JP2006090261A - Vane pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vane pump capable of reducing reduction of volume efficiency and reduction of mechanical efficiency as much as possible. <P>SOLUTION: This vane pump has a cam ring 20, a pair of side plates 40a, 40b provided at both opened ends of the cam ring 20, a rotor 30 stored rotatably in a space partitioned by the cam ring 20 and the pair of side plates 40a, 40b, and a vane 10 stored in such a way that a tip can retract while it is abutted on an inner peripheral cam face 21 of the cam ring 20 in each of a plurality of vane channels 31 formed radially in the rotor 30. The vane 10 moving in accordance with rotation of the rotor 30 passes through opening parts of ports 41a, 41b which become oil liquid passages formed in at least either of the pair of side plates 40a, 40b. In this case, this vane pump has a vane behavior suppressing means for suppressing predetermined behavior other than advance and retraction of the vane 10 in the vane channel 31. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a vane pump used as a pressure source for oil.

  2. Description of the Related Art Various vane pumps that have been used as oil pressure sources for vehicle power steering devices, fuel injection devices, and the like have been proposed (see, for example, Patent Document 1). In this type of vane pump, a rotor is rotatably accommodated in a space defined by a cam ring and a pair of side plates (side plates) provided at both ends of the cam ring. A plurality of vane grooves are formed radially on the rotor, and the vanes are accommodated in the plurality of vane grooves so that the tips can be advanced and retracted while abutting the inner circumferential cam surface of the cam ring. Each of the pair of side plates is provided with a port serving as an oil liquid passage (discharge side passage, suction side passage).

In the vane pump having such a structure, when the rotor rotates while the tip of each vane is pressed against the inner circumferential cam surface of the cam ring by the pressure of the oil supplied to the vane pump, each vane By sliding the cam surface, the cam surface moves forward and backward in the vane groove according to the shape of the inner peripheral cam surface. In this way, each vane moves forward and backward during the rotation of the rotor, the volume between the vanes increases and decreases, and when the vane passes through the opening of the port on the suction side formed in the side plate, the oil liquid is between The oil liquid between the vanes is sent out when the vane passes through the opening of the discharge side port.
JP-A-9-242679

  By the way, the thickness of the rotor and the vane is designed to be slightly smaller than the distance between the pair of side plates that sandwich the rotor and the vane in order to maintain the sliding sealability. For this reason, gaps (hereinafter referred to as clearances) are formed between the rotor and vanes and the side plates. The clearance between the vane and the rotor and the one side plate and the clearance between them and the other side plate are generally not equal, and the vane and the fluid are imbalanced by the fluid pressure of the fluid flowing through the clearance. The rotor is brought to the side plate side.

  In this way, the vane in the state of being brought close to one side plate side is, for example, a side other than the forward / backward movement according to the shape of the inner peripheral cam surface of the cam ring in the vane groove during the movement accompanying the rotation of the rotor. Inclined with respect to the plate, the inclined vane further falls into a port formed in the side plate, and the vane that has fallen into the port escapes from the port. As described above, the behavior of the vane other than the forward and backward movement in the vane groove does not make the contact state of the vane with the side plate uniform, and a large surface pressure can be generated locally. For this reason, wear and surface roughness of the vane and the side plate increase. When the wear of the vane and the side plate increases, the clearance between the vane and the side plate increases and the volumetric efficiency of the vane pump decreases. In addition, when the surface roughness increases, the friction of the vane that moves as the rotor rotates increases, and the mechanical efficiency of the vane pump decreases.

  The present invention has been made to solve the problems of the conventional vane pump as described above, and provides a vane pump capable of minimizing a decrease in volumetric efficiency and a decrease in mechanical efficiency.

  A vane pump according to the present invention includes a cam ring, a pair of side plates provided at both open ends of the cam ring, a rotor rotatably accommodated in a space defined by the cam ring and the pair of side plates, Each of the plurality of vane grooves formed radially on the rotor has vanes that are movably accommodated while abutting against the inner circumferential cam surface of the cam ring, and are formed on at least one of the pair of side plates. In a vane pump through which a vane moving as the rotor rotates passes through a port opening serving as an oil passage, vane behavior suppressing means for suppressing a predetermined behavior other than forward and backward movement of the vane in the vane groove. It is set as the structure which has.

