JP6609163B2 - Vane pump - Google Patents

Description

  The present invention relates to a vane pump.

  Patent Document 1 discloses a vane pump including a rotor that is rotationally driven, a plurality of vanes provided in the rotor, and a cam ring that houses the rotor. The vane reciprocates with the rotation of the rotor, and the tip of the vane is in sliding contact with the inner peripheral cam surface of the cam ring. A pump cover is disposed on one side of the rotor and cam ring, and a side plate is disposed on the other side. A pump chamber partitioned by a plurality of vanes is defined between the rotor and the cam ring by the pump cover and the side plate. A suction port is formed in the pump cover and the side plate, and working fluid is sucked into the pump chamber from the suction passage through the suction port.

  The vane pump disclosed in Patent Document 1 further includes a suction port formed as a through hole having openings on the outer peripheral surface and the inner peripheral cam surface of the cam ring. In addition to the suction port formed in the pump cover and the side plate, the working fluid is sucked into the pump chamber through the suction port formed in the cam ring. Therefore, the working fluid reaches the central portion of the pump chamber in the rotation axis direction.

JP 2009-52525 A

  In a vane pump, the pump chamber rotates with the vane. Therefore, when the working fluid in the suction passage is sucked into the pump chamber, the working fluid does not easily reach the front part in the rotational direction of the pump chamber as the rotation speeds up. As a result, the working fluid is insufficient with respect to the volume of the pump chamber, and cavitation may occur. For these reasons, there is a need for a vane pump having better suction characteristics.

  An object of this invention is to improve the suction characteristic of a vane pump.

According to a first aspect of the present invention, there is provided a rotor, a plurality of vanes, a cam ring having an inner peripheral cam surface, first and second side members defining a pump chamber, at least one of the cam ring, the first side member, and the second side member. A suction port that is provided in one and guides the working fluid to the pump chamber; and a guide portion that is provided in the suction port, and the first side member has a recess formed on a side surface that contacts the cam ring, suction port is partitioned and recess, and the end face of the cam ring facing the recess, the guide portion is provided on the bottom surface of the recess, characterized in Rukoto.

In the first invention, since the guide portion is provided in the suction port that guides the working fluid to the pump chamber, the working fluid in the suction port is easily sucked into the pump chamber, and is easily filled in the pump chamber even at a high rotational speed. . Further, since the suction port is defined by the recess and the end surface of the cam ring, the bottom surface of the recess is exposed in a state where the cam ring and the first side member are separated. In addition, since the guide portion is provided on the bottom surface of the hollow portion, no advanced technique is required for forming the guide portion. Therefore, a vane pump can be manufactured easily.

  The second invention is characterized in that the radially inner end portion of the guide portion is directed forward in the rotational direction of the pump from the radially outer end portion.

  In the second invention, the radially inner end of the guide portion is directed forward in the rotational direction of the pump from the radially outer end, so that the working fluid easily flows toward the forward portion in the rotational direction of the pump chamber. Therefore, the working fluid is easily filled in the rotational direction front portion of the pump chamber even at a high rotational speed, and the suction characteristics of the vane pump are further improved.

The third invention is characterized in that the guide portion is in contact with the end face of the cam ring.

In the third aspect of the invention, since the guide portion is in contact with the cam ring, the recessed portion is hardly deformed even when the first side member is pressed against the cam ring. Therefore, the size of the suction port can be maintained, and deterioration of the suction characteristics of the vane pump can be prevented.

According to a fourth aspect of the present invention, the recessed portion has a side wall positioned radially inward from the inner peripheral cam surface of the cam ring, and the guide portion has a gap between the side wall and the cam portion.

In the fourth invention, since the guide portion has a gap between the side wall of the recess portion, the working fluid in the suction port is sucked into the pump chamber through this gap even when the vane passes near the guide portion. . Therefore, the suction characteristics of the vane pump can be further improved.

The fifth invention is characterized in that the guide portion is inclined so as to become higher toward the radially inner side.

