JP2008240652A - Vane pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent abrasion of a vane, and to thin a casing, by efficiently sucking a working fluid by securing the contact area with an inner peripheral surface of a pump room of the vane. <P>SOLUTION: A suction port 20 communicating with an operation chamber 5 of a volume expanding process and a delivery port 21 communicating with the operation chamber 5 of a volume reducing process, are formed on the inner peripheral surface 2a of the pump room 2. The suction port 20 is arranged in a position dislocated from the respective vanes 4 in the thrust direction of a rotor 3. A suction passage 6 communicating with the suction port 20 and a delivery passage 7 communicating with the delivery port 21, are formed in the casing 10. The suction passage 6 and the delivery passage 7 are formed in a position overlapping with the pump room 2 when viewed from the radial direction of the rotor 3. A dimension in the thrust direction of the rotor 3 of the suction port 20, is set shorter than a diameter of an inlet part of the suction passage 6. A dimension in the direction along the inner peripheral surface 2a of the pump room 2 of the suction port 20, is set longer than the diameter of the inlet part of the suction passage 6. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a vane pump.

  The conventional vane pump 1 houses the rotor 3 in an eccentric position of the pump chamber 2 formed in the casing 10 as shown in FIG. 8, and forms a plurality of vane grooves 19 extending radially in the rotor 3, and the tip of each vane groove 19 has a tip. A vane 4 slidably in contact with the inner peripheral surface 2 a of the pump chamber 2 is provided to be slidable in the radial direction of the rotor 3. Further, a suction port 20 and a discharge port 21 are provided on the inner peripheral surface of the pump chamber 2, and a suction path 6 and a discharge path 7 communicating with the suction port 20 and the discharge port 21 are formed in the casing 10. The inlet part of the suction path 6 and the outlet part of the discharge path 7 are constituted by a connecting pipe part protruding from the outer surface of the casing 10 so that a pipe such as a hose (not shown) can be connected. In the figure, reference numeral 26 denotes a spring material provided in the vane groove 19.

  When the rotor 3 is rotationally driven, each vane 4 slides outward in the radial direction of the rotor 3 due to the centrifugal force of the rotor 3, and the tip of each vane 4 is in sliding contact with the inner peripheral surface 2 a of the pump chamber 2. As a result, the volume of the working chamber 5 surrounded by the inner surface of the pump chamber 2, the outer peripheral surface of the rotor 3, and the vane 4 changes in size, and the working fluid is sucked from the suction port 20 through the working chamber 5 and the discharge port. The working fluid is discharged from 21.

  By the way, the suction port 20 and the discharge port 21 are preferably formed at positions displaced from the vane 4 in the thrust direction of the rotor 3 on the inner peripheral surface 2 a of the pump chamber 2. The reason for this is that when the vane 4 is in a position corresponding to the suction port 20 and the discharge port 21 in the circumferential direction of the pump chamber 2, the contact area of the vane 4 with respect to the inner peripheral surface 2a of the pump chamber 2 is secured. This is because the suction and discharge can be efficiently performed, and the inner peripheral surface 2a on which the vane 4 slides can be smoothly formed without the suction port 20 and the discharge port 21, thereby preventing the vane 4 from being worn.

  Further, the suction path 6 and the discharge path 7 need to have a constant cross-sectional area over the entire length in the flow direction including the suction port 20 and the discharge port 21 in order to reduce flow path resistance. The cross-sectional area was made constant by having the same cross-sectional shape over the entire length in the direction. The cross-sectional shapes of the suction path 6 including the suction port 20 and the discharge path 7 including the discharge port 21 are determined by the cross-sections of the inlet portion and the outlet portion to which the pipe is connected.

Here, when the suction path 6 and the suction port 20 are formed at positions overlapping each other when viewed from the radial direction of the rotor 3 (that is, the same position as the pump chamber 2 in the thrust direction), there is no problem in reducing the thickness of the casing 10. As described above, when the suction port 20 is arranged at a position shifted from the vane 4 in the thrust direction of the rotor 3, the casing 10 becomes thicker by the dimension of the suction port 20, particularly reducing the flow path resistance. Therefore, when the suction port 20 is formed in the same cross-sectional shape as the inlet portion of the suction path 6, the casing 10 becomes thicker by the diameter of the inlet portion of the suction path 6, which hinders the thickness reduction of the casing 10. .
Japanese Utility Model Publication No.59-154881

  The present invention has been invented in view of the above-described conventional problems, and the suction port is disposed on the inner peripheral surface of the pump chamber at a position shifted from the vane in the thrust direction of the rotor, so that the inner periphery of the pump chamber of the vane is provided. Provided is a vane pump capable of ensuring a contact area with a surface and efficiently sucking a working fluid, preventing wear of vanes, and having a thin casing.