  With such a configuration, when the vane moves with the rotation of the rotor, the vane repeats advancing and retreating according to the shape of the inner peripheral cam surface of the cam ring in the vane groove, and repeats the suction and discharge of the oil liquid. . In the process, the predetermined behavior other than the advance / retreat of the vane is suppressed. For this reason, even if the predetermined behavior of the vane causes wear and surface roughness of the vane and the side plate, the wear and surface roughness can be suppressed.

  In addition, the vane pump according to the present invention can be configured to have a drop prevention structure that prevents the tip of the vane from dropping into a port formed in the side plate as the vane behavior suppressing means.

  With such a configuration, the behavior that the tip of the vane falls into the port formed in the side plate is prevented. For this reason, it is possible to avoid the occurrence of wear and surface roughness on the vane and the side plate, which may be caused by the vane falling into the port.

  Further, in the vane pump according to the present invention, as the vane behavior suppressing means, when the vane passes through the opening of the port, the corner of the tip portion of the vane that contacts the edge of the opening and the edge of the opening It can be set as the structure which chamfered at least one of these.

  With such a configuration, even if the tip of the vane falls into the port formed in the side plate, when the vane escapes from the port, the corner of the tip of the vane and the edge of the opening of the port Contact is made at the chamfered portion. Thereby, when the vane escapes from the port, the behavior that the corner of the tip portion of the vane is caught by the edge of the opening of the port is suppressed, and the tip of the vane and the edge of the opening of the port are suppressed. The stress generated by contact with is relaxed. As a result, wear and surface roughness of the vane tip portion and the edge of the port opening can be suppressed.

  Moreover, the vane pump according to the present invention can be configured such that the corner of the vane tip portion and the chamfering width of the edge of the opening are equal to or greater than the depth of depression of the vane into the port.

  With this configuration, when the vane that has fallen into the port escapes from the port, the contact between the corner of the tip end portion of the vane and the edge of the opening of the port is surely made through the chamfered portion. Become.

  In the vane pump according to the present invention, as the drop prevention structure, the port prevents the vane from advancing / retreating at the front end of the vane and the advancing / retreating range at the rear end of the vane when passing through the opening of the port. It can be set as the structure which formed.

  With such a configuration, when the vane advances and retreats in the vane groove of the rotating rotor according to the shape of the inner circumferential cam surface of the cam ring, the vane front end and the vane rear end are applied to the ports formed in the side plate. No, the end of the vane is prevented from falling into the port.

  Further, the vane pump according to the present invention has a pressing unit that presses the vane against one of the pair of side plates as the sagging prevention structure, and the side plate in which the vane is pressed by the pressing unit, The port may be formed such that the vane does not overlap the forward / backward movement range of the vane tip and the forward / backward movement range of the vane rear end when passing through the opening of the port.

  With such a configuration, when the vane advances and retreats in the vane groove of the rotating rotor according to the shape of the inner peripheral cam surface of the cam ring, the vane is pressed against one side of the pair of side plates. . For this reason, the behavior that the vane tilts in the vane groove is suppressed, and as a result, even if the port is formed at any position of the side plate where the vane is not pressed, the tip of the vane is Never fall into the port. In addition, the front and rear ends of the vane do not hit the port formed on the side plate against which the vane is pressed, and the end of the vane may fall into the port formed on the side plate against which the vane is pressed. Is prevented.

  In addition, the vane pump according to the present invention has a pressing unit that presses the vane against one of the pair of side plates as the sagging prevention structure, and the port on the side plate on which the vane is pressed by the pressing unit. It can be set as the structure which does not form.

  With such a configuration, when the vane advances and retreats in the vane groove of the rotating rotor according to the shape of the inner peripheral cam surface of the cam ring, the side plate in which the port is not formed in the pair of side plates. It will be in the state pressed against. For this reason, the behavior that the vane tilts in the vane groove is suppressed, and as a result, even if the port is formed at any position of the side plate where the vane is not pressed, the tip of the vane is Never fall into the port. Further, the side plate against which the vane is pressed has no port itself into which the vane falls.

