JP4348715B2 - Positive displacement fluid machinery - Google Patents

Description

  The present invention expands or reduces the volume of a working chamber by a rotor that revolves around a rotation axis of a drive shaft having an eccentric portion, and discharges a compressive fluid or an incompressible fluid sucked from the suction chamber. The present invention relates to a positive displacement fluid machine configured to be discharged from a fluid.

  As a positive displacement fluid machine of this type, a plurality of vanes 40 divide a plurality of working chambers 51, 52, 53 along the rotational direction of the drive shaft 20, and each of the working chambers 51, 52, 53 has a fluid flow. The suction and discharge are configured, and the fluid sucked into the working chambers 51, 52, and 53 is discharged from the discharge holes by the change in volume of the working chambers 51, 52, and 53 accompanying the revolution of the rotor 30. There is a fluid pump (see, for example, Patent Document 1 and FIG. 2).

JP 2002-303283 A

  However, in the above fluid pump, the end portion of the vane 40 is tapered, the contact area with the outer peripheral surface 301 of the rotor 30 is small, and is in contact with dots or lines, so the sealing performance of the working chamber is low. There was a problem.

  Therefore, an object of the present invention is to provide a positive displacement fluid machine with improved volumetric efficiency by improving the sealing performance of the working chamber.

In order to solve the above problems, the positive displacement fluid machine of the present invention employs the following technical means 1 to 5 .
1. The positive displacement fluid machine of this invention is
A drive shaft 15 provided with a suction side communication path 150 and a discharge side communication path 151 ;
An eccentric portion 20 formed on the drive shaft 15;
A bearing 23 disposed on the outer peripheral side of the eccentric portion 20;
A cylindrical rotor 22 mounted on the outer peripheral side of the bearing 23 and revolving around the drive shaft 15 as the drive shaft 15 rotates;
A casing 11 disposed concentrically with the drive shaft 15 and containing the rotor 22;
A main working chamber 40 formed between the inner peripheral surface 110 of the casing 11 and the outer peripheral surface 24 of the rotor 22;
A vane portion 51 which is accommodated in a vane groove 50 formed in the rotor 22 so as to be able to appear and retract and divides the main working chamber 40 into a low pressure side and a high pressure side;
A swing vane 56 that can swing in accordance with the revolution of the rotor 22 at the end of the vane portion 51 on the main working chamber 40 side;
The swing vane 56 includes a first pressure chamber 60 and a second pressure chamber 62 provided at the end portion on the vane portion 51 side and the end portion on the casing 11 side, respectively .
Furthermore, the inner part of the vane groove 50 in which the vane part 51 is accommodated is a sub working chamber 45, and the fluid pressure in the sub working chamber 45 is configured to act on the vane part 51 as a back pressure.
The rotor 22 is provided with a main working chamber communication hole 220 and a sub working chamber communication hole 221 both penetrating in the radial direction. The main working chamber communication hole 220 and the sub working chamber communication hole 221 have outer peripheral ends. The main working chamber 40 and the sub working chamber 45 communicate with each other.
The vane portion 51 and the swing vane 56 are provided with conduction holes 65 and 66 for introducing the fluid in the sub working chamber 45 into the first pressure chamber 60 or the second pressure chamber 62.
The rotor 22 revolves according to the rotation of the drive shaft 15, and the fluid sucked from the suction port 29 is caused to change by the change in volume of the main working chamber 40 accompanying the revolution of the rotor 22. 150 is led from the suction side distribution chamber 154 to the main working chamber 40 and the sub working chamber 45, and then discharged from the discharge side distribution chamber 155 through the discharge side communication passage 151 and from the discharge port 39.
In this positive displacement fluid machine,
The suction-side communication passage 150 and the discharge-side communication passage 151 are respectively formed with a suction-side distribution chamber 154 and a discharge-side distribution chamber 155 at one end, and at the other end, a suction-side opening 150a and a discharge-side opening. Part 151a is formed in communication,
The suction-side distribution chamber 154 and the discharge-side distribution chamber 155 are formed by notching the drive shaft 15 and having different axial positions and different phase ranges.
A state in which inner peripheral ends of the main working chamber communication hole 220 and the sub working chamber communication hole 221 communicate with the suction-side distribution chamber 154 or communicate with the discharge-side distribution chamber 155 according to the rotation of the rotary shaft 15; Thus, the outer peripheral end of the main working chamber communication hole 220 communicates with the main working chamber 40 in the volume expansion state or the main working chamber 40 in the volume reduction state,
In addition, the suction port 29 and the suction side communication path 150, and the discharge port 39 and the discharge side communication path 151 are always in communication with the suction side opening 150a and the discharge side opening 151a , respectively.

  2. In the positive displacement fluid machine described in 1 above, the suction side opening 150a and the discharge side opening 151a are formed at different axial positions by cutting out the drive shaft 15;
A suction-side circular groove 152 and a discharge-side circular groove 153 are formed around the entire circumference of the drive shaft 15 around the suction-side opening 150a and the discharge-side opening 151a, respectively.
A suction port 29 is formed at the tip of the suction-side circular groove 152, and a discharge port 39 is formed at the tip of the discharge-side circular groove 153, so that the suction port 29 and the suction side are connected regardless of the rotational phase of the rotating rotary shaft 15. The communication path 150, the discharge port 39, and the discharge side communication path 151 may be always in communication.

3. In the positive displacement fluid machine according to 1 or 2, the sliding contact surface 57 of the swing vane 56 may be formed in a convex arc shape substantially concentric with the inner peripheral surface 110 of the casing 11.

4). 4. The positive displacement fluid machine according to any one of 1 to 3, wherein an arc concave surface is formed at an end of the vane portion 51 on the swing vane 56 side, and an arc convex surface is formed at the end of the swing vane 56 on the vane portion 51 side. The swing vane 56 is slidably connected to the vane portion 51 by fitting the circular arc convex surface to the arc concave surface of the vane portion 51, and can swing in and out of the vane groove 50 together with the vane portion 51. It is good also as what is stored in .

