JP4344451B2 - Rotary fluid machine - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a rotary fluid machine that can be used as an expander or a compressor.
[0002]
[Prior art]
  Japanese Patent Application Laid-Open No. 59-41602 describes a double multi-vane rotary machine. In this structure, a circular vane support ring is arranged between an elliptical outer cam ring and an elliptical inner cam ring, and the outer ends and inner ends of a plurality of vanes supported radially slidably on the vane support ring. The ends are brought into contact with the inner peripheral surface of the outer cam ring and the outer peripheral surface of the inner cam ring, respectively. Therefore, when the vane support ring rotates relative to the outer cam ring and the inner cam ring, the volume of the plurality of working chambers partitioned by the vane between the outer cam ring and the vane support ring is expanded and reduced to function as an expander or a compressor. In addition, the volume of the plurality of working chambers partitioned by the vanes between the inner cam ring and the vane support ring is enlarged or reduced to function as an expander or a compressor.
[0003]
  In this double multi-vane rotating machine, the outer and inner rotating machines can be used as independent expanders, the outer and inner rotating machines can be used as independent compressors, and the outer and inner rotating machines can be used. One and the other can be used as an expander and a compressor, respectively.
[0004]
  Japanese Patent Application Laid-Open No. 60-206990 describes a vane type rotary machine that can be used as an expander or a compressor. In this arrangement, a circular intermediate cylinder is eccentrically disposed between a circular outer cam ring and a circular inner cam ring arranged concentrically, and the outer sides of a plurality of vanes supported slidably in the radial direction on the intermediate cylinder. The end and the inner end are brought into contact with the inner peripheral surface of the outer cam ring and the outer peripheral surface of the inner cam ring, respectively. Therefore, when the intermediate cylinder rotates relative to the outer cam ring and the inner cam ring, the volume of the plurality of working chambers partitioned by the vane between the outer cam ring and the vane support ring is enlarged and reduced to function as an expander or a compressor. In addition, the volume of the plurality of working chambers partitioned by the vanes between the inner cam ring and the vane support ring is enlarged and reduced to function as an expander or a compressor.
[0005]
  In this vane type rotating machine, the outer and inner rotating machines can be used as independent expanders, and the outer and inner rotating machines can be used as independent compressors. By allowing the working fluid that has passed through one to pass through the other, the outer and inner rotary machines can be connected in series and operated as a two-stage expander or a two-stage compressor.
[0006]
  Japanese Laid-Open Patent Publication No. 64-29676 discloses a radial plunger pump. In this type, a plurality of cylinders are radially formed in a rotor arranged eccentrically inside a circular cam ring, and the tip of a plunger that is slidably fitted to these cylinders is brought into contact with the inner peripheral surface of the cam ring to reciprocate. It is made to operate as a pump by moving it.
[0007]
[Problems to be solved by the invention]
  By the way, what is disclosed in the above-mentioned JP-A-59-41602 and JP-A-60-206990 includes a plurality of vane-type rotating machines arranged inside and outside in the radial direction. The structure of the pressure energy and mechanical energy conversion mechanism is simple and can handle a large amount of working fluid while having a compact structure, but it is highly efficient due to the large amount of working fluid leaked from the sliding part of the vane. There is a problem that it is difficult.
[0008]
  In addition, the radial plunger pump disclosed in Japanese Patent Laid-Open No. 64-29676 has a high working fluid sealability because the working fluid is compressed by a piston that is slidably fitted into the cylinder, and the working fluid is high pressure. Although the efficiency reduction due to leakage can be suppressed to a minimum even with the use of, the crank mechanism and the swash plate mechanism for converting the reciprocating motion of the piston into a rotational motion are required, and the structure becomes complicated.
[0009]
  The present invention has been made in view of the above-described circumstances, and an object thereof is to combine the advantages of a piston type and a vane type in a rotary fluid machine.
[0010]
[Means for Solving the Problems]
  In order to achieve the above object, according to the first aspect of the present invention, at least a first energy conversion means and a second energy conversion means are provided, and a working fluid having pressure energy is input to the first and second energy conversion means. Then, by converting the pressure energy into mechanical energy, the first and second energy conversion means can function as an expander that integrates and outputs the generated mechanical energy, and the mechanical energy is converted into the first energy. 1. Compression that is input to the second energy conversion means and converts the mechanical energy into pressure energy of the working fluid, thereby integrating and outputting the pressure energy of the working fluid generated by the first and second energy conversion means, respectively. In the rotary fluid machine capable of functioning as a container, the first energy conversion meansTheA cylinder formed radially on a rotor rotatably accommodated in the rotor chamber, and a piston that slides in the cylinderShiThe second energy conversion meansThe, Appearing radially from the rotor, OutsideThe peripheral surface is the inner peripheral surface of the rotor chamberThrough the seal memberConsists of sliding vanesThe vanes and the piston interlocking with the piston are engaged with a non-circular annular groove formed in the casing defining the rotor chamber, and the reciprocating motion of the piston and the rotational motion of the rotor are mutually converted by the engagement. And restricting the gap between the outer peripheral surface of the vane and the inner peripheral surface of the rotor chamberA rotary fluid machine characterized by this is proposed.
[0011]
  According to the above configuration, the first energy conversion means is composed of the cylinder formed radially in the rotor rotatably accommodated in the rotor chamber and the piston sliding in the cylinder. It is possible to improve the sealing performance of the working fluid and minimize the efficiency reduction due to leakage. The second energy conversion means is supported by the rotor so as to be movable in the radial direction, and is disposed on the inner peripheral surface of the rotor chamber.Through the seal memberSince the vane is in sliding contact, the structure of the pressure energy and mechanical energy conversion mechanism is simple, and a large flow rate of working fluid can be processed with a compact structure. As described above, by combining the first energy conversion means having the piston and the cylinder and the second energy conversion means having the vane, a high-performance rotary fluid machine having both features can be obtained.
