JP2005171955A - Rotating fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To minimize a phase difference generated between a swash plate and a rotor, when connecting the swash plate to the rotor of a rotating fluid machine by a connecting means. <P>SOLUTION: Since synchronizing pins 77 for regulating relative rotation of the swash plate 31 and the rotor 22 rotatably supported by a casing around the axis L of the rotor 22 and allowing the relative movement of the swash plate 31 and the rotor 22 in the axis L direction, are arranged in a plurality at equal intervals around the axis L of the rotor 22; output can be improved, and vibration can be reduced, by uniformizing the suction/exhaust timing of an operating medium for driving respective pistons 38 of an axial piston/cylinder group 55, by reducing a phase difference between the swash plate 31 and the rotor 22 caused by an inclination of the axis Ls of the swash plate 31 and the axis L of the rotor 22. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a rotary fluid machine that mutually converts pressure energy and mechanical energy of a working medium through an axial piston / cylinder group and a swash plate.

  Such a rotary fluid machine is known from Patent Document 1 and Patent Document 2 below. The device described in the following Patent Document 1 includes a first axial piston / cylinder group disposed radially inward and a second axial piston / cylinder group disposed radially outward, The pistons of this axial piston / cylinder group have their spherical heads in contact with the dimples formed on the swash plate, and the pistons of the second axial piston / cylinder group are connected to the swash plate via a connecting rod. The phase of the rotor supporting the first and second axial piston / cylinder groups and the phase of the swash plate are the same due to the contact between the spherical heads of the pistons of the first axial piston / cylinder group and the dimples of the swash plate. Is maintained.

In addition, what is described in the following Patent Document 2 is that a piston of an axial piston / cylinder group arranged in a casing and a swash plate rotatably supported by an output shaft are connected by a connecting rod, and the phase of the casing and the swash plate Are kept the same by the meshing of the gears provided on both.
JP 2002-256805 A Japanese Patent Laid-Open No. 50-100406

  By the way, what is described in the above-mentioned patent document 1 maintains the same phase of the swash plate and the rotor by bringing the spherical heads of the pistons of the first axial piston / cylinder group into contact with the dimples of the swash plate. Therefore, the bending moment acting on the piston from the swash plate may cause galling between the piston and the cylinder sleeve, causing abnormal wear. In particular, in an expander that uses high-temperature and high-pressure steam as a working medium, it is inevitable that water condensed with steam is mixed into the oil, and therefore the lubrication conditions of the piston and cylinder sleeve may deteriorate and abnormal wear may be promoted. is there.

  Moreover, since the piston and the swash plate are connected by the connecting rod, the bending moment does not act on the piston from the swash plate. However, since the gear provided on the casing and the gear provided on the swash plate are meshed to maintain the same phase, there is a difference in the amount of thermal expansion between the output shaft supporting the swash plate and the axial direction of the casing. If there is, there is a possibility that the meshing of the gears becomes poor and galling occurs.

  Therefore, the rotor and the swash plate are connected by one sync pin that restricts the relative rotation of the swash plate and the rotor around the axis and allows the swash plate and the rotor to move relative to each other in the axial direction. Can be considered.

  However, since the axis of the swash plate is inclined with respect to the axis of the rotor, the one sync pin constitutes an inconstant velocity joint, and the angular velocity of the swash plate fluctuates even when the rotor rotates at a constant angular velocity. As a result, the rotor phase and the swash plate phase become inconsistent with the rotation of the rotor. Therefore, there is a problem that the expansion ratio of the working medium becomes non-uniform for each expansion chamber of the axial piston cylinder group, and it is difficult to set optimal intake timing and exhaust timing for all the expansion chambers.

  The present invention has been made in view of the above circumstances, and an object thereof is to minimize a phase difference generated between a swash plate and a rotor when the swash plate and the rotor of a rotary fluid machine are connected by a connecting means. To do.

