JP2004197710A - Rotary fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To discharge to a vane chamber only a liquid-phase operating medium from a reservoir part of a rotor from which the liquid phase operating medium and the gas phase operating medium leak. <P>SOLUTION: A supplementary chamber 48h having a suction port 48i opened toward the inside in the radial direction of the rotor and a discharge port 48j opened toward the outside in the radial direction is formed inside a vane 48 slidably fitted to a vane groove 49 of the rotor. When the vane 48 moves inward in the radial direction, only the suction port 48i communicates with the reservoir part 78 to suck the liquid phase operating medium in the supplementary chamber 48h, and when the vane 48 moves outward in the radial direction, only the discharge port 48j communicates with the vane chamber 75 in the exhaust stroke to discharge the liquid phase operating medium in the supplementary chamber 48h. Thus, the suction port 48i and the discharge port 48j do not communicate with the liquid reservoir part 78 and the vane chamber 75 at the same time, whereby the gas phase operating medium in the liquid reservoir part 78 is inhibited from flowing to the vane chamber 75 through the supplementary chamber 48h, and the gas phase operating medium having usable pressure energy can be prevented from being discharged wastefully. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a vane type rotary fluid machine that mutually converts pressure energy of a gas phase working medium and rotational energy of a rotor.
[0002]
[Prior art]
A vane piston unit combining a vane and a piston is provided, and a piston slidably fitted to a cylinder provided on a rotor in a radial direction is driven by a power conversion device including an annular groove and a roller. The vanes, which convert the pressure energy of the phase working medium and the rotational energy of the rotor to each other, and are slidably supported by the rotor in the radial direction, mutually convert the pressure energy of the gas phase working medium and the rotational energy of the rotor to each other. 2. Description of the Related Art A rotating fluid machine is known from the following patent documents.
[0003]
This rotary fluid machine forms a hydrostatic bearing by supplying a pressurized liquid-phase working medium to a sliding surface between a vane groove formed in a rotor and a vane slidably fitted therein. The vane is supported in a floating state. Since the liquid-phase working medium leaked from the hydrostatic bearing accumulates in a pool on the inner periphery of the rotor and causes a rotation resistance to increase, a passage extending in the radial direction of the rotor is formed inside the vane. When the outer end in the radial direction communicates with the vane chamber in the exhaust stroke, the liquid phase working medium accumulated in the pool is discharged to the vane chamber through the vane passage due to the pressure difference between the high pressure reservoir and the low pressure vane chamber. It is supposed to.
[0004]
[Patent Document]
JP 2001-33649 A
[0005]
[Problems to be solved by the invention]
By the way, in the conventional rotary fluid machine, since both ends of the passage of the vane communicate with both the reservoir and the vane chamber at the same time, the gas phase working medium accumulated in the reservoir is discharged to the vane chamber together with the liquid phase working medium. As a result, there is a problem that the gas-phase working medium having the pressure energy still available is wasted.
[0006]
The present invention has been made in view of the above circumstances, and has as its object to discharge only a liquid-phase working medium to a vane chamber from a pool portion of a rotor from which a liquid-phase working medium and a gas-phase working medium have leaked. And
[0007]
[Means for Solving the Problems]
According to the first aspect of the present invention, there is provided a rotor chamber formed in a casing, a rotor rotatably accommodated in the rotor chamber, and a plurality of vane grooves radially formed in the rotor. A plurality of vanes slidably supported by each of them, a hydrostatic bearing for supporting the vanes in a floating state with a liquid phase working medium supplied to the vane grooves and the sliding surface of the vanes, and a radially inner side of the rotor. And a reservoir for storing a liquid-phase working medium functioning as the hydrostatic bearing, and a pressure energy of a gas-phase working medium supplied to a vane chamber defined by a rotor, a casing, and a vane through an intake stroke and an exhaust stroke. A rotary fluid machine that mutually converts the rotational energy of a rotor with a rotary fluid machine. A supplementary chamber having a discharge port to be formed is formed, and when the vane moves radially inward, only the suction port communicates with the reservoir and sucks the liquid-phase working medium into the supplementary chamber, and the vane moves radially outward. A rotary fluid machine is proposed in which only the discharge port communicates with the vane chamber in the lower pressure side stroke of either the intake stroke or the exhaust stroke to discharge the liquid-phase working medium in the supplementary chamber.
[0008]
According to the above configuration, since the supplementary chamber having the suction port and the discharge port is formed inside the vane, when the vane moves inward in the radial direction, only the suction port communicates with the accumulation portion and the supplementary chamber operates in the liquid phase. When the medium is sucked in and the vane moves radially outward, only the discharge port may communicate with the vane chamber in the low-pressure side stroke of either the intake stroke or the exhaust stroke to discharge the liquid-phase working medium in the supplementary chamber. it can. Moreover, since the suction port and the discharge port do not communicate with the liquid pool and the vane chamber at the same time, the gas phase working medium in the liquid pool is prevented from flowing out to the vane chamber through the supplementary chamber, and the pressure energy still available Is prevented from being wastefully discharged.
[0009]
According to the second aspect of the present invention, in addition to the configuration of the first aspect, the first energy conversion means slidably fitted to the piston on the cylinder provided on the rotor, and the vane groove of the rotor. The second energy conversion means having a vane slidably fitted therein, and when functioning as an expander, the first and second energy conversion means integrate and output the generated mechanical energy, respectively. When functioning as, the first and second energy conversion means integrate and output the generated pressure energy, and the air leaked from the high-pressure side energy conversion means of the first and second energy conversion means to the reservoir. A rotary fluid machine is proposed in which the phase working medium is supplied to the low-pressure side energy conversion means via a one-way valve.
[0010]
According to the above configuration, the first and second energy conversion means function as an expander that integrates and outputs the mechanical energy generated respectively, or integrates the pressure energy generated by the first and second energy conversion means. The rotary fluid machine that functions as a compressor that outputs the gas phase working medium leaked from the high-pressure side energy conversion means to the low-pressure side energy conversion means through a one-way valve, and thus leaks into the reservoir. The gas-phase working medium can be effectively used by the low-pressure-side energy conversion means without waste and the energy conversion efficiency can be increased. Moreover, when the pressure of the gas-phase working medium leaked from the high-pressure side energy converting means is lower than the pressure of the gas-phase working medium of the low-pressure side energy converting means, the backflow of the gas-phase working medium is prevented by the one-way valve. It is possible to prevent the efficiency of the energy conversion means on the low pressure side from decreasing.
[0011]
According to a third aspect of the present invention, in addition to the configuration of the second aspect, the first and second energy conversion means are sequentially and continuously operated by a common gas phase working medium. A rotary fluid machine is proposed.
