EP1428977A1 - Rotary fluid machine - Google Patents
Rotary fluid machine Download PDFInfo
- Publication number
- EP1428977A1 EP1428977A1 EP02772879A EP02772879A EP1428977A1 EP 1428977 A1 EP1428977 A1 EP 1428977A1 EP 02772879 A EP02772879 A EP 02772879A EP 02772879 A EP02772879 A EP 02772879A EP 1428977 A1 EP1428977 A1 EP 1428977A1
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- EP
- European Patent Office
- Prior art keywords
- rotor
- fixed shaft
- rotating shaft
- steam
- water
- Prior art date
- Legal status (The legal status 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 status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- 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
- F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
- F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
- F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
- F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
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- 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
- F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
- F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
- F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
- F01B13/068—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with an actuated or actuating element being at the inner ends of the cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F01C1/3446—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/602—Gap; Clearance
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/601—Shaft flexion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/605—Shaft sleeves or details thereof
Definitions
- a pair of notches 86a are formed on the outer peripheral face of the thick portion 87a of the fixed sleeve 86 with a phase difference of 180°, and these notches can communicate with the third steam passages S3.
- the notches 86a and the transit chamber 19 communicate with each other via four fourth steam passages S4 formed axially in the fixed sleeve 86, a fifth steam passage S5 formed within the fixed sleeve 86 and the fixed sleeve support member 82, and through holes 82b opening on the outer periphery of the boss portion 82a of the fixed sleeve support member 82.
- the water that has been supplied from the sixteenth water passage W16 and lubricated the sliding surfaces of the fixed sleeve 86 and the inner sleeve 85 of the rotating shaft 113 and the water that has lubricated the outer peripheral face of the rotating shaft 113 through the orifice penetrating the bearing members 22 and 23 and has also lubricated the sliding surfaces of the fixed sleeve 86 and the inner sleeve 85 of the rotating shaft 113 were to flow into the transit chamber 19 via the port holes 88d and the port channels 87d formed in the outer periphery of the fixed sleeve 86, the first decreased temperature, decreased pressure steam within the transit chamber 19 might be cooled, and the output of the expander 4 might be degraded.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Details Of Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
- Sealing Devices (AREA)
- Rotary Pumps (AREA)
Abstract
Description
- The present invention relates to a rotary fluid machine for interconverting the pressure energy of a gas-phase working medium and the rotational energy of a rotor.
- A rotary fluid machine disclosed in Japanese Patent Application Laid-open No. 2000-320543 is equipped with a vane piston unit in which a vane and a piston are combined; the piston, which is slidably fitted in a cylinder provided radially in a rotor, interconverts the pressure energy of a gas-phase working medium and the rotational energy of the rotor via a power conversion device comprising an annular channel and a roller, and the vane, which is radially and slidably supported in the rotor, interconverts the pressure energy of the gas-phase working medium and the rotational energy of the rotor.
- In such a rotary fluid machine, a rotary valve for supplying and discharging a high temperature gas-phase working medium is formed between the outer peripheral face of a fixed shaft fixed to a casing and the inner peripheral face of a hollow rotating shaft by fitting and rotatably supporting the rotating shaft, which rotates integrally with the rotor, on the outer periphery of the fixed shaft.
- In order to maintain the sealing characteristics for the gas-phase working medium in the rotary valve, since it is a mating seal, it is necessary to precisely control the clearance between the sliding surfaces of the fixed shaft and the rotating shaft. However, since it is impossible to avoid the occurrence of some degree of runout in the rotating rotor, if the above clearance is set so as to be small, the frictional resistance between the sliding surfaces of the fixed shaft and the rotating shaft is higher, and there is the problem of interference with the rotation of the rotor. Furthermore, if the clearance between the sliding surfaces of the fixed shaft and the rotating shaft is set so as to be appropriate when they are cold, the outer peripheral face of the fixed shaft is worn due to a difference in thermal expansion in the vicinity of the rotary valve where the high temperature gas-phase working medium passes through, and since contact with the outer peripheral face of the fixed shaft is uneven due to rotational runout of the rotor, resulting in eccentric wear, there are the problems of a degradation in the sealing characteristics for the gas-phase working medium, an increase in the sliding resistance, and degradation of the rotational behavior of the rotor.
- The present invention has been accomplished under the above-mentioned circumstances, and an object thereof is to lessen the influence of rotational runout of a rotor of a rotary fluid machine when a hollow rotating shaft provided integrally with the rotor is rotatably supported on the outer periphery of a fixed shaft fixed to a casing.
- In order to achieve the above object, in accordance with a first aspect of the present invention, there is proposed a rotary fluid machine that includes a rotor rotatably housed within a casing, a hollow rotating shaft that rotates integrally with the rotor, and a fixed shaft that is relatively rotatably fitted into the inner periphery of the rotating shaft, characterized in that the fixed shaft is floatingly supported in the casing via resilient support means having an alignment action.
- In accordance with this arrangement, since the fixed shaft is floatingly supported in the casing via the resilient support means having the alignment action, that is, it is connected with low rigidity and flexibly supported, and the hollow rotating shaft is supported on the outer periphery of the fixed shaft, when rotational runout of the rotor is transmitted to the fixed shaft via the rotating shaft, the rotational runout of the rotor can be suppressed by the alignment action of the resilient support means. The tracking ability of seal surfaces can thereby be improved, and the sealing characteristics can be enhanced by controlling the clearance with high precision, thus avoiding effectively any increase in the frictional resistance and any abnormal wear in a sliding section between the rotating shaft and the fixed shaft.
- Furthermore, in accordance with a second aspect of the present invention, in addition to the first aspect, there is proposed a rotary fluid machine wherein a rotary valve for controlling supplying and discharging of a high temperature gas-phase working medium is provided on sliding surfaces of the rotating shaft and the fixed shaft.
- In accordance with this arrangement, since the rotary valve for controlling supplying and discharging of the high temperature gas-phase working medium is provided on the sliding surfaces of the rotating shaft and the fixed shaft, even when the outer peripheral face of the fixed shaft is worn due to a difference in thermal expansion between the fixed shaft and the rotating shaft, rotational runout of the rotor can be suppressed by the alignment action of the resilient support means, the amount of wear of the outer peripheral face of the fixed shaft thus becomes uniform, and it is therefore possible to precisely control the clearance between the sliding surfaces of the fixed shaft and the rotating shaft when they are hot. Moreover, once uniform contact when hot is formed by the initial setting of the rotary fluid machine, the sealing characteristics can always be maintained for subsequent introduction of the gas-phase working medium, and the sealing characteristics for the gas-phase working medium can be ensured by maintaining a small and uniform clearance.