  To achieve the above object, according to the first aspect of the present invention, a rotor rotatably supported by a casing, an axial piston / cylinder group provided on the rotor so as to surround its axis, and a rotor A swash plate having an axis inclined with respect to the axis of the shaft and rotatably supported by the casing, a connecting rod for connecting the piston of the axial piston / cylinder group to the swash plate, and a connecting means for connecting the swash plate to the rotor The connecting means is a rotary fluid machine that restricts relative rotation of the swash plate and the rotor about the axis of the rotor and permits relative movement of the swash plate and the rotor in the axial direction. A rotating fluid machine is proposed in which a plurality of the connecting means are arranged around the axis of the rotor.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the plurality of connecting means are orthogonal to the axis of the swash plate through the intersection of the axis of the rotor and the axis of the swash plate. A rotating fluid machine is proposed which is arranged in the plane of rotation of the swash plate.

  According to the invention described in claim 3, in addition to the configuration of claim 2, a rotating fluid machine is proposed in which the plurality of connecting means are arranged at equal intervals in the circumferential direction.

  According to a fourth aspect of the present invention, in addition to the structure of any one of the first to third aspects, the plurality of connecting means are arranged between adjacent connecting rods. A rotating fluid machine is proposed.

  In addition, the synchro pin 77 of an Example respond | corresponds to the connection means of this invention.

  According to the first aspect of the present invention, the connecting means for restricting relative rotation of the swash plate and the rotor around the axis of the rotor and allowing the swash plate and the rotor to move relative to each other in the axial direction is provided. Because multiple axes are arranged around the axis, the phase difference between the swash plate and the rotor due to the inclination of the axis of the swash plate and the rotor is reduced, and each piston of the axial piston / cylinder group is driven. It is possible to improve the output and reduce the vibration by making the timing of suction and exhaust of the working medium to be uniform.

  According to the configuration of the second aspect, since the plurality of connecting means are arranged in the swash plate rotation plane that passes through the intersection of the axis of the rotor and the axis of the swash plate and is orthogonal to the axis of the swash plate, It is possible to smoothly transmit the torque of the swash plate to the rotor so that no offset load acts between them.

  According to the configuration of claim 3, since the plurality of connecting means are arranged at equal intervals in the circumferential direction, it is possible to effectively reduce the phase difference between the swash plate and the rotor and further enhance the vibration reduction effect. it can.

  According to the configuration of the fourth aspect, since the plurality of connecting means are arranged between the adjacent connecting rods, a compact layout can be achieved while avoiding interference between the connecting means and the connecting rod.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

  1 to 12 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an expander, FIG. 2 is a view taken along arrow 2-2 in FIG. 1, and FIG. 4 is a cross-sectional view taken along line 4-4 in FIG. 3, FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 3, FIG. 6 is a diagram illustrating the inclination of the connecting rod accompanying the rotation of the rotor, and FIG. FIG. 8 is a graph illustrating the effect of the offset of the spherical portion on the swash plate side, FIG. 8 is a graph showing the phase difference between the rotor and the swash plate when the rotor and the swash plate are coupled with one sync pin, and FIG. FIG. 10 is a graph showing the phase difference between the rotor and the swash plate for five synchro pins different by 72 °, FIG. 10 is a graph showing the phase difference between the rotor and the swash plate according to this embodiment, and FIG. Fig. 12 shows the locus of the synchro pin moving inside the long groove. Fig. 12 shows the position of the rotor. Is a diagram showing the positional relationship between the synchro pin and long groove Metropolitan that varies with the change.

  As shown in FIGS. 1-5, the expander E of a present Example is used for a Rankine-cycle apparatus, for example, converts the thermal energy and pressure energy of the high temperature / high pressure steam as a working medium into mechanical energy, and outputs it To do. The casing 11 of the expander E includes a casing main body 12, a front cover 15 coupled to the front opening of the casing main body 12 with a plurality of bolts 14 through a seal member 13, and a rear opening of the casing main body 12. A rear cover 18 coupled with a plurality of bolts 17 through a sealing member 16, and an oil pan 21 coupled with a plurality of bolts 20 with a lower surface opening of the casing body 12 through a sealing member 19. Consists of.