[0012]
According to the above configuration, since the first and second energy conversion means operate sequentially and continuously with the common gas-phase working medium, not only can the supply and discharge paths of the gas-phase working medium be simplified, but also the mechanical energy or pressure can be reduced. Energy generation efficiency can be increased.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
1 to 14 show an embodiment of the present invention. FIG. 1 is a schematic view of a waste heat recovery device of an internal combustion engine, and FIG. 2 is a longitudinal section of an expander corresponding to a cross-sectional view taken along line 2-2 of FIG. 2, FIG. 3 is an enlarged sectional view around the axis of FIG. 2, FIG. 4 is a sectional view taken along line 4-4 of FIG. 2, FIG. 5 is a sectional view taken along line 5-5 of FIG. 6 is a sectional view taken along line 7-7 of FIG. 5, FIG. 8 is a sectional view taken along line 8-8 of FIG. 5, FIG. 9 is a sectional view taken along line 9-9 of FIG. FIG. 11 is an exploded perspective view of a rotor, FIG. 12 is an exploded perspective view of a lubricating water distributing section of the rotor, FIG. 13 is a perspective view of a seal auxiliary member, an end of a spring and a vane seal, and FIG. It is a schematic diagram which shows the cross section shape of a rotor chamber and a rotor.
[0014]
As shown in FIG. 1, a waste heat recovery device 2 that recovers thermal energy of exhaust gas of an internal combustion engine 1 and outputs mechanical energy includes a high-temperature high-pressure steam by heating water using the exhaust gas of the internal combustion engine 1 as a heat source. Evaporator 3, an expander 4 that outputs an axial torque by expansion of the high-temperature and high-pressure steam, a condenser 5 that cools and cools down the low-temperature and low-pressure steam discharged from the expander 4, and a condenser 5 And a low-pressure pump 7 and a high-pressure pump 8 that supply the water in the tank 6 to the evaporator 3 again.
[0015]
The water in the tank 6 is pressurized to 2 to 3 MPa by the low-pressure pump 7 disposed on the passage P <b> 1, and is preheated through the heat exchanger 102 provided in the exhaust pipe 101 of the internal combustion engine 1. The water preheated by passing through the heat exchanger 102 is supplied to a water jacket 105 formed in a cylinder block 103 and a cylinder head 104 of the internal combustion engine 1 through a passage P2. Is cooled, and the temperature of the heating portion itself rises further by removing the heat of the heating portion. The water exiting the water jacket 105 is supplied to the distribution valve 106 via the passage P3, where a first system connected to the passage P4, a second system connected to the passage P5, and a third system connected to the passage P6, It is distributed to the fourth system connected to the passage P7.
[0016]
The water distributed to the first system composed of the passage P4 by the distribution valve 106 is pressurized to a high pressure of 10 MPa or more by the high-pressure pump 8 and supplied to the evaporator 3, where the water exchanges heat with the high-temperature exhaust gas. As a result, high-temperature high-pressure steam is supplied to a high-pressure section of the expander 4 (a cylinder 44 of the expander 4 described later). On the other hand, the water distributed to the second system connected to the passage P5 by the distribution valve 106 passes through the pressure reducing valve 107 interposed therein and becomes low-temperature and low-pressure steam as compared with the high-temperature and high-pressure steam. It is supplied to a low-pressure section (vane chambers 75 of the expander 4 described later). As described above, the heated water from the distribution valve 106 is converted into steam by the pressure reducing valve 107 and supplied to the low-pressure section of the expander 4, so that the water can effectively use the heat energy received by the water jacket 105 of the internal combustion engine 1. The output of the expander 4 can be increased by utilizing this. The water distributed to the third system connected to the passage P6 is supplied to the lubricated portion of the expander 4. At this time, since the lubricated portion of the expander 4 is lubricated by using the high-temperature water heated by the water jacket 105, it is possible to prevent the expander 4 from being overcooled and reduce the so-called cooling loss. The temperature-reduced pressure-decreasing steam containing water discharged from the expander 4 is supplied to the condenser 5 interposed in the passage P8, exchanges heat with cooling air from a cooling fan 109 driven by the electric motor 108, and condenses. The water is discharged to the tank 6. Further, the water distributed to the fourth system connected to the plurality of passages P7 is supplied to auxiliary equipment 110 such as a heater for heating the vehicle compartment and a thermoelectric element to radiate heat, and the water whose temperature has dropped is interposed in the passage P9. It is discharged to the tank 6 via the checked valve 111.
[0017]
The low-pressure pump 7, the high-pressure pump 8, the distribution valve 106, and the electric motor 108 are electronically controlled according to the operating state of the internal combustion engine 1, the operating state of the expander 4, the operating state of the accessory 110, the temperature of water in the tank 6, and the like. It is controlled by the control unit 112.
[0018]
As shown in FIGS. 2 and 3, the casing 11 of the expander 4 includes first and second casing halves 12 and 13 made of metal. The first and second casing halves 12, 13 are composed of main bodies 12a, 13a which cooperate to form the rotor chamber 14, and circular flanges 12b, 13b integrally connected to the outer periphery of the main bodies 12a, 13a. The two circular flanges 12b and 13b are connected via a metal gasket 15. The outer surface of the first casing half 12 is covered with a relay chamber outer wall 16 having a deep pot shape, and a circular flange 16a integrally connected to the outer periphery thereof is superimposed on the left side of the circular flange 12b of the first casing half 12. . The outer surface of the second casing half 13 is covered by an exhaust chamber outer wall 17 that houses a magnet coupling (not shown) that transmits the output of the expander 4 to the outside, and a circular flange 17a integrally connected to the outer periphery of the exhaust chamber outer wall 17. Are overlapped on the right side surface of the circular flange 13b of the second casing half 13. The four circular flanges 12b, 13b, 16a, 17a are fastened together by a plurality of bolts 18 arranged in a circumferential direction. A relay chamber 19 is defined between the relay chamber outer wall 16 and the first casing half 12, and an exhaust chamber 20 is defined between the exhaust chamber outer wall 17 and the second casing half 13. The exhaust chamber outer wall 17 is provided with an outlet (not shown) for guiding the temperature-reduced pressure-reduced steam, which has been worked by the expander 4, to the condenser 5.
[0019]
The body portions 12a, 13a of the two casing halves 12, 13 have hollow bearing cylinders 12c, 13c projecting outward in the left and right directions, and a rotating shaft 21 having a hollow portion 21a is provided in the hollow bearing cylinders 12c, 13c. It is rotatably supported via a pair of bearing members 22 and 23. Thus, the axis L of the rotating shaft 21 passes through the intersection of the major axis and the minor axis in the rotor chamber 14 having a substantially elliptical shape.
[0020]
A seal block 25 is housed inside a lubricating water introducing member 24 screwed to the right end of the second casing half 13 and fixed with a nut 26. A small-diameter portion 21b at the right end of the rotating shaft 21 is supported inside the seal block 25, and a pair of seal members 27, 27 are disposed between the seal block 25 and the small-diameter portion 21b. A pair of seal members 28, 28 are arranged between them, and a seal member 29 is arranged between the lubricating water introducing member 24 and the second casing half 13. Further, the filter 30 is fitted into a concave portion formed on the outer periphery of the hollow bearing cylinder 13 c of the second casing half 13, and is prevented from falling off by the filter cap 31 screwed to the second casing half 13. A pair of seal members 32 and 33 are provided between the filter cap 31 and the second casing half 13.