- A fixed
shaft support spring 95 of embodiments corresponds to the resilient support means of the present invention, and steam in the embodiments corresponds to the gas-phase working medium of the present invention. - FIG. 1 to FIG. 21 D illustrate a first embodiment of the present invention; FIG. 1 is a schematic view of a waste heat recovery system of an internal combustion engine; FIG. 2 is a longitudinal sectional view of an expander, corresponding a sectional view along line 2-2 of FIG. 4; FIG. 3 is an enlarged sectional view around the axis of FIG. 2; FIG. 4 is a sectional view along line 4-4 of FIG. 2; FIG. 5 is a sectional view along line 5-5 of FIG. 2; FIG. 6 is a sectional view along line 6-6 of FIG. 2; FIG. 7 is a sectional view along line 7-7 of FIG. 5; FIG. 8 is a sectional view along line 8-8 of FIG. 5; FIG. 9 is a sectional view along line 9-9 of FIG. 8; FIG. 10 is a sectional view along line 10-10 of FIG. 3; FIG. 11 is an exploded perspective view of a rotor; FIG. 12 is an exploded perspective view of a lubricating water distribution section of the rotor; FIG. 13 is a schematic view showing cross-sectional shapes of a rotor chamber and the rotor; FIG. 14 is an enlarged view of an essential part of FIG. 3, showing a rotary valve and a fixed shaft support spring; FIG. 15 is an enlarged view of an essential part of FIG. 2, showing the outer peripheral face of the fixed shaft; FIG. 16 is a sectional view along line 16-16 of FIG. 14; FIG. 17A is an enlarged view of an essential part of a first fixed shaft; FIG. 17B is a sectional view along
line 17B-17B of FIG. 17A; FIG. 18A is an enlarged view of a nozzle member; FIG. 18B is a sectional view alongline 18B-18B of FIG. 18A; FIG. 19 is a sectional view along line 19-19 of FIG. 14; FIG. 20A to FIG. 20D are diagrams for explaining the operation when a fixed sleeve is shrink-fitted; and FIG. 21A to FIG. 21 D are graphs showing relationships between the thermal expansion of the fixed shaft and that of the rotating shaft. FIG. 22 and FIG. 23 illustrate a second embodiment of the present invention; FIG. 22 is a view corresponding to FIG. 14; and FIG. 23 is a sectional view along line 23-23 of FIG. 22. - A first embodiment of the present invention is explained below with reference to FIG. 1 to FIG. 21 D.
- In FIG. 1, a waste
heat recovery system 2 for an internal combustion engine 1 includes anevaporator 3 that generates high temperature, high pressure steam by vaporizing a high pressure liquid (e.g. water) using as a heat source the waste heat (e.g. exhaust gas) of the internal combustion engine 1, anexpander 4 that generates an output by expansion of the steam, acondenser 5 that liquefies steam having decreased temperature and pressure as a result of conversion of the pressure energy into mechanical energy in theexpander 4, and asupply pump 6 that pressurizes the liquid (e.g. water) from thecondenser 5 and resupplies it to theevaporator 3. - As shown in FIG. 2 and FIG. 3, a
casing 11 of theexpander 4 is formed from first andsecond casing halves second casing halves main body portions rotor chamber 14, andcircular flanges main body portions circular flanges metal gasket 15. The outer face of thefirst casing half 12 is covered with a transit chamberouter wall 16 having a deep bowl shape, and acircular flange 16a, which is joined integrally to the outer periphery of the transit chamberouter wall 16, is superimposed on the left face of thecircular flange 12b of thefirst casing half 12. The outer face of thesecond casing half 13 is covered with an exhaust chamberouter wall 17 for housing a magnet coupling (not illustrated) for transmitting the output of theexpander 4 to the outside, and acircular flange 17a, which is joined integrally to the outer periphery of the exhaust chamberouter wall 17, is superimposed on the right face of thecircular flange 13b of thesecond casing half 13. The above-mentioned fourcircular flanges bolts 18 disposed in the circumferential direction. Atransit chamber 19 is defined between the transit chamberouter wall 16 and thefirst casing half 12, and anexhaust chamber 20 is defined between the exhaust chamberouter wall 17 and thesecond casing half 13. The exhaust chamberouter wall 17 is provided with an outlet (not illustrated) for guiding the decreased temperature, decreased pressure steam that has finished work in theexpander 4 to thecondenser 5. - The
main body portions casing halves tubes outer sleeve 21 having ahollow portion 21 a is rotatably supported by thesehollow bearing tubes members outer sleeve 21 thus passes through the intersection of the major axis and the minor axis of therotor chamber 14, which has a substantially elliptical shape. Theouter sleeve 21, which is made of metal, forms a rotatingshaft 113 in cooperation with a ceramicinner sleeve 85, which will be described later. - A
seal block 25 is housed within a lubricatingwater supply member 24 screwed onto the right-hand end of thesecond casing half 13, and secured by anut 26. Asmall diameter portion 21 b at the right-hand end of theouter sleeve 21 is supported within theseal block 25, a pair ofseals 27 are disposed between theseal block 25 and thesmall diameter portion 21 b, a pair ofseals 28 are disposed between theseal block 25 and the lubricatingwater supply member 24, and aseal 29 is disposed between the lubricatingwater supply member 24 and thesecond casing half 13. Afilter 30 is fitted in a recess formed in the outer periphery of thehollow bearing tube 13c of thesecond casing half 13, and is prevented from failing out by means of afilter cap 31 screwed into thesecond casing half 13. A pair ofseals filter cap 31 and thesecond casing half 13. - As is clear from FIG. 4 and FIG. 13, a
circular rotor 41 is rotatably housed within therotor chamber 14, which has a pseudo-elliptical shape. Therotor 41 is fitted onto and joined integrally to the outer periphery of theouter sleeve 21, and the axis of therotor 41 and the axis of therotor chamber 14 coincide with the axis L of theouter sleeve 21. The shape of therotor chamber 14 viewed in the axis L direction is pseudo-elliptical, and is similar to a rhombus having four rounded corners, the shape having a major axis DL and a minor axis DS. The shape of therotor 41 viewed in the axis L direction is a perfect circle having a diameter DR that is slightly smaller than the minor axis DS of therotor chamber 14. - The cross-sectional shapes of the
rotor chamber 14 and therotor 41 viewed in a direction orthogonal to the axis L are all racetrack-shaped. That is, the cross-sectional shape of therotor chamber 14 is formed from a pair offlat faces 14a extending parallel to each other at a distance d, and arc-shaped faces 14b having a central angle of 180° that are smoothly connected to the outer peripheries of theflat faces 14a and, similarly, the cross-sectional shape of therotor 41 is formed from a pair offlat faces 41a extending parallel to each other at the distance d, and arc-shaped faces 41b having a central angle of 180° that are smoothly connected to the outer peripheries of theflat faces 41 a. Theflat faces 14a of therotor chamber 14 and theflat faces 41 a of therotor 41 are in contact with each other, and a pair of crescent-shaped spaces are formed between the inner peripheral face of therotor chamber 14 and the outer peripheral face of the rotor 41 (see FIG. 4). - The structure of the
rotor 41 is now explained in detail with reference to FIG. 3 to FIG. 6, and FIG. 11. - The
rotor 41 is formed from arotor core 42 that is formed integrally with the outer periphery of theouter sleeve 21, and twelverotor segments 43 that are fixed so as to cover the periphery of therotor core 42 and form the outer shell of therotor 41. Twelve ceramic (or carbon)cylinders 44 are mounted radially in therotor core 42 at 30° intervals and fastened by means ofclips 45 to prevent them falling out. Asmall diameter portion 44a is projectingly provided at the inner end of each of thecylinders 44, and a gap between the base end of thesmall diameter portion 44a and theinner sleeve 85 is sealed via aC seal 46. The extremity of thesmall diameter portion 44a is fitted into the outer peripheral face of the hollowinner sleeve 85, and acylinder bore 44b communicates with first and second steam passages S1 and S2 within afixed shaft 102 via twelve third steam passages S3 running through thesmall diameter portion 44a and therotating shaft 113. Aceramic piston 47 is slidably fitted within each of thecylinders 44. When thepiston 47 moves to the radially innermost position, it retracts completely within the cylinder bore 44b, and when it moves to the radially outermost position, about half of the whole length projects outside the cylinder bore 44b. - Each of the
rotor segments 43 is a hollow wedge-shaped member having a central angle of 30°, and has tworecesses flat faces 14a of therotor chamber 14, therecesses water outlets recesses water outlets rotor segments 43, that is, the faces that areopposite vanes 48, which will be described later. - The