  The rotor 22 disposed so as to be rotatable around the axis L extending in the front-rear direction in the center of the casing 11 is supported by combination angular bearings 23f and 23r provided at the front portion of the front cover 15, and the rear portion thereof is supported by the casing body 12. Is supported by a radial bearing 24 provided on the surface. A swash plate holder 28 is integrally formed on the rear surface of the front cover 15, and a swash plate 31 is rotatably supported by the swash plate holder 28 via a radial bearing 29. The axis Ls of the swash plate 31 is inclined with respect to the axis L of the rotor 22, and the inclination angle is fixed.

  The rotor 22 includes an output shaft 32 supported by the front cover 15 by combined angular bearings 23f and 23r, a spherical member 26 fitted to the outer periphery of the output shaft 32 and fixed by a knock pin 25, and a rear portion of the output shaft 32. And a rotor head 36 coupled to the rear surface of the rotor body 33 by a plurality of bolts 35 via a metal gasket 34 and supported by the casing body 12 by the radial bearing 24. Prepare.

  The rotor body 33 is formed with five sleeve support holes 33a around the axis L at intervals of 72 °, and the five cylinder sleeves 37 are fitted into the sleeve support holes 33a from behind. A flange 37 a is formed at the rear end of each cylinder sleeve 37, and the flange 37 a is in contact with the metal gasket 34 in a state where the flange 37 a is fitted in a step portion 33 b formed in the sleeve support hole 33 a of the rotor body 33. Positioned in the direction (see FIG. 3). A piston 38 is slidably fitted inside each cylinder sleeve 37, and two compression rings 39, 39 and one oil ring 40 are supported on the outer periphery of the piston 38. A steam expansion chamber 42 is defined between the annular lid member 41 joined to the metal gasket 34 and the rotor head 36 and the top surface of the piston 38.

  A connecting rod holder 43 is fitted inside the piston 38 and is locked by a clip 44. A spherical portion 45a at the rear end of the connecting rod 45 is swingably connected to the connecting rod holder 43, and a spherical portion at the front end. 45b is connected to the swash plate 31 in a swingable manner. At this time, the cover member 76 is fixed to the rear surface of the swash plate 31 with a plurality of bolts 27. The spherical member 45 b at the front end of the connecting rod 45 is prevented from coming off by the cover member 76.

  The five cylinder sleeves 37 and the five pistons 38 constitute an axial piston / cylinder group 55.

  Five long grooves 26a... Extending in the direction of the axis L are formed in the spherical member 26 fixed to the outer periphery of the output shaft 32 at intervals of 72 °, and the male screw portion is formed on the inner peripheral surface of the opening 31a of the annular swash plate 31. The five sync pins 77... Which are fixed radially by 72 degrees by screwing 77a or by inlay fitting are loosely fitted in the corresponding long grooves 26a. As shown well in FIG. 5, the width of each long groove 26a of the spherical member 26 is constant in the radial direction around the axis L, but the head 77b of the synchro pin 77 loosely fitted in the long groove 26a is in the radial direction. Tapered with an angle of 2 ° so that the outside is thin. Therefore, when the output shaft 32 and the swash plate 31 are slightly rotated relative to each other, the head portion 77b of the sync pin 77 is in line contact with the inner surface of the long groove 26a, and wear can be suppressed by reducing the surface pressure of the contact portion. Further, the five sync pins 77 are arranged between the five connecting rods 45, so that interference between the sync pins 77 and the connecting rods 45 can be effectively avoided.