5). 5. The positive displacement fluid machine according to any one of 1 to 4, wherein the oscillating vane 56 biases the fluid pressure in the auxiliary working chamber 45 and the vane portion 51 toward the inner peripheral surface 110 of the casing 11. The slidable contact surface 57 of the swing vane 56 is oscillated with the revolution of the rotor 22 while being pressed against the inner peripheral surface 110 of the casing 11 by the urging force of the spring, and the inner peripheral surface 110 of the casing 11 is swung. It is good also as what keeps the contact to .

In the positive displacement fluid machine described above , the drive shaft 15 is provided with the suction side communication path 150 and the discharge side communication path 151, and the fluid sucked from the suction port 29 passes through the suction side communication path 150 and is mainly used. It is guided to the working chamber 40 and the sub working chamber 45 and then discharged from the discharge port 39 through the discharge side communication passage 151 .

Further, in the positive displacement fluid machine, the suction side distribution chamber 154 is formed by cutting the shaft portion 15 at a position closer to the rear plate 130 than the center portion of the rotor 22 of the shaft portion 15;
A discharge side distribution chamber 155 is formed by notching the shaft portion 15 at a position closer to the front plate 120 than the center portion of the rotor 22 of the shaft portion 15.
The rotor 22 is provided with a main working chamber communication hole 220 and a sub working chamber communication hole 221 whose outer peripheral ends communicate with the main working chamber 40 and the sub working chamber 45, respectively.
According to the rotation of the rotating shaft 15,
When the volumes of the main working chamber 40 and the sub working chamber 45 are enlarged, the inner peripheral ends of the main working chamber communication hole 220 and the sub working chamber communication hole 221 are communicated with the suction side distribution chamber 154 of the rotating shaft 15. Fluid is sucked from the suction port 29,
When the volumes of the main working chamber 40 and the sub working chamber 45 are reduced, the inner peripheral ends of the main working chamber communication hole 220 and the sub working chamber communication hole 221 are communicated with the discharge side distribution chamber 155 of the rotary shaft 15. The fluid in the main working chamber 40 and the sub working chamber 45 is discharged from the discharge port 39 through the discharge side communication path 151 .

  In the positive displacement fluid machine according to the present invention, the wide sliding contact surface provided in the swing vane is formed in an arc shape substantially concentric with the inner peripheral surface of the casing, and always follows the inner peripheral surface of the casing following the revolution of the rotor. Since the surface contact is made, the sealing performance in the working chamber is enhanced and the volumetric efficiency of the working chamber is improved.

Sectional drawing of the displacement type fluid machine of the reference form 1. FIG. Sectional drawing in alignment with the AA of FIG. Sectional drawing which follows the BB line of FIG. The enlarged view of the vane spring accommodating part shown in FIG. The enlarged view of the vane part shown in FIG. Sectional drawing which follows the CC line | wire of FIG. Sectional drawing which follows the DD line | wire of FIG. Sectional drawing by the side of the suction chamber of the positive displacement fluid machine of reference form 2. Sectional drawing by the side of the discharge chamber of the positive displacement fluid machine of the reference form 2. The perspective view of the positive displacement fluid machine of reference form 2. FIG. Sectional drawing of the displacement type fluid machine of the reference form 3. FIG. Sectional drawing which follows the EE line | wire of FIG. Sectional drawing which follows the FF line | wire of FIG. Sectional drawing which follows the GG line of FIG. Sectional drawing which follows the HH line | wire of FIG. Sectional drawing which follows the JJ line of FIG. Sectional drawing which follows the KK line | wire of FIG. Sectional drawing which follows the LL line | wire of FIG. The enlarged view of the vane part shown in FIG. Sectional drawing of the positive displacement fluid machine of the reference form 4 of this invention. Sectional drawing which follows the MM line | wire of FIG. Sectional drawing which follows the NN line | wire of FIG. Sectional drawing which follows the OO line of FIG. FIG. 21 is a cross-sectional view taken along the line P-P in FIG. 20 and shows changes in the operating state accompanying rotation of the drive shaft 15 at every 90 ° rotation angle of the drive shaft 15. Sectional drawing of the positive displacement fluid machine of the Example of this invention. The perspective view which showed the flow of the fluid of the positive displacement fluid machine of the Example of this invention. FIG. 26 is a sectional view taken along line WW in FIG. 25. FIG. 26 is a sectional view taken along line TT in FIG. 25. FIG. 26 is a sectional view taken along line VV in FIG. 25. FIG. 26 is a cross-sectional view taken along the line U-U in FIG. 25. FIG. 26 is a sectional view taken along line Q-Q in FIG. 25. FIG. 26 is a sectional view taken along line RR in FIG. 25. FIG. 26 is a cross-sectional view taken along line SS of FIG. 25.

(Reference form 1)
Hereinafter, a first reference embodiment of the present invention will be described with reference to the drawings. The positive displacement fluid machine 10 of the reference form 1 relates to a positive displacement fluid machine that handles a compressible fluid such as air or refrigerant gas for a refrigeration cycle. The structural member and the fluid storage chamber are formed in the casing 11 to form a compact structure. As shown in FIG. 1, a front plate 12 and a rear plate 13 are fastened to the casing 11 with bolts 14 so as to close both ends. The drive shaft 15 is disposed at the center portion of the positive displacement fluid machine 10 and extends to both side portions, and a connection portion for an input member is formed at one end portion. It is rotatably supported by bearings 16a and 16b attached to the front plate 12 and the rear plate 13.