[0021]
As is clear from FIGS. 4 and 14, a circular rotor 41 is rotatably housed inside the pseudo-elliptical rotor chamber. The rotor 41 is fitted and integrally connected to the outer periphery of the rotating shaft 21, and the axis of the rotor 41 and the axis of the rotor chamber 14 coincide with the axis L of the rotating shaft 21. The shape of the rotor chamber 14 as viewed in the direction of the axis L is a pseudo-elliptical shape similar to a rhombus with four rounded vertices, and has a major axis DL and a minor axis DS. The shape of the rotor 41 as viewed in the direction of the axis L is a perfect circle, and has a diameter DR slightly smaller than the short diameter DS of the rotor chamber 14.
[0022]
Each of the cross-sectional shapes of the rotor chamber 14 and the rotor 41 as viewed in a direction perpendicular to the axis L has a track-like shape for athletics. That is, the cross-sectional shape of the rotor chamber 14 includes a pair of flat surfaces 14a, 14a extending in parallel at a distance d, and an arc surface 14b having a central angle of 180 ° that smoothly connects the outer circumferences of these flat surfaces 14a, 14a. Similarly, the cross-sectional shape of the rotor 41 has a pair of flat surfaces 41a, 41a extending in parallel at a distance d, and a circular arc having a central angle of 180 ° which smoothly connects the outer circumferences of the flat surfaces 41a, 41a. And a surface 41b. Therefore, the flat surfaces 14a, 14a of the rotor chamber 14 and the flat surfaces 41a, 41a of the rotor 41 are in contact with each other, and a pair of crescent-shaped spaces are formed between the inner peripheral surface of the rotor chamber 14 and the outer peripheral surface of the rotor 41. (See FIG. 4) is formed.
[0023]
Next, the structure of the rotor 41 will be described in detail with reference to FIGS.
[0024]
The rotor 41 is composed of a rotor core 42 integrally formed on the outer periphery of the rotating shaft 21 and twelve rotor segments 43 which are fixed so as to cover the periphery of the rotor core 42 and form an outer shell of the rotor 41. Twelve ceramic (or carbon) cylinders 44 are radially mounted on the rotor core 42 at intervals of 30 ° and are stopped by clips 45. A small diameter portion 44a protrudes from the inner end of each cylinder 44, and the base end of the small diameter portion 44a is sealed with a sleeve 84 via a C seal 46. The tip of the small-diameter portion 44a is fitted to the outer peripheral surface of the hollow sleeve 84, and the cylinder bore 44b is connected to the rotary shaft 21 through the twelve third steam passages S3 penetrating the small-diameter portion 44a and the rotary shaft 21. The internal first and second steam passages S1; S2, S2 communicate with each other. A ceramic piston 47 is slidably fitted inside each cylinder 44. When the piston 47 moves radially inward, it completely retracts inside the cylinder bore 44b, and when it moves radially outward, about half of the entire length projects outside the cylinder bore 44b.
[0025]
Each rotor segment 43 is a hollow wedge-shaped member having a central angle of 30 °, and a surface of the rotor chamber 14 facing the pair of flat surfaces 14a, 14a has two arcs extending in an arc around the axis L. Recesses 43a and 43b are formed, and lubricating water outlets 43c and 43d are opened at the centers of the recesses 43a and 43b. In addition, four lubricating water jets 43e, 43e; 43f, 43f are opened on the end face of the rotor segment 43, that is, the face facing the vane 48 described later.
[0026]
The assembly of the rotor 41 is performed as follows. Twelve rotor segments 43 are fitted around the outer periphery of the rotor core 42 previously assembled with the cylinders 44, clips 45, and C seals 46, and twelve vane grooves 49 formed between adjacent rotor segments 43. Are fitted with the vanes 48. At this time, shims of a predetermined thickness are interposed on both surfaces of the vanes 48 in order to form a predetermined clearance between the vanes 48 and the rotor segments 43. In this state, the rotor segments 43 and the vanes 48 are tightened radially inward toward the rotor core 42 by using a jig, and the rotor segments 43 are precisely positioned with respect to the rotor core 42. 43 are temporarily fixed to the rotor core 42 with temporary fixing bolts 50 (see FIG. 8). Subsequently, two knock pin holes 51, 51 penetrating through the rotor core 42 are co-processed in each rotor segment 43, and four knock pins 52,... Are press-fitted into the knock pin holes 51, 51, and the rotor segments 43,. To join.
[0027]
As is clear from FIGS. 8, 9 and 12, a through hole 53 penetrating through the rotor segment 43 and the rotor core 42 is formed between the two knock pin holes 51, 51, and at both ends of the through hole 53. Recesses 54, 54 are formed respectively. Two pipe members 55 and 56 are fitted inside the through hole 53 via seal members 57 to 60, and an orifice forming plate 61 and a lubricating water distribution member 62 are fitted into each recess 54. It is fixed with a nut 63. The orifice forming plate 61 and the lubricating water distribution member 62 are rotated by two knock pins 64, 64 that penetrate through the knock pin holes 61a, 61a of the orifice forming plate 61 and fit into the knock pin holes 62a, 62a of the lubricating water distribution member 62. The rotation of the lubricating water distribution member 62 and the nut 63 is sealed by an O-ring 65.
[0028]
The small diameter portion 55a formed at the outer end of the one pipe member 55 communicates with the sixth water passage W6 inside the pipe member 55 through the through hole 55b, and the small diameter portion 55a is connected to the lubricating water distribution member 62. It communicates with a radial distribution groove 62b formed on the side surface. The distribution grooves 62b of the lubricating water distribution member 62 extend in six directions, and the ends thereof communicate with the six orifices 61b, 61b; 61c, 61c; 61d, 61d of the orifice forming plate 61. The structures of the orifice forming plate 61, the lubricating water distribution member 62, and the nut 63 provided at the outer end of the other pipe member 56 are the same as the structures of the orifice forming plate 61, the lubricating water distribution member 62, and the nut 63 described above. It is.
[0029]
The two orifices 61b of the orifice forming plate 61 are located downstream of the two orifices 61b through the seventh water passages W7 and W7 formed inside the rotor segment 43 so as to face the vanes 48. The two orifices 61c communicate with the lubricating water jets 43e, and the downstream sides of the other two orifices 61c face the vanes 48 via the eighth water passages W8 and W8 formed inside the rotor segment 43. The other two orifices 61d, 61d communicate with the two lubricating water jets 43f, 43f, which are opened at the downstream side, and the ninth water passages W9, W9 formed inside the rotor segment 43 communicate with the other two orifices 61d, 61d. Thus, it communicates with the two lubricating water jets 43c and 43d which are opened to face the rotor chamber 14.