  Further, in the vane pump according to the present invention, as the pressing means, the inner peripheral cam surface of the cam ring is a tapered surface that widens from the side plate side where the vane is not pressed toward the side plate side where the vane is pressed, The tip of the vane may be configured to match the inner peripheral cam surface of the cam ring that becomes the tapered surface.

  With such a configuration, when the vane advances and retreats in the vane groove of the rotating rotor according to the shape of the inner peripheral cam surface of the cam ring, the reaction force is applied from the inner peripheral cam surface where the tip of the vane becomes a tapered surface. Receive. The reaction force includes a thrust component force that presses against the side where the tapered surface spreads, and the vane is pressed against one side plate by the thrust component force.

  In addition, the vane pump according to the present invention may include a vane movement restricting unit that restricts the vane from sliding on both of the pair of side plates as the drop prevention structure.

  With such a configuration, when the vane advances and retreats in the vane groove of the rotating rotor according to the shape of the inner peripheral cam surface of the cam ring, the vane does not slide in contact with any of the pair of side plates. For this reason, the behavior that the vane tilts in the vane groove is suppressed, and as a result, even if a port is formed at any position of the pair of side plates, the tip of the vane does not fall into the port. Absent.

  Further, the vane pump according to the present invention is configured such that, as the vane movement restricting means, the inner peripheral cam surface of the cam ring is formed as a concave surface, and the tip of the vane matches the inner peripheral cam surface of the cam ring as the concave surface. The configuration may be a shape.

  With such a configuration, when the vane advances and retreats in the vane groove of the rotating rotor according to the shape of the inner peripheral cam surface of the cam ring, the tip of the vane and the inner peripheral cam surface of the cam ring are respectively uneven. It will be in the engaged state. Thereby, the vane is regulated so as not to be in sliding contact with both of the pair of side plates.

  In addition, the vane pump according to the present invention can be configured to include a coupling unit that key-couples the vane and the rotor while ensuring advancement and retraction of the vane in the vane groove.

  With such a configuration, as described above, the vane and the rotor that are regulated so as not to be in sliding contact with both of the pair of side plates are key-coupled while ensuring that the vane moves forward and backward in the vane groove. . For this reason, the rotor that is key-coupled to the vane is also regulated so as not to be in sliding contact with both of the pair of side plates, so that wear and surface roughness due to sliding contact between the rotor and the side plates can be suppressed. Become.

  According to the vane pump of the present invention, the vane and the side plate may be worn or roughened when the vane advances and retreats in the vane groove according to the shape of the inner peripheral cam surface during rotation of the rotor. Since the predetermined behavior other than the forward / backward movement of the vane is suppressed, the reduction in volumetric efficiency and the reduction in mechanical efficiency due to the wear and surface roughness can be minimized.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  The basic structure of the vane pump according to the first embodiment of the present invention is as shown in FIG. 1A is a cross-sectional view cut along a plane perpendicular to the rotation axis of the rotor, and FIG. 1B is a cross-sectional view cut along a plane parallel to the rotation axis of the rotor.

  1A and 1B, this vane pump is provided with a pair of side plates (side plates) 40a and 40b at both open ends of a cam ring 20 having an elliptical cam surface 21 formed on the inner periphery. A rotor 30 that is rotatable about the shaft 50 is accommodated in a space defined by the cam ring 20 and the side plates 40a and 40b. A plurality of vane grooves 31 (1), 31 (2),..., 31 (8) are formed radially on the rotor 30 around the shaft 50, and the vane grooves 31 (1) to 31 ( The vanes 10 (1), 10 (2),..., 10 (8) are accommodated in 8) so that the tip can be advanced and retracted while contacting the cam surface 21 of the cam ring 20. Further, as shown in FIG. 1 (b), the side plates 40a and 40b are formed with ports 41a and 41b serving as an oil passage for sucking the oil, and an oil for discharging the oil. Ports 42a and 42b serving as passages are formed. The rotor 30 and the vanes 10 (3), 10 (7) (10 (1), 10 (2), 10 (4) to 10 (6), 10 (8)) are shown in FIG. As shown, the rotor 30 and the vanes 10 (3), 10 (7) (10 (1), 10 (2), 10 (4) to 10 (10) are brought to the side plate 40a side. 6) A clearance S is formed between 10 (8)) and the other side plate 40b.