  As shown in FIGS. 1 and 2, the drive shaft 15 is formed with an eccentric portion 20 that decenters the central axis 22 c of the rotor 22 with respect to the rotation axis 15 c of the drive shaft 15. As shown in FIGS. 1, 2, and 7, rotor support bearings 23a and 23b are mounted. The centers of the bearings 23 a and 23 b for supporting the rotor and the center axis 22 c of the rotor 22 coincide with the center axis of the eccentric portion 20. As shown in FIGS. 2 and 3, the cylinder 30 fixed to the inner peripheral surface of the casing 11 with bolts 14 has six vane grooves 50 at intervals of approximately 60 ° along the rotational direction D of the drive shaft 15. Is formed. In each vane groove 50, vane portions 51a, 51b, 51c, 51d, 51e, 51f that divide the main working chamber 40 into a low pressure side and a high pressure side are accommodated slidably in the radial direction. In these vane portions 51a, 51b, 51c, 51d, 51e, and 51f, a swinging vane 56 is disposed at the radially inner end. An arc concave surface is formed at the end of the vane portion 51 on the swing vane 56 side, an arc convex surface is formed at the end of the swing vane 56 on the vane portion 51 side, and the swing vane 56 has an arc convex surface. The vane portion 51 is swingably connected to the vane portion 51 by fitting into the concave arc surface of the vane portion 51. In order to reduce the weight of the vane portion 51 and the swinging vane 56, hollow portions 68 are formed. Conical springs 52 that urge the vane portions 51 a, 51 b, 51 c, 51 d, 51 e, 51 f toward the rotor 22 are disposed on the closing portion side of the vane groove 50. By this conical spring 52, the sliding contact surface 57 of the swing vane 56 is pressed against the outer peripheral surface 24 of the rotor 22. Further, according to the revolution movement of the rotor 22, the vane portion 51 reciprocates in the vane groove 50, and the swing vane 56 swings following the displacement of the rotor sliding contact surface 24. Since the slidable contact surface 57 is also freely changed, the slidable contact surface between the slidable contact surface 24 of the rotor and the slidable contact surface 57 of the swing vane is always maintained in surface contact. Accordingly, the sealing performance of the main working chamber 40 is ensured even if the pressing force of the conical spring 52 that makes the sliding contact surface 57 abut against the rotor sliding contact surface 24 is small, so that the sliding resistance is reduced, and the positive displacement fluid machine 10 and the wear of the sliding contact portion are suppressed, the durability is improved, the power for reducing the spring during the compression stroke described later is reduced, and the input power is also reduced, so that the input efficiency is improved. Further, the auxiliary working chamber 45 is formed in order to reduce the size and weight of the apparatus by effectively using the closed portion side of each vane groove 50, that is, the back pressure chamber to increase the filling efficiency of the machine. This greatly increases the amount of fluid discharged from the positive displacement fluid machine 10.

  As shown in phantom lines in FIG. 1, a partition wall 35 is formed that is substantially parallel to the front plate 12 and that partitions the suction chamber 33 and the discharge chamber 36 at a substantially axial center portion of the cylinder 30. As shown in FIG. 3, the partition wall 35 may be formed so as to be orthogonal to the vane groove 50 and integrally formed with the cylinder 30. Thereby, the steel property of the cylinder 30 is enhanced, and the cylinder 30 is suppressed from being distorted by the fluid pressure acting on the main working chamber 40 and the sub working chamber 45.

FIG. 4 is an enlarged view of the storage portion of the conical spring 52 in the most contracted state of the conical spring 52 . In the reference form 1 , as a spring member which is an urging member, a stable urging force with a relatively small variation rate of the reaction force accompanying the extension of the spring is obtained, and a compact shape in a contracted state where the spring is compressed is a compact cone. A spring 52 is used. The conical spring 52 is accommodated in a spring accommodating portion 53 formed in the closing portion of the vane groove 50 and the radially outer end portion of the vane portion 51.

  FIG. 5 is an enlarged view of the vane portion 51. When the vane portion 51 moves radially outward as the rotor 22 advances, that is, during the compression stroke, the pressure at which the fluid stored in the main working chamber 40 is compressed is about to reach a peak. A force directed from the working chamber 40d toward the low pressure main working chamber 40c in the initial stage of the compression stroke acts on the side of the vane portion 51 in the direction of F1 indicated by an arrow, and a force acting on the vane portion 51 acts. The sliding resistance between the groove 50 and the vane part 51 is increased, and there arises a problem that the input efficiency is lowered and the side surface of the vane groove 50 and the sliding contact part of the vane part 51 are further worn away. In order to improve the above problem, a downward inclined surface 54 is formed in which the side surface of the radially outer end of the vane portion 51 faces the center axis 51Y of the vane portion 51 in the direction opposite to the rotational direction D of the drive shaft. As a result, a force acts on the inclined surface 54 in the direction F2 indicated by the arrow. On the other hand, the fluid pressure in the auxiliary working chamber 45 d guided to the side chamber 46 through the conduction hole 64 acts on the side portion of the vane portion 51 d facing the side chamber 46, as indicated by the arrow F 3. In the low-pressure working fluid acting on the main working chamber 40c, the force directed to the arrow F4 acts on the peripheral portion of the swing vane 56 and the side portion of the vane portion 51d. Further, the fluid pressure in the sub working chamber 45d guided to the second pressure chamber 62 through the conduction hole 65, the first pressure chamber 60, and the conduction hole 66 is provided with the swing vane 56 and the vane portion 51d in the direction indicated by the arrow F5. It is fast. The magnitudes of these forces F1, F2, F3, F4, and F5 are proportional to the pressures in the main working chamber 40 and the sub working chamber 45 and the pressure receiving areas thereof. For this reason, the inclination angle of the inclined surface 54 and the pressure receiving areas of the side chamber 46 and the second pressure chamber 62 are optimally adjusted. As a result, the forces acting on the side portions of the vane portion 51d cancel each other and are balanced. In this way, the vane portion 51 is maintained in a good posture and can be smoothly slid along the vane groove 50, thereby improving the problem.