rotor 41 is assembled as follows. The twelverotor segments 43 are fitted around the outer periphery of therotor core 42, which is preassembled with thecylinders 44, theclips 45, and theC seals 46, and thevanes 48 are fitted in twelvevane channels 49 formed betweenadjacent rotor segments 43. At this point, in order to form a predetermined clearance between thevanes 48 and therotor segments 43, shims having a predetermined thickness are disposed on opposite faces of thevanes 48. In this state, therotor segments 43 and thevanes 48 are tightened inward in the radial direction toward therotor core 42 by means of a jig so as to precisely position therotor segments 43 relative to therotor core 42, and each of therotor segments 43 is then provisionally retained on therotor core 42 by means of provisional retention bolts 50 (see FIG. 8). Subsequently each of therotor segments 43 and therotor core 42 are co-machined so as to make two knock pin holes 51 run therethrough, and fourknock pins 52 are press-fitted in the two knock pin holes 51 so as to join each of therotor segments 43 to therotor core 42. - As is clear from FIG. 8, FIG. 9, and FIG. 12, a through
hole 53 running through therotor segment 43 and therotor core 42 is formed between the two knock pin holes 51, and recesses 54 are formed at opposite ends of the throughhole 53. Twopipe members hole 53 viaseals 57 to 60, and an orifice-formingplate 61 and a lubricatingwater distribution member 62 are fitted into each of therecesses 54 and secured by anut 63. The orifice-formingplate 61 and the lubricatingwater distribution member 62 are prevented from rotating relative to therotor segments 43 by two knock pins 64 running through knock pin holes 61 a of the orifice-formingplate 61 and fitted intoknock pin holes 62a of the lubricatingwater distribution member 62, and a gap between the lubricatingwater distribution member 62 and thenut 63 is sealed by anO ring 65. - A
small diameter portion 55a formed in an outer end portion of one of thepipe members 55 communicates with a sixth water passage W6 within thepipe member 55 via a throughhole 55b, and thesmall diameter portion 55a also communicates with aradial distribution channel 62b formed on one side face of the lubricatingwater distribution member 62. Thedistribution channel 62b of the lubricatingwater distribution member 62 extends in six directions, and the extremities thereof communicate with sixorifices plate 61. The structures of the orifice-formingplate 61, the lubricatingwater distribution member 62 and thenut 63 provided at the outer end portion of theother pipe member 56 are identical to the structures of the above-mentioned orifice-formingplate 61, lubricatingwater distribution member 62, andnut 63. - Downstream sides of the two
orifices 61 b of the orifice-formingplate 61 communicate with the two lubricatingwater outlets 43e, which open so as to be opposite thevane 48, via seventh water passages W7 formed within therotor segments 43; downstream sides of the twoorifices 61c communicate with the two lubricatingwater outlets 43f, which open so as to be opposite thevane 48, via eighth water passages W8 formed within therotor segment 43; and downstream sides of the twoorifices 61 d communicate with the two lubricatingwater outlets rotor chamber 14, via ninth water passages W9 formed within therotor segment 43. - As is clear from reference in addition to FIG. 5, an
annular channel 67 is defined by a pair of O rings 66 on the outer periphery of thecylinder 44, and the sixth water passage W6 formed within said one of thepipe members 55 communicates with theannular channel 67 via four throughholes 55c running through thepipe member 55 and a tenth water passage W10 formed within therotor core 42. Theannular channel 67 communicates with sliding surfaces of thecylinder bore 44b and thepiston 47 via anorifice 44c. The position of theorifice 44c of thecylinder 44 is set so that it stays within the sliding surface of thepiston 47 when thepiston 47 moves between top dead center and bottom dead center. - As is clear from FIG. 3 and FIG. 9, the first water passage W1 formed in the lubricating
water supply member 24 communicates with thesmall diameter portion 55a of said one of thepipe members 55 via a second water passage W2 formed in theseal block 25, third water passages W3 formed in thesmall diameter portion 21 b of theouter sleeve 21, anannular channel 68a formed in the outer periphery of a waterpassage forming member 68 fitted in the center of theouter sleeve 21, a fourth water passage W4 formed in theouter sleeve 21, apipe member 69 bridging therotor core 42 and therotor segments 43, and fifth water passages W5 formed so as to bypass theknock pin 52 on the radially inner side of therotor segment 43. - As shown in FIG. 7, FIG. 9, and FIG. 11, twelve
vane channels 49 are formed betweenadjacent rotor segments 43 of therotor 41 so as to extend in the radial direction, and the plate-shapedvanes 48 are slidably fitted in therespective vane channels 49. Each of thevanes 48 has a substantially U-shaped form comprisingparallel faces 48a following the parallel faces 14a of therotor chamber 14, an arc-shapedface 48b following the arc-shapedface 14b of therotor chamber 14, and anotch 48c positioned between theparallel faces 48a.Rollers 71 having a roller bearing structure are rotatably supported on a pair ofsupport shafts 48d projecting from theparallel faces 48a. - A U-shaped
synthetic resin seal 72 is retained in the arc-shapedface 48b of thevane 48, and the extremity of theseal 72 projects slightly from the arc-shapedface 48b of thevane 48 and comes into sliding contact with the arc-shapedface 14b of therotor chamber 14. Tworecesses 48e are formed on each side of thevane 48, and theserecesses 48e are opposite the two radially innerlubricating water outlets 43e that open on the end faces of therotor segment 43. Apiston receiving member 73, which is provided so as to project radially inward in the middle of thenotch 48c of thevane 48, abuts against the radially outer end of thepiston 47. - As is clear from FIG: 4, two pseudo-elliptical
annular channels 74 having a similar shape to that of a rhombus with its 4 apexes rounded are provided in theflat faces 14a of therotor chamber 14 defined by the first and second casing halves 12 and 13, and the pair ofrollers 71 of each of thevanes 48 are rollably engaged with theseannular channels 74. The distance between theseannular channels 74 and the arc-shapedface 14b of therotor chamber 14 is constant throughout the whole circumference. Therefore, when therotor 41 rotates, thevane 48 having therollers 71 guided by theannular channels 74 reciprocates radially within thevane channel 49, and theseal 72 mounted on the arc-shapedface 48b of thevane 48 slides along the arc-shapedface 14b of therotor chamber 14 with a constant amount of compression. This enables direct physical contact between therotor chamber 14 and thevanes 48 to be prevented andvane chambers 75 defined betweenadjacent vanes 48 to be reliably sealed while preventing any increase in the sliding resistance or the occurrence of wear. - As is clear from FIG. 2, a pair of
circular seal channels 76 are formed in theflat faces 14a of therotor chamber 14 so as to surround the outside of theannular channels 74. A pair of ring seals 79 equipped with two O rings 77 and 78 are slidably fitted in thecircular seal channels 76, and the seal surfaces are opposite therecesses rotor segments 43. The pair of ring seals 79 are prevented from rotating relative to the first and second casing halves 12 and 13 by knock pins 80. - As is clear from FIG. 2, FIG. 3, FIG. 10, and FIG. 14, an
opening 16b is formed at the center of the transit chamberouter wall 16; aboss portion 81 a of aspring support member 81 and aboss portion 82a of a fixedsleeve support member 82 disposed on the axis L are tightened together to the inner face of theopening 16b by a plurality ofbolts 83, and the fixedsleeve support member 82 is secured to thefirst casing half 12 by means of anut 84. Theinner sleeve 85, which is formed in a cylindrical shape using a material having a small coefficient of thermal expansion such as ceramic, is fixed in thehollow portion 21 a of theouter sleeve 21, which is made of metal, by shrink-fitting, and a fixedsleeve 86 is relatively rotatably fitted into the inner peripheral face of theinner sleeve 85. The fixedsleeve 86 is formed from aninner sleeve 87 made of a material having small coefficient of thermal expansion such as ceramic and anouter sleeve 88 made of metal, theouter sleeve 88 being united with the outer periphery of theinner sleeve 87 by shrink-fitting, and the left-hand end of the fixedsleeve 86 is supported by the fixedsleeve support member 82 via anOldham coupling 89 that allows relative movement in the radial direction. A gap between the fixedsleeve 86 and thefirst casing half 12 is sealed by aseal 90 at a position close to theOldham coupling 89. - Disposed within the hollow fixed