[0012]
  Further, since the roller interlocking with the vane and the piston moving in the radial direction with respect to the rotor rotating inside the rotor chamber is engaged with the non-circular annular groove formed in the casing defining the rotor chamber, the roller and A simple structure consisting of an annular groove can convert the reciprocating motion of the piston into the rotational motion of the rotor when it functions as an expander, and the reciprocating motion of the rotor when it functions as a compressor. Can be converted to In addition, by guiding the movement trajectory of the roller with the annular groove, the gap between the outer peripheral surface of the vane and the inner peripheral surface of the rotor chamber can be regulated to prevent occurrence of abnormal wear and leakage.
[0013]
  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the first energy converting means converts the reciprocating motion of the piston and the rotational motion of the rotating shaft to each other, and A rotary fluid machine is proposed in which the two energy conversion means mutually converts the movement of the vane in the circumferential direction and the rotational movement of the rotary shaft.
[0014]
  According to the above configuration, the first energy converting means mutually converts the reciprocating motion of the piston and the rotating motion of the rotating shaft, and the second energy converting means is the movement of the vane in the circumferential direction and the rotating motion of the rotating shaft. Are mutually converted, so that the fluid is compressed by the first and second energy converting means by the input of external force from the rotating shaft, and the rotating shaft is driven by the first and second energy converting means by supplying the high pressure fluid. Can do. Thereby, the mechanical energy can be integrated and output by the first and second energy conversion means, or the pressure energy of the working fluid can be integrated and output by the first and second energy conversion means.
[0015]
  According to the invention described in claim 3, in addition to the structure of claim 2, a rotary fluid machine is proposed in which the rotating shaft supports a rotor.
[0016]
  According to the above configuration, since the rotor is supported on the rotating shaft, the mechanical energy generated by the pistons and cylinders or vanes provided on the rotor can be efficiently output to the rotating shaft, and the mechanical energy can be applied to the rotating shaft. Just by inputting, the working fluid can be efficiently compressed by the piston and cylinder or vane provided on the rotor supported by the rotating shaft.
[0017]
  According to a fourth aspect of the present invention, in addition to the configuration of the first aspect, when functioning as an expander, the total amount of the working fluid that has passed through the first energy conversion unit is the second energy conversion unit. When rotating and functioning as a compressor, a rotary fluid machine is proposed in which the entire amount of working fluid that has passed through the second energy conversion means passes through the first energy conversion means.
[0018]
  According to the above configuration, when the first and second energy conversion means are connected in series and function as an expander, first, a high-pressure working fluid is passed through the first energy conversion means, and a part of the pressure energy is mechanically transmitted. By converting the working fluid whose pressure has been reduced as a result of passing through the second energy converting means to convert the remainder of the pressure energy into mechanical energy, the pressure energy of the working fluid is efficiently converted into mechanical energy. Can be converted. Conversely, when functioning as a compressor, the rotating shaft is rotated by mechanical energy, the working fluid is compressed by the second energy conversion means, and the compressed working fluid is further compressed by the first energy conversion means. The mechanical energy can be efficiently converted into the pressure energy of the working fluid.
[0019]
  According to the fifth aspect of the present invention, in addition to the configuration of the first aspect, when functioning as an expander, the pressure energy of the working fluid is converted into mechanical energy at two positions where the phase of the rotor is shifted by 180 °. In addition, a rotary fluid machine is proposed that converts mechanical energy into pressure energy of the working fluid at two locations where the rotor phase is 180 ° shifted when functioning as a compressor.
[0020]
  According to the above configuration, the portion that converts the pressure energy of the working fluid into the mechanical energy or the portion that converts the mechanical energy into the pressure energy of the working fluid is arranged at two positions whose phases of the rotor are shifted by 180 °. As a result, the rotor can rotate smoothly and the intake timing and exhaust timing can be made more efficient.The
[0021]
  And claims6According to the invention described in claim1In addition to the above structure, a rotary fluid machine is proposed in which the rotation axis of the rotor is aligned with the center of the rotor chamber.
[0022]
  According to the above configuration, since the rotation axis of the rotor coincides with the center of the rotor chamber, it is possible to prevent the load from being applied to the rotor and to prevent vibration associated with the rotation of the rotor.
[0023]
  In addition, the output shaft 23 of an Example respond | corresponds to the rotating shaft of this invention, and the cylinder member 39 of an Example respond | corresponds to the cylinder of this invention.
[0024]
DETAILED DESCRIPTION OF THE INVENTION
  In FIG. 1, a waste heat recovery device 2 of an internal combustion engine 1 uses a waste heat of the internal combustion engine 1, for example, exhaust gas, as a heat source, a high pressure state steam that is raised in temperature from a high pressure liquid, for example, water, that is, a high temperature. An evaporator 3 that generates high-pressure steam, an expander 4 that generates output due to expansion of the high-temperature and high-pressure steam, and steam that has been discharged from the expander 4 and that has fallen in temperature and pressure, that is, a temperature drop It has a condenser 5 for liquefying the low-pressure steam, and a supply pump 6 for supplying a liquid such as water from the condenser 5 to the evaporator 3 under pressure.
[0025]
  The inflator 4 has a special structure and is configured as follows.
[0026]
  2-5, the casing 7 is comprised from the metal 1st, 2nd half bodies 8 and 9. As shown in FIG. Both halves 8 and 9 are composed of a main body 11 having a substantially elliptical recess 10 and a circular flange 12 integral with the main body 11, and the both circular flanges 12 are overlapped with a metal gasket 13 to form a substantially elliptical shape. The rotor chamber 14 is formed. The outer surface of the main body 11 of the first half 8 is covered with a deep bowl-shaped main body 16 of a shell-shaped member 15, and a circular flange 17 integral with the main body 16 is attached to the circular flange 12 of the first half 8. The three circular flanges 12, 12, and 17 are fastened by bolts 19 at a plurality of positions in the circumferential direction. Thus, a relay chamber 20 is formed between the main bodies 11 and 16 of the shell-shaped member 15 and the first half 8.