  Further, the fluid pressure acting in each auxiliary working chamber 45 at the peak of the compression stroke presses the vane portion 51d and the swing vane 56 toward the sliding contact surface 24 of the rotor with an excessive force. For this reason, the friction between the sliding contact surface 55 of the vane portion and the sliding contact surface 58 of the swinging vane and the sliding contact surface 24 of the rotor and the sliding contact surface 57 of the swinging vane increases, and the swinging vane 56 is smoothly swung. There is a problem that the dynamic motion is impaired and the sliding resistance accompanying the rotation of the rotor 22 is increased, thereby reducing the efficiency and durability of the positive displacement fluid machine 10. In order to improve the above problem, as shown in FIGS. 4 and 5, a first pressure chamber 60 that is cut off from the main working chamber 40 is provided between the vane portion 51 and the swing vane 56. In addition, a conduction hole 65 is formed in the vane portion 51 along the central axis 51 </ b> Y of the vane portion 51. Further, a second pressure chamber 62 that is blocked by the outer peripheral surface 24 of the rotor 22 and is cut off from the main working chamber 40 is provided at the end of the swing vane 56 on the rotor 22 side. In the swing vane 56, a conduction hole 66 is formed along the central axis 51Y of the vane portion 51. The fluid in the sub working chamber 45 is led to the first pressure chamber 60 through the conduction hole 65 and then led to the second pressure chamber 62 through the conduction hole 66. As a result, the fluid pressure in the sub working chamber 45 acts on the first pressure chamber 60 and the second pressure chamber 62, and the sliding contact surface 55 of the vane portion 51, the sliding contact surface 58 of the swing vane 56, and the sliding of the rotor 22. The contact surface 24 and the sliding contact surface 57 of the oscillating vane 56 generate a retreating force, the friction is reduced, the above problems are improved, and the efficiency and durability of the positive displacement fluid machine 10 are improved. FIG. 6 is a cross-sectional view of the suction chamber 33 defined by the partition wall 35. A suction port 29 is connected to the suction chamber 33. A communication groove 32 through which fluids sucked into the respective suction chambers 33 circulate is formed in the periphery of the cylinder 30. Between the closed portion of the vane groove 50 and the suction chamber 33, a suction-side check valve 34 that allows fluid to pass from the suction chamber 33 to the auxiliary working chamber 45 and prevents backflow is provided. Thus, when the vane portion 51 moves from the top dead center to the bottom dead center, that is, when the main working chamber 40 and the sub working chamber 45 are performing the suction stroke, the fluid is sucked through the suction port 29 and sucked. After being guided to the chamber 33, it is sucked into the auxiliary working chamber 45 through the flow groove 32 and the check valve 34, and further sucked into the main working chamber 40 through the communication hole 59.

FIG. 7 is a cross-sectional view of the discharge chamber 36 partitioned by the partition wall 35. When the vane portion 51 moves from the bottom dead center to the top dead center, that is, when the main working chamber 40 and the sub working chamber 45 perform the operation of the compression stroke, the fluid filled in the main working chamber 40 passes through the communication hole 59. And pushed out toward the sub working chamber 45. The check valve 37 on the discharge side is opened and circulated by the compression pressure of the fluid filled in the sub working chamber 45, and the fluid filled in each discharge chamber 36 is circulated around the periphery of the cylinder 30. The fluid in the main working chamber 40 and the sub working chamber 45 is discharged from the discharge port 39 to the outside of the positive displacement fluid machine 10 through the communication groove 38 and the discharge chamber 36 .

(Reference form 2)
Next, the positive displacement fluid machine 10 according to the second embodiment of the present invention will be described with reference to FIGS. In addition, since the following reference form 2 is based on the same principle as the above-mentioned reference form 1, the same code | symbol is attached | subjected to the member similar to the above-mentioned embodiment, and the detailed description is abbreviate | omitted. The positive displacement fluid machine 10 according to the reference form 2 handles an incompressible fluid as in the first reference form described above. 8 is a cross-sectional view on the suction chamber 33 side in Reference Embodiment 2. As apparent from FIG. 8, in the reference form 2, the communication hole 59 formed in the vane portion 51 in the reference form 1 is omitted. As apparent from FIGS. 8 and 10, instead of the communication hole 59, each suction chamber 33 has a drive shaft at a portion where the suction chamber 33 formed by the cylinder 30 and the main working chamber 40 are closest to each other. A check valve 44 that passes fluid from the suction chamber 33 side to the main working chamber 40 side and prevents backflow is disposed at a position near the rotational direction D of 15. For this reason, although an increase in cost is unavoidable as compared with the reference embodiment 1, in the above-described reference embodiment 1, the main working chambers 40a, 40b, 40c, 40d, and the like are connected via the communication holes 59 formed in the vane portion 51. Compared to the case where fluid is sucked into each of 40e and 40f, the main operation of the fluid sucked from the suction port 29 and stored in the suction chamber 33 via the check passage 44 is short-circuited via the check valve 44. The fluid is taken into each of the chambers 40a, 40b, 40c, 40d, 40e, and 40f, and the suction efficiency is improved. FIG. 9 is a cross-sectional view of the discharge chamber 36 side in Reference Embodiment 2. In the reference form 2, the communication hole 59 formed in the vane portion 51 is omitted. As is apparent from FIGS. 9 and 10, instead of the communication hole 59, each discharge chamber 36 has a drive shaft at a portion where the discharge chamber 36 formed by the cylinder 30 and the main working chamber 40 are closest to each other. A check valve 47 that passes a fluid from the main working chamber 40 side to the discharge chamber 36 side and prevents backflow is disposed at a position near the rotation direction D of 15. For this reason, although an increase in cost is unavoidable as compared with the configuration of the reference form 1, in the above-described reference form 1, the main working chambers 40a, 40b, 40c, Compared to the case of the first embodiment in which fluid is discharged from each of 40d, 40e, and 40f to the discharge chamber 36, the main working chambers 40a, 40b, 40c, 40d, 40e, and 40f are connected via check valves 37, respectively. The discharge efficiency is improved by discharging into the discharge chamber 36 through the short-circuited flow passage.