  As shown in detail in FIGS. 3 and 6, the axis L of the rotor 22 and the axis Ls of the swash plate 31 intersect at an intersection C, and the swash plate rotation surface Ps (the axis of the swash plate 31 passes through the intersection C). The spherical portions 45b on the swash plate 31 side of the five connecting rods 45 are offset to the pistons 38 side by a predetermined distance δ with respect to the plane perpendicular to Ls). Due to this offset, the spherical portion 45b on the swash plate 31 side of the connecting rod 45 is displaced downward in FIG. 3, but at this time, the piston 38 at the top dead center (the piston 38 shown on the upper side in FIG. 3) is displaced. The offset amount is set so that the connecting rods 45 that are continuous are substantially parallel to the axis L of the rotor 22. Accordingly, when the piston 38 is at the top dead center, the connecting rod 45 is substantially parallel to the axis L of the rotor 22, and the connecting rod 45 moves from the top dead center to the top dead center again through the bottom dead center. It will incline with respect to the axis L.

  Further, since the five sync pins 77 are arranged on the swash plate rotation surface Ps, when transmitting the torque of the swash plate 31 to the spherical member 26, smooth torque transmission is performed so that no offset load is generated. Can be possible.

  A plate-like bearing holder 92 is superimposed on the front surface of the front cover 15 via a seal member 91 and fixed with bolts 93... And the pump body 95 of the oil pump 49 is connected to the front surface of the bearing holder 92 via a seal member 94. Are overlapped and fixed with bolts 96. The combined angular bearings 23f and 23r are sandwiched between the step portion of the front cover 15 and the bearing holder 92 and fixed in the direction of the axis L.

  A shim 97 having a predetermined thickness is sandwiched between the spherical member 26 fixed to the output shaft 32 and the inner races of the combined angular bearings 23f and 23r, and the combined angular bearing 23f, The 23r inner race is tightened. As a result, the output shaft 32 is positioned in the direction of the axis L with respect to the combined angular bearings 23f and 23r, that is, with respect to the casing 11.

  An oil passage 32 a extending on the axis L is formed inside the output shaft 32 integral with the rotor 22, and the inner periphery of the rear end portion of the oil passage 32 a is closed by the oil passage closing member 61. The front end of the oil passage 32a branches in the radial direction and communicates with the annular groove 32b on the outer periphery of the output shaft 32, the middle portion of the oil passage 32a communicates with the oil hole 32g extending in the radial direction, and the rear of the oil passage 32a. The ends communicate with annular grooves 33c formed in the sleeve support holes 33a through oil holes 32c extending in the radial direction. The annular grooves 33c and the outer peripheral surface of the piston 38 communicate with each other through oil holes 37b penetrating the cylinder sleeves 37, and the oil holes 32g are formed with oil holes 26b formed in the spherical member 26. To communicate with the inner surface of the long groove 26a.

  A trochoid oil pump 49 disposed between a recess 95a formed on the front surface of the pump body 95 and a pump cover 58 fixed to the front surface of the pump body 95 with a plurality of bolts 57 through a seal member 56 is provided. The outer rotor 50 is rotatably fitted in the recess 95a, and the inner rotor 51 is fixed to the outer periphery of the output shaft 32 and meshes with the outer rotor 50. The internal space of the oil pan 21 communicates with the suction port 53 of the oil pump 49 through the oil pipe 52 and the oil passage 95b of the pump body 95, and the discharge port 54 of the oil pump 49 passes through the oil passage 95c of the pump body 95. The output shaft 32 communicates with the annular groove 32b.

  A rotary valve 64 that supplies and discharges steam to and from the five expansion chambers 42 of the rotor 22 is disposed on the axis L behind the rotor 22. The rotary valve 64 includes a valve main body 65, a fixed side valve plate 66, and a movable side valve plate 67. The movable valve plate 67 is fixed to the rear surface of the rotor 22 by a bolt 69 that is screwed into the oil passage closing member 61 while being positioned in the rotational direction by a knock pin 68. The fixed side valve plate 66 that contacts the movable side valve plate 67 via the flat sliding surface 70 is formed integrally with the valve main body portion 65, and the valve main body portion 65 is connected to the rear cover 18 by the knock pin 71 in the direction of the axis L. And is locked so as not to move in the rotational direction. By pressing the valve body 65 forward against the rear cover 18 with a plurality of preload springs 72 arranged so as to surround the axis L, the fixed valve plate 66 and the movable valve plate 67 slide on the sliding surface 70. In close contact. A steam supply pipe 73 is connected to the rear surface of the valve main body 65.