  The basic operation of the vane pump having such a structure is as follows.

  The rotor 30 rotates in a state where the tips of the vanes 10 (1) to 10 (8) are pressed against the cam surface 21 of the cam ring 20 by the pressure of the oil liquid. When the rotor 30 rotates, the vanes 10 (1) to 10 (8) slide along the cam surface 21, thereby causing the vane grooves 31 (1) to 31 (31) to 31 according to the elliptical shape of the cam surface 21. (8) Move forward and backward within. As described above, during rotation of the rotor 30 (see the arrow line in FIG. 1A), the vanes 10 (1) to 10 (8) move back and forth to increase or decrease the volume between the vanes. When passing through the openings of the ports 41a and 41b, the oil is drawn between the vanes, and when the vane passes through the openings of the ports 42a and 42b on the discharge side, the oil between the vanes is sent to the outside.

  Further, the detailed positional relationship between the rotor 30, the cam ring 20, the vanes 10 (1) to 10 (8), and the ports 41a and 41b formed in the side plates 40a and 40b will be described with reference to FIGS. To do. 2 and 3, the vane is indicated by reference numeral 10 and the vane groove is indicated by reference numeral 31, respectively (hereinafter the same).

  In FIG. 2, the outer edge 41fe of the port 41a in the radial direction of the rotor 30 does not overlap the forward / backward movement range Δ1 of the tip of the vane 10 when the vane 10 passes through the opening of the port 41a, and the rotor 30 The port 41a is formed in the side plate 40a so that the inner edge 41te of the port 41a in the radial direction does not overlap the advance / retreat range Δ2 of the rear end of the vane 10 when the vane 10 passes through the opening of the port 41a. ing. That is, the port 41a is formed so as not to overlap both the advance / retreat range Δ1 at the tip of the vane 10 and the advance / retreat range Δ2 at the rear end of the vane 10.

  The port 41b is also formed in the side plate 40b with the same positional relationship as the positional relationship of the port 41a with respect to the vane 10 described above.

  Since the ports 41a and 41b are formed in the side plates 40a and 40b in such a positional relationship with respect to the vane 10, the vanes of the rotating rotor 30 are rotated as shown in FIG. When the vane 10 moves back and forth in the groove 31 according to the shape of the cam surface 21 of the cam ring 20, it may be slightly inclined with respect to the side plates 40a and 40b by the clearances Sa and Sb with the side plates 40a and 40b. However, the front end of the vane 10 and the rear end of the vane 10 do not cover the ports 41a and 41b. Therefore, the end of the vane 10 is prevented from falling into the ports 41a and 41b.

  Since the vane 10 is prevented from falling into the ports 41a and 41b as described above, the wear and surfaces of the vane 10 and the side plates 40a and 40b that may be generated when the vane 10 falls into the ports 41a and 41b are prevented. Roughness is avoided. For example, damage to the tip of the vane 10 that has fallen into the ports 41a and 41b and the edges of the openings of the ports 41a and 41b is prevented. Since the occurrence of such wear and surface roughness is avoided, the decrease in volumetric efficiency and mechanical efficiency of the vane pump can be minimized.

  As shown in FIG. 4 (indicated by arrows BB in FIG. 2), the outer diameter of the opening of the port 41a (same for the port 41b) in the radial direction of the rotor 30 is the same as the outer diameter of the port 41 in the conventional structure. By making the reduced amount α1 and the reduced amount α2 of the opening 41 of the port 41a with respect to the same inner diameter of the port 41 in the conventional structure substantially the same, the flow path area of the oil liquid in the port is substantially the same as that of the conventional structure. Can be kept in. Further, by chamfering the corner of the rotor 30 facing the port 41a to form the tapered surface 30a, it is possible to secure a larger fluid flow path area.

  Further, the ports 42a and 42b on the discharge side shown in FIG. 1B are also formed on the side plates 40a and 40b with the same positional relationship as the positional relationship of the ports 41a and 41b with respect to the vane 10 described above. .