sleeve 86 are asteam supply pipe 91, a first fixedshaft 92, a second fixedshaft 93, a thirdfixed shaft 94, and a fixedshaft support spring 95. Thesteam supply pipe 91, which is disposed on the axis L, runs through theboss portion 81 a of thespring support member 81 and is secured by a nut 97. The first fixedshaft 92 is a pipe-shaped member having the right-hand end thereof closed, and the right-hand end of thesteam supply pipe 91 is fitted into an open portion at the left-hand end of the first fixedshaft 92. Theinner sleeve 87 of the fixedsleeve 86 has athick portion 87a projecting radially inward, the second fixedshaft 93, which is a pipe-shaped member having a central portion thereof closed, is held between the inner periphery of thethick portion 87a and the outer periphery of the first fixedshaft 92, and seals 98 and 99 are disposed between thethick portion 87a of theinner sleeve 87 and the second fixedshaft 93. A threaded portion at the right-hand end of the second fixedshaft 93 is screwed into the inner peripheral face of the third fixedshaft 94, which is a pipe-shaped member having the right-hand end thereof closed, and twoseals shaft 94 are in intimate contact with the inner peripheral face of theinner sleeve 87 of the fixedsleeve 86 and the inner peripheral face of theouter sleeve 21 of therotating shaft 113. - The fixed
sleeve 86, the first fixedshaft 92, the second fixedshaft 93, and the third fixedshaft 94 form the fixedshaft 102 of the present invention. - As is most clearly shown in FIG. 14 and FIG. 19, the fixed
shaft support spring 95 disposed around the outer periphery of thesteam supply pipe 91 provides a connection between acylindrical spring portion 81 b forming a multicylindrical support portion extending rightward from theboss portion 81 a of thespring support member 81 and acylindrical spring portion 93a similarly forming a multicylindrical support portion and extending leftward from the central portion of the second fixedshaft 93. That is, the fixedshaft support spring 95 comprises sevencylindrical springs cylindrical springs cylindrical spring portion 81 b of thespring support member 81 so that there are gaps therebetween and are welded to each other at the ends; the threecylindrical springs cylindrical spring portion 93a of the second fixedshaft 93 so that there are gaps therebetween and are welded to each other at the ends; and opposite ends of thecylindrical spring 105 on the outermost peripheral side are welded to thecylindrical springs - As is clear from FIG. 10 and FIG. 14, two
collars 106 are fitted around the second fixedshaft 93, which is sandwiched between the first fixedshaft 92 and theinner sleeve 87, and twonozzle members 107 are fitted in thethick portion 87a of theinner sleeve 87. The first steam passage S1, which communicates with thesteam supply pipe 91, is formed in the center of the first fixedshaft 92 in the axial direction, and the two second steam passages S2, which pass through the interiors of thecollars 106 and thenozzle members 107, run radially through the first fixedshaft 92, the second fixedshaft 93, and the fixedsleeve 86 with a phase difference of 180°. As described above, the twelve third steam passages S3 run through thesmall diameter portions 44a of the twelvecylinders 44 retained at intervals of 30° in therotor 41 fixed to therotating shaft 113 and theinner sleeve 85 of therotating shaft 113, and radially inner end portions of these third steam passages S3 are opposite the radially outer end portions of the second steam passages S2 so as to be able to communicate therewith. - A pair of
notches 86a are formed on the outer peripheral face of thethick portion 87a of the fixedsleeve 86 with a phase difference of 180°, and these notches can communicate with the third steam passages S3. Thenotches 86a and thetransit chamber 19 communicate with each other via four fourth steam passages S4 formed axially in the fixedsleeve 86, a fifth steam passage S5 formed within the fixedsleeve 86 and the fixedsleeve support member 82, and throughholes 82b opening on the outer periphery of theboss portion 82a of the fixedsleeve support member 82. - As shown in FIG. 2 and FIG. 4, a plurality of radially aligned
intake ports 108 are formed in thefirst casing half 12 and thesecond casing half 13 at positions that are advanced by 15° in the direction of rotation R of therotor 41 relative to the minor axis of therotor chamber 14. The interior space of therotor chamber 14 communicates with thetransit chamber 19 by means of theseintake ports 108. Furthermore, a plurality ofexhaust ports 109 are formed in thesecond casing half 13 at positions that are retarded by 15° to 75° in the direction of rotation R of therotor 41 relative to the minor axis of therotor chamber 14. The inner space of therotor chamber 14 communicates with theexhaust chamber 20 by means of theseexhaust ports 109. Theseexhaust ports 109 open inshallow depressions 13d formed within thesecond casing half 13 so that theseals 72 of thevanes 48 are not damaged by the edges of theexhaust ports 109. - The second steam passages S2 and the third steam passages S3, and the
notches 86a of the fixedsleeve 86 and the third steam passages S3, form a rotary valve V, which provides periodic communication therebetween by rotation of therotating shaft 113 relative to the fixed shaft 102 (see FIG. 10). - As is clear from FIG. 17A and FIG. 17B, a plurality of
notches 92a are formed in a left-hand end outer peripheral portion of the first fixedshaft 92, andconvex portions 92b formed between thenotches 92a are in intimate contact with thecylindrical spring 93a of the fixedshaft support spring 95. Even when the temperature of the first fixedshaft 92, through which high temperature, high pressure steam passes, increases, by making only theconvex portions 92b come into contact with thecylindrical spring 93a, the heat transmitted to the fixedshaft support spring 95 can be minimized. - As is clear from FIG. 18A and FIG. 18B, an
annular channel 107a is formed on the outer periphery of thenozzle member 107, which is fitted in theinner sleeve 87, and a plurality ofnotches 107b are formed in an end portion of thenozzle member 107. This enables transmission to theinner sleeve 87 of heat of thenozzle member 107, through which high temperature, high pressure steam passes, to be minimized. - As is clear from FIG. 14 to FIG. 16, a plurality (twelve in the embodiment) of annularly
disposed port holes 88d are formed at two positions of theouter sleeve 88 on either side of the rotary valve V, and two annularlydisposed port channels 87d communicating with the port holes 88d are formed in theinner sleeve 87. The port holes 88d and theport channels 87d communicate with thetransit chamber 19 via twopassages 87b formed in the axis L direction on the mating surfaces of theinner sleeve 87 and theouter sleeve 88, anannular channel 87c formed in theinner sleeve 87, and a throughhole 88a formed in theouter sleeve 88. Segmentedspiral channels 88b extending in a spiral shape are formed axially outside the two lines ofport holes 88d of the outer peripheral face of theouter sleeve 88. The directions of inclination of thespiral channels 88b on either side of the two lines ofport holes 88d are opposite to each other. Two abradedpowder collecting channels 88c are formed axially inside the two lines ofport holes 88d on the outer peripheral face of theouter sleeve 88. - As is clear from FIG. 2,
pressure chambers 110 are formed at the rear face of the ring seals 79 fitted in thecircular seal channels 76 of the first and second casing halves 12 and 13. An eleventh water passage W11 formed in the first and second casing halves 12 and 13 communicates with the twopressure chambers 110 via a twelfth water passage W12 and a thirteenth water passage W13, which are formed from pipes, and the ring seals 79 are urged toward the side face of therotor 41 by virtue of water pressure applied to the twopressure chambers 110. - The eleventh water passage W11 communicates with the outer peripheral face of the
annular filter 30 via a fourteenth water passage W14, which is a pipe, and the inner peripheral face of thefilter 30 communicates with a sixteenth water passage W16 formed in thesecond casing half 13 via a fifteenth water passage W15 formed in thesecond casing half 13. Water supplied to the sixteenth water passage W16 lubricates sliding surfaces between theouter sleeve 88 of the fixedshaft 102 and theinner sleeve 85 of therotating shaft 113. Water supplied to the outer periphery of the bearingmember 23 from the inner peripheral face of thefilter 30 via a seventeenth water passage W17 lubricates the outer peripheral face of theouter sleeve 21 of therotating shaft 113 through an orifice penetrating the bearingmembers 23, and also forms a hydrostatic bearing to support therotating shaft 113 in a floating state, thereby reducing the frictional force and preventing seizing. On the other hand, water supplied to the outer periphery of the bearingmembers 22 from the eleventh water passage W11 via an eighteenthwater passage W 18, which is a pipe, lubricates the outer peripheral face of theouter sleeve 21 of therotating shaft 113 through an orifice penetrating the bearingmember 22, and also lubricates the sliding surfaces between theouter sleeve 88 of the fixedshaft 102 and theinner sleeve 85 of therotating shaft 113. - Operation of the present embodiment having the above-mentioned arrangement is now explained.