  Next, the operation of the expander E of the present embodiment having the above configuration will be described.

  High-temperature and high-pressure steam generated by heating water with an evaporator passes through a steam passage formed in the valve main body 65 and the fixed valve plate 66 of the rotary valve 64 from the steam supply pipe 73 and slides on the movable valve plate 67. Reach plane 70. The steam passage opening in the sliding surface 70 is instantaneously communicated with a corresponding steam passage formed in the movable valve plate 67 rotating integrally with the rotor 22 during a predetermined intake period, and the high-temperature and high-pressure steam is transferred to the movable valve plate. The steam passage 67 is supplied to the expansion chamber 42 in the cylinder sleeve 37.

  Even after the supply of steam to the expansion chamber 42 is cut off as the rotor 22 rotates, the high-temperature and high-pressure steam expands in the expansion chamber 42, so that the piston 38 fitted to the cylinder sleeve 37 moves downward from the top dead center. The connecting rod 45 that is pushed forward toward the dead point and connected to the piston 38 presses the swash plate 31. As a result, a rotational torque is applied to the swash plate 31 by the reaction force received from the swash plate holder 28, and the rotational torque is fitted to the outer periphery of the heads 77 b of the five sync pins 77 fixed to the swash plate 31. It is transmitted from the long groove 26 a to the output shaft 32 through the spherical member 26 and rotates the output shaft 32 together with the rotor 22. Each time the rotor 22 rotates by one fifth, high-temperature and high-pressure steam is supplied into adjacent new expansion chambers 42, and the rotor 22 is continuously rotated.

  The low-temperature and low-pressure steam pushed out from the expansion chamber 42 is integrated with the rotor 22 while the piston 38 reaching the bottom dead center with the rotation of the rotor 22 is pressed by the swash plate 31 and retreats toward the top dead center. The movable valve plate 67 is discharged to the condenser through the sliding surface 70, the fixed valve plate 66 and the valve body 65.

  As the rotor 22 rotates, an oil pump 49 provided on the output shaft 32 operates, and oil drawn from the oil pan 21 through the oil pipe 52, the oil passage 95b of the pump body 95, and the suction port 53 is discharged from the discharge port 54. The oil passage 95c of the pump body 95, the annular groove 32b of the output shaft 32, the oil passage 32a of the output shaft 32, the oil hole 32c of the output shaft 32, the annular groove 33c of the rotor body 33, and the oil in the cylinder sleeve 37 are discharged. It is supplied to the sliding surfaces of the pistons 38 and the cylinder sleeves 37 through the holes 37b to lubricate the sliding surfaces. The oil in the oil passage 32a of the output shaft 32 is supplied to the long groove 26a through the oil hole 32g of the output shaft 32 and the oil hole 26b of the spherical member 26, and the long groove 26a and the head 77b of the synchro pin 77. Lubricate the sliding surface.

  When converting the thrust in the direction of the axis L generated by the pistons 38 of the axial piston / cylinder group 55 into the rotational force of the rotor 22 via the swash plate 31, the pistons 38 are not brought into direct contact with the swash plate 31. Since the pistons 38 are connected to the swash plate 31 via the connecting rods 45, the bending moment acting on the pistons 38 due to the reaction force received from the swash plate 31 can be minimized. As a result, even if water condensed with high-temperature and high-pressure steam is mixed into the oil and the lubrication conditions are deteriorated, the sliding surfaces of the pistons 38 and the cylinder sleeves 37 are prevented from being squeezed to prevent the occurrence of abnormal wear. And the frictional force of the said sliding surface can be reduced and the efficiency of the expander E can be improved. Also, since the bending moment of the pistons 38 can be minimized, the size of the piston 38 can be reduced by reducing the dimension in the direction of the axis L, and the required strength of the pistons 38 can be reduced to reduce the weight. it can. Furthermore, since the heat mass is reduced by downsizing the pistons 38, the heat escape through the pistons 38 can be reduced, and the efficiency of the expander E can be increased.