  In order to solve the above problems, a vane pump according to the present invention includes a pump chamber 2 formed in a casing 10, a rotor 3 housed in the pump chamber 2, a plurality of circumferentially arranged rotors 3, and a tip of the pump chamber 2. And a working chamber 5 surrounded by the inner surface of the pump chamber 2, the inner surface of the pump chamber 2, the outer peripheral surface of the rotor 3, and the vane 4, the volume of which is changed by the rotational driving of the rotor 3. A suction port 20 communicating with the working chamber 5 in the volume expansion process and a discharge port 21 communicating with the working chamber 5 in the volume reduction process are formed on the inner peripheral surface 2 a of the chamber 2, and the suction port 20 is arranged in the thrust direction of the rotor 3. Disposed at a position shifted from each vane 4, a suction path 6 communicating with the suction port 20 and a discharge path 7 communicating with the discharge port 21 are formed in the casing 10, and the suction path 6 and the discharge path 7 are connected to the rotor. The suction chamber 20 is formed in a position overlapping the pump chamber 2 as viewed from the radial direction of the suction chamber 20, and the size of the suction port 20 in the thrust direction of the rotor 3 is made shorter than the diameter of the inlet portion of the suction passage 6. The dimension in the direction along the inner peripheral surface 2a is longer than the diameter of the inlet portion of the suction path 6. Thus, by disposing the suction port 20 at a position shifted from each vane 4 in the thrust direction of the rotor 3, when the vane 4 is at a position corresponding to the suction port 20 in the circumferential direction of the pump chamber 2, the vane 4. The contact area with respect to the inner peripheral surface 2a of the pump chamber 2 can be secured, the working fluid can be sucked efficiently, and the vane 4 can be prevented from being worn. Further, the suction path 6 and the discharge path 7 are formed at positions overlapping the pump chamber 2 when viewed from the radial direction of the rotor 3, and the dimension of the suction port 20 in the thrust direction of the rotor 3 is larger than the diameter of the inlet portion of the suction path 6. The thickness of the casing 10 (in the thrust direction of the rotor 3) is reduced by shortening the length of the suction chamber 20 in the direction along the inner peripheral surface 2a of the pump chamber 2 from the diameter of the inlet portion of the suction passage 6. Dimension) can be shortened, and a sufficient cross-sectional area of the suction port 20 can be secured.

  When the front end of the working chamber 5 in the rotation direction of the rotor 3 is in communication with the discharge port 21, the region of the pump chamber 2 in which the working chamber 5 is formed is a pressurizing region, and the suction port It is preferable to form 20 up to just before the pressure region in the rotation direction of the rotor 3. By forming the suction port 20 just before the pressurization region in the rotation direction of the rotor 3, the dimension of the suction port 20 in the direction along the inner peripheral surface 2a can be increased in the pump chamber 2, and the cross-sectional area of the suction port 20 can be increased. The thickness dimension of the casing 10 can be further shortened while ensuring sufficiently.

  The downstream end of the suction path 6 includes an inner surface 40 that faces the suction port 20, and the distance between the inner surface 40 and the suction port 20 gradually increases toward the front side in the rotation direction of the rotor 3. It is preferable to shorten it. The working fluid can be guided to the suction port 20 side by the inner side surface 40.

  The downstream end portion of the suction path 6 includes an inner surface 40 that faces the suction port 20, and the bottom surface of the downstream end portion of the suction path 6 is inclined so that the bottom becomes deeper toward the suction port 20 side. 41 is also preferable. The inclined surface 41 can guide the working fluid to the suction port 20 side.

  In the invention according to claim 1, by arranging the suction port at a position shifted from each vane in the thrust direction of the rotor, an effect that the working fluid can be sucked efficiently can be obtained, and the casing can be thinned, and Sufficient cross-sectional area of the suction port can be secured to reduce the flow resistance at the suction port, whereby the working fluid flowing through the suction path can be smoothly introduced into the pump chamber.

