JP2003097203A - Rotary fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To change exhaust timing in a rotary fluid machine using a simple structure. SOLUTION: The rotary fluid machine has a rotor accommodated in a casing, and a side surface of the rotor is sealed by a ring seal 79' which is rotatably engaged with a circular seal groove 76 formed on the casing. A notch 79c is formed on a part of a peripheral surface of the ring seal 79', thereby providing an arcuate exhaust passage 93 between the circular seal groove 76 and the ring seal 79'. By rotating the ring seal 79' using exhaust timing changing means 70, an inlet end of the exhaust passage 93 is shifted between positions (a) and (a'). In this manner, the timing when a vane chamber rotated along with the rotor communicates with an exhaust port 91 via the exhaust passage 93 and a recess 11a of the casing is continuously changed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary fluid machine for mutually converting pressure energy of a vapor phase working medium and rotation energy of a rotor.

[0002]

2. Description of the Related Art A rotary fluid machine disclosed in Japanese Unexamined Patent Publication No. 2000-320543 is equipped with a vane piston unit having a combination of vanes and pistons, and is slidably fitted to a cylinder radially provided on a rotor. A piston for converting the pressure energy of the vapor-phase working medium and the rotation energy of the rotor to each other via a power conversion device composed of an annular groove and a roller, and supported by the rotor so as to be slidable in the radial direction. The vanes are adapted to mutually convert the pressure energy of the vapor working medium and the rotational energy of the rotor.

[0003]

When operating such a rotary fluid machine as, for example, an expander, heat of the vapor-phase working medium supplied from the intake port at the cold start of the expander is deprived of the expansion ratio. In order to reduce the size, it is necessary to advance the exhaust timing, and conversely, it is necessary to restore the exhaust timing after the expander has been warmed up. Also, if the exhaust timing can be changed according to the temperature and pressure conditions of the vapor phase working medium supplied from the intake port, the vapor phase working medium will expand completely before the exhaust port opens, and negative work will be performed. Therefore, it is possible to prevent the output of the expander from decreasing. However, the above-mentioned conventional ones cannot solve the above problems because the exhaust timing of the rotary fluid machine is fixed.

The present invention has been made in view of the above circumstances, and an object of the present invention is to make it possible to change the exhaust timing of a rotary fluid machine with a simple structure.

[0005]

In order to achieve the above object, according to the invention described in claim 1, a rotor chamber formed in a casing, a rotor rotatably accommodated in the rotor chamber, and a rotor A plurality of vane grooves radially formed on the rotor, a plurality of vanes slidably supported in the respective vane grooves, and a circular seal groove formed in the casing are rotatably supported to seal between the side surface of the rotor. A rotary fluid machine including a ring seal, a vane chamber partitioned by a rotor, a casing, and a vane, and an intake port and an exhaust port for supplying and discharging a vapor-phase working medium to the vane chamber, the outer peripheral surface of the ring seal. Between the notch formed in the circumferential direction and the circular seal groove, the end of the rotor in the direction of rotation communicates with the exhaust port, and the end of the rotor in the direction of delay in the direction of rotation. Defines an exhaust passage communicating with the vane chamber between the intake port and the exhaust port, and the ring timing is rotated along the circular seal groove by the exhaust timing changing means, so that the end portion of the exhaust passage is delayed in the rotational direction of the rotor. There is proposed a rotary fluid machine characterized in that the exhaust timing is changed by changing the position of.

According to the above-mentioned structure, when the ring seal having the notch extending in the circumferential direction on the outer peripheral surface is rotated along the circular seal groove of the casing by the exhaust timing changing means, the gap is formed between the notch and the circular seal groove. The position of the end of the exhaust passage on the side in the rotation direction lag is changed in a state where the exhaust passage formed in the section rotates and the end of the rotor in the rotation direction on the advance side of the rotor communicates with the exhaust port. As a result, the timing at which the vane chamber rotating with the rotor communicates with the exhaust port via the exhaust passage changes, and the exhaust timing can be changed.

Further, according to the invention described in claim 2,
In addition to the structure of claim 1, there is proposed a rotary fluid machine characterized in that the exhaust timing changing means can adjust the rotation angle of the ring seal steplessly.

According to the above construction, since the rotation angle of the ring seal is adjusted steplessly by the exhaust timing changing means, the exhaust timing can be changed steplessly.

The steam and water in the examples correspond to the vapor-phase working medium and the liquid-phase working medium of the present invention, respectively.

[0010]

1 to 17 show a first embodiment of the present invention. FIG. 1 is a schematic view of a waste heat recovery system for an internal combustion engine, and FIG. 2 is a sectional view taken along line 2-2 of FIG. 2 is a longitudinal sectional view of an expander corresponding to the drawing, 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, and FIG. 5 is a sectional view taken along line 5-5 of FIG. 6 is a sectional view taken along line 6-6 of FIG. 2, FIG. 7 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, and FIG. 9 is sectional view 9-9 of FIG.
11 is a sectional view taken along line 10-10 of FIG.
FIG. 12 is an exploded perspective view of the rotor, FIG. 12 is an exploded perspective view of a lubricating water distributor of the rotor, FIG. 13 is a schematic view showing a cross-sectional shape of the rotor chamber and the rotor, FIG. 14 is a front view of the ring seal, and FIG. FIG. 15 is an enlarged view of 15 parts of FIG.
FIG. 6 is an enlarged sectional view taken along line 6-16, and FIG. 17 is an operation explanatory view corresponding to FIG.