  Next, a vane pump according to a second embodiment of the present invention will be described. The vane pump according to the second embodiment does not prevent the vane 10 from dropping into the ports 41a and 41b, but the predetermined behavior when the vane 10 that has dropped into the ports 41a and 41b escapes from the ports 41a and 41b. It is characterized by suppressing.

  The basic structure of the vane pump according to the second embodiment of the present invention is the same as that shown in FIG. However, the structure of the vane 10 and the positional relationship between the vane 10 and the ports 41a and 41b formed in the side plates 40a and 40b are as shown in FIGS. 6 is a cross-sectional view taken along the line CC in FIG.

  In FIG. 5, the forward / backward movement range Δ1 of the tip of the vane 10 when the vane 10 that moves forward / backward in the vane groove 31 of the rotating rotor 30 passes through the openings of the ports 41a, 41b. Ports 41a and 41b are formed in the side plates 40a and 40b so as to overlap (see FIG. 2). With such a positional relationship between the vane 10 and the ports 41a and 41b, when the vane 10 passes through the openings of the ports 41a and 41b, the tip portion of the vane 10 falls into one of the ports, for example, the port 41a. become.

  As shown in FIG. 6, the four corners of the tip portion of the vane 10 are chamfered to form convex curved surfaces 11a, 11b, 11c, and 11d. In addition, the edge that the vane 10 of the opening of the port 41a crosses is also chamfered to form tapered surfaces 411a and 411b, and the edge that the vane 10 of the opening of the port 41b crosses is also chamfered to form the tapered surface 411c, 411d is formed. Further, as shown in an enlarged view in FIG. 7, the width L1 of each chamfer (tapered surface 411a, 411b) at the edge of the opening of the port 41a is equal to or greater than the depression depth L0 of the vane 10 into the port 41a. Further, the width L2 of the chamfer (curved surface 11a, 11b) at the corner of the tip portion of the vane 10 is also greater than or equal to the sagging depth L0 of the vane 10 into the port 41a. Similarly, the width of the chamfer (tapered surfaces 411c and 411d) at the opening of the port 41b and the width of the chamfer (curved surfaces 11c and 11d) at other corners of the tip of the vane 10 are also the vane 41b of the vane 10. It is more than the depth of depression.

  In the vane pump having such a structure, the vane 10 moves with the rotation of the rotor 30 (see the arrow in FIG. 7), and when the tip portion of the vane 10 that has fallen into the port 41a in the process escapes from the port 41a, A curved surface 11a formed at a corner of the tip portion of the vane 10 contacts a tapered surface 411a formed at the edge of the opening of the port 41a. And the front-end | tip part of the vane 10 escapes from the port 41a, the curved surface 11a sliding on the taper surface 411a.

  Thus, when the vane 10 escapes from the port 41a, contact between the corner of the tip portion of the vane 10 and the edge of the opening of the port 41a is made by the curved surface 11a and the tapered surface 411a (chamfered portion). The behavior that the corner of the tip portion of the vane 10 is caught by the edge of the opening portion of the port 41a is suppressed, and the stress generated by the contact between the tip portion of the vane 10 and the edge of the opening portion of the port 41a is relieved. As a result, wear and surface roughness of the edge portion of the vane 10 and the opening of the port 41a are suppressed, and a decrease in volumetric efficiency and mechanical efficiency of the vane pump can be minimized.

  Note that the chamfering described above may be performed only on the tip portion of the vane 10 or only on the edge of the opening of the port 41a (41b). Further, the chamfered width (L1, L2 in FIG. 7) may be smaller than the depth of depression (L0 in FIG. 7) of the tip portion of the vane 10 into the port 41a (41b). However, from the viewpoint of suppressing the behavior that the corner of the tip of the vane 10 is caught on the edge of the opening of the port 41a as much as possible, as described above, the corner of the tip of the vane 10 and the opening of the port 41a (41b). It is preferable to chamfer both edges of the portion and make the chamfer width equal to or greater than the depth of depression of the tip portion of the vane 10 into the port 41a (41b).

  In addition, the discharge-side ports 42a and 42b shown in FIG. 1 are also configured similarly to the ports 41a and 41b described above.

  Next, a vane pump according to a third embodiment of the present invention will be described. In the vane pon according to the third embodiment, the inclination of the vane 10 is suppressed by pressing the vane 10 against the one side plate 40b, and as a result, the vane 10 is prevented from dropping into the port.