[0027]
  The main body 11 of both halves 8, 9 has hollow bearing cylinders 21, 22 projecting outward on their outer surfaces, and a hollow output shaft 23 penetrating the rotor chamber 14 in the hollow bearing cylinders 21, 22. The large diameter portion 24 is rotatably supported via a bearing metal (or resin bearing) 25. As a result, the axis L of the output shaft 23 passes through the intersection of the major axis and the minor axis in the rotor chamber 14 having a substantially elliptical shape. The small-diameter portion 26 of the output shaft 23 protrudes outside from a hole portion 27 in the hollow bearing cylinder 22 of the second half 9 and is connected to the transmission shaft 28 via a spline coupling 29. A space between the small diameter portion 26 and the hole portion 27 is sealed by two seal rings 30.
[0028]
  A circular rotor 31 is accommodated in the rotor chamber 14, and the shaft mounting hole 32 at the center thereof and the large-diameter portion 24 of the output shaft 23 are in a fitting relationship. Is provided. As a result, the rotation axis of the rotor 31 coincides with the axis L of the output shaft 23, so that “L” is shared as the code of the rotation axis.
[0029]
  In the rotor 31, a plurality of, in this embodiment, twelve slot-like spaces 34 extending radially from the shaft mounting hole 32 around the rotation axis L are formed at equal intervals on the circumference. Each space 34 has a substantially U-shape in a virtual plane orthogonal to both end surfaces 35 so that the circumferential width is narrow and opens continuously to both end surfaces 35 and the outer peripheral surface 36 of the rotor 31.
[0030]
  In each slot-like space 34, first to twelfth vane piston units U1 to U12 having the same structure are mounted so as to be reciprocally movable in the radial direction as follows. In a substantially U-shaped space 34, a stepped hole 38 is formed in a portion 37 that divides the inner peripheral side, and a stepped cylinder member 39 made of ceramic (or carbon) is fitted into the stepped hole 38. . The end surface of the small-diameter portion a of the cylinder member 39 abuts on the outer peripheral surface of the large-diameter portion 24 of the output shaft 23, and the small-diameter hole b communicates with a through hole c that opens on the outer peripheral surface of the large-diameter portion 24. A guide tube 40 is disposed outside the cylinder member 39 so as to be coaxial with the member 39. The outer end portion of the guide cylinder 40 is locked to the opening portion of the space 34 existing on the outer peripheral surface of the rotor 31, and the inner end portion is fitted into the large-diameter hole d of the stepped hole 38 and comes into contact with the cylinder member 39. . The guide tube 40 has a pair of long grooves e extending from the outer end portion to the vicinity of the inner end portion, and both the long grooves e face the space 34. A piston 41 made of ceramic is slidably fitted in the large-diameter cylinder hole f of the cylinder member 39, and the tip end side of the piston 41 is always located in the guide cylinder 40.
[0031]
  As shown in FIGS. 2 and 6, the cross section B of the rotor chamber 14 in the virtual plane A including the rotation axis L of the rotor 31 has a pair of semicircular cross sections B1 with the diameter g facing each other, The circular cross section B1 is composed of a square cross section B2 formed by connecting one opposing end and the other opposing end of both diameters g, and forms a substantially competition track shape. In FIG. 6, the solid line portion indicates the maximum cross section including the major axis, while the part indicated by a two-dot chain line indicates the minimum cross section including the minor axis. The rotor 31 has a cross section D that is slightly smaller than the minimum cross section including the minor axis of the rotor chamber 14, as indicated by a dotted line in FIG.
[0032]
  As clearly shown in FIGS. 2 and 7 to 10, the vane 42 has a vane body 43 having a substantially U-shaped plate (horse-shoe shape), and a sealing member 44 having a substantially U-shaped plate attached to the vane body 43. And a vane spring 58.
[0033]
  The vane body 43 includes a semicircular arc-shaped portion 46 corresponding to the inner peripheral surface 45 defined by the semicircular sectional portion B1 of the rotor chamber 14 and a pair of parallel portions 48 corresponding to the opposed inner end surface 47 defined by the rectangular sectional portion B2. A U-shaped notch 49 on the end side of each parallel portion 48, a rectangular blind hole 50 opening on the bottom surface thereof, and further outward from the notch 49 on the end side. A short shaft 51 is provided. Further, a series of U-shaped grooves 52 opening outward are formed in the outer peripheral portions of the semicircular arc-shaped portion 46 and both parallel portions 48, and both end portions of the U-shaped groove 52 communicate with both notches 49, respectively. . Further, a pair of protrusions 53 having a non-circular cross section are provided on both planar portions of the semicircular arc portion 46. Both protrusions 53 are arranged so that the axis L1 of the virtual cylinder formed by them coincides with a straight line that bisects the interval between the parallel parts 48 and bisects the semicircular arc-shaped part 46 in the circumferential direction. ing. Further, the inner end portions of both protrusions 53 slightly protrude into the space between both parallel portions 48.
[0034]
  The seal member 44 is made of, for example, PTFE, and slides a semicircular arc-shaped portion 55 that slides on the inner peripheral surface 45 by the semicircular cross-sectional portion B1 of the rotor chamber 14 and an opposing inner end surface 47 by the quadrangular cross-sectional portion B2. And a pair of parallel portions 56 that move. A pair of elastic claws 57 are provided on the inner peripheral surface side of the semicircular arc-shaped portion 55 so as to warp inward.