In FIG. 1, a waste heat recovery device 2 for an internal combustion engine 1 uses a waste heat (for example, exhaust gas) of the internal combustion engine 1 as a heat source to vaporize a high-pressure liquid (for example, water) in a high-temperature and high-pressure state. And an expander 4 that generates an output by expansion of the vapor, and a condenser 5 that converts pressure energy into mechanical energy in the expander 4 to liquefy vapor whose temperature and pressure have dropped. , A supply pump 6 that pressurizes the liquid (for example, water) from the condenser 5 and supplies it to the evaporator 3 again.

As shown in FIG. 2 and FIG. 3, the casing 11 of the expander 4 is made of metal first and second casing halves 1.
It is composed of 2 and 13. First and second casing halves 1
2 and 13 are composed of main body portions 12a and 13a that cooperate with each other to form the rotor chamber 14, and circular flanges 12b and 13b that are integrally connected to the outer peripheries of the main body portions 12a and 13a. It is connected via the metal gasket 15. The outer surface of the first casing half body 12 is covered with a deep pot-shaped outer wall 16 of the relay chamber, and a circular flange 16a integrally connected to the outer periphery of the first casing half body 12 is superposed on the left side surface of the circular flange 12b of the first casing half body 12. . The outer surface of the second casing half 13 is
A circular flange 1 that is covered with an outer wall 17 of an exhaust chamber that houses a magnetic coupling (not shown) that transmits the output of the expander 4 to the outside, and is integrally connected to the outer periphery thereof.
7a is superposed on the right side surface of the circular flange 13b of the second casing half body 13. The four circular flanges 12b, 13b, 16a, 17a are fastened together by a plurality of bolts 18 arranged in the circumferential direction. The relay chamber 19 is partitioned between the relay chamber outer wall 16 and the first casing half body 12, and the exhaust chamber 20 is partitioned between the exhaust chamber outer wall 17 and the second casing half body 13. The exhaust chamber outer wall 17 is provided with an exhaust port (not shown) that guides the temperature-lowered step-down steam that has finished work in the expander 4 to the condenser 5.

Body portion 12 of both casing halves 12, 13.
a and 13a are hollow bearing cylinders 12c and 1 that protrude outward to the left and right.
3c, and these hollow bearing cylinders 12c, 13c
The rotary shaft 21 having the hollow portion 21a is rotatably supported by the pair of bearing members 22 and 23. As a result, the axis L of the rotary shaft 21 passes through the intersection of the major axis and the minor axis in the rotor chamber 14 having a substantially elliptical shape.

A seal block 25 is housed inside a lubricating water introducing member 24 which is screwed into the right end of the second casing half 13 and is fixed by a nut 26. The small diameter portion 21b at the right end of the rotary shaft 21 is supported inside the seal block 25, and a pair of seal members 27, 27 are arranged between the seal block 25 and the small diameter portion 21b.
And a pair of sealing members 28 between the lubricating water introducing members 24,
28 is arranged, and further, a seal member 29 is arranged between the lubricating water introducing member 24 and the second casing half body 13. Further, the filter 30 is fitted in the recess formed in the outer periphery of the hollow bearing cylinder 13c of the second casing half body 13, and is prevented from coming off by the filter cap 31 screwed into the second casing half body 13. A pair of seal members 32 and 33 are provided between the filter cap 31 and the second casing half 13.

As is apparent from FIGS. 4 and 13, a rotor 41 having a circular shape is rotatably housed inside the rotor chamber 14 having a pseudo elliptical shape. The rotor 41 is fitted onto the outer circumference of the rotary shaft 21 and is integrally coupled, and the axis line of the rotor 41 and the axis line of the rotor chamber 14 coincide with the axis line L of the rotary shaft 21. The shape of the rotor chamber 14 as viewed in the direction of the axis L is a pseudo ellipse similar to a rhombus with four vertices rounded, and has its major axis DL and minor axis DS. The shape of the rotor 41 when viewed in the direction of the axis L is a perfect circle, and has a diameter DR slightly smaller than the minor diameter DS of the rotor chamber 14.

The cross-sectional shapes of the rotor chamber 14 and the rotor 41 when viewed in the direction orthogonal to the axis L are track-like 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 the flat surfaces 14a, 14a. Similarly, the rotor 41 has a sectional shape of a pair of flat surfaces 41a, 41a extending in parallel at a distance d, and an arc having a central angle of 180 ° for smoothly connecting 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.

Next, the structure of the rotor 41 will be described in detail with reference to FIGS. 3 to 6 and FIG.

The rotor 41 is composed of a rotor core 42 integrally formed on the outer circumference of the rotary shaft 21, and twelve rotor segments 43 ... Which are fixed so as to cover the periphery of the rotor core 42 and form the outer shell of the rotor 41. It Twelve ceramic (or carbon) cylinders 44 ... Are radially attached to the rotor core 42 at intervals of 30.degree. A small-diameter portion 44a is provided so as to project from the inner end of each cylinder 44, and the base end of the small-diameter portion 44a is sealed between the sleeve 84 and the 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 has the small-diameter portion 44a.
a and 12 third steam passages S penetrating the rotating shaft 21
3 to communicate with the first and second steam passages S1; S2, S2 inside the rotary shaft 21. A ceramic piston 47 is slidably fitted inside each cylinder 44. When the piston 47 moves to the innermost side in the radial direction, it completely retracts inside the cylinder bore 44b, and when it moves to the outermost side in the radial direction, about half of its entire length projects to the outside of the cylinder bore 44b.

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 extends in an arc shape about the axis L. Two recesses 43a,
43b is formed, and the lubricating water jet ports 43c and 43d are opened at the centers of the recesses 43a and 43b. In addition, the end surface of the rotor segment 43, that is, the vane 48 described later.
The four lubricating water jets 43e, 43e on the surface facing
43f and 43f open.