(Reference form 3)
Next, with reference to FIG. 11 thru | or 18, the positive displacement fluid machine 10 by the reference form 3 is demonstrated. The positive displacement fluid machine 10 according to the reference embodiment 3 is suitable for a positive displacement fluid machine such as a hydraulic pump and a hydraulic motor using, for example, hydraulic oil which is an incompressible fluid, unlike the reference embodiment 1 and the reference embodiment 2 described above. FIG. 11 is a longitudinal sectional view of the positive displacement fluid machine 10 according to the third embodiment of the present invention. A partition wall 35 that divides a suction chamber 33 formed so as to communicate with the suction port 29 indicated by a virtual line and a discharge chamber 36 connected to the discharge port 39 indicated by a virtual line is indicated by a virtual line. The cylinder 30 is formed with communication holes 72, 73, 74 indicated by phantom lines and communicating with a suction chamber, which will be described later, and communication holes 77, 78, 79 communicating with the discharge chamber. As shown in FIG. 11, in Reference Mode 3, the disc 70 is fixed to the drive shaft 15 by appropriate means such as spline or shrink fitting so as to rotate integrally with the drive shaft 15. On the other hand, in the vicinity of the other end of the drive shaft 15, a spline or shrink fit is used so that the disc 75 provided with the spool 76 is rotated 180 ° in phase with the spool 71 provided on the disc 70. It is fixed by appropriate means. As shown in FIG. 12, the side chamber 46 and the inclined surface 54 seen in the above-described reference embodiments 1 and 2 are omitted, and the end portion on the radially outer side of the vane portion 51 and the closing portion of the vane groove 50 in the reference embodiment 3 are vane. It is formed at right angles to the groove 50. The shape and configuration of the partition wall 35 are the same as those in the first and second embodiments. As shown in FIG. 13, the disk 70 is formed with a rotary on-off valve, that is, a spool 71 formed of an arcuate groove. As shown in FIGS. 11 and 13, the airtightness of the side surface of the disk 70 formed in parallel with the spool 71 and the side surface of the cylinder 30 in which the communication holes 72, 73, 74 are formed are increased. A sliding contact surface 81 is formed. Note that a sealing member such as an O-ring may be interposed on these sliding contact surfaces 81. The fluid sucked from the suction port 29 shown in FIG. 14 is guided and filled into the suction chambers 33 through the communication grooves 32. FIG. 15 is a cross-sectional view of the positive displacement fluid machine 10 on the suction chamber 33 side. The end of the communication hole 72 formed in the cylinder 30 located on the suction chamber 33 side opens into the suction chamber 33. The end of the communication hole 73 opens into the main working chamber 40. The end of the communication hole 74 opens into the sub working chamber 45. These other ends are opened in a trajectory of a turning circle drawn by a spool 71 indicated by a virtual line. FIG. 16 is a transverse cross-sectional view of the positive displacement fluid machine 10 on the discharge chamber 36 side. An end of a communication hole 77 formed in the cylinder 30 located on the discharge chamber 36 side opens into the discharge chamber 36. The end of the communication hole 78 opens into the main working chamber 40. The end of the communication hole 79 opens into the sub working chamber 45. These other ends are open in the trajectory of the turning circle drawn by the spool 76 indicated by the phantom line. As shown in FIG. 17, the disc 75 is formed with a rotary on-off valve, that is, a spool 76 formed of an arc-shaped groove. As shown in FIGS. 11 and 17, the side surface of the disk 75 formed in parallel with the spool 76 and the side surface of the cylinder 30 in which the communication holes 77, 78, 79 are formed are provided with high airtightness. A sliding contact surface 82 is formed. Note that, for example, a sealing member such as an O-ring may be interposed on these sliding surfaces. As shown in FIG. 18, the fluid stored in the main working chamber 40 and the sub working chamber 45 whose volume is being reduced is pushed out to the discharge chamber 36 and led to the discharge port 39 through the communication groove 38. It is discharged outside. FIG. 19 shows an enlarged view of the vicinity of the main working chambers 40e and 40d and the sub working chamber 45e. In the case of the positive displacement fluid machine 10 using the incompressible working fluid as in the reference form 3, unlike the reference forms 1 and 2 that handle the compressible fluid, the volume is equal to each working chamber whose volume is being reduced. Pressure is acting.
(Reference form 4)

20 is a cross-sectional view of a positive displacement fluid machine according to a fourth embodiment of the present invention, FIG. 21 is a cross-sectional view taken along line MM in FIG. 20, FIG. 22 is a cross-sectional view taken along line NN in FIG. FIG. 21 is a sectional view taken along line OO in FIG. 20. FIGS. 24A to 24D are cross-sectional views taken along the line P-P in FIG. 20, and show changes in the operating state accompanying rotation of the drive shaft 15 at every 90 ° rotation angle of the drive shaft 15. In addition, the same code | symbol is attached | subjected to the same or equivalent member as the reference forms 1 thru | or 3.

The configurations of the vane portion 51 and the swing vane 56 are the same as those in the first to third embodiments, such as the first pressure chamber 60, the second pressure chamber 62, and the conduction holes 65 and 66 (FIGS. 4, 5, and 19). Basically, the sliding contact surface 57 of the swinging vane 56 is brought into contact with the inner peripheral surface 110 of the casing 11, so that the sliding contact surface 57 of the swinging vane 56 is the casing 11. This is different in that it is formed in a convex arc shape that is substantially concentric with the inner peripheral surface 110. With this configuration, the fluid tightness between the sliding contact surface 57 of the swing vane 56 and the inner peripheral surface 110 of the casing 11 when the swing vane 56 swings following the revolution of the rotor 22. Will improve.