[0030]
5, an annular groove 67 defined by a pair of O-rings 66 is formed on the outer periphery of the cylinder 44, and the sixth water formed inside one pipe member 55 is formed. The passage W6 communicates with the annular groove 67 via four through holes 55c penetrating the pipe member 55 and a tenth water passage W10 formed inside the rotor core 42. The annular groove 67 communicates with the sliding surface of the cylinder bore 44b and the piston 47 via the orifice 44c. The position of the orifice 44c of the cylinder 44 is set so that the piston 47 does not come off the sliding surface of the piston 47 when moving between the top dead center and the bottom dead center.
[0031]
As is clear from FIGS. 3 and 9, the first water passage W1 formed in the lubricating water introduction member 24 is the second water passage W2 formed in the seal block 25 and the third water passage W2 formed in the small diameter portion 21 b of the rotating shaft 21. The water passages W3 ... straddle the annular groove 68a formed on the outer periphery of the water passage forming member 68 fitted to the center of the rotating shaft 21, the fourth water passage W4 formed on the rotating shaft 21, the rotor core 42 and the rotor segment 43. The pipe member 69 communicates with the small-diameter portion 55a of the one pipe member 55 through fifth water passages W5 and W5 formed so as to bypass the knock pin 52 on the radially inner side of the rotor segment 43.
[0032]
As shown in FIGS. 5, 7, 9 and 11, twelve vane grooves 49 extending in the radial direction are formed between adjacent rotor segments 43 of the rotor 41, and these vane grooves 49 are formed. The plate-like vanes 48 are slidably fitted respectively. Each vane 48 has a parallel surface 48a, 48a along the parallel surface 14a, 14a of the rotor chamber 14, an arc surface 48b along the arc surface 14b of the rotor chamber 14, and a notch 48c located between the parallel surfaces 48a, 48a. The rollers 71 having a roller bearing structure are rotatably supported by a pair of support shafts 48d projecting from the parallel surfaces 48a.
[0033]
A slit-like seal holding groove 48f is formed from the arc surface 48b of the vane 48 to the pair of parallel surfaces 48a, 48a. A V-shaped synthetic resin vane seal 72 is held in the seal holding groove 48f, and the tip of the vane seal 72 slightly projects from the outer peripheral surface of the vane 48 to the inner peripheral surface of the rotor chamber 14. Make sliding contact. A pair of parallel surfaces 48a, 48a of the vane are formed with locking holes 48g, 48g having a circular cross section connected to the radially inner end of the seal holding groove 48f in the direction of the axis L, and these locking holes 48g, 48g are formed in these holes. The cylindrical seal auxiliary members 76, 76 fit without any gap. As is clear from FIG. 13, the seal assisting members 76, 76 are formed with slits 76a, 76a that open radially outward and axially outward, respectively. The radially inner ends of the vane seals 72 are formed in these slits 76a, 76a. Fit without gap. The seal assisting members 76, 76 are urged outward in the direction of the axis L (in the direction protruding from the engaging holes 48g, 48g) by springs 77, 77 disposed at the bottoms of the engaging holes 48g, 48g.
[0034]
Two recesses 48 e, 48 e are formed on both side surfaces of the vane 48, and these recesses 48 e, 48 e are two radially inner lubricating water jets 43 e, opening in the end face of the rotor segment 43. 43e. A trapping chamber 48h extending inward and outward in the radial direction is formed inside the vane 48, and the inside of the trapping chamber 48h in the radial direction is connected to the rotor core 42 and the rotor segment via suction ports 48i, 48i opened on both side surfaces of the vane 48. 43 communicates with the reservoir 78 formed therebetween, and communicates with the vane chamber 75 via a discharge port 48j that opens on the side surface of the vane 48 on the leading side in the rotation direction R in the rotation direction R. Then, a piston receiving member 73 projecting radially inward at the center of the notch 48 c of the vane 48 abuts on the radially outer end of the piston 47.
[0035]
As is clear from FIG. 2, the reservoir 78 formed between the rotor core 42 and the rotor segments 43 and the relay chamber 19 communicate with each other through a communication hole 12d penetrating the first casing 12, and this communication hole 12d A one-way valve 79 is provided to allow the movement of the steam from the reservoir 78 to the relay chamber 19 and regulate the movement of the steam from the relay chamber 19 to the reservoir 78.
[0036]
As is apparent from FIG. 4, the flat surfaces 14a, 14a of the rotor chamber 14, which are defined by the first and second casing halves 12, 13, have a pseudo-elliptical annular shape similar to a rhombus with four rounded vertices. Grooves 74, 74 are recessed, and a pair of rollers 71, 71 of each vane 48 are rotatably engaged with both annular grooves 74, 74. The distance between the annular grooves 74, 74 and the arc surface 14b of the rotor chamber 14 is constant over the entire circumference. Therefore, when the rotor 41 rotates, the vanes 48 guided by the rollers 71, 71 in the annular grooves 74, 74 reciprocate in the radial direction in the vane grooves 49, and the vane seal 72 mounted on the arc surface 48b of the vane 48 is fixed. The slider slides along the arc surface 14b of the rotor chamber 14 in a state of being compressed only. This prevents the rotor chamber 14 and the vanes 48 from coming into direct solid contact, and prevents the increase in sliding resistance and the occurrence of wear, while ensuring that the vane chambers 75 partitioned between the adjacent vanes 48 are formed. Can be sealed.
[0037]
As is clear from FIGS. 2, 3, and 10, an opening 16b is formed at the center of the relay chamber outer wall 16, and the boss portion 81a of the fixed shaft support member 81 disposed on the axis L is connected to the opening 16b. It is fixed to the inner surface with a plurality of bolts 82 and is fixed to the first casing half 12 with nuts 83. A cylindrical sleeve 84 made of ceramic is fixed to the hollow portion 21a of the rotating shaft 21. The outer peripheral surface of the fixed shaft 85 integrated with the fixed shaft support member 81 is fixed to the inner peripheral surface of the sleeve 84. Fits rotatably. The left end of the fixed shaft 85 is sealed with the first casing half 12 by a seal member 86, and the right end of the fixed shaft 85 is sealed with the rotary shaft 21 by a seal member 87.
[0038]
A steam supply pipe 88 is fitted inside a fixed shaft support member 81 arranged on the axis L and fixed with a nut 89. The right end of the steam supply pipe 88 is press-fitted into the center of the fixed shaft 85. A first steam passage S1 connected to the steam supply pipe 88 is formed in the center of the fixed shaft 85 in the axial direction, and a pair of second steam passages S2 and S2 are formed in the fixed shaft 85 in the radial direction with a phase difference of 180 °. Penetrate. As described above, the twelve third steam passages S3 penetrate the small-diameter portions 44a of the twelve cylinders 44 held at intervals of 30 ° by the rotor 41 fixed to the rotating shaft 21 and the sleeve 84. The radially inner ends of the third steam passages S3 are opposed to the radially outer ends of the second steam passages S2 and S2 so as to be able to communicate with each other.