The rotor 41 is assembled as follows. The cylinder 44, the clip 45, and the C-seal 46 are attached to the outer periphery of the rotor core 42 in advance.
12 rotor vanes 4 formed between adjacent rotor segments 43 ... by fitting the rotor segments 43 ...
Fit the vanes 48 ... to 9 ... At this time, vane 4
In order to form a predetermined clearance between 8 and the rotor segments 43, shims having a predetermined thickness are provided on both sides of the vanes 48. In this state, a jig is used to attach the rotor segments 43 and the vanes 48 to the rotor core 42.
To the rotor core 42, the rotor segments 43 ... Are precisely positioned with respect to the rotor core 42, and then the rotor segments 43 ...
... (see FIG. 8) to temporarily fix the rotor core 42. Subsequently, two knock pin holes 51, 51 penetrating the rotor core 42 are co-machined in each rotor segment 43, and four knock pins 52 ... Are press-fitted into these knock pin holes 51, 51 to press the rotor segment 43 into the rotor segment 43. To join.

As is apparent from FIGS. 8, 9 and 12, a through hole 53 penetrating the rotor segment 43 and the rotor core 42 is formed between the two knock pin holes 51, 51, and the through hole 53 is formed. Concave portions 54, 54 are formed at both ends of, 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 in the respective recesses 54. It is fixed with a nut 63. The orifice forming plate 61 and the lubricating water distribution member 62 are
Of the knocking pin holes 61a, 61a of the lubricating water distributing member 62 fitted into the knocking pin holes 62a, 62a of the lubricating water distributing member 62 are prevented from rotating with respect to the rotor segment 43, and the lubricating water distributing member 62 and Nut 6
An O-ring 65 seals between the three.

The small-diameter portion 55a formed on the outer end portion of one pipe member 55 is provided with a pipe member 55 through a through hole 55b.
The small diameter portion 55a communicates with the sixth water passage W6 in the inside, and communicates with a radial distribution groove 62b formed on one side surface of the lubricating water distribution member 62. Distribution groove 62b of the lubricating water distribution member 62
Extend in six directions, and the tips of the six orifices 61b, 61b of the orifice forming plate 61;
c, 61c; communicates with 61d, 61d. The structures of the orifice forming plate 61, the lubricating water distribution member 62, and the nut 63 provided at the outer end portion 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. Is.

The downstream side of the two orifices 61b, 61b of the orifice forming plate 61 is opened so as to face the vane 48 via the seventh water passages W7, W7 formed inside the rotor segment 43. The rotor segment 43 is connected to the two lubricating water jet ports 43e and 43e, and the downstream side of the other two orifices 61c and 61c is the rotor segment 43.
Via the eighth water passages W8, W8 formed inside of the above, communicating with the two lubricating water jet openings 43f, 43f opening so as to face the vanes 48, and further two other orifices 61d, 61d. The downstream side of the above is communicated with the two lubricating water jet outlets 43c and 43d opened so as to face the rotor chamber 14 via the ninth water passages W9 and W9 formed inside the rotor segment 43.

As will be apparent by referring to FIG. 5 together,
An annular groove 67 defined by a pair of O-rings 66, 66 is formed on the outer periphery of the cylinder 44, and a sixth water passage W6 formed inside one of the pipe members 55 penetrates the pipe member 55. The individual through holes 55c and the tenth water passage W10 formed inside the rotor core 42 communicate with the annular groove 67. Then, the annular groove 67 is connected to the cylinder bore 44b and the piston 4 via the orifice 44c.
It communicates with the sliding surface of 7. Orifice 44 of cylinder 44
The position of c is set to a position that does not come off from the sliding surface of the piston 47 when the piston 47 moves between the top dead center and the bottom dead center.

As is apparent from FIGS. 3 and 9, the first water passage W1 formed in the lubricating water introducing member 24 is formed in the second water passage W2 formed in the seal block 25 and the small diameter portion 21b of the rotary shaft 21. The third water passage W3 ..., 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. It communicates with the small diameter portion 55a of the one pipe member 55 via fifth water passages W5, W5 formed so as to bypass the straddling pipe member 69 and the knock pin 52 on the radially inner side of the rotor segment 43.

As shown in FIGS. 7, 9 and 11, twelve vane grooves 49 extending radially are formed between the adjacent rotor segments 43 of the rotor 41.
The plate-shaped vanes 48 are slidably fitted in the vane grooves 49. Each vane 48 has parallel surfaces 48 a, 4 along the parallel surfaces 14 a, 14 a of the rotor chamber 14.
8a, a circular arc surface 48b along the circular arc surface 14b of the rotor chamber 14, and a notch 48c located between the parallel surfaces 48a, 48a, and is formed in a substantially U-shape from the parallel surfaces 48a, 48a. A pair of protruding support shafts 48d, 48
The rollers 71, 71 having a roller bearing structure are rotatably supported by d.

A U-shaped synthetic resin sealing member 72 is held on the arc surface 48b of the vane 48, and the tip of the sealing member 72 has an arc surface 4 of the vane 48.
8b slightly projecting from the circular arc surface 1 of the rotor chamber 14
Sliding contact with 4b. Two recesses 48e and 48e are formed on both side surfaces of the vane 48, respectively.
8e and 48e are opposed to the two lubricating water jet outlets 43e and 43e on the inner side in the radial direction, which are open at the end surface of the rotor segment 43. A piston receiving member 73 protruding inward in the radial direction is provided at the center of the notch 48 c of the vane 48, and
Abuts on the radially outer end of the.