- Operation of the
expander 4 is first explained. In FIG. 3, high temperature, high pressure steam from theevaporator 3 is supplied to thesteam supply pipe 91, the first steam passage S1 passing through the center of the fixedshaft 102, and the pair of second steam passages S2 and S2 passing radially through the fixedshaft 102. In FIG. 10, when theinner sleeve 85 that rotates integrally with therotor 41 and theouter sleeve 21 in the direction shown by the arrow R reaches a predetermined phase relative to the fixedshaft 102, the pair of third steam passages S3 that are present on the advanced side in the direction of rotation R of therotor 41 relative to the position of the minor axis of therotor chamber 14 are made to communicate with the pair of second steam passages S2, and the high temperature, high pressure steam of the second steam passages S2 is supplied to the interiors of a pair of thecylinders 44 via the third steam passages S3 and pushes thepistons 47 radially outward. In FIG. 4, when thevanes 48 pushed by thepistons 47 move radially outward, since the pair ofrollers 71 provided on thevanes 48 are engaged with theannular channels 74, the forward movement of thepistons 47 is converted into rotational movement of therotor 41. - Even after the communication between the second steam passages S2 and the third steam passages S3 is blocked as a result of the rotation of the
rotor 41, the high temperature, high pressure steam within thecylinders 44 continues to expand, thus making thepistons 47 move further forward and thereby enabling therotor 41 to continue to rotate. When thevanes 48 reach the position of the major axis of therotor chamber 14, the third steam passages S3 communicating with the correspondingcylinders 44 also communicate with the pair ofnotches 86a formed on the outer peripheral face of the fixedsleeve 86, thepistons 47 are pushed by thevanes 48 whoserollers 71 are guided by theannular channels 74 and move radially inward, and the steam within thecylinders 44 accordingly passes through the third steam passages S3, thenotches 86a, the fourth passages S4, the fifth passage S5, and the throughholes 82b, and is supplied to thetransit chamber 19 as a first decreased temperature, decreased pressure steam. The first decreased temperature, decreased pressure steam is the high temperature, high pressure steam that has been supplied from thesteam supply pipe 91, has finished work of driving thepistons 47 and, as a result, has a decreased temperature and pressure. The thermal energy and the pressure energy of the first decreased temperature, decreased pressure steam are lower than those of the high temperature, high pressure steam, but are still sufficient for driving thevanes 48. - The first decreased temperature, decreased pressure steam within the
transit chamber 19 is supplied to thevane chambers 75 within therotor chamber 14 via theintake ports 108 of the first and second casing halves 12 and 13, and further expands therein to push thevanes 48, thus rotating therotor 41. A second decreased temperature, decreased pressure steam that has finished the work and accordingly has a further decreased temperature and pressure is discharged from theexhaust ports 109 of thesecond casing half 13 into theexhaust chamber 20, and is supplied therefrom to thecondenser 5. - In this way, the expansion of the high temperature, high pressure steam enables the twelve
pistons 47 to operate in turn to rotate therotor 41 via therollers 71 and theannular channels 74, and the expansion of the first decreased temperature, decreased pressure steam, which is the high temperature, high pressure steam whose temperature and pressure have decreased, enables therotor 41 to rotate via thevanes 48, thereby providing an output from therotating shaft 113. - Lubrication of the
vanes 48 and thepistons 47 of theexpander 4 with water is now explained. - Lubricating water is supplied using the supply pump 6 (see FIG. 1) for supplying water under pressure from the
condenser 5 to theevaporator 3, and a portion of the water discharged by thesupply pump 6 is supplied to the first water passage W1 of thecasing 11 for the purpose of lubrication. Such use of thesupply pump 6 for supplying water to the hydrostatic bearing of each section of theexpander 4 eliminates the need for a special pump and enables the number of components to be reduced. - In FIG. 3 and FIG. 8, the water that has been supplied to the first water passage W1 of the lubricating
water supply member 24 flows into thesmall diameter portion 55a of one of thepipe members 55 via the second water passages W2 of theseal block 25, the third water passages W3 of theouter sleeve 21, theannular channel 68a of the waterpassage forming member 68, the fourth water passage W4 of theouter sleeve 21, and the fifth water passages W5 formed in thepipe member 69 and therotor segment 43, and the water that has flowed into thesmall diameter portion 55a flows into thesmall diameter portion 56a of theother pipe member 56 via the throughhole 55b of said one of thepipe members 55, the sixth water passage W6 formed in thepipe members hole 56b formed in theother pipe member 56. - A portion of the water that has passed through the six
orifices plate 61 from thesmall diameter portions pipe members distribution channel 62b of the lubricatingwater distribution member 62 issues from the fourlubricating water outlets rotor segment 43, and another portion of the water issues from the lubricatingwater outlets recesses rotor segment 43. - In this way, the water issuing from the lubricating
water outlets rotor segments 43 into thevane channel 49 supports thevane 48 in a floating state by forming a hydrostatic bearing between thevane channel 49 and thevane 48, which is slidably fitted in thevane channel 49, thus preventing physical contact between the end face of therotor segment 43 and thevane 48 and thereby preventing the occurrence of seizing and wear. Supplying the water for lubricating the sliding surfaces of thevane 48 via the water passages provided in a radial shape within therotor 41 in this way not only enables the water to be pressurized by virtue of centrifugal force but also enables the temperature of the periphery of therotor 41 to be stabilized, thus lessening the effect of thermal expansion and thereby minimizing the leakage of steam by maintaining a preset clearance. - Since water is retained in the
recesses 48e, two of which are formed on each of the opposite faces of thevane 48, theserecesses 48e function as pressure reservoirs, thereby suppressing any decrease in pressure due to leakage of water. As a result thevane 48, which is held between the end faces of the pair ofrotor segments 43, is in a floating state due to the water, and the sliding resistance can thereby be reduced effectively. Furthermore, when thevane 48 reciprocates, the radial position of thevane 48 relative to therotor 41 changes, and since therecesses 48e are provided not on therotor segment 43 side but on thevane 48 side and in the vicinity of therollers 71, where the largest load is imposed on thevane 48, the reciprocatingvane 48 can always be kept in a floating state, and the sliding resistance can thereby be reduced effectively. - The water that has lubricated the sliding surfaces of the
vane 48 that are opposite therotor segments 43 moves radially outward by virtue of centrifugal force and lubricates the sliding section between theseal 72 provided on the arc-shapedface 48b of thevane 48 and the arc-shapedface 14b of therotor chamber 14. Water that has finished lubricating is discharged from therotor chamber 14 via theexhaust ports 109. - In FIG. 2, by supplying water into the