[0035]
  A seal member 44 is mounted in the U-shaped groove 52 of the vane main body 43, a vane spring 58 is fitted in each blind hole 50, and a roller 59 having a ball bearing structure is attached to each short shaft 51. Each vane 42 is slidably accommodated in each slot-like space 34 of the rotor 31. At this time, both protrusions 53 of the vane main body 43 are in the guide tube 40, and both side portions of both protrusions 53 are guides. The inner end surfaces of both protrusions 53 can be brought into contact with the outer end surfaces of the pistons 41, respectively. Both rollers 59 are respectively engaged with a substantially elliptical annular groove 60 formed on the opposed inner end faces 47 of the first and second halves 8 and 9 in a freely rotatable manner. The distance between these annular grooves 60 and the rotor chamber 14 is constant over their entire circumference. Further, the forward movement of the piston 41 is converted into the rotational movement of the rotor 31 by the engagement of the roller 59 and the annular groove 60 via the vane 42.
[0036]
  With the cooperation of the roller 59 and the annular groove 60, as clearly shown in FIG. 5, the semicircular tip end surface 61 in the semicircular arc portion 46 of the vane main body 43 extends from the inner peripheral surface 45 of the rotor chamber 14 and both. The parallel portions 48 are always separated from the opposed inner end face 47 of the rotor chamber 14 respectively, thereby reducing the friction loss. Since the track is regulated by the annular groove 60 constituted by a pair of two strips, the vane 42 is rotated by a minute displacement angle in the axial direction via the roller 59 due to a left and right track error. The contact pressure with the peripheral surface 45 is increased. At this time, in the vane body 43 having a substantially U-shaped plate (horse-shoe shape), the radial direction length of the contact portion with the casing 7 is shorter than that of the square (rectangular) vane, so that the amount of displacement can be greatly reduced. As clearly shown in FIG. 2, in the seal member 44, the two parallel portions 56 are brought into close contact with the opposed inner end surface 47 of the rotor chamber 14 by the elastic force of the vane springs 58, and particularly the end portions of the two parallel portions 56. A sealing action is performed on the annular groove 60 between the vanes 42. The semicircular arc-shaped portion 55 is in close contact with the inner peripheral surface 45 when both elastic claws 57 are pressed between the vane body 43 and the inner peripheral surface 45 in the rotor chamber 14. That is, since the substantially U-shaped vane 42 has no inflection point with respect to the square (rectangular) vane, the adhesion is improved. Square vanes have corners, making it difficult to maintain sealing properties. Thereby, the sealing performance between the vane 42 and the rotor chamber 14 is improved. Further, the vane 42 and the rotor chamber 14 are deformed with the thermal expansion. At this time, the substantially U-shaped vane 42 is deformed more uniformly with a similar shape to the square vane, so that there is little variation in the clearance between the vane 42 and the rotor chamber 14, and the sealing performance can be maintained well.
[0037]
  The sealing action between the vane body 43 and the inner peripheral surface of the rotor chamber 14 includes the spring force of the seal member 44 itself, the centrifugal force acting on the seal member 44 itself, and the high pressure side rotor chamber 14 to the vane body 43. The steam that has entered the U-shaped groove 52 is generated by the steam pressure that pushes up the seal member 44. Thus, since the sealing action is not affected by excessive centrifugal force acting on the vane body 43 according to the rotational speed of the rotor 31, the seal surface pressure does not depend on the centrifugal force applied to the vane body 43, It is always possible to achieve both good sealing properties and low friction properties.
[0038]
  2 and 3, the large-diameter portion 24 of the output shaft 23 is a thick portion 62 supported by the bearing metal 25 of the second half 9, and the bearing of the first half 8 extending from the thick portion 62. A thin portion 63 supported by the metal 25. A hollow shaft 64 made of ceramic (or metal) is fitted into the thin-walled portion 63 so as to rotate integrally with the output shaft 23. A fixed shaft 65 is disposed inside the hollow shaft 64, and the fixed shaft 65 includes a large-diameter solid portion 66 fitted to the hollow shaft 64 so as to be within the axial thickness of the rotor 31, and an output shaft. A small-diameter solid portion 69 fitted into a hole 67 in the thick-walled portion 62 of the 23 through two seal rings 68, and a thin-walled portion extending from the large-diameter solid portion 66 and fitted into the hollow shaft 64. The hollow portion 70 is formed. A seal ring 71 is interposed between the outer peripheral surface of the end portion of the hollow portion 70 and the inner peripheral surface of the hollow bearing cylinder 21 of the first half 8.
[0039]
  In the main body 16 of the shell-shaped member 15, an end wall 73 of a hollow cylindrical body 72 that is coaxial with the output shaft 23 is attached to the inner surface of the center portion via a seal ring 74. The inner end side of the short outer cylinder portion 75 extending inward from the outer peripheral portion of the end wall 73 is connected to the hollow bearing cylinder 21 of the first half 8 via a connection cylinder 76. The end wall 73 is provided with a long inner pipe portion 77 having a small diameter so as to pass through the end wall 73, and the inner end side of the inner pipe portion 77 has a large fixed shaft 65 together with a short hollow connecting pipe 78 protruding therefrom. It is fitted into a stepped hole h existing in the diameter solid portion 66. The outer end portion of the inner pipe portion 77 protrudes outward from the hole 79 of the shell-shaped member 15, and the inner end of the first high-temperature and high-pressure steam introduction pipe 80 inserted into the inner pipe portion 77 from the outer end portion. The side is fitted into the hollow connecting tube 78. A cap member 81 is screwed to the outer end portion of the inner pipe portion 77, and the cap member 81 causes the flange 83 of the holder cylinder 82 that holds the introduction pipe 80 to pass through the seal ring 84 to the outer end surface of the inner pipe portion 77. And crimped.