As is apparent from FIG. 4, the flat surfaces 14a, 14a of the rotor chamber 14 defined by the first and second casing halves 12, 13 have pseudo ellipses similar to a rhombus with four vertices rounded. Annular grooves 74, 74 are recessed, and the pair of rollers 71, 71 of each vane 48 are rotatably engaged with both annular grooves 74, 74. These circular grooves 74, 74 and the circular arc surface 14 of the rotor chamber 14.
The distance between b is constant over the entire circumference. Therefore, the rotor 4
When 1 rotates, the vanes 48 guided by the rollers 71, 71 in the annular grooves 74, 74 reciprocate in the vane groove 49 in the radial direction, and the sealing member 72 mounted on the arc surface 48b of the vane 48 is compressed by a certain amount. Rotor chamber 1
It slides along the circular arc surface 14b. This prevents the rotor chambers 14 and the vanes 48 from coming into direct solid contact with each other, and prevents the increase of sliding resistance and the occurrence of wear, while the vane chambers 75 partitioned between the adjacent vanes 48.
Can reliably seal ...

As is apparent from FIGS. 2, 7, 8 and 15, the flat surfaces 14a, 14a of the rotor chamber 14 are shown.
A pair of circular seal grooves 76, 76 are formed on the outer peripheral surface of the annular groove 74, 74 so as to surround the outer sides of the annular grooves 74, 74. Two O-rings 77 and 7 are provided in the two circular seal grooves 76 and 76, respectively.
A pair of ring seals 79, 79 'provided with 8 are slidably fitted, and their sealing surfaces face recesses 43a, 43b (see FIG. 4) formed in each rotor segment 43. . The ring seal 79 on the first casing half 12 side is locked by a knock pin 80,
The ring seal 79 ′ on the second casing half 13 side is rotationally driven along the circular seal groove 76 by the exhaust timing changing means 70.

Each of the ring seals 79, 79 'is provided with a metal main body 79a and a carbon lining 79b adhered to the surface of the main body 79a facing the rotor 41, and the second casing half. The ring seal 79 'on the body 13 side is provided with arcuate cutouts 79c at two locations diametrically spaced from each other on the outer peripheral surface thereof in the range from the vicinity of one O-ring 77 to the sliding surface of the lining 79b. It
Therefore, with the ring seal 79 'fitted in the circular seal groove 76, the ring seal 79' and the circular seal groove 7 are
An arc-shaped exhaust passage 93 is formed between the six. Further, in the area where the recess 13d where the exhaust ports 91 ... Are opened is formed, a recess 11a is formed on the inner surface of the casing 11 so as to face the circular seal groove 76 radially outward.

By the exhaust timing changing means 70, the ring seal 79 'can rotate within the circular seal groove 76 over a predetermined angle range. Exhaust timing changing means 7
0 is a motor 94 provided in the second casing half 13 and
A worm 95 provided on the output shaft of the motor 94, an intermediate shaft 96 supported by the second casing half body 13, a worm wheel 97 provided at one end of the intermediate shaft 96 and meshing with the worm 95, and an intermediate shaft 96 It comprises a drive gear 98 provided at the other end and a driven gear 79d formed on a part of the outer circumference of the ring seal 79 '. Therefore, the motor 94
When is driven, the ring seal 79 'is rotated via the worm 95, the worm wheel 97, the intermediate shaft 96, the drive gear 98 and the driven gear 79d, and the rotational position can be arbitrarily changed. When the ring seal 79 ′ rotates, the leading end of the exhaust passage 93 in the rotation direction R of the rotor 41 always faces the recess 11a of the casing 11, and the trailing end of the exhaust passage 93 in the rotation direction R is located. Are exhaust ports 91 ... And intake ports 90 ... of the casing 11.
The phase changes in time.

As is apparent from FIGS. 2, 3 and 10, an opening 16b is formed in the center of the outer wall 16 of the relay chamber, and the boss portion 81a of the fixed shaft support member 81 arranged on the axis L is the above-mentioned. A plurality of bolts 8 are provided on the inner surface of the opening 16b.
2 and is fixed to the first casing half 12 with a nut 83. A cylindrical sleeve 84 made of ceramic is fixed to the hollow portion 21a of the rotary shaft 21, and an outer peripheral surface of a fixed shaft 85 integrated with the fixed shaft support member 81 is opposed to an inner peripheral surface of the sleeve 84. It fits freely. 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.

Fixed shaft support member 81 arranged on the axis L
A steam supply pipe 88 is fitted inside and fixed by a nut 89, and the right end of the steam supply pipe 88 is press-fitted into the center of a fixed shaft 85. A first steam passage S1 is formed in the axial direction at the center of the fixed shaft 85 and is connected to the steam supply pipe 88, and the fixed shaft 85 has a pair of second steam passages S2, S.
2 penetrates in the radial direction with a phase difference of 180 °. As described above, the rotor 41 fixed to the rotary shaft 21 is
Small diameter part 4 of 12 cylinders 44 ...
4a ... and the sleeve 84 with twelve third steam passages S3
... pass through, and the radially inner ends of the third steam passages S3 are opposed to the radially outer ends of the second steam passages S2, S2 so as to communicate with each other.

A pair of notches 85 is formed on the outer peripheral surface of the fixed shaft 85.
a and 85a are formed with a phase difference of 180 °, and the notches 85a and 85a are formed in the third steam passage S3.
Can communicate with ... The notches 85 a, 85 a and the relay chamber 19 are formed by a pair of fourth axially formed on the fixed shaft 85.
The steam passages S4, S4, an annular fifth steam passage S5 formed in the fixed shaft support member 81 in the axial direction, and the fixed shaft support member 8
1 communicates with each other via through holes 81b ...