  The basic structure of the vane pump according to the third embodiment of the present invention is the same as that shown in FIG. However, the ports 41a and 41b and the cam ring 20 formed in the rotor 30, the vane 10, the side plates 40a and 40b are configured as shown in FIG.

  In FIG. 8, the cam surface 21a of the cam ring 20 is a tapered surface that spreads from one side plate 40a side to the other side plate 40b side. And the front-end | tip of the vane 10 becomes a shape which corresponds to the cam surface 21a of the cam ring 20 used as the said taper surface. Further, as in the first embodiment described above, the port 41b is formed on the side plate 40b so as not to overlap both the advance / retreat range of the vane 10 front end and the advance / retreat range of the vane 10 rear end. Has been. In the side plate 40a, the port 41a is formed so as to overlap the forward / backward movement range at the tip of the vane 10 as in the second embodiment.

  In the vane pump having such a structure, when the vane 10 moves back and forth in the vane groove 31 of the rotating rotor 30 according to the shape of the cam surface 21a of the cam ring 20, the cam surface 21a has a tapered surface at the tip of the vane 10. Receive reaction force from. This reaction force includes a thrust component force that presses against the side where the taper surface expands, that is, the side plate 40b, and the vane 10 is pressed against the side plate 40b by this thrust component force.

  When the vane 10 moves with the rotation of the rotor 30, the vane 10 is pressed against the side plate 40 b as described above, so that the behavior of the vane 10 tilting in the vane groove 31 is suppressed, and the tip portion of the vane 10 is suppressed. Does not fall into the port 41a formed in the side plate 40a. Further, the tip of the vane 10 does not hit the port 41b formed on the side plate 40b against which the vane 10 is pressed, as in the case of the first embodiment described above, and the vane 10 falls into the port 41b. There is nothing.

  As described above, the behavior of the vane 10 being pressed by the side plate 40b and being tilted in the vane groove 31 is suppressed, so that the contact state between the vane 10 and the side plate 40b becomes uniform, and the vane 10 and the side plate 40b. The generation of a large surface pressure on the contact surface with the surface is suppressed. Therefore, wear and surface roughness on the contact surface between the vane 10 and the side plate 40b are suppressed. Further, since the tip portion of the vane 10 does not fall into any of the ports 41a and 41b formed in the side plates 40a and 40b, the vane 10 and the side plate that can be generated when the vane 10 falls into the ports 41a and 41b. The occurrence of wear and surface roughness at 40a and 40b is also avoided. Thereby, the volumetric efficiency reduction and mechanical efficiency reduction of the vane pump can be minimized.

  The discharge-side port 42a shown in FIG. 1 is configured in the same manner as the above-described port 41a, and the discharge-side port 42b is configured in the same manner as the above-described port 41b.

  Next, a vane pump according to a fourth embodiment of the invention will be described.

  In the vane pump according to the fourth embodiment, the port 41b shown in FIG. 8 is not formed in the side plate 40b as shown in FIG. Other configurations are the same as those of the vane pump according to the third embodiment described above.

  In the vane pump having such a structure, as in the case of the vane pump according to the third embodiment described above, the behavior in which the vane 10 is pressed against the side plate 40b and the vane 10 tilts is suppressed. As a result, the generation of a large surface pressure on the contact surface between the vane 10 and the side plate 40b is suppressed, and the tip portion of the vane 10 is located at the ports 41a and 41b formed on the side plates 40a and 40b. Depressing is also prevented. Therefore, wear and surface roughness of the vane 10 and the side plates 40a and 40b are suppressed, and the decrease in volumetric efficiency and mechanical efficiency of the vane pump can be minimized.

  Next, a vane pump according to a fifth embodiment of the invention will be described. In the vane pump according to the fifth embodiment, by restricting the vane 10 from sliding to both the side plates 40a and 40b, the inclination of the vane 10 is suppressed, and as a result, the vane 10 is connected to the port of the vane 10. Prevents depression.

  The basic structure of the vane pump according to the fifth embodiment of the present invention is the same as that shown in FIG. However, the ports 41a and 41b and the cam ring 20 formed in the rotor 30, the vane 10, the side plates 40a and 40b are configured as shown in FIG.