[0040]
  As shown in FIGS. 2 to 4 and 11, the large-diameter solid portion 66 of the fixed shaft 65, the cylinder member 39 of the first to twelfth vane piston units U 1 to U 12, the hollow shaft 64 and the output shaft 23 High temperature and high pressure steam is supplied through a plurality of series formed, twelve through holes c in this embodiment, and is discharged from the cylinder member 39 through the first temperature-decreasing and lowering steam after the expansion. A rotary valve V is provided as follows.
[0041]
  FIG. 11 shows the structure of a rotary valve V that supplies and discharges steam to each cylinder member 39 of the expander 4 at a predetermined timing. In the large-diameter solid portion 66, first and second hole portions 86 and 87 extending in opposite directions from a space 85 communicating with the hollow connection pipe 78 are formed, and the first and second hole portions 86 and 87 are formed as follows. Opening is made on the bottom surfaces of the first and second recesses 88 and 89 that are opened on the outer peripheral surface of the large-diameter solid portion 66. Carbon first and second seal blocks 92 and 93 having supply ports 90 and 91 are attached to the first and second recesses 88 and 89, and their outer peripheral surfaces rub against the inner peripheral surface of the hollow shaft 64. The first and second supply pipes 94 and 95 are coaxially inserted into the first and second hole parts 86 and 87 so as to be inserted into the outer peripheral surfaces on the front end side of the first and second supply pipes 94 and 95. The tapered outer peripheral surfaces i and j of the fitted first and second seal cylinders 96 and 97 are located inside the supply ports 90 and 91 of the first and second seal blocks 92 and 93 and are connected to the tapered holes k and m Fits to the inner peripheral surface. The large-diameter solid portion 66 includes first and second annular recesses n and o surrounding the first and second supply pipes 94 and 95, and first and second blind hole-shaped recesses p and q adjacent to the first and second annular recesses p and q. Is formed so as to face the first and second seal blocks 92, 93, and the first and second annular recesses n, o are fitted to the outer peripheral surfaces of the first and second seal cylinders 96, 97 on one end side. 1 and second bellows-like elastic bodies 98 and 99, and first and second blind hole-like recesses p and q contain first and second coil springs 100 and 101, respectively. The first and second seal blocks 92 and 93 are pressed against the inner peripheral surface of the hollow shaft 64 by the elastic force of the elastic bodies 98 and 99 and the first and second coil springs 100 and 101.
[0042]
  In the large-diameter solid portion 66, the first coil spring 100 and the second bellows-like elastic body 99 and the second coil spring 101 and the first bellows-like elastic body 98 always communicate with the two through holes c. 1 and second concave discharge portions 102 and 103, and first and second discharge holes 104 and 105 extending from the discharge portions 102 and 103 in parallel with the introduction pipe 80 and opening into the hollow portion r of the fixed shaft 65. Is formed.
[0043]
  The first seal block 92 and the second seal block 93, which are the same kind of members and are given the letters “first” and “second”, are fixed shafts. It is point-symmetric with respect to 65 axes.
[0044]
  The inside of the hollow portion r of the fixed shaft 65 and the inside of the outer cylinder portion 75 of the hollow cylinder 72 is a first cooling / falling steam passage s, and the passage s has a plurality of through holes penetrating the peripheral wall of the outer cylinder portion 75. It communicates with the relay chamber 20 via t.
[0045]
  As shown in FIGS. 2 and 5, the first and second portions formed of a plurality of introduction holes 106 arranged in the radial direction in the vicinity of both ends of the short diameter of the rotor chamber 14 in the outer periphery of the main body 11 of the first half 8. The introduction hole groups 107 and 108 are formed, and the first temperature-decreasing pressure-lowering steam in the relay chamber 20 is introduced into the rotor chamber 14 through the introduction hole groups 107 and 108. Further, in the outer peripheral portion of the main body 11 of the second half 9, a first lead-out composed of a plurality of lead-out holes 109 arranged in the radial direction and the circumferential direction between the long-diameter end of the rotor chamber 14 and the second introduction hole group 108. A hole group 110 is formed, and a second outlet hole group 111 including a plurality of outlet holes 109 arranged in the radial direction and the circumferential direction is formed between the other end portion having the long diameter and the first inlet hole group 107. From these first and second lead-out hole groups 110 and 111, the second temperature-decreasing pressure-decreased steam whose temperature and pressure have further decreased due to expansion between the adjacent vanes 42 is discharged to the outside.
[0046]
  The output shaft 23 and the like are lubricated with water, and the lubricating water channel is configured as follows. That is, as shown in FIGS. 2 and 3, the water supply pipe 113 is connected to the water supply hole 112 formed in the hollow bearing cylinder 22 of the second half 9. The water supply hole 112 is formed in the housing 114 where the bearing metal 25 on the second half 9 side faces, the housing 114 is formed in the water passage hole u formed in the thick portion 62 of the output shaft 23, and the water passage hole u. Are communicated with a plurality of water grooves v (see also FIG. 11) extending in the direction of the outer peripheral surface of the hollow shaft 64, and each water groove v communicates with a housing 115 facing the bearing metal 25 on the second half 8 side. To do. An annular recess w is provided on the inner end surface of the thick portion 62 of the output shaft 23 to communicate the water passage hole u with the sliding portion between the hollow shaft 64 and the large-diameter solid portion 66 of the fixed shaft 65. .
[0047]
  Thereby, between each bearing metal 25 and the output shaft 23 and between the hollow shaft 64 and the fixed shaft 65 is lubricated by water, and by the water that has entered the rotor chamber 14 from the gap between both the bearing metal 25 and the output shaft 23, Lubrication is performed between the casing 7 and the seal member 44 and each roller 59.