  Further, in the invention according to claim 2, in addition to the effect of the invention according to claim 1, the pump chamber of the suction port can be lengthened in the direction along the inner peripheral surface, and the cross-sectional area of the suction port can be sufficiently secured. However, the casing can be made thinner.

  Further, in the invention according to claim 3, in addition to the effect of the invention according to claim 1 or 2, the working fluid can be guided to the suction port side by the inner surface of the downstream end portion of the suction path, so that smoother. The working fluid can be introduced into the pump chamber.

  In the invention according to claim 4, in addition to the effect of the invention according to any one of claims 1 to 3, the working fluid can be guided to the suction port side by the bottom surface of the downstream end portion of the suction path. The working fluid can be introduced into the pump chamber more smoothly.

  Hereinafter, the present invention will be described based on embodiments shown in the accompanying drawings. A vane pump 1 according to an example of the present embodiment shown in FIGS. 1 to 7 stores a rotor 3 eccentrically in a pump chamber 2 formed in a casing 10, and a tip is slidably contacted with an inner peripheral surface 2 a of the pump chamber 2. A plurality of vanes 4 are provided on the rotor 3, and the volume of the working chamber 5 surrounded by the inner surface of the pump chamber 2, the outer peripheral surface of the rotor 3, and the vanes 4 is changed in size by rotating the rotor 3 by the stator 23. Thus, the working fluid from the suction port 20 is discharged from the discharge port 21 through the working chamber 5. In the following description, it is assumed that one side in the thrust direction of the rotor 3 (the axial direction of the rotor 3) is the upper side and the other side is the lower side.

  As shown in FIG. 3, the casing 10 that accommodates the rotor 3 has a substantially rectangular shape in plan view, and is formed by combining an upper case 11 positioned above and a lower case 12 positioned below. In the figure, reference numeral 14 denotes a fastener hole for fastening the upper case 11 and the lower case 12 together.

  The upper case 11 is formed with an upper recess 15 that is recessed upward from the mating surface with the lower case 12, and the upper case 11 is recessed downward from the mating surface with the upper case 11. A lower recess 16 communicating with 15 is formed. A fitting portion 24 projects from the central portion of the bottom surface of the upper recess 15, and notches 24 a are formed at two locations 180 degrees apart in the circumferential direction of the outer peripheral portion of the fitting portion 24. An annular ring member 17 is fitted into the upper recess 15, and the fitting portion 24 is fitted into the upper end portion of the central hole 17 a of the ring member 17. Thus, the pump chamber 2 which accommodates the rotor 3 is formed by combining the upper recess 15 and the lower recess 16 into which the ring material 17 is inserted, that is, the pump chamber 2 includes the lower surface of the fitting portion 24. The bottom surface of the upper recess 15, the inner peripheral surface of the ring material 17, and the inner surface of the lower recess 16 are configured.

  The rotor 3 is formed in a circular shape in plan view, and is composed of an upper rotor body 8 and a magnet portion 22 (see FIG. 7) composed of a lower permanent magnet. As shown in FIG. 1, the rotor 3 has an outer peripheral surface 8 a of the rotor main body 8 that faces the inner peripheral surface 2 a of the pump chamber 2 (the inner peripheral surface of the ring member 17), and serves as one thrust surface of the rotor main body 8. The upper surface is accommodated in the pump chamber 2 so as to face the inner bottom surface of the pump chamber 2 (that is, the bottom surface of the upper recess 15 including the fitting portion 24).

  A plurality of vane grooves 19 extending radially in the circumferential direction (four in this example) are radially formed on the upper surface of the rotor body 8 having a circular shape in plan view at equal intervals in the circumferential direction. It opens from the outer peripheral surface 8 a of the main body 8. In each vane groove 19, a rectangular parallelepiped vane 4 is accommodated so as to be slidable in the radial direction of the rotor 3, so that the front portion of each vane 4 can be moved in and out of the outer peripheral surface 8 a of the rotor body 8. . The top surface of each vane 4 faces the bottom surface of the upper recess 15.

  A large number of teeth 25 projecting outward in the radial direction of the rotor 3 are juxtaposed in the circumferential direction on the outer peripheral surface of the rotor body 8, and these teeth 25 serve to increase the pressure in the working chamber during discharge. Further, a flange portion 27 is provided at the lower end portion of the rotor body 8 so as to protrude outward in the radial direction of the rotor 3 from the tooth portion 25. The outer peripheral portion of the flange portion 27 is as shown in FIG. It protrudes outward from the inner peripheral surface of the ring member 17 and faces the lower surface of the ring member 17. The magnet portion 22 is housed in the lower recess 16. A shaft 32 protrudes upward from the bottom surface of the lower recess 16, and the shaft 32 is inserted into the center of the rotor 3 to rotatably support the rotor 3.