pressure chambers 110 at the bottom portions of thecircular seal channels 76 of thefirst casing half 12 and thesecond casing half 13 so as to urge the ring seals 79 toward the side faces of therotor 41, and making the water issue from the lubricatingwater outlets recesses rotor segments 43 so as to form a hydrostatic bearing on the sliding surfaces with theflat faces 14a of therotor chamber 14, the flat faces 41 a of therotor 41 can be sealed by the ring seals 79 that are in a floating state within thecircular seal channels 76 and, as a result, the steam within therotor chamber 14 can be prevented from leaking through a gap with therotor 41. In this process, the ring seals 79 and therotor 41 are isolated from each other by a film of water supplied from the lubricatingwater outlets rotor 41 tilts, the damping effect of the ring seals 79 tracking the tilting within thecircular seal channels 76 enables stable sealing characteristics to be maintained while minimizing the frictional force. - The water that has lubricated the sliding section between the ring seals 79 and the
rotor 41 is supplied to therotor chamber 14 by virtue of centrifugal force, and discharged therefrom to the exterior of thecasing 11 via theexhaust ports 109. - Furthermore, in FIG. 5, water that has been supplied from the sixth water passage W6 within the
pipe member 55 to the sliding surfaces between thecylinder 44 and thepiston 47 via the tenth water passage W10 within therotor segments 43 and theannular channel 67 of the outer periphery of thecylinder 44 exhibits a sealing function by virtue of the viscous properties of the film of water formed on the sliding surfaces, thereby preventing effectively the high temperature, high pressure steam supplied to thecylinder 44 from leaking past the sliding surfaces with thepiston 47. Since the water that is supplied to the sliding surfaces between thecylinder 44 and thepiston 47 through the interior of theexpander 4, which is in a high temperature state, is heated, it is possible to minimize any decrease in output of theexpander 4 that might be caused by this water cooling the high temperature, high pressure steam supplied to thecylinder 44. - Moreover, since water, which is the same substance as steam, is used as a medium for sealing, there will be no problem even when the steam is contaminated with water. If the sliding surfaces of the
cylinder 44 and thepiston 47 were sealed by an oil, since it would be impossible to prevent the oil from contaminating the water or steam, a special filter device for separating the oil would be required. Furthermore, since a portion of the water for lubricating the sliding surfaces of thevane 48 and thevane channels 49 is separated for sealing the sliding surfaces of thecylinder 44 and thepiston 47, it is unnecessary to specially provide an extra water passage for guiding the water to the sliding surfaces, thus simplifying the structure. - In order to maintain the sealing characteristics for the steam in the rotary valve V, it is necessary to precisely control the clearance between the sliding surfaces of the
rotating shaft 113 and the fixedshaft 102. When theexpander 4 is cold, the fixedshaft 102, through which the high temperature steam passes, first expands thermally in the vicinity of the rotary valve V, therotating shaft 113 then thermally expands after a time lag, and the difference in thermal expansion causes wear of the outer peripheral face of the fixedshaft 102. During this process, if the fixedshaft 102 is firmly fixed to thecasing 11, rotational runout of therotor 41 results in uneven contact with the outer peripheral face of the fixedshaft 102, thereby causing eccentric wear, and giving rise to problems such as degradation of the sealing characteristics for the steam in the rotary valve V, an increase in the sliding resistance, and degradation in the rotational behavior of therotor 41. - However, in accordance with the present embodiment, since the fixed
shaft 102 is floatingly supported by the fixedshaft support spring 95 relative to thecasing 11, when the rotational runout of therotor 41 is transmitted to the fixedshaft 102 via therotating shaft 113, the alignment action arising from tracking exhibited by the damping effect of the fixedshaft support spring 95 suppresses the rotational runout of therotor 41, and any increase in the frictional resistance in the sliding section between the fixedshaft 102 and therotating shaft 113 and the occurrence of abnormal wear can be prevented effectively. In this way, if the outer peripheral face of the fixedshaft 102 is uniformly worn by the action of the fixedshaft support spring 95, the clearance of the uniformly worn section of the fixedshaft 102 is uniformly reduced when theexpander 4 is hot, and the sealing characteristics of the rotary valve V can be ensured. Since the left-hand end of the fixedshaft 102 is supported via theOldham coupling 89 in a non-rotatable but radially movable manner, the alignment action of the fixedshaft 102 due to the tracking exhibited by the damping effect of the fixedshaft support spring 95 can be exhibited without any problem. - Suppressing the thermal expansion of the fixed
shaft 102 due to the heat of the steam to a low level enables wear of the outer peripheral face of the fixedshaft 102 in the vicinity of the rotary valve V to be further reduced. In the present embodiment, the fixedsleeve 86 is therefore formed by shrink-fitting theouter sleeve 88, which is made of metal, around the outer periphery of theinner sleeve 87, which is made of ceramic, etc. having a small coefficient of thermal expansion. - That is, as shown in FIG. 20A, the outer diameter Do of the
inner sleeve 87 is larger than the inner diameter Di of theouter sleeve 88 at room temperature, and theouter sleeve 88 is fitted around the outer periphery of theinner sleeve 87 in a state, as shown in FIG. 20B, in which the inner diameter Di' thereof is made larger than the outer diameter Do of theinner sleeve 87 by heating theouter sleeve 88, which is made of metal, so as to thermally expand it. When theouter sleeve 88 is cooled so as to shrink it in this state, the inner peripheral face of theouter sleeve 88 comes into intimate contact with the outer peripheral face of theinner sleeve 87 as shown in FIG. 20C, thus completing the shrink-fitting. In a state in which the shrink-fitting is completed, theouter sleeve 88, whose inner diameter should have decreased to Di (broken line), is restrained by theinner sleeve 87, and the inner diameter only decreases to an inner diameter D", which is larger than the above Di (Di < Di" < D'), and theouter sleeve 88 is in a state in which an internal stress acts on it in a tensile direction. - Therefore, as shown in FIG. 20D, when the
outer sleeve 88 and theinner sleeve 87 are heated by steam, the thermal expansion of theouter sleeve 88 is canceled by the internal stress in the tensile direction, and the outer diameter of theouter sleeve 88 does not increase substantially. In practice, the outer diameter of theouter sleeve 88 is controlled by the small amount of thermal expansion of theinner sleeve 87, which is made of ceramic, etc. having a small coefficient of thermal expansion, and increases slightly due to being widened by theinner sleeve 87. In this way, since the change due to thermal expansion in the outer diameter of the fixedsleeve 86 having theouter sleeve 88, which is a collar made of an easily stretched metal and is in sliding contact with theinner sleeve 85 of therotating shaft 113, can be suppressed by shrink-fitting, wear of the outer peripheral face of the fixedsleeve 86 can be minimized, thereby preventing the leakage of steam from the rotary valve V. - Since the
outer sleeve 88 of the fixedsleeve 86 is made of metal, a coating of a low friction material, which is difficult to apply to a ceramic sleeve, can be applied to theouter sleeve 88 and this, together with the structure of the shrink-fitting on therotating shaft 113 side, enables the frictional resistance between theouter sleeve 88 and theinner sleeve 85 to be further reduced, thus suppressing any increase in the clearance and reducing the leakage of steam. - In the same way as for the fixed
sleeve 86 of the above-mentionedfixed shaft 102, therotating shaft 113 is also formed by uniting theouter sleeve 21, which is made of metal, with the outer periphery of the ceramicinner sleeve 85 by shrink-fitting, and theouter sleeve 21 is in a state in which an internal stress acts in the tensile direction. - The effect of the shrink-fitting is now explained with reference to FIG. 21 A to FIG. 21D.