Hereinafter, Reference Embodiment 4 will be described with reference to FIGS. As shown in FIG. 21, the rotor 22 has three vane groove portions 50 formed at equal intervals of 120 ° along the rotational direction D of the drive shaft 15. Each vane groove 50 accommodates a vane portion 51 that can be protruded and retracted in the radial direction, and urges a swing vane 56 disposed at a tip portion of the vane portion 51 toward the inner peripheral surface 110 side of the casing 11. A conical spring 52 is accommodated. The rotor 22 is provided with a plurality of hollow portions 68 in order to reduce the weight.

  The arcuate tip (sliding contact surface 57) of the swing vane 56 is in contact with the inner peripheral surface 110 of the casing 11, and the main working chamber is made up of the first to third main working chambers by the three vanes 51. It is divided into 40a, 40b, and 40c. Further, the closed portion side (back pressure chamber) of each vane groove 50, that is, the space formed in the vane groove 50 by the vane portion 51 is used as the first to third auxiliary working chambers 45a, 45b, and 45c.

As shown in FIG. 20, the front plate 120 is bolted to one end of the drive shaft 15 (on the suction port 29 side) so as to close the opening on one end side of the casing 11, and the disk-shaped disk 70. Are fixed by appropriate means such as spline or shrink fitting so as to rotate integrally with the drive shaft 15 .

A rear plate 130 is bolted to the other end (the discharge port 39 side) of the drive shaft 15 so as to close the opening on the other end side of the casing 11. As shown in FIG. 23, the rear plate 130 has a main working chamber discharge hole 711 that can communicate with the main working chamber suction distribution hole 710 and a sub working chamber discharge hole 721 that can communicate with the sub working chamber suction distribution hole 720. Is formed .

  As shown in FIGS. 20 and 23, three cylindrical pins 90 are mounted on the surface of the rotor 22 on the rear plate 130 side, and these pins 90 follow the rotational direction D of the drive shaft 15. Are arranged at equal intervals of 120 °. Further, on the surface of the rear plate 130 on the rotor 22 side, three cylindrical pin engagement holes 91 into which the protruding portions of the pins 90 are inserted are formed.

  The pin engagement hole 91 defines the movement range of the pin 90 and prevents the rotor 22 from rotating. Therefore, the pin engagement hole 91 and the pin 90 act as a rotation prevention mechanism that restricts the rotation of the rotor 22. Thereby, the peripheral speed of the sliding contact surface 57 of the rocking vane 56 can be suppressed. The pin engagement hole 91 and the pin 90 are set in dimensions, relative positions, and the like so as not to hinder the revolving motion of the rotor 22 accompanying the rotation of the drive shaft 15.

  In the above configuration, as the drive shaft 15 rotates, the rotor 22 revolves around the rotation axis 15c of the drive shaft 20, and due to the revolving motion of the rotor 22, FIG. 24 (a) → FIG. 24 (b) → FIG. The position of the rotor 22 changes in the order of 24 (c) → FIG. 24 (d), and the volumes of the first to third main working chambers 40a, 40b, 40c and the first to third sub working chambers 45a, 45b, 45c are as follows. , Repeats enlargement and reduction with a phase difference of 120 °.

  Here, the main working chamber suction distribution holes 710 and the sub working chamber suction distribution holes 720 of the disc 70 are respectively arranged in the first to third main working chambers 40a, 40b, 40c and the first to third sub working chambers 45a, 45b, 45c sequentially communicates with the working chamber whose volume is expanding. For example, while the volumes of the main working chamber 40a and the sub working chamber 45b are expanded, the fluid from the suction port 29 is supplied to the main working chamber 40a and the sub working chamber 45b. It is sucked into the chamber 45b.

  Next, while the volumes of the main working chamber 40a and the sub working chamber 45b are reduced, the fluid sucked into the main working chamber 40a and the sub working chamber 45b is distributed to the main working chamber discharge hole 711 and the sub working chamber discharge hole 721, respectively. It is guided to the discharge port 39 through the check valve 80 provided and discharged outside the apparatus.

Figure 25 is positive-displacement fluid machine of a cross-sectional view of an embodiment of the present invention, FIG 26 is a perspective view showing the flow of displacement fluid machine of the fluid embodiment, FIG. 27 is taken along the line W-W in FIG. 25 cross-section FIG. 28 is a sectional view taken along line TT in FIG. 25, FIG. 29 is a sectional view taken along line V-V in FIG. 25, FIG. 30 is a sectional view taken along line U-U in FIG. 25 is a sectional view taken along line Q-Q in FIG. 25, FIG. 32 is a sectional view taken along line RR in FIG. 25, and FIG. 33 is a sectional view taken along line SS in FIG. In addition, the same code | symbol is attached | subjected to the same or equivalent member as the reference forms 1 thru | or 4 .

The positive displacement fluid machine of the embodiment is suitable for a hydraulic pump, a hydraulic motor, or the like using hydraulic fluid of an incompressible fluid as a medium. In the fourth embodiment , the rotor 22 is provided with the three vane grooves 50 to store the three vane portions 51. In the embodiment , as shown in FIG. 31, the rotor 22 rotates the drive shaft 15 as shown in FIG. Seven vane grooves 50 are formed at intervals of about 51 ° along the direction D, and the vane portions 51 are accommodated in the respective vane grooves 50 so as to be protruded and retracted in the radial direction. By adding the vane portions in this manner, fluid pulsation can be reduced and the load on each vane portion can be distributed. In addition, the configurations and operations of the vane portion 51 and the swing vane 56 are the same as those in the first to fourth embodiments (see FIGS. 4, 5, and 19). In the fourth embodiment , the check valve 80 is disposed in the fluid flow passage. In the present embodiment, the check valve is omitted and the suction side and the discharge side can be communicated in both directions. Yes.