  A suction port 20 for drawing the working fluid into the working chamber 5 and a discharge port 21 for discharging the working fluid from the working chamber 5 are formed at the upper end of the inner circumferential surface 2 a of the pump chamber 2 constituted by the inner circumferential surface of the ring material 17. is doing. The suction port 20 and the discharge port 21 are formed at positions facing each other on the inner peripheral surface 2 a of the pump chamber 2, and communicate with each notch 24 a formed in the fitting portion 24. The suction port 20 and the discharge port 21 are located at the same level and are located above the vanes 4 provided in the rotor 3. As a result, when the vane 4 is in a position corresponding to the suction port 20 and the discharge port 21 in the circumferential direction of the pump chamber 2, the contact area of the vane 4 with respect to the inner peripheral surface 2a of the pump chamber 2 is ensured and the working fluid is efficiently used. Suction / discharge can be performed well and wear of the vanes 4 can be prevented. Further, a suction path 6 and a discharge path 7 communicating with the suction port 20 and the discharge port 21 are formed in the casing 10.

  As shown in FIG. 2, a stator housing recess 34 is formed on the lower surface of the lower case 12, and the stator 23 is disposed in the stator housing recess 34. Then, by rotating the magnet portion 22 through the casing 10 by the electromagnetic force of the stator 23 arranged outside the pump chamber 2, the rotor 3 in the pump chamber 2 is moved to the arrow a in FIG. It can be rotated in the direction shown.

  When the rotor 3 is rotationally driven by the stator 23, each vane 4 receives an action of centrifugal force due to the rotation of the rotor 3 and projects outward from the outer peripheral surface 8 a of the rotor body 8, and its tip is pumped The inner surface 2 a of the chamber 2 is slidably contacted. At this time, the pump chamber 2 is formed with a plurality of working chambers 5 surrounded by the inner surface (the inner peripheral surface 2a and the inner bottom surface) of the pump chamber 2, the outer peripheral surface 8a of the rotor body 8, the flange portion 27, and the vane 4. The Since the rotor main body 8 is in an eccentric position of the pump chamber 2 formed inside the ring material 17, the inner peripheral surface 2 a of the pump chamber 2 (the inner peripheral surface of the ring material 17) and the outer peripheral surface 8 a of the rotor main body 8. The distance varies depending on the rotational position of the rotor 3 and the amount of protrusion of the vane 4 from the rotor 3 also varies depending on the rotational position of the rotor 3. By rotating the rotor 3, each working chamber 5 rotates in the rotational direction of the rotor 3. The volume is changed to large or small while moving to. That is, the volume of each working chamber 5 increases with the rotation of the rotor 3 when it is in a position communicating with the suction port 20, and the volume decreases with the rotation of the rotor 3 when it is in a position communicating with the discharge port 21. Is done. Accordingly, when the rotor 3 is driven to rotate, the working fluid flows into the working chamber 5 communicating with the working fluid from the suction port 20 via the suction path 6, and is compressed from the discharge port 21 after being compressed in the working chamber 5. It is discharged through the discharge path 7 and functions as a pump.

  Hereinafter, the suction port 20 and the discharge port 21, and the suction path 6 and the discharge path 7 communicating with the suction port 20 and the discharge port 21 will be described in detail.

  The suction port 20 is formed along an inner peripheral edge portion of the upper surface of the ring member 17 and has an arc-shaped recess 26 opened from the inner peripheral surface of the ring member 17, and an upper recess 15 blocking the upper portion of the arc-shaped recess 26. It consists of a bottom. The suction port 20 is formed in a range of about ¼ of the circumferential direction of the ring member 17 and has an arc shape in plan view, and is formed in a horizontally long rectangular shape when viewed from the pump chamber 2 side. The discharge port 21 includes an opening edge portion on the pump chamber 2 side of the discharge-side flow channel 28 formed on the upper surface of the ring material 17 and a bottom surface of the upper recess 15 that closes the upper portion of the discharge port 21. The discharge port 21 is formed in a range of about ¼ of the circumferential direction of the ring member 17 and has an arc shape in plan view, and is formed in a horizontally long rectangular shape when viewed from the pump chamber 2 side. The width direction dimension of the suction port 20 and the discharge port 21 along the inner peripheral surface of the ring member 17 is shorter than the distance between the tips of the vanes 4 in the direction along the inner peripheral surface of the ring member 17. .