  In particular, when the piston 38 is in the vicinity of the top dead center, that is, in the intake stroke, the high-temperature and high-pressure steam is supplied to the expansion chamber 42 and the piston 38 is pushed forward with the maximum load, and the reaction force from the swash plate 31 is reduced. When acting strongly on the piston 38 via the connecting rod 45, the connecting rod 45 is substantially parallel to the axis L of the rotor 22, so that the radial load applied to the sliding surfaces of the piston 38 and the cylinder sleeve 37 is minimized. It is possible to suppress the occurrence of galling and abnormal wear on the sliding surface, and to reduce the frictional resistance, thereby contributing to the improvement of the output of the expander E.

  Note that the inclination angle of the connecting rod 45 with respect to the axis L of the rotor 22 becomes large at the end of the expansion stroke or the exhaust stroke, but at this time, the reaction load acting on the piston 38 via the connecting rod 45 from the swash plate 31 is small. Therefore, there is no possibility that the sliding surfaces of the piston 38 and the cylinder sleeve 37 will be damaged or abnormally worn.

  As described above, even if the output of the expander E is improved by enlarging the diameter of the swash plate 31 and increasing the stroke of the pistons 38, the spherical shape of the connecting rod 45 with respect to the swash plate rotation surface Ps. When the center of the spherical portion 45b is projected in the direction of the axis L of the rotor 22 by offsetting the portion 45b to the piston 38 side by a predetermined distance δ, the locus is offset in the direction of the bottom dead center by δ · sin α. It becomes possible to reduce the frictional resistance of the sliding surfaces of the pistons 38 and the cylinder sleeves 37 by reducing the inclination angle of the connecting rod 45 of the piston 38 near the top dead center (FIG. 7 ( A)).

  On the other hand, as shown in FIG. 7C, simply increasing the diameter of the swash plate 31 increases the inclination angle of the connecting rod 45 connected to the piston 38 at the top dead center. As shown in FIG. 7B, when the diameter of the swash plate 31 is reduced, the inclination angle of the connecting rod 45 is reduced, but the stroke of the piston 38 is reduced. As a result, the output of the expander E decreases.

  FIG. 8 shows a phase difference between the rotor 22 and the swash plate 31 when it is assumed that the rotor 22 and the swash plate 31 are coupled with one sync pin. In this case, since the axis L of the rotor 22 and the axis Ls of the swash plate 31 are inclined, the one sync pin constitutes a non-uniform joint, and even if the rotor 22 rotates at a constant angular velocity, the rotor 22 is inclined. The angular velocity of the plate 31 varies. For this reason, the phase of the rotor 22 and the phase of the swash plate 31 do not coincide with the rotation of the rotor 22.

  For example, when the # 1 piston 38 is at the top dead center in FIG. 8 and the phase of the rotor 22 and the phase of the swash plate 31 are both coincident at 0 °, the rotor 22 is rotated during one rotation of the rotor 22. And the phase difference of the swash plate 31 fluctuates over two periods in a sine wave shape. Accordingly, when the # 2 piston 38 reaches the top dead center, the phase difference becomes about + 1 °, and when the # 3 piston 38 reaches the top dead center, the phase difference becomes about −2 °. When the 4 piston 38 reaches the top dead center, the phase difference becomes about + 2 °, and when the # 5 piston 38 reaches the top dead center, the phase difference becomes about −2 °.

  Thus, if the phase difference between the rotor 22 and the swash plate 31 differs for each piston 38, the volume of the expansion chamber 42 changes due to the phase difference between the rotor 22 and the swash plate 31. The expansion ratio of the high-pressure steam becomes non-uniform, and even when the optimal intake timing and exhaust timing are set for the specific expansion chamber 42, the optimal timing cannot be obtained for the other expansion chambers 42. And since the output for each set of each cylinder sleeve 37 and piston 38 is different, there is a problem that low-order (rotation primary or secondary) vibration occurs.