[0039]
A pair of notches 85a, 85a are formed on the outer peripheral surface of the fixed shaft 85 with a phase difference of 180 °, and these notches 85a, 85a can communicate with the third steam passages S3. The notches 85a, 85a and the relay chamber 19 are formed by a pair of fourth steam passages S4, S4 formed in the fixed shaft 85 in the axial direction, and an annular fifth steam passage S5 formed in the fixed shaft support member 81 in the axial direction. Are communicated with each other through through holes 81b, which are opened on the outer periphery of the boss portion 81a of the fixed shaft support member 81.
[0040]
As shown in FIGS. 2 and 4, the first casing half 12 and the second casing half 13 have a position at 15 ° on the leading side in the rotation direction R of the rotor 41 with respect to the minor axis direction of the rotor chamber 14. Are formed, a plurality of intake ports 90 arranged in a radial direction. By the intake ports 90, the internal space of the rotor chamber 14 communicates with the relay chamber 19. A plurality of exhaust ports 91 are formed in the second casing half 13 at positions 15 ° to 75 ° on the delay side in the rotation direction R of the rotor 41 with respect to the minor diameter direction of the rotor chamber 14. The exhaust ports 91 communicate the internal space of the rotor chamber 14 with the exhaust chamber 20. The exhaust ports 91 open into shallow recesses 13d formed inside the second casing half 13, so that the vane seals 72 of the vanes 48 are not damaged by the edges of the exhaust ports 91.
[0041]
The notches 85a, 85a of the fixed shaft 85 and the third steam passages S3,..., And the second steam passages S2, S2, the third steam passage S3,. The valve V is configured (see FIG. 10).
[0042]
As is clear from FIG. 2, the eleventh water passage W11 formed in the first and second casing halves 12, 13 communicates with the outer peripheral surface of the annular filter 30 via the fourteenth water passage W14 formed of a pipe. The inner peripheral surface of the filter 30 communicates with a sixteenth water passage W16 formed in the second casing half 13 via a fifteenth water passage W15 formed in the second casing half 13. The water supplied to the sixteenth water passage W16 lubricates the sliding surfaces of the fixed shaft 85 and the sleeve 84. Further, water supplied from the inner peripheral surface of the filter 30 to the outer periphery of the bearing member 23 via the seventeenth water passage W17 lubricates the outer peripheral surface of the rotary shaft 21 through an orifice penetrating the bearing member 23. On the other hand, water supplied to the outer periphery of the bearing member 22 from the eleventh water passage W11 through the eighteenth water passage W18 formed of a pipe lubricates the outer peripheral surface of the rotary shaft 21 through an orifice penetrating the bearing member 22, The sliding surfaces of the fixed shaft 85 and the sleeve 84 are lubricated.
[0043]
Next, the operation of the present embodiment having the above configuration will be described.
[0044]
First, the operation of the expander 4 will be described. In FIG. 3, high-temperature and high-pressure steam from the evaporator 3 passes through a steam supply pipe 88, a first steam passage S1 passing through the center of the fixed shaft 85, and a pair of second steam passages S2 and S2 penetrating through the fixed shaft 85 in the radial direction. Supplied to In FIG. 10, when the sleeve 84 rotating in the direction of the arrow R integrally with the rotor 41 and the rotation shaft 21 reaches a predetermined phase with respect to the fixed shaft 85, the rotation direction of the rotor 41 in the rotation direction R A pair of third steam passages S3 and S3 on the leading side communicate with a pair of second steam passages S2 and S2, and high-temperature and high-pressure steam in the second steam passages S2 and S2 passes through the third steam passages S3 and S3. Supplied inside the pair of cylinders 44, 44, the pistons 47, 47 are pressed radially outward. In FIG. 4, when the vanes 48, 48 pressed by the pistons 47, 47 move outward in the radial direction, a pair of rollers 71, 71 provided on the vanes 48, 48 engage with the annular grooves 74, 74 to cause the engagement. The forward movement of the pistons 47, 47 is converted into the rotational movement of the rotor 41.
[0045]
Even after the communication between the second steam passages S2 and S2 and the third steam passages S3 and S3 is cut off with the rotation of the rotor 41, the high-temperature and high-pressure steam in the cylinders 44 and 44 continues to expand, thereby causing the piston 47, 47 are still advanced, whereby the rotation of the rotor 41 is continued. When the vanes 48, 48 reach the long diameter position of the rotor chamber 14, the third steam passages S3, S3 communicating with the corresponding cylinders 44, 44 communicate with the notches 85a, 85a of the fixed shaft 85, and connect the rollers 71, 71 with the annular grooves. As the pistons 47, 47 pressed by the vanes 48, 48 guided by 74, 74 move inward in the radial direction, the steam in the cylinders 44, 44 is transferred to the third steam passages S 3, S 3, notches 85 a, 85 a, Through the fourth steam passages S4, S4, the fifth steam passage S5, and the through-holes 81b, the steam is supplied to the relay chamber 19 as the first temperature-lowering steam. The first temperature-decreased pressure-decreased steam is obtained by decreasing the temperature and the pressure after the high-temperature and high-pressure steam supplied from the steam supply pipe 88 finishes the work of driving the pistons 47, 47. Although the heat energy and pressure energy of the first temperature-lowering / low-pressure steam are lower than those of the high-temperature / high-pressure steam, they still have enough heat energy and pressure energy to drive the vanes 48.
[0046]
The first temperature-reduced and reduced-pressure steam in the relay chamber 19 is supplied from the intake ports 90 of the first and second casing halves 12 and 13 to the vane chambers 75 in the rotor chamber 14, where the steam is further expanded so that the vanes 48 are expanded. Are pressed to rotate the rotor 41. After the work is completed, the second reduced-temperature and reduced-pressure steam whose temperature and pressure are further reduced is discharged from the exhaust ports 91 of the second casing half 13 to the exhaust chamber 20 and is supplied to the condenser 5 therefrom.
[0047]
As described above, the twelve pistons 47 are operated one after another by the expansion of the high-temperature and high-pressure steam to rotate the rotor 41 through the rollers 71, 71 and the annular grooves 74, 74. The rotor 41 is rotated via the vanes 48 due to the expansion of the temperature-reduced pressure-reducing steam, so that the mechanical energy generated by the pistons 47 and the mechanical energy generated by the vanes 48 can be integrated to obtain an output from the rotary shaft 21. In addition, the pressure energy of the high-temperature high-pressure steam can be converted into mechanical energy.
[0048]
Further, the first energy conversion means is constituted by the cylinders 44 radially formed on the rotor 41 rotatably accommodated in the rotor chamber 14 and the pistons 47 sliding in the cylinders 44. In addition, the sealing performance of the high-temperature and high-pressure gas-phase working medium can be enhanced to minimize the decrease in efficiency due to leakage. Further, since the second energy conversion means is constituted by the vanes 48 which are movably supported by the rotor 41 in the radial direction and slidably contact the inner peripheral surface of the rotor chamber 14, the structure of the pressure energy and mechanical energy conversion mechanism is simple. With a compact structure, it can process a large amount of the gas-phase working medium. By combining the first energy conversion means having the cylinders 44 and the pistons 47 with the second energy conversion means having the vanes 48, a high-performance rotary fluid machine having both features is provided. Obtainable.