As shown in FIGS. 2 and 4, the first casing half 12 and the second casing half 13 have a leading side 15 in the rotational direction R of the rotor 41 with reference to the minor axis direction of the rotor chamber 14. A plurality of intake ports 90, ..., which are aligned in the radial direction are formed at the positions of °. The intake port 90 ... Communicates the internal space of the rotor chamber 14 with the relay chamber 19. Further, a plurality of exhaust ports 91 ... Are formed in the second casing half body 13 at positions of 15 ° to 75 ° on the delay side of the rotation direction R of the rotor 41 with respect to the minor axis direction of the rotor chamber 14. This exhaust port 9
1, the internal space of the rotor chamber 14 communicates with the exhaust chamber 20. The sealing member 72 of the vane 48 ...
So as not to be damaged at the edges of the exhaust ports 91 ... Open to the shallow recesses 13d, 13d formed inside the second casing half body 13.

The second steam passages S2, S2 and the third steam passage S3 ..., and the notches 85a, 85a of the fixed shaft 85 and the third steam passage S3 ... Are fixed shaft 85 and rotary shaft 21.
The rotary valve V that periodically communicates with each other is formed by relative rotation (see FIG. 10).

As is apparent from FIG. 2, the pressure chambers 92, 9 are formed on the back surfaces of the ring seals 79, 79 'which fit into the circular seal grooves 76, 76 of the first and second casing halves 12, 13.
2 is formed, and the first and second casing halves 12,
The eleventh water passage W11 formed in No. 13 communicates with both pressure chambers 92, 92 via a twelfth water passage W12 and a thirteenth water passage W13, which are pipes, and the water pressure applied to both pressure chambers 92, 92 The ring seals 79, 79 'are the rotor 41
Is urged toward the side of.

The eleventh water passage W11 communicates with the outer peripheral surface of the annular filter 30 through the fourteenth water passage W14 formed of a pipe, and the inner peripheral surface of the filter 30 is formed in the second casing half 13 in the fifteenth portion. The 16th water passage W16 formed in the 2nd casing half body 13 is open for free passage via water passage W15. The water supplied to the 16th water passage W16 has a fixed shaft 85.
And the sliding surface of the sleeve 84 is lubricated. Water supplied from the inner peripheral surface of the filter 30 to the outer peripheral surface of the bearing member 23 via the seventeenth water passage W17 lubricates the outer peripheral surface of the rotary shaft 21 through the orifice penetrating the bearing member 23.
On the other hand, the water supplied to the outer circumference of the bearing member 22 from the eleventh water passage W11 through the eighteenth water passage W18 made of a pipe lubricates the outer peripheral surface of the rotating shaft 21 through an orifice penetrating the bearing member 22, Lubricate the sliding surfaces of the fixed shaft 85 and the sleeve 84.

Next, the operation of this embodiment having the above construction will be described.

First, the operation of the expander 4 will be described.
In FIG. 3, the high-temperature and high-pressure steam from the evaporator 3 passes through the center of the steam supply pipe 88 and the fixed shaft 85 in the first steam passage S.
1, and is supplied to the pair of second steam passages S2 and S2 that penetrate the fixed shaft 85 in the radial direction. In FIG. 10, when the sleeve 84 that rotates integrally with the rotor 41 and the rotating shaft 21 in the arrow R direction reaches a predetermined phase with respect to the fixed shaft 85, the rotational direction R of the rotor 41 from the minor axis position of the rotor chamber 14 is changed. A pair of third steam passages S3, S3 on the leading side
Communicate with the pair of second steam passages S2, S2, and the high-temperature high-pressure steam in the second steam passages S2, S2 is connected to the third steam passage S3.
It is supplied to the inside of the pair of cylinders 44, 44 via S3 and presses the pistons 47, 47 radially outward. In FIG. 4, when the vanes 48, 48 pressed by these pistons 47, 47 move radially outward, the vanes 4
A pair of rollers 71, 71 and an annular groove 7 provided in 8, 48
By the engagement with 4, 74, the forward movement of the pistons 47, 47 is converted into the rotational movement of the rotor 41.

As the rotor 41 rotates, the second steam passage S
Even after the communication between S2 and S2 and the third steam passages S3 and S3 is cut off, the high temperature and high pressure steam in the cylinders 44 and 44 continues to expand, so that the pistons 47 and 47 are further advanced. The rotation of the rotor 41 is continued.
When the vanes 48, 48 reach the major axis position of the rotor chamber 14, the third steam passages S3, S3 connected to the corresponding cylinders 44, 44 communicate with the notches 85a, 85a of the fixed shaft 85, and the rollers 71, 71 are formed into the annular groove. The pistons 47, 47 pressed by the vanes 48, 48 guided by 74, 74 move inward in the radial direction, so that the cylinders 44, 4
The steam in 4 is the third steam passages S3, S3 and the notches 85a, 8
After passing through 5a, the fourth steam passages S4, S4, the fifth steam passage S5, and the through holes 81b, the first temperature-reduced step-down steam is supplied to the relay chamber 19. The first temperature-falling step-down steam is
The high-temperature high-pressure steam supplied from the steam supply pipe 88 has finished the work of driving the pistons 47, 47, and the temperature and pressure have dropped. Although the thermal energy and pressure energy of the first temperature-falling step-down steam are lower than those of the high-temperature high-pressure steam, they still have sufficient thermal energy and pressure energy to drive the vanes 48 ...

The first temperature-decreasing depressurized steam in the relay chamber 19 is the intake port 9 of the first and second casing halves 12 and 13.
0 is supplied to the vane chambers 75 in the rotor chamber 14, and further expanded there to press the vanes 48 to rotate the rotor 41. Then, the second temperature-decreasing step-down steam, which has finished its work and whose temperature and pressure have further decreased, is discharged from the exhaust ports 91 of the second casing half body 13 to the exhaust chamber 20, and then supplied to the condenser 5.

In this way, the expansion of the high-temperature high-pressure steam results in 1
The two pistons 47 ...
When the rotor 41 is rotated through 71 and the annular grooves 74, 74, and the first temperature-reduced stepped-down steam, which has been cooled by the high-temperature high-pressure steam, is expanded, the rotor 41 is rotated through the vanes 48. can get.