  In FIG. 10, the cam surface 21b of the cam ring 20 is a wedge-shaped concave surface. And the front-end | tip of the vane 10 becomes a convex shape which corresponds to the cam surface 21b of the cam ring 20 used as the said wedge-shaped concave surface. Ports 41a and 41b are formed at predetermined positions of the side plates 40a and 40b. In order to facilitate the processing of the cam surface (concave surface) 21b, the cam ring 20 may be divided into two parts along the rotation axis (left-right direction in the figure).

  In the vane pump having such a structure, the vane is pressed in the radial direction of the rotor 30 by the pressing member 32 in the vane groove 31 of the rotor 30 (may be pressed by oil as in the case of the above-described embodiments). 10 and the cam surface 21b of the cam ring 20 are engaged with each other by a concavo-convex shape. In this state, the tip of the vane 10 slides on the cam surface 21b of the cam ring 20 as the rotor 30 rotates, and the vane 10 moves forward and backward in the vane groove 31 according to the shape of the cam surface 21b.

  As described above, since the tip of the vane 10 having the convex shape is engaged with the cam surface 21b of the cam ring 20 having the wedge shape (concave surface), the movement of the vane 10 in the axial direction of the rotor 30 is restricted. Is not in sliding contact with any of the side plates 40a, 40b. For this reason, the behavior that the vane 10 tilts in the vane groove 31 is suppressed, and the tip portion of the vane 10 does not fall into the ports 41a and 41b formed in the side plates 40a and 40b. Therefore, the occurrence of wear and surface roughness on the vane 10 and the side plates 40a and 40b, which may occur when the vane 10 falls into the ports 41a and 41b, is avoided. Further, since the vane 10 does not slidably contact both the side plates 40a and 40b, the occurrence of wear and surface roughness due to the slidable contact between the vane 10 and the side plates 40a and 40b is avoided. As a result, the volumetric efficiency and mechanical efficiency of the vane pump can be minimized.

  Next, the vane pump according to the sixth embodiment of the present invention has the structure shown in FIG. 11 in addition to the structure shown in FIG. 10 described above. 11 is a cross-sectional view taken along the line DD in FIG.

  In FIG. 11, key grooves 15, 16 extending in the radial direction of the rotor 30 are formed on the surface of the vane 10 facing the inner wall of the vane groove 31, and a key 33 protruding from the inner wall of the vane groove 31 in the key grooves 15, 16. , 34 (connecting means) are slidably fitted. As a result, as described above, the vane 10 that is regulated so as not to be in sliding contact with any of the side plates 40 a and 40 b is key-coupled to the rotor 30 while ensuring forward and backward movement in the vane groove 31.

  In the vane pump having such a structure, when the vane 10 moves back and forth in the vane groove 31 of the rotating rotor 30 according to the shape of the cam surface 21 of the cam ring 20, the vane 10 is moved to both the side plates 40a and 40b. Do not slide. Thus, the vane 10 and the rotor 30 that are regulated so as not to be in sliding contact with either of the side plates 40a and 40b are key-coupled while the advancement and retraction of the vane 10 in the vane groove 31 is ensured. 30 is also regulated so as not to slidably contact any of the side plates 40a, 40b. Therefore, it becomes possible to suppress wear and surface roughness due to sliding contact between the rotor 30 and the side plates 40a, 40b, and further reduce the volumetric efficiency and mechanical efficiency of the vane pump.

  As described above, the vane pump according to the present invention has an effect that the volumetric efficiency and mechanical efficiency can be reduced as much as possible due to wear and surface roughness of the vane and the side plate. It is useful as a vane pump used as a pressure source (for example, a fuel injection pump for a diesel engine).