In the fifth aspect of the invention, since the guide portion is inclined so as to increase inward in the radial direction, the flow resistance of the working fluid generated by the guide portion is reduced and the working fluid is efficiently guided. Therefore, the suction characteristics of the vane pump can be further improved.

6th invention is provided with two or more guide parts, and some guide parts of several guide parts have the height substantially equal to the depth of a hollow part, and other guide parts among several guide parts Is characterized by being lower than the depth of the indentation.

In the sixth invention, since a part of the plurality of guide portions has a height substantially equal to the depth of the recessed portion, the recessed portion is not easily deformed even when the first side member is pressed against the cam ring. Moreover, since the other guide part is low compared with the depth of a hollow part, the friction which arises between another guide part and a vane is small. Accordingly, it is possible to prevent the vane pump suction characteristics from deteriorating and to prevent the vane resistance from increasing.

The seventh invention is characterized in that the guide portion is curved.

In the seventh invention, since the guide portion is curved, the direction of the flow of fluid guided from the suction port to the pump chamber gradually changes. Therefore, the flow resistance at the suction port is reduced, and the suction characteristics of the vane pump can be further improved.

The eighth invention is characterized in that the inclination angle with respect to the radial direction in the guide portion is smaller than the inclination angle with respect to the radial direction in the guide portion located rearward in the rotation direction.

In the eighth invention, since the inclination angles in the respective guide portions are different, the flow of the working fluid in the suction port is orthogonal to the vane at various timings during the operation of the vane pump. Therefore, the working fluid easily spreads forward in the rotational direction of the pump chamber, and the suction characteristics of the vane pump are further improved.

  According to the present invention, the suction characteristics of the vane pump can be improved.

It is sectional drawing of the vane pump which concerns on embodiment of this invention. It is the top view which looked at the rotor, the vane, and the cam ring from the pump cover side. It is a side view of a cam ring and the 1st and 2nd side plate. It is the top view which looked at the 1st side plate from the cam ring side. It is a perspective view of a rotor, a vane, a cam ring, and a 1st side plate. It is the top view which looked at the rotor, the vane, the cam ring, and the first side plate from the pump cover side. It is sectional drawing which follows the VIIA-VIIA line | wire shown in FIG. It is sectional drawing which shows the other example of a 1st side plate corresponding to FIG. 7A. It is sectional drawing which shows the other example of a 1st side plate corresponding to FIG. 7A. It is an enlarged view of the periphery of the suction port located in an expansion area. It is the top view which looked at the 2nd side plate from the cam ring side. It is the side view which looked at the 2nd side plate and the cam ring from the diameter direction outside. It is the top view which looked at the other example of the 1st side plate from the cam ring side.

  Hereinafter, a vane pump 100 according to an embodiment of the present invention will be described with reference to the drawings. Here, although the vane pump 100 in which working oil is used as the working fluid will be described, other fluids such as working water may be used as the working fluid.

  FIG. 1 is a cross-sectional view of the vane pump 100. The vane pump 100 is used as a hydraulic pressure supply source of a hydraulic device 1 (for example, a power steering device or a transmission) mounted on a vehicle.

  The vane pump 100 includes a drive shaft 10, a rotor 20 connected to the drive shaft 10, a plurality of vanes 30 provided in the rotor 20, and a cam ring 40 that houses the rotor 20 and the vanes 30.

  The drive shaft 10 is rotatably supported by the pump body 50 and the pump cover 60. When the power of the engine or the electric motor (not shown) is transmitted to the drive shaft 10, the rotor 20 rotates as the drive shaft 10 rotates.

  In the following, the rotation center axial direction of the rotor 20 is also simply referred to as “axial direction”, the radial direction of the rotor 20 is also simply referred to as “radial direction”, and the rotational direction of the rotor 20 is also simply referred to as “rotational direction”.