By the way, the notch 79 of the ring seal 79 '
exhaust passage 93 formed between c and the circular seal groove 76
When the inlet end of the and the inlet ends of the recesses 13d, 13d of the casing 11 are aligned (see line a in FIG. 14),
When the vane chamber 75, which moves with the rotation of the rotor 41, reaches the line a, the vane chamber 75 has the concave portions 13d, 1
The exhaust port 91 is communicated with the vane chamber 75 through 3d.
The steam inside is discharged from the exhaust ports 91 .... From this state, the exhaust timing changing means 70 is used to set the ring seal 7
When 9'is rotated on the delay side of the rotation direction R of the rotor 41 (clockwise in FIG. 14), the notch 79 of the ring seal 79 'is formed.
exhaust passage 93 formed between c and the circular seal groove 76
Of the rotor 41 projects from the position of line a to the position of line a ′ in FIG.
As a result, the vane chamber 75 that moves with the rotation of the rotor 41 is located at the position of the line a ′ before the position of the line a (that is, the vane chamber 75 is located at the inlet end of the recesses 13d and 13d where the exhaust ports 91 ... Are opened. Exhaust passage 9 before communication
The steam in the vane chamber 75 is discharged from the exhaust passage 93 through the recess 11a formed in the casing 11 to the exhaust ports 91 ...

That is, as the angle at which the exhaust timing changing means 70 rotates the ring seal 79 'to the delayed side in the rotational direction R of the rotor 41 increases, the exhaust timing of the steam from the vane chamber 75 is advanced. Therefore,
For example, by advancing the exhaust timing at the cold start when the expansion ratio of the steam in the vane chamber 75 becomes small, the vapor phase working medium expands completely before the vane chamber 75 communicates with the exhaust ports 91, and negative work is performed. Can be avoided, and the output of the expander 4 can be prevented from decreasing. Then, after the warm-up of the expander 4 is completed, the exhaust timing is returned to the original state. The method of controlling the exhaust timing is not limited to the above embodiment, and the exhaust timing can be changed by any method according to the temperature condition and pressure condition of the steam supplied from the intake ports 90. Particularly, according to the exhaust timing changing means 70 of the present embodiment, the exhaust timing changes continuously (that is, steplessly), so that precise control can be performed.

Next, the lubrication of the vanes 48 and the pistons 47 of the expander 4 with water will be described.

The water for lubrication is supplied by using the supply pump 6 (see FIG. 1) for supplying the water from the condenser 5 to the evaporator 3 under pressure, and the water discharged by the supply pump 6 is supplied. A part is supplied to the first water passage W1 of the casing 11 for lubrication. By using the supply pump 6 for supplying water to the hydrostatic bearings of each part of the expander 4 in this way, a special pump is not required and the number of parts is reduced.

In FIGS. 3 and 8, the water supplied to the first water passage W1 of the lubricating water introducing member 24 is the second water passage W2 of the seal block 25, and the third water passage W of the rotary shaft 21.
3, the annular groove 68a of the water passage forming member 68, the rotary shaft 21
Through the fourth water passage W4, the pipe member 69 and the fifth water passages W5 and W5 formed in the rotor segment 43 into the small diameter portion 55a of the one pipe member 55, and the water flowing into the small diameter portion 55a is Through hole 55b of the pipe member 55, the sixth water passage W6 formed in both pipe members 55 and 56, and the through hole 56 formed in the other pipe member 56.
After passing through b, it flows into the small diameter portion 56a of the other pipe member 56.

Small diameter portion 55 of each pipe member 55, 56
a, 56a to the distribution groove 62 of each lubricating water distribution member 62
Part of the water that has passed through the six orifices 61b, 61b; 61c, 61c; 61d, 61d of the orifice forming plate 61 via b, and has four lubricating water jet ports 43e, 43e opening to the end surface of the rotor segment 43. 43f, 4
3f, and the other part is ejected from the lubricating water ejection ports 43c and 43d in the arc-shaped recesses 43a and 43b formed on the side surface of the rotor segment 43.

Thus, the water jetted into the vane groove 49 from the lubricating water jet ports 43e, 43e; 43f, 43f on the end surface of each rotor segment 43 is vane 48 slidably fitted in the vane groove 49. To form a hydrostatic bearing to support the vane 48 in a floating state.
The solid contact between the end face of 3 and the vane 48 is prevented to prevent seizure and abrasion. Like this, vane 48
By supplying water that lubricates the sliding surface of the rotor 41 through the water passage radially provided inside the rotor 41, not only the water can be pressurized by centrifugal force but also the temperature around the rotor 41 can be stabilized. The influence of thermal expansion can be reduced and the set clearance can be maintained to minimize steam leakage.

Further, since water is retained in the recesses 48e, 48e formed in two pieces on each side of the vane 48, the recesses 48e, 48e serve as pressure reservoirs and suppress the pressure drop due to water leakage. As a result, the vanes 48 sandwiched between the end surfaces of the pair of rotor segments 43, 43 are floated by the water, and the sliding resistance can be effectively reduced. Further, when the vane 48 reciprocates, the relative position of the vane 48 in the radial direction with respect to the rotor 41 changes, but the recesses 48e and 48e are provided not on the rotor segment 43 side but on the vane 48 side, and the vane 48 is most loaded. Since it is provided in the vicinity of the rollers 71, 71 on which the sliding motion is applied, it is possible to effectively keep the reciprocating vane 48 in a floating state and effectively reduce the sliding resistance.