  Hereinafter, the present embodiment will be described with reference to FIGS. As shown in FIGS. 26 and 27, the drive shaft 15 is provided with a suction side communication path 150 and a discharge side communication path 151, and the fluid sucked from the suction port 29 passes through the suction side communication path 150. Then, it is guided to the main working chamber 40 and the sub working chamber 45 and then discharged from the discharge port 39 through the discharge side communication passage 151.

  As shown in FIG. 28, the suction port 29 is provided in the rear plate 130 so as to open toward the left in a front view, and communicates with a suction-side communication passage 150 provided in the drive shaft 15 via a suction-side opening 150a. To do. Since the suction-side circular groove 152 is formed around the drive shaft 15, the suction port 29 and the suction-side communication path 150 are always in communication with each other regardless of the position of the rotating rotation shaft 15, and fluid can flow in. It has become.

  As shown in FIG. 29, the discharge port 39 is provided in the rear plate 130 so as to open toward the right in front view, and communicates with a discharge side communication path 151 provided in the drive shaft 15 via a discharge side opening 151a. To do. Since the discharge-side circular groove 153 is formed around the drive shaft 15, the discharge port 39 and the discharge-side communication path 151 are always in communication regardless of the position of the rotating rotary shaft 15, and fluid can be discharged. It has become.

  As shown in FIGS. 25 and 30, the rear plate 130 and the front plate 120 are each formed with seven pin engagement holes 91, and the seven pins 90 respectively attached to the both end faces of the rotor 22 correspond to each other. The rotation of the rotor 22 is prevented by being inserted into the pin engaging hole 91 to be rotated.

  As shown in FIGS. 32 and 33, the rotor 22 is provided with a plurality of main working chamber communication holes 220 and sub working chamber communication holes 221. The outer peripheral end of the main working chamber communication hole 220 communicates with the main working chamber 40, and the outer peripheral end of the sub working chamber communication hole 221 communicates with the sub working chamber 45. In addition, the inner peripheral ends of the main working chamber communication hole 220 and the sub working chamber communication hole 221 communicate with a suction side distribution chamber 154 (FIG. 32) or a discharge side distribution according to the rotation of the rotating shaft 15. It communicates with the chamber 155 (FIG. 33).

  As shown in FIG. 25, the shaft portion 15 having the eccentric portion 20 is provided with a suction-side distribution chamber 154 at a position closer to the rear plate 130 than the center portion of the rotor 22. As shown in FIGS. 26 and 32, the suction side distribution chamber 154 is formed by cutting out the shaft portion 15.

  Further, as shown in FIG. 25, the shaft portion 15 having the eccentric portion 20 is provided with a discharge-side distribution chamber 155 at a position closer to the front plate 120 than the center portion of the rotor 22. The discharge side distribution chamber 155 is also formed by notching the shaft portion 15 as shown in FIGS.

  In the above configuration, the rotor 22 revolves around the rotation axis 15 c of the drive shaft 20 as the drive shaft 15 rotates. As the rotor 22 revolves, the volumes of the main working chamber 40 and the sub working chamber 45 repeatedly expand and contract.

  When the volumes of the main working chamber 40 and the sub working chamber 45 are enlarged, the main working chamber communication hole 220 and the sub working chamber communication hole 221 are communicated with the suction side distribution chamber 154 of the rotary shaft 15 (see FIG. 32) The fluid is sucked from the suction port 29.

  On the contrary, when the main working chamber 40 and the sub working chamber 45 reduce their volumes, the main working chamber communication hole 220 and the sub working chamber communication hole 221 communicate with the discharge side distribution chamber 155 of the rotary shaft 15. Thus, the fluid in the main working chamber 40 and the sub working chamber 45 is discharged from the discharge port 39 through the discharge side communication passage 151.

  In the case of a hydraulic pump or hydraulic motor using hydraulic fluid of an incompressible fluid as a medium as in the present embodiment, an equal pressure acts on each main working chamber. For this reason, in the conventional vane type positive displacement fluid machine, as shown in FIG. 31, in the compression process, the vane portion 51 facing each main working chamber 40 has a larger pressure receiving area (F1) than a smaller one (F2). ), And the vane portion 51 slides while being pressed against the constituent wall of the vane groove 50. Therefore, the sliding resistance of the vane portion 51 with respect to the vane groove 50 is increased, and the mechanical efficiency and durability are deteriorated.

On the other hand, in the embodiment , the fluid in the sub working chamber 45 is guided to the first pressure chamber 60 through the conduction hole 65 and then guided to the second pressure chamber 62 through the conduction hole 66. As a result, the fluid pressure of the sub working chamber 45 is applied to the second pressure chamber 62 formed between the swing vane 56 attached to the tip of the vane portion 51 and the inner peripheral surface 110 of the casing 11. . As a result, the opposing biasing force (F3) in a suitable direction generated according to the swing angle of the swing vane 56 acts on the vane portion 51, so that sliding resistance is reduced and durability and mechanical efficiency can be improved.

Also, as in the embodiment, the case of using an incompressible fluid such as hydraulic oil, and the outer peripheral surface 24 of the inner peripheral surface 110 and the rotor 22 of the casing 11 be in a non-contact state, functions as a main working chamber . As a result, friction between the inner peripheral surface 110 of the casing 11 and the outer peripheral surface (sliding contact surface) 24 of the rotor 22 is eliminated, so that mechanical efficiency and durability can be further improved, and compared with the case where a compressive fluid is used. Thus, since the processing accuracy associated with the manufacturing can be reduced, the manufacturing cost can be reduced.