  The suction path 6 and the discharge path 7 extend horizontally from the same side surface of the upper case 11 located closer to the discharge port 21 than the suction port 20 toward the rotor 3, and communicate with the suction port 20 and the discharge port 21. ing. Both the suction path 6 and the discharge path 7 are formed at positions overlapping the pump chamber 2 when viewed from the radial direction of the rotor 3.

  The suction path 6 includes a suction side upstream portion 6a and a suction side downstream portion 6b. The upstream suction side upstream portion 6 a is a hole formed in the upper case 11, and extends from the outer surface of the upper case 11 to the inner peripheral surface of the upper recess 15. The downstream suction side downstream portion 6 b closes the suction side flow channel 29 formed on the upper surface of the ring material 17 from the outer peripheral surface to the inner peripheral surface and the upper opening of the suction side flow channel 29. It consists of the bottom surface of the upper recess 15. An inlet portion which is an upstream end portion of the suction path 6 is configured by a circular inner surface of the suction side connection pipe portion 35 protruding from the outer surface of the upper case 11, and the suction side connection pipe portion 35 includes a hose or the like. The pipe on the suction side is connected.

  As shown in FIG. 3B, the suction port 20 is located at the same level as the upper end portion of the suction side upstream portion 6a. The cross-sectional shape of the suction port 20 is different from the cross-sectional shape of the inlet portion of the suction path 6. Specifically, the cross-section of the suction port 20 is such that the vertical dimension in the thrust direction of the rotor 3 (the dimension indicated by e in FIG. 3B) is the diameter of the inlet portion of the suction path 6 (the dimension indicated by f in FIG. 1). The pump chamber 2 has a rectangular shape in which the dimension in the width direction in the direction along the inner peripheral surface 2a (the dimension indicated by d in FIG. 1) is longer than the diameter of the inlet portion of the suction path 6. Note that the dimension of the suction port 20 in the illustrated example in the width direction indicated by d in FIG. 1 is longer than π × r, where r is the radius of the inlet portion of the suction path 6.

  Since the vertical dimension of the suction port 20 is made shorter than the diameter of the inlet portion of the suction path 6 in this way, the vertical dimension of the casing 10 is reduced despite the formation of the suction port 20 on the inner peripheral surface of the pump chamber 2. Can be suppressed. In addition, since the dimension in the width direction of the suction port 20 is longer than the diameter of the inlet portion of the suction path 6, the cross-sectional area of the suction port 20 can be made substantially the same as the inlet portion of the suction path 6. Accordingly, the flow resistance at 20 can be reduced, and the working fluid flowing through the suction path 6 can be smoothly introduced into the pump chamber 2 via the suction port 20.

  When the front end of the working chamber 5 in the rotational direction of the rotor 3 is in communication with the discharge port 21, the region of the pump chamber 2 in which the working chamber 5 is formed (that is, the range indicated by the arrow b in FIG. 1). The region where the working fluid in the working chamber 5 is pressurized) is defined as the pressurized region, and the suction port 20 is formed up to just before the pressurized region in the rotation direction of the rotor 3. The suction port 20 is a decompression region, that is, a region of the pump chamber 2 in which the working chamber 5 is formed when the rear end of the working chamber 5 in the rotation direction of the rotor 3 is in communication with the suction port 20. It is formed immediately after. Thus, by forming the suction port 20 just before the pressure region in the rotation direction of the rotor 3, the dimension of the suction port 20 in the direction along the inner peripheral surface 2 a can be increased in the pump chamber 2. The thickness dimension of the casing 10 can be further shortened while ensuring a sufficient cross-sectional area.

