of stainless steel, of which the end 61 is induction hardened and the middle 62 is hardened. Is done.
  • corrosion resistance of the top part 6 3 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 sleep 41, and a plurality of oil holes 41c are formed in the annular groove 41b.
  • the hole 32 formed in the output shaft 32 and the hole formed in the sleeve support flange 34 in the center of the mouth 22 are formed. (See Fig. 4 and Fig. 6) communicate with the annular groove 41b.
  • the space 68 formed between the sleeve support flanges 33, 35 on the front and rear sides of the rotor 22 and the heat insulating cover 40 is formed by oil holes 40a formed in the heat insulating cover 40 (Fig. 4). And see Fig. 7) through the casing 11 to the internal space.
  • An annular lid member 69 is welded to the front side or the expansion chamber 43 side of the rotor head 38 connected with a port 37 on the rear surface of the sleeve support flange 33 on the front side of the rotor 22.
  • An annular heat insulating space 70 (see FIG. 9) is defined on the rear or 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 mouth re-valve 71 arranged along the axis L of the mouth 22 has a valve body 72, a fixed valve plate 73, and a movable valve plate 73. Rate 7 4 is provided.
  • 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 bolts 76 also have a function of fixing the rotor head 38 to the output shaft 32.
  • the fixed valve plate 73 which comes into contact with the movable valve plate 74 via the flat sliding surface 77, has one port at the center of the front surface of the valve body 72.
  • it is fixed to the outer periphery of the valve body 72 by an annular fixing ring 79 and a plurality of ports 80.
  • the step part 79 a formed on the inner circumference of the fixing ring 79 fits in with the outer circumference of the fixed valve plate 73.
  • the stepped portion 79 b formed on the outer circumference of the fixing ring 79 is fitted into the outer circumference of the valve body 72 by the in-row fitting. Coaxiality is ensured.
  • 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.
  • the fixed-side valve plate 73 and the movable-side valve plate 74 are made of highly durable materials such as carbon and ceramics, and the sliding surface 77 has heat resistance, lubricity, and corrosion resistance. The durability can be further improved by interposing or coating a wear-resistant member.
  • 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 with a seal member 87 is formed between the casing body 12 and the rear cover 18 and the mouth 22 and the steam discharge chamber 88 is formed.
  • the sliding surface 77 is formed via the sixth and seventh steam passages P 6 and P 7 formed inside the valve body 72 and the fifth steam passage P 5 formed on the fixed valve plate 73. Communicate.
  • the first and second steam passages PI and P2 are connected to the mating surface of the valve body 72 and the fixed side pulp plate 73.
  • a seal member 90 surrounding the connection of the fifth and sixth steam passages P5 and P6.
  • the both ends of the five fourth steam passages P4 communicate with the third steam passages P3 and the expansion chambers 43, respectively.
  • 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 integrated with the first steam passage P 1 formed in the valve body 72 of the rotary valve 71 from the steam supply pipe 86 and the valve body 72.
  • the second steam passage P2 formed in the fixed-side valve plate 73 it reaches the sliding surface 77 with the movable-side valve plate 74.
  • the second steam passage P2 opening to the sliding surface 77 is provided for a predetermined intake period in the corresponding third steam passage P3 formed in the movable valve plate 7'4 which rotates integrally with the mouth 22.
  • the high-temperature and high-pressure steam is supplied instantaneously 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 with the rotation of the mouth 22 and the oil pipe 52 from the oil pan 21, the oil passage 15 b of the front cover 15, and the suction port
  • the oil sucked in through 5 3 is discharged from the discharge port 54 and the oil passage 15 of the front cover 15, the oil passage 3 2 a of the output shaft 32, and the annular groove 3 2 b of the output shaft 32 , Through the oil hole 3 2c "'of the output shaft 32, the annular groove 41b of the cylinder sleeve 41 and the oil hole 41c of the cylinder sleeve 41, and formed in the intermediate portion 62 of the piston 42.
  • the oil is supplied to the space between the small diameter portion 62b and the cylinder sleeve 41.
  • Part of the oil held in the small diameter portion 62b is formed in a spiral shape formed in the intermediate portion 62 of the piston 42. Flows into the oil groove 6 2 d of the cylinder sleeve to lubricate the sliding surface with the cylinder sleeve 41. Compression ring 6 6 provided on the flop portion 6 3, 6 6 and to lubricate the sliding sliding surface of the oil ring 6 7 and cylinder sleeve 4 1.
  • the hollow space 62.a communicates with the inside of the cylinder sleeve 41 through a plurality of oil holes 62c extending through the intermediate portion 62 of the piston 42, and the cylinder sleeve 41 Communicates with the annular groove 41b on the outer periphery of the cylinder sleeve 41 through a plurality of oil holes 41c.
  • the periphery of the annular groove 4 1 b is covered by the sleeve support flange 3 4 at the center of the rotor 22, but the sleeve support flange 34 has an oil hole 34 b so that the piston 42 is hollow.