It is sectional drawing which shows the basic structure of the vane pump which concerns on the 1st Embodiment of this invention. It is sectional drawing which shows the detailed structure of the rotor, vane, cam ring, and port in the vane pump which concerns on the 1st Embodiment of this invention. It is AA sectional drawing in FIG. It is sectional drawing which showed the position of the port (by BB arrow in FIG. 2) in the vane pump which concerns on the 1st Embodiment of this invention compared with the position of the port in the vane pump of a conventional structure. It is sectional drawing which shows the detailed structure of the rotor, vane, cam ring, and port in the vane pump which concerns on the 2nd Embodiment of this invention. It is CC sectional drawing in FIG. It is sectional drawing which expands and shows the vane front-end | tip part which fell in the port. It is sectional drawing which shows the detailed structure of the rotor, vane, cam ring, and port in the vane pump which concerns on the 3rd Embodiment of this invention. It is sectional drawing which shows the detailed structure of the rotor, vane, cam ring, and port in the vane pump which concerns on the 4th Embodiment of this invention. It is sectional drawing which shows the detailed structure of the rotor, vane, cam ring, and port in the vane pump which concerns on the 5th Embodiment of this invention. It is sectional drawing which shows the detailed structure of the rotor, vane, cam ring, and port in the vane pump which concerns on the 6th Embodiment of this invention.

Explanation of symbols

10, 10 (1) to 10 (8) Vane 11a, 11b, 11c, 11d Curved surface 15, 16 Keyway 20 Cam ring 21 Cam surface 21a Tapered surface (cam surface)
21b Concave surface (cam surface)
30 Rotor 31, 31 (1) to 31 (8) Vane groove 33, 34 Key 40a, 40b Side plate (side plate)
41a, 41b port (intake side)
42a, 42b Port (discharge side)
50 Shaft 411a, 411b, 411c, 411d Tapered surface

Claims (11)

A cam ring, a pair of side plates provided at both open ends of the cam ring, a rotor rotatably accommodated in a space defined by the cam ring and the pair of side plates, and a radial shape formed on the rotor Each of the plurality of vane grooves has a vane that is accommodated so as to be able to advance and retreat while abutting against the inner circumferential cam surface of the cam ring, and is a port that serves as an oil liquid passage formed in at least one of the pair of side plates In the vane pump through which the vane moving with the rotation of the rotor passes,
A vane pump comprising vane behavior suppressing means for suppressing a predetermined behavior other than forward and backward movement of the vane in the vane groove. 2. The vane pump according to claim 1, wherein the vane behavior suppressing means has a drop prevention structure for preventing the tip of the vane from dropping into a port formed in the side plate. As the vane behavior suppressing means, at least one of the corner of the tip portion of the vane that contacts the edge of the opening and the edge of the opening when the vane passes through the opening of the port is chamfered. The vane pump according to claim 1. 4. The vane pump according to claim 3, wherein the corner of the vane tip portion and the chamfering width of the edge of the opening are equal to or greater than a depth of the vane into the port. The port is formed so as not to overlap the forward / backward movement range of the vane tip and the backward / backward movement range of the vane rear end when the vane passes through the opening of the port as the sagging prevention structure. Item 2. A vane pump according to item 2. As the sagging prevention structure, while having a pressing means for pressing the vane to one of the pair of side plates,
In the side plate in which the vane is pressed by the pressing means, the port is set so as not to overlap with the advance / retreat range of the vane tip and the advance / retreat range of the vane rear end when the vane passes through the opening of the port. The vane pump according to claim 2, wherein the vane pump is formed. As the sagging prevention structure, while having a pressing means for pressing the vane to one of the pair of side plates,
The vane pump according to claim 2, wherein the port is not formed in a side plate on which the vane is pressed by the pressing means. As the pressing means, the inner circumferential cam surface of the cam ring is a tapered surface that spreads from the side plate side where the vane is not pressed toward the side plate side where the vane is pressed,
The vane pump according to claim 6 or 7, wherein a tip of the vane has a shape that matches an inner peripheral cam surface of the cam ring serving as the tapered surface. The vane pump according to claim 2, further comprising vane movement restricting means for restricting the vane from slidingly contacting both of the pair of side plates as the sagging prevention structure. As the vane movement restricting means, the inner circumferential cam surface of the cam ring is formed as a concave surface,
The vane pump according to claim 9, wherein a tip of the vane has a convex shape that matches an inner peripheral cam surface of the cam ring that is the concave surface. 11. The vane pump according to claim 9, further comprising connecting means for key-connecting the vane and the rotor while ensuring advancement and retraction of the vane in the vane groove.

Images