  The suction-side downstream portion 6b includes an upstream-side linear flow path portion 37 formed in a straight line shape in plan view and a downstream-side formed in an arc shape in plan view along the suction port 20 in the same manner as the suction-side upstream portion 6a. The arc-shaped channel portion 38 communicates with the upper end portion thereof facing the suction port 20. As shown in FIG. 3, the front end (that is, the downstream end) in the rotation direction of the rotor 3 on the bottom surface of the arc-shaped channel portion 38 is located at the same level as the bottom surface of the suction port 20. The bottom surface of the suction side downstream portion 6b has an upward slope 30 that gradually slopes upward toward the downstream side, and the downstream end portion of the arcuate flow path portion 38 via the upward slope 30 formed in the suction path 6 The bottom surface of the suction-side upstream portion 6a located below is smoothly continuous.

  As shown in FIG. 1, the arc-shaped flow path portion 38 that constitutes the downstream end portion of the suction path 6 includes an inner side surface 40 that faces the suction port 20, and the inner side surface 40 includes the inner side surface 40 and the suction port 20. Is inclined such that the distance (the dimension indicated by g in FIG. 1) gradually decreases toward the front side in the rotation direction of the rotor 3. Further, the bottom surface of the suction side downstream portion 6b constituted by the upward slope 30 gradually becomes deeper as it goes from the inner surface 40 side to the suction port 20 side as shown in FIGS. 7 (a) and 7 (b). It becomes an inclined surface. As a result, the working fluid flowing through the arc-shaped channel portion 38 can be guided to the suction port 20 side at the bottom surface formed by the inner side surface 40 and the inclined surface 41 of the arc-shaped channel portion 38, and in addition, the arc-shaped flow of the suction-side downstream portion 6b The working fluid can be introduced into the pump chamber 2 more smoothly at the bottom surface formed by the inclined surface 41 at the upstream side of the passage portion 38.

  On the other hand, the discharge path 7 includes a discharge side upstream portion 7a and a discharge side downstream portion 7b. The upstream discharge side upstream portion 7a includes the discharge side flow channel 28 extending from the inner peripheral surface of the ring member 17 to the outer peripheral surface, and the bottom surface of the upper recess 15 that closes the upper opening of the discharge side flow channel 28. Consists of. The downstream discharge side downstream portion 7 b is formed by a hole formed in the upper case 11. The outlet portion serving as the downstream end portion of the discharge path 7 is constituted by an inner surface having a circular cross section of the discharge side connection pipe portion 36 protruding from the outer surface on which the suction side connection pipe portion 35 of the upper case 11 is formed. A discharge side pipe such as a hose is connected to the connection pipe portion 36. The cross-sectional area of the outlet portion of the discharge path 7 is smaller than the cross-sectional area of the inlet portion of the suction path 6, but the center of the outlet portion of the discharge path 7 and the inlet portion of the suction path 6 in the thrust direction of the rotor 3. The position is in the same position and not shifted. Further, both the suction-side connecting pipe part 35 and the discharge-side connecting pipe part 36 project vertically from the same outer surface located outside the rotor 3 of the upper case 11 in the radial direction.

  As shown in FIG. 2, the discharge port 21 is located at the same level as the upper end portion of the discharge-side downstream portion 7b. The cross-sectional shape of the discharge port 21 is different from the cross-sectional shape of the outlet portion of the discharge path 7. Specifically, the cross section of the discharge port 21 is such that the dimension in the thrust direction of the rotor 3 (height dimension indicated by h in FIG. 2) is larger than the diameter of the outlet portion of the discharge path 7 (dimension indicated by i in FIG. 2). The pump chamber 2 has a rectangular shape in which the dimension in the direction along the inner peripheral surface 2 a (width dimension indicated by j in FIG. 1) is longer than the diameter of the outlet portion of the discharge path 7. The width dimension indicated by j in FIG. 1 of the discharge port 21 in the illustrated example is longer than π × r, where r is the radius of the outlet portion of the discharge path 7.

  Thus, in this example, since the vertical dimension of the discharge port 21 is made shorter than the diameter of the outlet part of the discharge path 7, the discharge port 21 is formed on the inner peripheral surface of the pump chamber 2, but the casing 10 The vertical dimension can be suppressed. In addition, since the dimension in the width direction of the discharge port 21 is longer than the diameter of the outlet portion of the discharge path 7, the cross-sectional area of the discharge port 21 can be made the same as the outlet portion of the discharge path 7. Thus, the working fluid in the pump chamber 2 can be smoothly led out through the discharge port 21.