The water that lubricates the sliding surface of the vane 48 with respect to the rotor segment 43 moves outward in the radial direction by the centrifugal force, and the sealing member 7 provided on the arc surface 48b of the vane 48.
2 lubricates the sliding portion between the circular arc surface 14b of the rotor chamber 14 and the rotor 2. The water that has been lubricated is stored in the rotor chamber 14
From the exhaust port 91 ...

In FIG. 2, the circular seal grooves 76, 76 of the first casing half 12 and the second casing half 13 are shown.
Water is supplied to the pressure chambers 92, 92 at the bottom of the rotor to urge the ring seals 79, 79 ′ toward the side surface of the rotor 41, and the lubricating water formed inside the recesses 43 a, 43 b of each rotor segment 43. A ring seal in a floating state inside the circular seal grooves 76, 76 is formed by jetting water from the jet ports 43c, 43d and forming a hydrostatic bearing on the sliding surface of the rotor chamber 14 with the flat surfaces 14a, 14a. 7
The flat surfaces 41a, 41a of the rotor 41 can be sealed with 9,79 ', and as a result, steam in the rotor chamber 14 can be prevented from leaking through a gap between the rotor 41 and the rotor 41. At this time, the ring seals 79, 79 '
The rotor 41 and the rotor 41 are separated from each other by the water film supplied from the lubricating water jets 43c and 43d and do not come into solid contact with each other.
By tilting the ring seals 79, 79 'in 6, 76, it is possible to secure stable sealing performance while minimizing the frictional force.

The ring seals 79 and 79 'and the rotor 4 are
The water that has lubricated the sliding portion with 1 is supplied to the rotor chamber 14 by the centrifugal force, and is then discharged from the casing 11 through the exhaust ports 91.

Further, in FIG. 5, the cylinder 44 and the piston 47 slide 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 water supplied to the moving surface exhibits a sealing function due to the viscosity of the water film formed on the sliding surface, and the high-temperature high-pressure steam supplied to the cylinder 44 leaks through the sliding surface with the piston 47. Effectively prevent At this time, the cylinder 44 and the piston 47 pass through the inside of the expander 4 in the high temperature state.
Since the water supplied to the sliding surface of is heated, it is possible to minimize the decrease in the output of the expander 4 due to the cooling of the high-temperature high-pressure steam supplied to the cylinder 44 by the water. .

The first water passage W1 and the eleventh water passage W11
, And supplies water at the required pressure in each lubrication section. 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 bearings as described above, it can oppose the load fluctuation. High pressure is required. On the other hand, the water supplied from the eleventh water passage W11 is
Mainly, the fixed shaft 85 is water-lubricated, and high-temperature high-pressure steam leaking from the third steam passages S3, S3 to the outer periphery of the fixed shaft 85 is sealed to fix the fixed shaft 85, the rotary shaft 21, and the rotor 4.
Since the effect of thermal expansion such as 1 is reduced, the pressure may be at least higher than the pressure in the relay chamber 19.

As described above, since the two water supply systems of the first water passage W1 for supplying high-pressure water and the eleventh water passage W11 for supplying water of lower pressure than that are provided, the high-pressure water is supplied. It is possible to solve the problem when only one water supply system for supplying is provided. That is, excessive pressure of water is supplied around the fixed shaft 85 to increase the outflow amount of water to the relay chamber 19, and the fixed shaft 85, the rotary shaft 21, and the rotor 4 are connected.
It is possible to prevent the problem that the steam temperature is lowered due to supercooling of the first and the like, and it is possible to increase the output of the expander 4 while reducing the supply amount of water.

Moreover, since water, which is the same substance as steam, is used as the sealing medium, there is no problem even if water is mixed into the steam. For example, the cylinder 44 and the piston 4
When the sliding surface of 7 is sealed with oil, it is unavoidable that oil mixes with water or steam, so a special filter device for separating the oil is required. Further, the sliding surfaces of the cylinder 44 and the piston 47 are sealed by partially bypassing the water that lubricates the sliding surfaces of the vanes 48 and the vane grooves 49, so that the water that guides the water to the sliding surfaces is sealed. The structure can be simplified by eliminating the need to separately provide a passage.

Next, a second embodiment of the present invention will be described with reference to FIGS.

Exhaust timing changing means 70 of the first embodiment
Is to change the exhaust timing steplessly using the motor 94, the exhaust timing changing means 70 of the second embodiment sets the exhaust timing in advance when the expander 4 is assembled. As for possible exhaust timing, any one exhaust timing is selected from a plurality of exhaust timings.

That is, the lining 7 of the ring seal 79 '
A plurality of (eight in the embodiment) knock pin holes 79e ... Are formed at three locations in the circumferential direction of the main body 79a on the side opposite to 9b, and the plurality of knock pin holes 79e. By engaging the knock pins 80 ... With any of them, the rotational position of the ring seal 79 'can be changed stepwise. Ring seal 79 '
Since the exhaust passage 93 is formed between the circular seal groove 76 and the circular seal groove 76, the exhaust timing can be changed by rotating the ring seal 79 'as in the first embodiment.

In addition to the embodiments described above, the piston 4
As a structure of a power conversion device for converting the forward motion of 7 ... into the rotary motion of the rotor 41, the forward motion of the piston 47 is directly received by the rollers 71, not through the vanes 48, and the engagement with the annular grooves 74, 74 is performed. It can also be converted into rotary motion. Further, the vanes 48 ... Also the rollers 71 ... And the annular grooves 74, 7
As described above, the pistons 47 and the rollers 71, and the vanes 48 and the rollers 71 are respectively separated from each other by a constant distance from the inner peripheral surface of the rotor chamber 14 in cooperation with each other. It may independently cooperate with the annular grooves 74, 74.