- FIG. 21 D corresponds to a conventional example in which both the
rotating shaft 113 and the fixedshaft 102 are made of metal, and when high temperature steam is supplied to the rotary valve V through the interior of the fixedshaft 102 when it is cold, the fixedshaft 102 side first expands thermally to a large extent and comes into contact with the inner peripheral face of therotating shaft 113, and wear of the sliding surfaces occurs between point a and point b. This wear occurs only when running theexpander 4 for the first time after assembly. When, after time has elapsed, it is hot, that is, when the temperatures of both the fixedshaft 102 and therotating shaft 113 are sufficiently high, the amount of expansion of therotating shaft 113 becomes larger than the amount of expansion of the fixedshaft 102, and the clearance therebetween gradually enlarges. In this way, in the conventional arrangement, both the fixedshaft 102 and therotating shaft 113 expand thermally, thus generating wear of the sliding surfaces and increasing the clearance when hot. - On the other hand, FIG. 21 A shows the characteristics of the present embodiment in which shrink-fitting is employed for both the
rotating shaft 113 and the fixedshaft 102. The radii of therotating shaft 113 and the fixedshaft 102 hardly change from when they are cold to when they are hot, and the clearance between the sliding surfaces thereof is always maintained substantially constant. - FIG. 21B shows the characteristics when shrink-fitting is employed only for the
rotating shaft 113 side. The fixedshaft 102 side expands thermally accompanying the starting of the supply of steam and comes into contact with the inner peripheral face of therotating shaft 113, which hardly expands at all, thereby generating wear on the outer peripheral face of the fixedshaft 102. This wear occurs only when running theexpander 4 for the first time after assembly, and once bedding in due to the wear is completed, the clearance between the sliding surfaces is always maintained substantially constant in subsequent running. - FIG. 21 C shows the characteristics when shrink-fitting is employed only for the fixed
shaft 102 side. Therotating shaft 113 side expands thermally accompanying the starting of the supply of steam and the clearance between itself and therotating shaft 113, which hardly expands at all thermally, gradually increases, but since contact between the fixedshaft 102 and therotating shaft 113 is avoided, wear will not be caused, and the sliding resistance therebetween can be minimized. - As hereinbefore described, the maximum effect can be obtained when shrink-fitting is employed for both the
rotating shaft 113 and the fixedshaft 102, and the expected effect can also be obtained when shrink-fitting is employed for only one of therotating shaft 113 or the fixedshaft 102. - Even if an attempt is made to prevent the steam from leaking from the rotary valve V as described above, it is impossible to prevent a slight amount of steam from leaking past the sliding surfaces of the
rotating shaft 113 and the fixedshaft 102. This leaked steam is captured by the port holes 88d and theport channels 87d annularly formed on the outer peripheral face of the fixedsleeve 86, and is supplied therefrom to thetransit chamber 19 via the twopassages 87b formed on the mating surfaces between theinner sleeve 87 and theouter sleeve 88, theannular channel 87c formed in theinner sleeve 87, and the throughhole 88a formed in theouter sleeve 88. The steam that has been supplied to thetransit chamber 19 is combined with the first decreased temperature, decreased pressure steam that has finished driving thepistons 47, and is provided for driving thevanes 48. In this way, the steam that has leaked from the rotary valve V is captured by the port holes 88d and theport channels 87d and reused, thereby contributing an improvement of the overall energy efficiency of theexpander 4. - When the
outer sleeve 88, which is made of metal, of the fixedsleeve 86 is worn due to sliding against the ceramicinner sleeve 85 of therotating shaft 113, the abraded powder thus formed is collected by the abradedpowder collecting channels 88c formed on the outer peripheral face of theouter sleeve 88, and thereby prevented from accumulating on the sliding surfaces of the fixedsleeve 86 and theinner sleeve 85 ofrotating shaft 113. It is thereby possible to avoid any increase in the frictional resistance and the occurrence of seizure of the sliding surfaces. - If the water that has been supplied from the sixteenth water passage W16 and lubricated the sliding surfaces of the fixed
sleeve 86 and theinner sleeve 85 of therotating shaft 113 and the water that has lubricated the outer peripheral face of therotating shaft 113 through the orifice penetrating the bearingmembers sleeve 86 and theinner sleeve 85 of therotating shaft 113 were to flow into thetransit chamber 19 via the port holes 88d and theport channels 87d formed in the outer periphery of the fixedsleeve 86, the first decreased temperature, decreased pressure steam within thetransit chamber 19 might be cooled, and the output of theexpander 4 might be degraded. - However, in accordance with the present embodiment, when the water that lubricates the sliding surfaces of the fixed
sleeve 86 and theinner sleeve 85 of therotating shaft 113 flows from opposite ends of the fixedsleeve 86 toward the port holes 88d and theport channels 87d in the center, thespiral channels 88b formed on the outer periphery of theouter sleeve 88 can exhibit an effect of generating a pressure so as to push back the lubricating water away from the port holes 88d and theport channels 87d. That is, as a result of the relative rotation between theinner sleeve 85 of therotating shaft 113 and the fixedsleeve 86 the lubricating water retained in thespiral channels 88b is pressurized by a spring pump action and pushed back in a direction away from the port holes 88d and the port channels. - If the
spiral channels 88b were made to communicate with the port holes 88d and theport channels 87d without being sectioned into short lengths, there is the possibility that high pressure lubricating water might pass through the interior of thespiral channels 88b without being stopped and flow into the lowpressure port holes 88d and theport channels 87d, but this problem can be solved by sectioning thespiral channels 88b into short lengths. - Furthermore, the first water passage W1 and the eleventh water passage W11 are independent from each other, and water is supplied at a pressure that is required for each of the lubrication sections. More specifically, the water that is supplied from the first water passage W1 is mainly for floatingly supporting the
vanes 48 and therotor 41 by means of a hydrostatic bearing as described above, and it is required to have a high pressure that can counterbalance variations in the load. In contrast, the water that is supplied from the eleventh water passage W11 mainly lubricates the surroundings of the fixedshaft 102 and the bearingmembers shaft 102 so as to reduce the influence of thermal expansion of the fixedshaft 102, therotating shaft 113, therotor 41, etc., it is required to have a pressure that is at least higher than the pressure of thetransit chamber 19. - Since there are provided in this way two water supply lines, that is, the first water passage W1 for supplying high pressure water and the eleventh water passage W11 for supplying lower pressure water, problems caused when only one water supply line for supplying high pressure water is provided can be eliminated. That is, the problem of water having excess pressure being supplied to the surroundings of the fixed
shaft 102, thus increasing the amount of water flowing into thetransit chamber 19, and the problem of the fixedshaft 102, therotating shaft 113, therotor 41, etc. being overcooled, thus decreasing the temperature of the steam, can be prevented, and as a result the output of theexpander 4 can be increased while reducing the amount of water supplied. - A second embodiment of the present invention is now explained with reference to FIG. 22 and FIG. 23. The second embodiment is different from the first embodiment with respect to the structure of the fixed
shaft support spring 95, and the structures of the other parts are the same as those of the first embodiment. - In the second embodiment, a second fixed
shaft 93 extends leftward so as to cover the outer periphery of asteam supply pipe 91, and the left-hand end of the second fixedshaft 93 is fitted in and fixed to aboss portion 81 a of aspring support member 81. A plurality (eight in this embodiment) ofslits 93b extending in the axis L direction are formed in the second fixedshaft 93 adjacent to theboss portion 81 a of thespring support member 81, and the section where theseslits 93b are formed functions as a fixedshaft support spring 95. The fixedshaft support spring 95 can easily be elastically deformed in the radial direction by virtue of theslits 93b and, moreover, it can withstand a load in the axis L direction without being deformed. - In order to prevent steam that has leaked from the section where the right-hand end of the
steam supply pipe 91 and the left-hand end of the first fixedshaft 92 are fitted together from passing through theslits 93b of the fixedshaft support spring 95 and leaking into thetransit chamber 19, the outer periphery of the fixedshaft support spring 95 is covered by a sealingtube 111 and bellows 112. The right-hand end of the sealingtube 111 is held between the second fixedshaft 93 and theinner sleeve 87, and the left-hand end thereof extends to a middle section of the fixedshaft support spring 95. The left-hand end of thebellows 112 is welded to theboss portion 81 a of thespring support member 81, and the right-hand end thereof is welded to the right-hand end of the sealingtube 111. Since the sealingtube 111 and thebellows 112 can easily flex in the radial direction, elastic deformation of the fixedshaft support spring 95 is not inhibited. - This second embodiment can also achieve the same effects as those obtained by the above-mentioned first embodiment.