  As shown in FIG. 2, the bottom surface of the discharge-side upstream portion 7 a has a downward slope 42 that gradually slopes downward toward the downstream side, and the bottom surface of the discharge port 21 through the downward slope 42 formed in the discharge path 7. And the bottom surface of the discharge-side upstream portion 7a located below is smoothly continuous. Further, as shown in FIGS. 6A and 6B, the flow path constituted by the discharge port 21 and the discharge-side upstream portion 7a has a dimension in the width direction as seen from the thrust direction of the rotor 3 (in the figure, k). The dimension shown in the drawing is gradually shortened toward the downstream side, whereby the cross-sectional area of the flow path constituted by the discharge port 21 and the discharge side upstream portion 7a is made constant over the entire length in the flow direction of the working fluid; The cross-sectional area of the outlet portion of the discharge path 7 is the same. That is, the cross-sectional area of the flow path including the discharge path 7 and the discharge port 21 is constant over the entire length in the flow direction of the working fluid. Therefore, the working fluid in the pump chamber 2 can be derived more smoothly.

  Furthermore, the discharge-side upstream portion 7a constituting the upstream side of the discharge path 7 includes an inner side surface 43 that faces the discharge port 21. The inner side surface 43 is a distance between the inner side surface 43 and the discharge port 21 ( 1 is inclined so as to gradually become shorter toward the front side in the rotation direction of the rotor 3. Further, the inner side surface 43 is located on a tangent line of the inner peripheral surface of the ring member 17 passing through the rear end in the rotation direction of the rotor 3 of the discharge port 21 in plan view, and is smoothly continuous with the inner peripheral surface of the ring member 17. Yes. As a result, the working fluid flowing into the discharge path 7 can be led out from the pump chamber 2 more smoothly.

  The working fluid of the vane pump 1 in each of the above examples is a liquid such as water, alcohol, or antifreeze, but may be other liquids.

It is an example of an embodiment of the invention and is a horizontal sectional view of a vane pump. FIG. 2 is a side view partially cut away at A-A in FIG. 1. (A) is the partially broken perspective view of a vane pump, (b) is a side view of the vane pump partially broken like (a). It is a perspective view of the upper case and ring material of a vane pump same as the above. It is the perspective view seen from the lower side of the upper case same as the above. (A) is DD sectional drawing of FIG. 1, (b) is CC sectional drawing of FIG. 1, (c) is BB sectional drawing of FIG. (A) is FF sectional drawing of FIG. 1, (b) is EE sectional drawing of FIG. It is sectional drawing of the conventional vane pump.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Vane pump 2 Pump chamber 2a Inner peripheral surface 3 Rotor 4 Vane 5 Actuation chamber 6 Suction path 7 Discharge path 10 Casing 20 Suction port 21 Discharge port

Claims (4)

  A pump chamber formed in the casing, a rotor housed in the pump chamber, a plurality of vanes provided in the circumferential direction of the rotor and having tips slidably contacting the inner peripheral surface of the pump chamber, an inner surface of the pump chamber, and an outer peripheral surface of the rotor A working chamber that is surrounded by a vane and that changes its volume by rotational driving of the rotor is provided, and is connected to an inner peripheral surface of the pump chamber to a working chamber in the volume expansion process and to a working chamber in the volume reduction process. In addition to forming the discharge port, the suction port is disposed at a position shifted from each vane in the thrust direction of the rotor, and forms a suction path that communicates with the suction port and a discharge path that communicates with the discharge port in the casing. The passage and the discharge passage are formed at a position overlapping the pump chamber when viewed from the radial direction of the rotor, and the dimension of the suction port in the thrust direction of the rotor is shorter than the diameter of the inlet portion of the suction passage. Vane pump, characterized by comprising a dimension along the inner peripheral surface of Rutotomoni suction inlet of the pump chamber is made longer than the diameter of the inlet portion of the suction passage.   When the front end of the working chamber in the rotational direction of the rotor is in communication with the discharge port, the region of the pump chamber in which the working chamber is formed is a pressurizing region, and the suction port is added in the rotational direction of the rotor. The vane pump according to claim 1, wherein the vane pump is formed up to just before the pressure region.   The downstream end portion of the suction path has an inner surface facing the suction port, and the distance between the inner surface and the suction port is gradually shortened toward the front side in the rotation direction of the rotor, The vane pump according to claim 1 or 2.   The downstream end portion of the suction path has an inner surface facing the suction port, and the bottom surface of the downstream end portion of the suction path is formed as an inclined surface that becomes deeper toward the suction port side. The vane pump according to any one of claims 1 to 3.

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