[0049]
Next, lubrication of the vanes 48 and the pistons 47 of the expander 4 with water will be described.
[0050]
As the water for lubricating each part of the expander 4, high-temperature water heated by the water jacket 105 and then distributed to the passage P <b> 6 by the distribution valve 106 is used.
[0051]
3 and 8, the water supplied to the first water passage W1 of the lubricating water introduction member 24 is supplied to the second water passage W2 of the seal block 25, the third water passage W3 of the rotary shaft 21, and the water passage formation. Through the annular groove 68a of the member 68, the fourth water passage W4 of the rotating shaft 21, the pipe member 69, and the fifth water passages W5 and W5 formed in the rotor segment 43, it flows into the small diameter portion 55a of one pipe member 55, The water flowing into the small-diameter portion 55a passes through a through hole 55b of one pipe member 55, a sixth water passage W6 formed in both pipe members 55 and 56, and a through hole 56b formed in the other pipe member 56. Flows into the small diameter portion 56a of the pipe member 56 of FIG.
[0052]
From the small diameter portions 55a, 56a of the respective pipe members 55, 56, the six orifices 61b, 61b; 61c, 61c; 61d, 61d of the orifice forming plate 61 passed through the distribution grooves 62b of the respective lubricating water distribution members 62. Part of the water is jetted from four lubricating water jets 43e, 43e; 43f, 43f opening to the end face of the rotor segment 43, and the other part is an arc-shaped recess 43a formed on the side surface of the rotor segment 43. , 43b from the lubricating water outlets 43c, 43d.
[0053]
Thus, water spouted into the vane groove 49 from the lubricating water ejection ports 43e, 43e; 43f, 43f at the end faces of the respective rotor segments 43 is interposed between the vane 48 slidably fitted in the vane groove 49. The vane 48 is supported in a floating state by forming a static pressure bearing, and solid contact between the end face of the rotor segment 43 and the vane 48 is prevented to prevent seizure and wear. In this way, by supplying the water for lubricating the sliding surface of the vane 48 through the water passage radially provided inside the rotor 41, not only can the water be pressurized by centrifugal force, but also the periphery of the rotor 41 Temperature can be stabilized to reduce the influence of thermal expansion, and the set clearance can be maintained to minimize steam leakage.
[0054]
Further, since water is held in the recesses 48e, 48e formed two on each side of the vane 48, the recesses 48e, 48e serve as pressure pools to suppress a pressure drop due to water leakage. As a result, the vane 48 sandwiched between the end faces of the pair of rotor segments 43, 43 is floated by the water, and the sliding resistance can be effectively reduced. When the vane 48 reciprocates, the relative position of the vane 48 in the radial direction with respect to the rotor 41 changes. However, the recesses 48e, 48e are provided not on the rotor segment 43 side but on the vane 48 side, and , The reciprocating vane 48 is always kept in a floating state, and the sliding resistance can be effectively reduced.
[0055]
When each vane 48 rotates together with the rotor 41, the vane seal 72 fitted in the seal holding groove 48f is urged radially outward by centrifugal force, so that the vane seal 72 is formed at a portion corresponding to the arc surface 48b of the vane 48. Is pressed against the inner peripheral surface of the rotor chamber 14 to exhibit a sealing property. Although the pressing force of the vane seal 72 due to the centrifugal force cannot be expected in the portion corresponding to the parallel surfaces 48a, 48a of the vanes 48, the vane seal is pressed by the pressure introduced from the high pressure side vane chamber 75 to the bottom of the seal holding groove 48f of the vane 48. Since the 72 is urged in the direction of being pushed out from the seal holding groove 48f, the entire outer peripheral surface of the vane seal 72 is pressed against the inner peripheral surface of the rotor chamber 14, and the sealing property is exhibited.
[0056]
At this time, if the pressure escapes from both ends of the seal holding groove 48f, the pressing force of the vane seal 72 disappears, but in this embodiment, it is fitted into the locking holes 48g, 48g connected to both ends of the seal holding groove 48f. The ends of the vane seal 72 are fitted into the slits 76a, 76a of the mating seal auxiliary members 76, 76, and the slits 76a, 76a of the seal auxiliary members 76, 76 open radially outward and radially inward. The outer end surfaces of the seal auxiliary members 76, 76 which are closed and the slits 76a, 76a are opened are urged toward the inner peripheral surface of the rotor chamber 14 by the elastic force of the springs 77, 77. Therefore, the ends of the vane seal 72 are brought into close contact with the slits 76a, 76a of the seal auxiliary members 76, 76, and pressure relief from both ends of the seal holding groove 48f is performed. It can be a by preventing ensure the sealing of the vane seal 72.
[0057]
In particular, when the expander 4 is cold and the pressure at the bottom of the seal holding groove 48f does not rise sufficiently, the ends of the seal assisting members 76, 76 and the vane seal 72 are rotated by the elastic force of the springs 77, 77. The sealing performance can be ensured by pressing against the inner peripheral surface of the chamber 14.
[0058]
Further, in FIG. 5, the sliding surface of the cylinder 44 and the piston 47 extends from the sixth water passage W6 inside the pipe member 55 through the tenth water passage W10 inside the rotor segment 43 and the annular groove 67 on the outer periphery of the cylinder 44. The supplied water exerts a sealing function due to the viscosity of a water film formed on the sliding surface, and the high-temperature and high-pressure steam supplied to the cylinder 44 has an effect of leaking through the sliding surface with the piston 47. Prevention. At this time, since the water supplied to the sliding surfaces of the cylinder 44 and the piston 47 through the inside of the expander 4 in a high temperature state is heated, the high-temperature high-pressure steam supplied to the cylinder 44 by the water is heated. It is possible to minimize a decrease in output of the expander 4 due to cooling.
[0059]
The first water passage W1 and the eleventh water passage W11 are independent of each other, and supply water at a required pressure in each lubricating portion. Specifically, since the water supplied from the first water passage W1 mainly supports the vanes 48 and the rotor 41 in a floating state by the static pressure bearing as described above, the water can antagonize the load variation. High pressure is required. On the other hand, the water supplied from the eleventh water passage W11 mainly lubricates around the fixed shaft 85 and seals the high-temperature and high-pressure steam leaking from the third steam passages S3 and S3 to the outer periphery of the fixed shaft 85. In order to reduce the influence of thermal expansion of the fixed shaft 85, the rotating shaft 21, the rotor 41, and the like, the pressure should be at least higher than the pressure of the relay chamber 19.
[0060]
As described above, since the two water supply systems of the first water passage W1 for supplying the high-pressure water and the eleventh water passage W11 for supplying the lower-pressure water are provided, the first water passage W1 for supplying the high-pressure water is provided. The problem when only one water supply system is provided can be eliminated. That is, excessive pressure of water is supplied around the fixed shaft 85 to increase the amount of water flowing out to the relay chamber 19, or the fixed shaft 85, the rotating shaft 21, the rotor 41, etc. are supercooled and the steam temperature decreases. Trouble can be prevented, and the output of the expander 4 can be increased while reducing the supply amount of water.