  • the oil in the space 62 a is urged radially outward by centrifugal force, and is insulated through the oil hole 34 b of the sleeve support flange 34.
  • the oil is discharged to the space 68 inside the cover 40 and then returned to the oil pan 21 through the oil holes 40 a of the heat insulating cover 40.
  • 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. Therefore, it is possible to reliably lubricate the entire area of the piston 42 in the axial direction.
  • the oil flows inside the hollow space 62 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 piston 42 is locally reduced. 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. Since the heat insulation space 70 is also formed in the rotor head 38 facing the expansion chamber 43, the heat from the expansion chamber 43 to the piston 42 and the rotor head 38 is formed. Escape can be minimized, which contributes to the performance improvement of the expander M. In addition, since a large-volume hollow space 62 a is formed inside the piston 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 from the expansion chamber 43. Can be more effectively reduced.
  • a metal gasket 36 was interposed between the rear sleeve support flange 35 and the low-end head 38 to seal the expansion chamber 43.
  • the amount of waste polymer around the seal can be reduced, thereby securing a large volume ratio (expansion ratio) of the expander M, increasing the thermal efficiency and improving the output. Can be achieved.
  • the cylinder sleeve 41 is constructed separately from the rotor 22, the material of the cylinder sleeve 41 is not limited by the material of the rotor 22, taking into account thermal conductivity, heat resistance, strength, wear resistance, etc. And replace only the worn 'damaged cylinder sleeve 41'. It is economical because you can.
  • the outer peripheral surface of the cylinder sleeve 41 is exposed from the two notches 57, 58 formed in the outer peripheral surface of the rotor 22 in the circumferential direction, not only can the weight of the rotor 22 be reduced, but also the rotor 22 can be reduced.
  • the heat efficiency can be improved by reducing the heat mass of No. 2, and the heat escape from the cylinder sleeve 41 can be suppressed by making the notches 57, 58 function as heat insulating spaces.
  • 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 orifice valve 71 supplies and discharges steam to the axial piston cylinder group 56 through the flat sliding surface 77 between the fixed side valve plate 73 and the movable side valve plate 74, the steam Leakage can be effectively prevented.
  • 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.
  • a plurality of preload springs 85 apply a preset load to the valve body 72 to generate a surface pressure on the sliding surfaces 77 of the fixed valve plate 73 and the movable valve plate 74. Leakage of steam from the sliding surfaces 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 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 evenly and closely 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 through which high-temperature and high-pressure steam passes becomes hot, but the swash plate 3 1 and the output shaft 3 2 that require lubrication with oil are arranged on the opposite side of the rotary valve 71 with the rotor 22 interposed therebetween. Therefore, it is possible to prevent the oil from being heated by the heat of the rotary valve 71, which is heated to a high temperature, and thereby reducing the lubrication performance of the swash plate 31 and the output shaft 32.
  • 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 material, heat treatment, surface treatment, and the like of the end portion 61, the intermediate portion 62, and the top portion 63 of the piston 42 are not limited to those of the embodiment, and may be appropriately changed as long as they maintain desired characteristics. It is possible.
  • 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, dans laquelle une vapeur à haute pression et à haute température est injectée dans une chambre de détente (43) formée entre des pistons (42) et un manchon de cylindre (41) pour appuyer sur un plateau oscillant (31) au moyen des pistons, de sorte à entraîner de manière rotative un rotor (22) pour une lubrification des surfaces coulissantes des pistons (42) et du manchon de cylindre (41) au moyen d'huile injectée par un orifice d'huile (32c). Les pistons (42) sont constitués de parties supérieures (63) exposées à la vapeur à haute pression et à haute température, dans la chambre de détente (43), de parties d'extrémité (61) pouvant buter contre le plateau oscillant (31), et de parties intermédiaires (62) venant en contact coulissant avec le manchon de cylindre (41) entre les parties d'extrémité (61) et les parties supérieures (63). Les parties supérieures (63) sont constituées d'une matière résistante à la corrosion et résistante à la chaleur, les parties d'extrémité (61) étant formées d'une matière résistante à la pression superficielle, et les parties intermédiaires (62) étant constituées d'une matière résistante à l'usure, ce qui permet d'augmenter la durabilité des pistons (42) de la machine à détente de type à cylindre de piston axial.
PCT/JP2003/000454 2002-02-13 2003-01-21 Machine a detente WO2003069126A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US10/501,540 US20050147507A1 (en) 2002-02-13 2003-01-21 Expander