  However, according to the present embodiment, the five synchro pins 77 are arranged at equal intervals in the circumferential direction, and the five synchro pins 77 are made to function in order as the rotor 22 rotates. 38, the phase difference between the rotor 22 and the swash plate 31 can be made uniform, and the above-mentioned problems can be solved. The reason will be further described below.

  The five sine waves shown in FIG. 9 are obtained when the phase difference between the rotor 22 and the swash plate 31 is set to 0 ° when the # 1 piston 38 to the # 5 piston 38 are at top dead center. The fluctuation of the phase difference of the swash plate 31 is shown. When the number of synchro pins 77 is one, the phase difference fluctuates within a range of ± 2 °. However, the five synchro pins 77 arranged at intervals of 72 ° have a phase difference between the rotor 22 and the swash plate 31. By sequentially suppressing the occurrence, the phase difference takes a substantially constant value near + 2 ° as shown by a thick solid line in FIG. 10, and all of the five expansion chambers 42 are uniform and It is possible to improve the output of the expander E and suppress vibrations by setting the optimal intake timing and exhaust timing.

  11 and 12 illustrate how the synchro pin 77 moves in the long groove 26a of the spherical member 26 of the output shaft 32. The synchro pin 77 painted black in FIG. 12 moves as the rotor 22 rotates. The same synchro pin 77 is shown. When the sync pin 77 is at the top dead center of phase 0 ° (see FIG. 12A), the sync pin 77 is at the position (1) in the center of the long groove 26a in the width direction (rotation direction of the rotor 22). When the rotor 22 rotates to the position of the phase 45 ° (see FIG. 12B), the sync pin 77 moves to the advance side in the rotation direction of the rotor 22 while moving in the axis L direction inside the long groove 26a. It contacts the position (2) on one side. In this state, torque is transmitted from the swash plate 31 to the rotor 22 through the sync pin 77.

  When the rotor 22 rotates to the position of the phase 90 ° (see FIG. 12C), the sync pin 77 moves in the direction of the axis L while moving the inside of the long groove 26a toward the rotation direction delay side of the rotor 22 and moves to the long groove 26a. When returning to the position (3) in the center in the width direction and the rotor 22 further rotates to the position of phase 135 ° (see FIG. 12D), the sync pin 77 moves while moving in the direction of the axis L in the long groove 26a. 22 moves to the delay side in the rotational direction and contacts the position (4) on the other side surface of the long groove 26a. Since the other side surface of the long groove 26a is on the delay side in the rotational direction of the rotor 22, the synchro pin 77 is a swash plate. It does not contribute to torque transmission from 31 to the rotor 22. When the rotor 22 rotates to the position of phase 180 ° (see FIG. 12E), the sync pin 77 moves to the advance side in the rotation direction of the rotor 22 while moving in the axis L direction inside the long groove 26a, and the long groove 26a. It returns to the position (5) in the center in the width direction.

  When the rotor 22 rotates in the second half part from the phase 180 ° to the phase 360 °, the synchro pin 77 has the first half part from the phase 0 ° to the phase 180 ° inside the long groove 26a as shown by a chain line in FIG. And move in the opposite direction. At this time, the sync pin 77 abuts on one side surface of the long groove 26a on the advancing direction in the rotational direction at a position of phase 225 ° (that is, position (6)). In this state, the torque of the rotor 22 is transmitted from the swash plate 31 through the sync pin 77. Note that the numbers (1) to (9) in parentheses in FIG. 11 correspond to the numbers (1) to (9) in parentheses in FIG.

  As described above, by providing the five sync pins 77, the five sync pins 77 sequentially come into contact with the one side surface of the long groove 26a in the rotation direction advance side twice while the rotor 22 makes one rotation. Thus, torque transmission from the swash plate 31 to the rotor 22 is continuously performed. The timing at which the torque is transmitted is the same for all the synchro pins 77 at the 45 ° and 225 ° phases from the top dead center. Can contribute to driving evenly.