[0061]
In addition, since water, which is the same substance as steam, is used as a sealing medium, there is no problem even if water is mixed into steam. If the sliding surfaces of the cylinder 44 and the piston 47 are sealed with oil, it is inevitable that oil is mixed into water or steam, so that a special filter device for separating oil is required. In addition, since the sliding surfaces of the cylinders 44 and the pistons 47 are sealed by bypassing while also using a part of the water for lubricating the sliding surfaces of the vanes 48 and the vane grooves 49, the water is guided to the sliding surfaces. The structure can be simplified by eliminating the need to separately provide a passage.
[0062]
By the way, the liquid-phase working medium supplied to the sliding surface between the vane 48 and the vane groove 49 and constituting the hydrostatic bearing has a reservoir 78 formed between the rotor core 42 and the rotor segments 43 after completing its function. Accumulate in Since the annular grooves 74, 74 for guiding the rollers 71, 71 provided on the vane 48 communicate with the pool 78, the rollers 71, 71 are moved by the liquid-phase working medium flowing into the annular grooves 74, 74. In such a case, a large resistance is generated, and there is a concern that the output of the expander 4 is reduced.
[0063]
However, according to the present embodiment, the function of the trapping chamber 48h provided in the vane 48 allows the liquid-phase working medium in the reservoir 78 to be discharged to the exhaust ports 91 through the vane chamber 75. That is, as shown on the right side of FIG. 5, when the vane 48 is retracted most inside the vane groove 49, the suction ports 48i, 48i communicating with the radially inner end of the trapping chamber 48h communicate with the pool 78. Thus, the liquid-phase working medium in the reservoir 78 is captured by the capturing chamber 48h. When the rotor 41 rotates in the direction indicated by the arrow R, the vane 48 projects radially outward from the vane groove 49 as shown in the lower part of FIG. The liquid-phase working medium trapped in the trapping chamber 48h is discharged to the vane chamber 75 by communicating with the vane chamber 75 located at the position shown in FIG.
[0064]
As the rotor 41 rotates in the direction indicated by the arrow R in this manner, the liquid-phase working medium in the pool 78 is discharged into the vane chamber 75 by the trap chambers 48h provided in the respective vanes 48 and collected in the pool 78. It is possible to prevent the rotation of the rotor 41 from being braked by the resistance of the liquid phase working medium. In addition, when the suction ports 48i, 48i communicate with the pool 78, the discharge port 48j does not communicate with the vane chamber 75, and when the discharge port 48j communicates with the vane chamber 75, the suction ports 48i, 48i do not communicate with the pool 78. That is, since the suction ports 48i and 48i and the discharge port 48j do not communicate with the pool 78 and the vane chamber 75 at the same time, the pressure energy leaked from the sliding surfaces of the cylinder 44 and the piston 47 and captured by the pool 78 Is not wasted to the vane chamber 75 through the capture chamber 48h.
[0065]
Further, the high-temperature and high-pressure steam having the pressure energy leaked from the sliding surfaces of the cylinder 44 and the piston 47 and captured in the pool 78 passes through the communication hole 12d of the first casing 12 and the one-way valve 79 (see FIG. 2). Since the high-temperature and high-pressure steam is supplied to the relay chamber 19, the high-temperature and high-pressure steam can be supplied from the intake ports 90 to the vane chambers 75 and reused effectively. If the pressure in the reservoir 78 becomes lower than the pressure in the relay chamber 19 for any reason, the one-way valve 79 closes to prevent the temperature-reduced and reduced-pressure steam in the relay chamber 19 from flowing back to the reservoir 78. It is possible to prevent the pressure from escaping from 19 and prevent the efficiency of the expander 4 from decreasing.
[0066]
Next, the operation of the cooling system of the internal combustion engine 1 including the waste heat recovery device 2 will be described mainly with reference to FIGS.
[0067]
The water pumped from the tank 6 by the low-pressure pump 7 is supplied to the heat exchanger 102 provided in the exhaust pipe 101 via the passage P1, where it is preheated and then supplied to the water jacket 105 of the internal combustion engine 1 via the passage P2. . The water flowing in the water jacket 105 cools the cylinder block 103 and the cylinder head 104, which are the heat generating parts of the internal combustion engine 1, and is supplied to the distribution valve 106 in a state where the temperature has risen. As described above, since the water preheated by the heat exchanger 102 of the exhaust pipe 101 is supplied to the water jacket 105, the warm-up of the internal combustion engine 1 can be promoted at a low temperature and the supercooling of the internal combustion engine 1 can be prevented. As a result, the performance of the evaporator 3 can be improved by raising the exhaust gas temperature.
[0068]
Part of the high-temperature water distributed by the distribution valve 106 is pressurized by the high-pressure pump 8 interposed in the passage P4 and supplied to the evaporator 3, where it exchanges heat with exhaust gas to form high-temperature high-pressure steam. Become. The high-temperature and high-pressure steam generated in the evaporator 3 is supplied to a steam supply pipe 88 of the expander 4, passes through the cylinders 44 and the vane chambers 75, drives the rotary shaft 21, and is then discharged to the condenser 5.
[0069]
Another part of the high-temperature water distributed by the distribution valve 106 is reduced in pressure by the pressure reducing valve 107 interposed in the passage P5 to become steam, and is supplied to the relay chamber 19 of the expander 4. The steam supplied to the relay chamber 19 is supplied from the steam supply pipe 88 and merges with the first temperature-reduced pressure-reducing steam that has passed through the cylinders 44..., And after being driven on the rotating shaft 21, is discharged to the condenser 5. As described above, a part of the high-temperature water from the distribution valve 106 is vaporized by the pressure reducing valve 107 and supplied to the expander 4, so that the water can effectively utilize the heat energy received by the water jacket 105 of the internal combustion engine 1. The output of the expander 4 can be increased. Another part of the high-temperature water distributed by the distribution valve 106 is supplied to the first water passage W1 of the expander 4 via the passage P6, and lubricates each portion to be lubricated. Since the lubricated portion of the expander 4 is lubricated by using the high-temperature water in this way, it is possible to prevent the expander 4 from being overcooled and reduce the so-called cooling loss. The water that has entered the vane chambers 75 in the expansion stroke after lubrication is heated and vaporized by mixing with the steam in the vane chambers 75, and the output of the expander 4 is increased by the expansion action. Then, the second temperature-reduced pressure-reduced steam discharged from the expander 4 to the passage P8 is supplied to the condenser 5, where it is cooled by the cooling fan 109 to water and returned to the tank 6. Another part of the high-temperature water distributed by the distribution valve 106 is cooled by exchanging heat with the auxiliary device 110 interposed in the passage P7, and then returned to the tank 6 via the check valve 111.