When the expander 4 is used as a compressor, the rotor 41 is rotated by the rotary shaft 21 in the direction of the arrow R in FIG. 4, and the outside air is exhausted by the vanes 48 from the exhaust port 91 to the rotor chamber 14. Inhale and compress,
The low-compressed air thus obtained is used for the intake port 90 ...
To relay chamber 19, through hole 81b ..., Fifth steam passage S
5, fourth steam passages S4, S4, notches 85 of the fixed shaft 85
a, 85a and the third steam passage S3 ...
4 is sucked into the inside, and compressed there by the piston 47 so as to become highly compressed air. The highly compressed air thus obtained is discharged from the cylinders 44 through the third steam passages S3, the second steam passages S2, S2, the first steam passage S1 and the steam supply pipe 88. When the expander 4 is used as a compressor, the steam passages S1 to S5 and the steam supply pipe 88 are read as the air passages S1 to S5 and the air supply pipe 88, respectively.

The embodiments of the present invention have been described in detail above, but the present invention can be modified in various ways without departing from the scope of the invention.

For example, although the expander 4 is illustrated as the rotary fluid machine in the embodiments, the present invention can be applied as a compressor.

Although steam and water are used as the vapor-phase working medium and the liquid-phase working medium in the embodiment, other suitable working mediums can be used.

In the embodiment, of the pair of ring seals 79, 79 'of the first and second casing halves 12, 13,
Only the ring seal 79 ′ on the second casing half 13 side is rotated by the exhaust timing changing means 70, but both ring seals 79, 7 are rotated by the exhaust timing changing means 70.
9'may be rotated in conjunction with each other.

[0068]

As described above, according to the invention described in claim 1, the ring seal having the notch extending in the circumferential direction on the outer peripheral surface is rotated along the circular seal groove of the casing by the exhaust timing changing means. Then, the exhaust passage formed between the notch and the circular seal groove rotates, and the rotor of the exhaust passage rotates while the end of the exhaust passage on the advance side in the rotation direction of the rotor communicates with the exhaust port. The position of the end on the direction delay side changes. As a result, the timing at which the vane chamber rotating with the rotor communicates with the exhaust port via the exhaust passage changes, and the exhaust timing can be changed.

According to the invention described in claim 2,
Since the rotation angle of the ring seal is adjusted steplessly by the exhaust timing changing means, the exhaust timing can be changed steplessly.

[Brief description of drawings]

FIG. 1 is a schematic diagram of a waste heat recovery device for an internal combustion engine.

2 is a vertical cross-sectional view of an expander corresponding to the cross-sectional view taken along line 2-2 of FIG.

FIG. 3 is an enlarged cross-sectional view around the axis of FIG.

FIG. 4 is a sectional view taken along line 4-4 of FIG.

5 is a sectional view taken along line 5-5 of FIG.

6 is a sectional view taken along line 6-6 of FIG.

7 is a sectional view taken along line 7-7 of FIG.

8 is a sectional view taken along line 8-8 of FIG.

9 is a sectional view taken along line 9-9 of FIG.

10 is a sectional view taken along line 10-10 of FIG.

FIG. 11 is an exploded perspective view of a rotor

FIG. 12 is an exploded perspective view of a lubricating water distributor of the rotor.

FIG. 13 is a schematic diagram showing a cross-sectional shape of a rotor chamber and a rotor.

FIG. 14 is a front view of a ring seal.

FIG. 15 is an enlarged view of part 15 in FIG.

16 is an enlarged sectional view taken along line 16-16 of FIG.

FIG. 17 is an operation explanatory view corresponding to FIG.

FIG. 18 is a diagram corresponding to FIG. 14 according to the second embodiment of the present invention.

19 is an enlarged sectional view taken along line 19-19 of FIG.

20 is an enlarged cross-sectional view taken along line 20-20 of FIG.

[Explanation of symbols] 11 casing 14 rotor chamber 41 rotor 48 vanes 49 vane groove 70 Exhaust timing changing means 75 vane room 76 circular seal groove 79 'ring seal 79c cutout 90 intake port 91 Exhaust port 93 Exhaust passage

Continued front page    (72) Inventor Hiroshi Ichikawa             1-4-1 Chuo Stock Market, Wako City, Saitama Prefecture             Inside Honda Research Laboratory (72) Inventor Yasunari Kimura             1-4-1 Chuo Stock Market, Wako City, Saitama Prefecture             Inside Honda Research Laboratory

Claims (2)

[Claims] 1. A rotor chamber (14) formed in a casing (11), a rotor (41) rotatably accommodated in the rotor chamber (14), and a plurality of vane grooves radially formed in the rotor (41). (49) and a plurality of vanes (48) slidably supported in the respective vane grooves (49)
And a circular seal groove (7) formed in the casing (11).
A ring seal (79 ') that is rotatably supported by 6) and seals the side surface of the rotor (41);
1), a vane chamber (75) partitioned by a casing (11) and a vane (48), and an intake port (90) and an exhaust port (91) for supplying / discharging a vapor phase working medium to / from the vane chamber (75). A rotary fluid machine comprising: a ring seal (79 '), wherein a circular seal groove (76) and a notch (79c) formed in a circumferential direction on an outer peripheral surface of the ring seal (79') advance in a rotational direction of the rotor (14). The end on the side is the exhaust port (9
An exhaust passage (93) communicating with the vane chamber (75) between the intake port (90) and the exhaust port (91), the exhaust passage (93) communicating with the exhaust passage (93), By rotating the ring seal (79 ') along the circular seal groove (76) by the exhaust timing changing means (70), the position of the end of the exhaust passage (93) on the side of the rotor (14) lagging in the rotational direction is changed. A rotating fluid machine characterized by changing the exhaust timing. 2. The rotary fluid machine according to claim 1, wherein the exhaust timing changing means (70) is capable of continuously adjusting the rotation angle of the ring seal (79 ′).