- Other than the embodiments described above, as an arrangement for a power conversion device for converting the forward movement of
pistons 47 into the rotational movement of arotor 41, the forward movement of thepistons 47 can be directly transmitted torollers 71 without involvingvanes 48, and can be converted into rotational movement by engagement withannular channels 74. Furthermore, as long as thevanes 48 are always spaced from the inner peripheral face of arotor chamber 14 by a substantially constant gap as a result of cooperation between therollers 71 and theannular channels 74 as described above, thepistons 47 and therollers 71, and also thevanes 48 and therollers 71, can independently work together with theannular channels 74. - When the
expander 4 is used as a compressor, therotor 41 is rotated by therotating shaft 113 in a direction opposite to the arrow R in FIG. 4, outside air is drawn in by thevanes 48 from theexhaust ports 109 into therotor chamber 14 and compressed, and the low pressure compressed air thus obtained is drawn in from theintake ports 108 into thecylinders 44 via thetransit chamber 19, the throughholes 82b, the fifth steam passages S5, the fourth steam passages S4, thenotches 86a of the fixedshaft 102 and the third steam passages S3, and compressed there by thepistons 47 to give high pressure compressed air. The high pressure compressed air thus obtained is discharged from thecylinders 44 via the third steam passages S3, the second steam passages S2, the first steam passage S1, and thesteam supply pipe 91. When theexpander 4 is used as a compressor, the steam passages S1 to S5 and thesteam supply pipe 91 are read instead as air passages S1 to S5 andair supply pipe 91. - Although embodiments of the present invention are described in detail above, the present invention can be modified in a variety of ways without departing from the scope and spirit thereof.
- For example, in the embodiments, the
expander 4 is illustrated as the rotary fluid machine, but the present invention can also be applied to a compressor. - Furthermore, in the embodiments, steam and water are used as the gas-phase working medium and the liquid-phase working medium, but other appropriate working media can also be employed.
- The present invention can desirably be applied to an expander employing steam (water) as a working medium, but can also be applied to an expander employing any other working medium and a compressor employing any working medium.
Claims (2)
- A rotary fluid machine comprising a rotor (41) rotatably housed within a casing (11), a hollow rotating shaft (113) that rotates integrally with the rotor (41), and a fixed shaft (102) that is relatively rotatably fitted into the inner periphery of the rotating shaft (113),
characterized in that the fixed shaft (102) is floatingly supported in the casing (11) via resilient support means (95) having an alignment action. - The rotary fluid machine according to Claim 1, wherein a rotary valve (V) for controlling supplying and discharging of a high temperature gas-phase working medium is provided on sliding surfaces of the rotating shaft (113) and the fixed shaft (102).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001289387A JP2003097211A (en) | 2001-09-21 | 2001-09-21 | Rotary fluid machine |
JP2001289387 | 2001-09-21 | ||
PCT/JP2002/009719 WO2003027439A1 (en) | 2001-09-21 | 2002-09-20 | Rotary fluid machine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1428977A1 true EP1428977A1 (en) | 2004-06-16 |
Family
ID=19111885
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02772879A Withdrawn EP1428977A1 (en) | 2001-09-21 | 2002-09-20 | Rotary fluid machine |
Country Status (4)
Country | Link |
---|---|
US (1) | US20050019161A1 (en) |
EP (1) | EP1428977A1 (en) |
JP (1) | JP2003097211A (en) |
WO (1) | WO2003027439A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8022028B2 (en) * | 2008-06-17 | 2011-09-20 | Colgate-Palmolive Company | Light duty liquid cleaning compositions and methods of manufacture and use thereof comprising organic acids |
US7718595B2 (en) * | 2008-06-17 | 2010-05-18 | Colgate Palmolive Company | Light duty liquid cleaning compositions and methods of manufacture and use thereof comprising organic acids |
US20090312226A1 (en) * | 2008-06-17 | 2009-12-17 | Colgate-Palmolive Company | Light Duty Liquid Cleaning Compositions And Methods Of Manufacture And Use Thereof |
US8247362B2 (en) | 2008-06-17 | 2012-08-21 | Colgate-Palmolive Company | Light duty liquid cleaning compositions and methods of manufacture and use thereof |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3585904A (en) * | 1968-11-26 | 1971-06-22 | Meyer P White | Compressor |
US3574493A (en) * | 1969-04-21 | 1971-04-13 | Abex Corp | Vane-type pumps |
US5993173A (en) * | 1996-03-06 | 1999-11-30 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Turbocharger |
CN1510252A (en) * | 1999-03-05 | 2004-07-07 | 本田技研工业株式会社 | Rotary fluid machinery, blade fluid machinery and waste heat recovering device of IC engine |
JP2002070501A (en) * | 2000-09-04 | 2002-03-08 | Honda Motor Co Ltd | Rotary fluid machinery |
-
2001
- 2001-09-21 JP JP2001289387A patent/JP2003097211A/en active Pending
-
2002
- 2002-09-20 EP EP02772879A patent/EP1428977A1/en not_active Withdrawn
- 2002-09-20 US US10/489,641 patent/US20050019161A1/en not_active Abandoned
- 2002-09-20 WO PCT/JP2002/009719 patent/WO2003027439A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO03027439A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2003027439A1 (en) | 2003-04-03 |
JP2003097211A (en) | 2003-04-03 |
US20050019161A1 (en) | 2005-01-27 |
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