  If the number of sync pins 77 is n (n is a natural number of 2 or more), 2n-order phase fluctuations occur during one rotation of the rotor 22, and the vibration period becomes shorter as n increases. It can contribute to reduction. In addition, when the number of synchro pins 77 increases, the load borne by each synchro pin 77 decreases, so that the durability can be enhanced. In particular, by arranging the five sync pins 77 at equal intervals, the phase difference between the rotor 22 and the swash plate 31 can be effectively reduced and the vibration reduction effect can be further enhanced.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the use of the rotary fluid machine of the present invention is not limited to the expander E that uses a compressible fluid as a working medium, but a compressor that uses a compressible fluid as a working medium, a pump that uses an incompressible fluid as a working medium, or It may be a motor.

  Although the embodiment includes five sync pins 77, the number of sync pins 77 can be appropriately changed as long as there are a plurality of sync pins 77, and the phase difference is effectively reduced as the number increases. Can be made.

  Moreover, although the head 77b of the synchro pin 77 of the embodiment has a circular cross section, it can be a rectangular cross section or an elliptic cross section. When the rectangular cross section is adopted, the head of the synchro pin 77 comes into surface contact with the long groove 26a, so that the durability can be further improved.

Vertical section of expander 2-2 line view of FIG. 3 enlarged view of FIG. Sectional view taken along line 4-4 in FIG. Sectional view along line 5-5 in FIG. The figure explaining the inclination of a connecting rod accompanying rotation of a rotor The figure explaining the effect by the offset of the spherical part by the side of the swash plate of a connecting rod The graph which shows the phase difference of a rotor and a swash plate at the time of connecting a rotor and a swash plate with one synchro pin Graph showing the phase difference between the rotor and the swash plate for five synchro pins whose phases differ by 72 ° The graph which shows the phase difference of the rotor and swash plate by a present Example The figure which shows the locus | trajectory of the synchro pin which moves the inside of a long groove with the change of the phase of a rotor The figure which shows the positional relationship of the synchro pin and long groove which change with the change of the phase of a rotor

Explanation of symbols

11 Casing 22 Rotor 31 Swash plate 38 Piston 45 Connecting rod 55 Axial piston / cylinder group 77 Sync pin (connecting means)
C Intersection of rotor axis and swash plate axis L Rotor axis Ls Swash plate axis Ps Swash plate rotation surface

Claims (4)

A rotor (22) rotatably supported by the casing (11);
An axial piston / cylinder group (55) provided on the rotor (22) so as to surround the axis (L);
A swash plate (31) having an axis (Ls) inclined with respect to the axis (L) of the rotor (22) and rotatably supported by the casing (11);
A connecting rod (45) for connecting the piston (38) of the axial piston / cylinder group (55) to the swash plate (31);
Connecting means (77) for connecting the swash plate (31) to the rotor (22);
With
The connecting means (77) restricts relative rotation of the swash plate (31) and the rotor (22) around the axis (L) of the rotor (22), and the swash plate (31) and the rotor (22) A rotary fluid machine that allows relative movement in the direction of the axis (L),
A rotary fluid machine comprising a plurality of the connecting means (77) arranged around the axis (L) of the rotor (22).   The plurality of connecting means (77) are passed through the intersection (C) between the axis (L) of the rotor (22) and the axis (Ls) of the swash plate (31), and the axis (Ls) of the swash plate (31). The rotary fluid machine according to claim 1, wherein the rotary fluid machine is disposed in a swash plate rotation surface (Ps) orthogonal to the rotation plane.   The rotary fluid machine according to claim 2, wherein the plurality of connecting means (77) are arranged at equal intervals in the circumferential direction. The rotary fluid machine according to any one of claims 1 to 3, wherein the plurality of connecting means (77) are arranged between adjacent connecting rods (45).

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