[0048]
  In FIG. 4, the first and seventh vane piston units U <b> 1 and U <b> 7 that are point-symmetric with respect to the rotation axis L of the rotor 31 perform the same operation. The same applies to the second and eighth vane piston units U2, U8, etc., which have a point-symmetric relationship.
[0049]
  For example, referring also to FIG. 11, the axis of the first supply pipe 94 is slightly deviated counterclockwise in FIG. 4 from the short diameter position E of the rotor chamber 14, and the first vane piston unit U1 is also shorted. In the radial position E, high-temperature high-pressure steam is not supplied to the large-diameter cylinder hole f, and therefore the piston 41 and the vane 42 are in the retracted position.
[0050]
  When the rotor 31 is slightly rotated counterclockwise in FIG. 4 from this state, the supply port 90 and the through hole c of the first seal block 92 communicate with each other, and the high-temperature high-pressure steam from the introduction pipe 80 passes through the small-diameter hole b. It is introduced into the large diameter cylinder hole f. As a result, the piston 41 moves forward, and the forward movement of the piston 41 is caused by the sliding movement of the vane 42 toward the major axis position F of the rotor chamber 14, and the roller 59 integral with the vane 42 and the annular groove 60 are interposed via the vane 42. In combination, the rotation of the rotor 31 is converted. When the through-hole c is displaced from the supply port 90, the high-temperature and high-pressure steam expands in the large-diameter cylinder hole f and further advances the piston 41, whereby the rotation of the rotor 31 is continued. The expansion of the high-temperature and high-pressure steam ends when the first vane piston unit U1 reaches the major axis position F of the rotor chamber 14. Thereafter, as the rotor 31 rotates, the first temperature-decreasing steam in the large-diameter cylinder hole f is retracted by the vane 42 so that the piston 41 is retracted, whereby the small-diameter hole b, the through-hole c, and the first concave discharge portion 102. , The first discharge hole 104, the passage s (see FIG. 3) and each through hole t are discharged into the relay chamber 20, and then, as shown in FIGS. And is further expanded between the adjacent vanes 42 to rotate the rotor 31, and then the second temperature-decreasing pressure-lowering steam is discharged from the first outlet hole group 110 to the outside.
[0051]
  As described above, the piston 41 is operated by the expansion of the high-temperature high-pressure steam to rotate the rotor 31 through the vane 42, and the rotor 31 is rotated through the vane 42 by the expansion of the temperature-decreasing step-down steam by the pressure drop of the high-temperature high-pressure steam. Thus, an output is obtained from the output shaft 23.
[0052]
  In addition to the embodiment, as a configuration for converting the forward movement of the piston 41 into the rotational movement of the rotor 31, the forward movement of the piston 41 is directly received by the roller 59 without using the vane 42 and is engaged with the annular groove 60. It can also be converted into rotational motion. Further, the vane 42 may be always separated from the inner peripheral surface 45 and the opposed inner end surface 47 of the rotor chamber 14 at a substantially constant interval by the cooperation of the roller 59 and the annular groove 60 as described above. , And each of the vane 42 and the roller 59 may cooperate with the annular groove 60 exceptionally.
[0053]
  When the expander 4 is used as a compressor, the rotor 31 is rotated in the clockwise direction in FIG. 4 by the output shaft 23, and the outside air as the fluid is supplied to the first and second outlet hole groups 110 and 111 by the vanes 42. From the first and second introduction hole groups 107 and 108 to the relay chamber 20, each through hole t, the passage s, the first and second discharge holes. 104, 105, first and second concave discharge portions 102, 103, and through-hole c are supplied to large-diameter cylinder hole f, and piston 41 is operated by vane 42 to convert low-pressure air into high-pressure air. The high-pressure air is introduced into the introduction pipe 80 through the through hole c, the supply ports 90 and 91, and the first and second supply pipes 94 and 95.
[0054]
  In the expander 4 described above, the first energy conversion means constituted by the cylinder member 39 and the piston 41 and the second energy conversion means constituted by the vane 42 are provided in the common rotor 31, and are connected in series. The energy of the high-temperature and high-pressure steam is taken out to the output shaft 23 as mechanical energy by the cooperation of the connected first and second energy conversion means. Therefore, the mechanical energy output from the first energy conversion means and the mechanical energy output from the second energy conversion means can be automatically integrated via the rotor 31, and special energy having power transmission means such as gears can be obtained. No integration means is required.
[0055]
  Since the first energy conversion means is composed of a combination of the cylinder 39 and the piston 41 that is easy to seal the working fluid and does not easily leak, it is possible to improve the sealing performance of the high-temperature and high-pressure steam and minimize the efficiency reduction due to the leak. . On the other hand, since the second energy conversion means is composed of a vane 42 supported by the rotor 31 so as to be movable in the radial direction, the vapor pressure applied to the vane 42 is directly converted into the rotational motion of the rotor 31, and the reciprocating motion is converted into the rotational motion. The special conversion mechanism is eliminated, and the structure is simplified. Moreover, since the second energy conversion means that can effectively convert a large flow rate of steam at a low pressure into mechanical energy is disposed so as to surround the outer periphery of the first energy conversion means, the overall size of the expander 4 can be made compact. it can.
[0056]
  The first energy conversion means composed of the cylinder 39 and the piston 41 has a high conversion efficiency between pressure energy and mechanical energy when high-temperature and high-pressure steam is used as the working fluid, and the second energy conversion means composed of the vane 42 has a relatively low temperature. Even when low-pressure steam is used as the working fluid, the conversion efficiency between pressure energy and mechanical energy is high. Therefore, the first and second energy conversion means are connected in series, and first, the high-temperature high-pressure steam is converted into mechanical energy through the first energy conversion means, and as a result, the first temperature-decreasing pressure-decreased steam whose pressure has decreased is converted. By passing the second energy conversion means and converting it to mechanical energy again, the energy contained in the original high-temperature and high-pressure steam can be effectively converted into mechanical energy without leaving a surplus.