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002/35614 2002-02-13
JP2002035614A JP3923331B2 (ja) 2002-02-13 2002-02-13 膨張機

Publications (1)

Publication Number Publication Date
WO2003069126A1 true WO2003069126A1 (fr) 2003-08-21

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US (1) US20050147507A1 (fr)
JP (1) JP3923331B2 (fr)
WO (1) WO2003069126A1 (fr)

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JP2004080937A (ja) * 2002-08-20 2004-03-11 Honda Motor Co Ltd 発電電動機装置
JP5103952B2 (ja) * 2007-03-08 2012-12-19 ダイキン工業株式会社 冷凍装置
DE102008047275C5 (de) * 2007-12-13 2013-07-11 Renate Geipel Expansionsmaschine
DE102010052508A1 (de) * 2010-11-26 2012-05-31 Daimler Ag Abwärmenutzungsvorrichtung
KR101603091B1 (ko) * 2014-09-11 2016-03-14 주식회사 엔진텍 사판식 팽창기의 윤활시스템
DE102015204367A1 (de) * 2015-03-11 2016-09-15 Mahle International Gmbh Axialkolbenmaschine
US11118681B2 (en) * 2019-04-24 2021-09-14 Purdue Research Foundation Piston-type positive displacement machine with a pressure-adaptive piston-cylinder interface
JP7398289B2 (ja) 2020-02-05 2023-12-14 パナソニックホールディングス株式会社 レシプロ膨張機及びランキンサイクル装置

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JPS5519972A (en) * 1978-07-31 1980-02-13 Toyoda Autom Loom Works Ltd Swash plate type compressor
JPS5657901U (fr) * 1979-10-08 1981-05-19
JPS60120242U (ja) * 1984-01-24 1985-08-14 愛知機械工業株式会社 内燃機関用ピストン
US4805516A (en) * 1986-09-12 1989-02-21 Ckd Corporation Axial air motor
JPS6453568U (fr) * 1987-09-28 1989-04-03
JPH01130074A (ja) * 1987-11-16 1989-05-23 Riken Corp 斜板式圧縮機
JPH09268915A (ja) * 1996-04-01 1997-10-14 Isuzu Ceramics Kenkyusho:Kk 低質油を燃料とするディーゼルエンジン
JPH11351136A (ja) * 1998-06-15 1999-12-21 Unisia Jecs Corp プランジャポンプ
EP1092871A2 (fr) * 1999-10-13 2001-04-18 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston creux d'un compresseur à plateau en biais avec alésages

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