[0070]
As described above, after the water pumped from the tank 6 by the low-pressure pump 7 is supplied to the water jacket 105 to cool the heat generating portion of the internal combustion engine 1, the water is supplied to the auxiliary machine 110 to be cooled, and then the tank 6 is cooled. And a part of the water that has exited the water jacket 105 is distributed as a working medium, and the water is returned to the tank 6 via the high-pressure pump 8, the evaporator 3, the expander 4, and the condenser 5 to recover waste heat. The water circulation path of the internal combustion engine 1 passing through the water jacket 105 and the accessory 110 is combined with the water circulation path of the waste heat recovery apparatus 2 and the water circulation path of the waste heat recovery apparatus 2 and the high pressure small flow rate. Therefore, it is possible to supply water having a flow rate and a pressure suitable for the cooling system of the internal combustion engine 1 and the waste heat recovery device 2, respectively, and to generate the water of the internal combustion engine 1 while maintaining the performance of the waste heat recovery device 2. It is possible to eliminate the radiator part sufficiently cooled. Moreover, since the water supplied from the low-pressure pump 7 to the water jacket 105 is preheated by the heat exchanger 102 provided in the exhaust pipe 101, the waste heat of the internal combustion engine 1 can be used more effectively.
[0071]
Further, since the heat exchanger 102 to which low-temperature water is supplied from the low-pressure pump 7 is provided downstream of the exhaust pipe 101 in which the temperature of the exhaust gas is lower than the position of the evaporator 3, excess waste gas of the exhaust gas is provided. The heat can be efficiently recovered without any excess. Further, since the water preheated by the heat exchanger 102 is supplied to the water jacket 105, the supercooling of the internal combustion engine 1 is prevented, and the combustion heat, that is, the exhaust gas is further heated to increase the heat energy of the exhaust gas. Waste heat recovery efficiency can be improved.
[0072]
Although the embodiments of the present invention have been described in detail, various design changes can be made in the present invention without departing from the gist thereof.
[0073]
For example, in the embodiments, the expander 4 has been exemplified as the rotary fluid machine, but the present invention can also be applied as a compressor.
[0074]
Further, in the embodiment, steam and water are used as the gas phase working medium and the liquid phase working medium, but any other suitable working medium can be used.
[0075]
【The invention's effect】
As described above, according to the first aspect of the present invention, since the supplementary chamber having the suction port and the discharge port is formed inside the vane, only the suction port accumulates when the vane moves radially inward. When the vane moves to the outside in the radial direction, only the discharge port communicates with the vane chamber in the low-pressure side stroke of either the intake stroke or the exhaust stroke when the vane moves radially outward. Liquid working medium can be discharged. Moreover, since the suction port and the discharge port do not communicate with the liquid pool and the vane chamber at the same time, the gas phase working medium in the liquid pool is prevented from flowing out to the vane chamber through the supplementary chamber, and the pressure energy still available Is prevented from being wastefully discharged.
[0076]
According to the invention described in claim 2, the first and second energy conversion means function as an expander for integrating and outputting the mechanical energy generated respectively, or the first and second energy conversion means respectively function as an expander. The rotating fluid machine that functions as a compressor that integrates and outputs the generated pressure energy supplies the gas-phase working medium leaked from the high-pressure side energy conversion means to the low-pressure side energy conversion means via a one-way valve. In addition, the gas-phase working medium leaked to the reservoir can be effectively used by the low-pressure-side energy conversion means without wasting, thereby increasing the energy conversion efficiency. Moreover, when the pressure of the gas-phase working medium leaked from the high-pressure side energy converting means is lower than the pressure of the gas-phase working medium of the low-pressure side energy converting means, the backflow of the gas-phase working medium is prevented by the one-way valve. It is possible to prevent the efficiency of the energy conversion means on the low pressure side from decreasing.
[0077]
According to the third aspect of the present invention, since the first and second energy conversion means operate sequentially and continuously with the common gas-phase working medium, the supply / discharge path of the gas-phase working medium can be simplified. Instead, the efficiency of generating mechanical energy or pressure energy can be increased.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of a waste heat recovery device for an internal combustion engine.
FIG. 2 is a longitudinal sectional view of the expander corresponding to a sectional view taken 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 taken along line 4-4 in FIG. 2;
FIG. 5 is a sectional view taken along line 5-5 in FIG. 2;
FIG. 6 is a sectional view taken along line 6-6 in FIG. 2;
FIG. 7 is a sectional view taken along line 7-7 of FIG. 5;
8 is a sectional view taken along line 8-8 in FIG. 5;
9 is a sectional view taken along line 9-9 in FIG.
FIG. 10 is a sectional view taken 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 lubricant distribution section of the rotor.
FIG. 13 is a perspective view of an end of a seal auxiliary member, a spring, and a vane seal.
FIG. 14 is a schematic diagram showing a cross-sectional shape of a rotor chamber and a rotor.
[Explanation of symbols]
4 Expander
11 Casing
14 Rotor chamber
41 rotor
44 cylinder
47 piston
48 Vane
48h supplementary room
48i suction port
48j outlet
49 Vane Groove
75 Vane Room
78 pool
79 One-way valve

Claims (3)

A rotor chamber (14) formed in the casing (11), a rotor (41) rotatably housed in the rotor chamber (14), and a plurality of vane grooves (49) radially formed in the rotor (41). A plurality of vanes (48) slidably supported on the vane, and a static pressure for supporting the vanes (48) in a floating state by a liquid-phase working medium supplied to the vane groove (49) and the sliding surface of the vane (48). A bearing and a reservoir (78) formed radially inward of the rotor (41) and for storing a liquid-phase working medium functioning as the hydrostatic bearing;
The pressure energy of the gas-phase working medium supplied to the vane chamber (75) partitioned by the rotor (41), the casing (11) and the vane (48) during the intake stroke and the exhaust stroke and the rotational energy of the rotor (41). A rotary fluid machine that converts each other,
Inside the vane (48), a supplementary chamber (48h) having a suction port (48i) opening radially inward of the rotor (41) and a discharge port (48j) opening radially outward is formed, and the vane (41) is formed. ) Moves radially inward, only the suction port (48i) communicates with the reservoir (78) to suck the liquid-phase working medium into the supplementary chamber (48h), and the vane (48) moves radially outward. Then, only the discharge port (48j) communicates with the vane chamber (75) in the low pressure side stroke of either the intake stroke or the exhaust stroke to discharge the liquid phase working medium in the supplementary chamber (48h). Rotary fluid machinery. First energy conversion means in which a piston (47) is slidably fitted to a cylinder (44) provided in a rotor (41), and a vane (48) slides in a vane groove (49) of the rotor (41). The second energy conversion means fitted freely,
When functioning as the expander (4), the first and second energy conversion means integrate and output the generated mechanical energy, respectively, and when functioning as the compressor, the first and second energy conversion means respectively generate the generated pressure. Integrate and output energy,
Of the first and second energy conversion means, the gas-phase working medium leaked from the high-pressure energy conversion means to the reservoir (78) is supplied to the low-pressure energy conversion means via the one-way valve (79). The rotary fluid machine according to claim 1, wherein: 3. The rotary fluid machine according to claim 2, wherein the first and second energy conversion units are sequentially and continuously operated with a common gas-phase working medium. 4.

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