[0057]
  Even when the expander 4 of this embodiment is used as a compressor, the air sucked into the rotor chamber 14 by rotating the rotor 31 with external mechanical energy can be effectively used even with a relatively low temperature and low pressure working fluid. The compressed and heated air is compressed by the second energy conversion means that operates, and the temperature of the compressed / heated air is further compressed by the first energy conversion means that is effectively operated by the relatively high temperature and pressure working fluid to raise the temperature. By this, mechanical energy can be efficiently converted into pressure energy (thermal energy) of compressed air. Thus, by combining the first energy conversion means comprising the cylinder 39 and the piston 41 and the second energy conversion means comprising the vane 42, it is possible to obtain a high-performance rotary fluid machine having both features. it can.
[0058]
  Further, when the rotation axis L of the rotor 31 (that is, the rotation axis L of the output shaft 23) coincides with the center of the rotor chamber 14, and the rotor 31 is divided into four parts by 90 ° vertically and horizontally in FIGS. Since the conversion from pressure energy to mechanical energy is performed in the upper right quadrant and the lower left quadrant that are point-symmetric with respect to the rotation axis L, it is possible to prevent an uneven load from being applied to the rotor 31 and suppress the occurrence of vibration. be able to. That is, the portion that converts the pressure energy of the working fluid into mechanical energy or the portion that converts the mechanical energy into pressure energy of the working fluid is disposed at two positions that are shifted by 180 ° about the rotation axis L of the rotor 31. The load applied to the rotor 31 becomes a couple and enables smooth rotation, and the intake timing and exhaust timing can be made more efficient.
[0059]
  Thus, in this embodiment, the evaporator 3 that heats water with the thermal energy of the exhaust gas of the internal combustion engine 1 to generate high-temperature and high-pressure steam, and the high-temperature and high-pressure steam supplied from the evaporator 3 outputs the shaft output with a constant torque. Rankine cycle comprised of an expander 4 that converts to a liquefied temperature, a condenser 5 that liquefies the temperature-decreasing step-down steam discharged from the expander 4, and a supply pump 6 that supplies water liquefied by the condenser 5 to the evaporator 3 The expander 4 is a positive displacement type. This positive displacement expander 4 is capable of recovering energy with high efficiency in a wide rotational speed range from low speed to high speed, as compared with a non positive displacement expander such as a turbine. It also has excellent followability and responsiveness to changes in the heat energy of exhaust gas (temperature change and flow rate change of exhaust gas) accompanying the increase and decrease in the rotational speed of 1. In addition, the double expansion in which the expander 4 is arranged in the radial direction inside and outside by connecting the first energy conversion means constituted by the cylinder member 39 and the piston 41 and the second energy conversion means constituted by the vane 42 in series. Since the mold is used, the thermal energy recovery efficiency by the Rankine cycle can be further improved while reducing the size and weight of the expander 4 and improving the space efficiency.
[0060]
  As mentioned above, although the Example of this invention was explained in full detail, this invention can perform a various design change in the range which does not deviate from the summary.
[0061]
  For example, in the embodiment, the expander 4 is exemplified as the rotary fluid machine, but the present invention can also be applied as a compressor.
[0062]
  Moreover, in the expander 4 of an Example, after supplying high temperature high pressure steam first to the cylinder member 39 and piston 41 which are 1st energy conversion means, the 1st temperature fall pressure-decreased steam which carried out temperature fall is pressure-reduced by the 2nd energy conversion means. The vane 42 is supplied. For example, the through hole t for discharging the first temperature-decreasing pressure-decreasing steam from the first energy conversion means shown in FIG. 2 and the relay chamber 20 are connected or disconnected, and further relayed. By configuring the chamber 20 to be capable of supplying steam independently to the second energy conversion means via the shell-shaped member 16, steam having different temperatures and pressures is supplied to the first and second energy conversion means, respectively. May be supplied separately. Further, the steam having different temperatures and pressures may be individually supplied from the first and second energy conversion means, and the steam whose temperature has been lowered after passing through the first energy conversion means may be further supplied to the second energy conversion means. good.
[0063]
【The invention's effect】
  As described above, according to the first aspect of the present invention, the first energy conversion means includes the cylinder formed radially in the rotor rotatably accommodated in the rotor chamber, and the sliding in the cylinder. Therefore, it is possible to improve the sealing performance of the high-pressure working fluid and minimize the efficiency reduction due to leakage. The second energy conversion means is supported by the rotor so as to be movable in the radial direction, and is disposed on the inner peripheral surface of the rotor chamber.Through the seal memberSince the vane is in sliding contact, the structure of the pressure energy and mechanical energy conversion mechanism is simple, and a large flow rate of working fluid can be processed with a compact structure. As described above, by combining the first energy conversion means having the piston and the cylinder and the second energy conversion means having the vane, a high-performance rotary fluid machine having both features can be obtained.
[0064]
  Further, since the roller interlocked with the vane and the piston moving in the radial direction with respect to at least the rotor rotating inside the rotor chamber is engaged with the non-circular annular groove formed in the casing defining the rotor chamber, the roller In addition, when it functions as an expander, it can convert the reciprocating motion of the piston into the rotational motion of the rotor, and when it functions as a compressor, the rotational motion of the rotor is reciprocated by the piston. Can be converted into motion. In addition, by guiding the movement trajectory of the roller with the annular groove, the gap between the outer peripheral surface of the vane and the inner peripheral surface of the rotor chamber can be regulated to prevent occurrence of abnormal wear and leakage.