DESCRIPTION OF SYMBOLS 10 Positive displacement fluid machine 11 Casing 15 Drive shaft 15c Drive shaft centerline 22 Rotor 24 Outer peripheral surface (sliding contact surface)
29 Suction port 30 Cylinder 31 Inner peripheral surface 33 Suction chamber 35 Partition wall 36 Discharge chamber 39 Discharge port 40 Main working chamber 45 Sub working chamber 50 Vane groove 51 Vane portion 56 Oscillating vane 60 First pressure chamber 62 Second pressure chamber 70 yen Plate 75 Disc 90 Pin 91 Engagement hole
710 Main working chamber suction distribution hole
711 Main chamber discharge hole
720 Sub working chamber suction distribution hole
721 Sub working chamber discharge hole
150 Suction side communication passage
151 Discharge side communication passage
152 Suction side circular groove
153 Discharge side circular groove
154 Suction side distribution chamber
155 Discharge side distribution chamber
220 Main working chamber communication hole
221 Sub working chamber communication hole

Claims (5)

A drive shaft (15) provided with a suction side communication passage (150) and a discharge side communication passage (151), an eccentric portion (20) formed in the drive shaft (15), and an outer periphery of the eccentric portion (20) And a cylindrical rotor (22) mounted on the outer peripheral side of the bearing (23) and revolving around the drive shaft (15) as the drive shaft (15) rotates. ), A casing (11) that is arranged concentrically with the drive shaft (15) and accommodates the rotor (22), an inner peripheral surface (110) of the casing (11), and an outer peripheral surface of the rotor (22) (24) and a main working chamber (40) formed between the main working chamber (40) and a vane groove (50) formed in the rotor (22) so that the main working chamber (40) can be projected and retracted. A vane portion (51) partitioned into a side and an end of the vane portion (51) on the main working chamber (40) side The swing vane (56) swingable according to the revolution of the rotor (22), the end of the swing vane (56) on the vane portion (51) side, and the end on the casing (11) side. A first pressure chamber (60) and a second pressure chamber (62) respectively provided;
The inner part of the vane groove (50) in which the vane part (51) is accommodated is a sub working chamber (45), and the fluid pressure in the sub working chamber (45) acts on the vane part (51) as a back pressure. The rotor (22) has a main working chamber communication hole (220) and a sub working chamber communication hole (the outer end of which communicates with the main working chamber (40) and the sub working chamber (45), respectively). 221) are provided penetrating in the radial direction, and fluid in the auxiliary working chamber (45) is supplied to the vane portion (51) and the swinging vane (56) from the first pressure chamber (60) to the second pressure chamber (56). Conduction holes (65, 66) for introducing into the two pressure chambers (62) are provided,
The rotor (22) revolves according to the rotation of the drive shaft (15), and is sucked from the suction port (29) by the change in the volume of the main working chamber (40) accompanying the revolution of the rotor (22). The fluid flows through the suction side communication passage (150) from the suction side distribution chamber (154) to the main working chamber (40) and the sub working chamber (45), and then from the discharge side distribution chamber (155) to the discharge side. In the positive displacement fluid machine discharged from the discharge port (39) through the communication passage (151),
Each of the suction side communication passage (150) and the discharge side communication passage (151) is formed with a suction side distribution chamber (154) and a discharge side distribution chamber (155) in communication with one end side, and with suction on the other end side. The side opening (150a) and the discharge side opening (151a) are formed in communication,
The suction-side distribution chamber (154) and the discharge-side distribution chamber (155) are formed at different axial positions and different phase ranges by cutting out the drive shaft (15). (220) and the inner peripheral end of the auxiliary working chamber communication hole (221) communicate with the suction-side distribution chamber (154) or the discharge-side distribution chamber (155) according to the rotation of the rotating shaft (15). The outer end of the main working chamber communication hole (220) communicates with the main working chamber (40) in the expanded volume state or the main working chamber (40) in the reduced volume state, and is inhaled. The inlet (29) and the suction side communication path (150), and the discharge port (39) and the discharge side communication path (151) are always in communication with the suction side opening (150a) and the discharge side opening (151a), respectively. A positive displacement fluid device. The suction side opening (150a) and the discharge side opening (151a) are formed at different axial positions by notching the drive shaft (15), and around the suction side opening (150a) and the discharge side opening (151a). ) A suction side circular groove 152 and a discharge side circular groove 153 are formed around the circumference of the drive shaft (15), and the suction port (29) is provided at the tip of the suction side circular groove (152). In addition, a discharge port (39) is formed in communication with the tip of the discharge-side circular groove (153), and the suction port (29) and the suction-side communication passage (150) regardless of the rotation phase of the rotating rotating shaft (15). The positive displacement fluid device according to claim 1 , wherein the discharge port (39) and the discharge side communication passage (151) are always in communication with each other .   The positive displacement type according to claim 1 or 2, wherein the sliding contact surface (57) of the swing vane (56) is formed in a convex arc shape substantially concentric with the inner peripheral surface (110) of the casing (11). Fluid machinery. An arc concave surface is formed at the end of the vane portion (51) on the swing vane (56) side, and an arc convex surface is formed at the end of the swing vane (56) on the vane portion (51) side. The dynamic vane (56) is swingably connected to the vane portion (51) by fitting the arc convex surface to the arc concave surface of the vane portion (51), and is moved together with the vane portion (51) in the vane groove (50). The positive displacement fluid machine according to any one of claims 1 to 3, wherein the positive displacement fluid machine is housed in a retractable manner . The oscillating vane (56) biases the fluid pressure in the auxiliary working chamber (45) and the spring biasing the vane portion (51) toward the inner peripheral surface (110) of the casing (11). And swaying along with the revolution of the rotor (22) while being pressed against the inner peripheral surface (110) of the casing (11), and the sliding contact surface (57) of the swinging vane (56) is moved to the casing ( The positive displacement fluid machine according to any one of claims 1 to 4, which maintains contact with the inner peripheral surface (110) of 11) .

Images