[0065]
  According to the second aspect of the present invention, the first energy converting means converts the reciprocating motion of the piston and the rotational motion of the rotating shaft to each other, and the second energy converting means is the movement of the vane in the circumferential direction. Since the rotary motion of the rotary shaft is mutually converted, the fluid is compressed by the first and second energy converting means by the input of external force from the rotary shaft, and the first and second energy converting means are supplied by supplying the high pressure fluid. Can drive the rotating shaft. Thereby, the mechanical energy can be integrated and output by the first and second energy conversion means, or the pressure energy of the working fluid can be integrated and output by the first and second energy conversion means.
[0066]
  According to the invention described in claim 3, since the rotor is supported on the rotating shaft, the mechanical energy generated by the piston and cylinder provided on the rotor or the vane can be efficiently output to the rotating shaft, Further, the working fluid can be efficiently compressed by simply inputting mechanical energy to the rotating shaft by means of pistons and cylinders or vanes provided on the rotor supported by the rotating shaft.
[0067]
  According to the invention described in claim 4, when the first and second energy conversion means are connected in series and function as an expander, first, the high-pressure working fluid is passed through the first energy conversion means. The pressure energy of the working fluid is converted by converting a part of the pressure energy into mechanical energy and, as a result, the working fluid having a reduced pressure is further passed through the second energy converting means to convert the remainder of the pressure energy into mechanical energy. Can be efficiently converted into mechanical energy. Conversely, when functioning as a compressor, the rotating shaft is rotated by mechanical energy, the working fluid is compressed by the second energy conversion means, and the compressed working fluid is further compressed by the first energy conversion means. The mechanical energy can be efficiently converted into the pressure energy of the working fluid.
[0068]
  According to the fifth aspect of the present invention, the portion that converts the pressure energy of the working fluid into mechanical energy, or the portion that converts the mechanical energy into pressure energy of the working fluid has two locations where the phase of the rotor is shifted by 180 °. Therefore, the load applied to the rotor becomes a couple, and the rotor can rotate smoothly, and the intake timing and exhaust timing can be made more efficient.The
[0069]
  And claims6According to the invention described in (1), since the rotation axis of the rotor coincides with the center of the rotor chamber, it is possible to prevent an uneven load from being applied to the rotor and to prevent vibration associated with the rotation of the rotor.
[Brief description of the drawings]
FIG. 1 is a schematic view of a waste heat recovery device for an internal combustion engine.
2 is a longitudinal sectional view of an inflator corresponding to the sectional view taken along line 2-2 of FIG.
3 is an enlarged cross-sectional view around the rotation axis of FIG.
4 is a cross-sectional view taken along line 4-4 of FIG.
5 is an enlarged cross-sectional view taken along line 5-5 in FIG.
FIG. 6 is an explanatory diagram showing the cross-sectional shape of the rotor chamber and the rotor.
FIG. 7 is a front view of the vane body.
FIG. 8 is a side view of the vane body.
9 is a cross-sectional view taken along line 9-9 in FIG.
FIG. 10 is a front view of a sealing member.
11 is an enlarged view around the rotation axis in FIG. 4;
[Explanation of symbols]
7 Casing
4 Inflator
14 Rotor chamber
23 Output shaft (rotary shaft)
31 rotor
39 Cylinder member (cylinder)
41 piston
42 Vane
59 Laura
60 annular groove

Claims (6)

Comprising at least first energy conversion means and second energy conversion means,
The working fluid having pressure energy is input to the first and second energy conversion means and the pressure energy is converted into mechanical energy, whereby the mechanical energy generated by the first and second energy conversion means is integrated and output. Can function as an inflator (4)
The mechanical energy is input to the first and second energy conversion means to convert the mechanical energy into the pressure energy of the working fluid, thereby integrating the pressure energy of the working fluid generated by the first and second energy conversion means, respectively. In a rotary fluid machine that can function as a compressor that outputs
Said first energy conversion means, piston sliding with rotatably accommodated a cylinder formed radially in the rotor (31) (39) therein, inside the cylinder (39) of the rotor chamber (14) ( 41) and constitute from, the second energy converting means, infested radially from the rotor (31), an outer peripheral surface in sliding contact with a sealing member (44) on the inner peripheral surface of the rotor chamber (14) A non-circular annular groove (60) formed of a vane (42) and having a roller (59) interlocking with the vane (42) and the piston (41) formed in a casing (7) defining the rotor chamber (14). By this engagement, the reciprocating motion of the piston (41) and the rotational motion of the rotor (31) are mutually converted, and the outer peripheral surface of the vane (42) and the rotor chamber (14) Rotary fluid machine which is characterized by regulating the gap between the circumferential surface.  The first energy converting means mutually converts the reciprocating motion of the piston (41) and the rotating motion of the rotating shaft (23), and the second energy converting means is configured to move the vane (42) in the circumferential direction. The rotary fluid machine according to claim 1, wherein the rotary motion of the rotary shaft (23) and the rotary shaft (23) are mutually converted.  The rotary fluid machine according to claim 2, wherein the rotating shaft (23) supports a rotor (31).  When functioning as an expander (4), the entire amount of working fluid that has passed through the first energy conversion means has passed through the second energy conversion means, and when functioning as a compressor, it has passed through the second energy conversion means. The rotary fluid machine according to claim 1, wherein the entire amount of the working fluid passes through the first energy conversion means.  When functioning as an expander (4), the pressure energy of the working fluid is converted into mechanical energy at two locations where the phase of the rotor (31) is shifted by 180 °, and when functioning as a compressor, the phase of the rotor (31) is The rotary fluid machine according to claim 1, wherein mechanical energy is converted into pressure energy of the working fluid at two positions shifted by 180 °. Characterized in that the rotation axis of the rotor (31) is aligned with the center of the rotor chamber (14), a rotary fluid machine according to claim 1.

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