  FIG. 2 is a plan view of the rotor 20, the vane 30, and the cam ring 40 as viewed from the pump cover 60 side. As shown in FIG. 2, a plurality of slits 22 having openings 21 on the outer peripheral surface are radially formed in the rotor 20 at predetermined intervals. The opening 21 of the slit 22 is formed in a raised portion 23 that protrudes radially outward from the outer periphery of the rotor 20. In other words, the protruding portions 23 are formed on the outer periphery of the rotor 20 by the number of the slits 22. A back pressure chamber 24 is defined by the vane 30 in the slit 22.

  The vanes 30 are slidably inserted into the slits 22 and reciprocate in the radial direction as the rotor 20 rotates. The distal end portion 31 of the vane 30 faces the inner peripheral surface 40 a of the cam ring 40, and the proximal end portion 32 of the vane 30 faces the back pressure chamber 24.

  Hydraulic oil is guided to the back pressure chamber 24. The vane 30 is pressed in a direction protruding from the slit 22 by the pressure of the hydraulic oil in the back pressure chamber 24, and the tip portion 31 of the vane 30 is in contact with the inner peripheral surface 40 a of the cam ring 40.

  Refer to FIG. 1 again. The vane pump 100 further includes first and second side plates 70 and 80 as first and second side members disposed with the rotor 20 and the cam ring 40 sandwiched in the axial direction.

  FIG. 3 is a sectional view of the cam ring 40 and the first and second side plates 70 and 80. In FIG. 3, a high pressure chamber 53, a passage 54, and a low pressure chamber 61, which will be described later, are indicated by two-dot chain lines.

  As shown in FIG. 3, the first and second side plates 70 and 80 have side surfaces 70 a and 80 a that contact the rotor 20 and the cam ring 40, respectively, and are partitioned by the vane 30 between the rotor 20 and the cam ring 40. The pump chamber 41 is partitioned.

  As shown in FIG. 2, the inner peripheral surface 40a of the cam ring 40 is formed in a substantially oval shape. Hereinafter, the inner peripheral surface 40a is also referred to as an “inner peripheral cam surface 40a”.

  Since the inner circumferential cam surface 40a of the cam ring 40 is formed in a substantially oval shape, the vane 30 reciprocates with respect to the rotor 20 as the rotor 20 rotates, and the pump chamber 41 repeats expansion and contraction. When the pump chamber 41 expands, the hydraulic oil is sucked into the pump chamber 41, and when the pump chamber 41 contracts, the hydraulic oil is discharged from the pump chamber 41.

  In this embodiment, while the rotor 20 makes one rotation, the vane 30 reciprocates twice, and the pump chamber 41 repeats expansion and contraction twice. That is, the vane pump 100 alternately has two expansion regions 42a and 42c in which the pump chamber 41 expands and two contraction regions 42b and 42d in which the pump chamber 41 contracts in the rotation direction.

  As shown in FIG. 1, the pump body 50 is formed with a housing recess 51 that houses the rotor 20, the cam ring 40, and the first side plate 70. The first side plate 70 is disposed on the bottom surface 51 a of the housing recess 51.

  An annular groove 52 is formed on the bottom surface 51 a of the housing recess 51. The annular groove 52 and the first side plate 70 define a high pressure chamber 53 into which hydraulic oil discharged from the pump chamber 41 flows. The high pressure chamber 53 is connected to the hydraulic device 1, and hydraulic oil discharged from the pump chamber 41 is supplied to the hydraulic device 1 through the high pressure chamber 53.

  FIG. 4 is a plan view of the first side plate 70 viewed from the cam ring 40 side. As shown in FIGS. 3 and 4, the first side plate 70 is formed in an annular shape having a hole 71 at the center thereof. The drive shaft 10 (see FIG. 1) is inserted through the hole 71.

  The first side plate 70 is provided with two discharge ports 72 that guide the hydraulic oil discharged from the pump chamber 41 to the high-pressure chamber 53. The discharge port 72 passes through the first side plate 70 and opens toward the pump chamber 41 and the high pressure chamber 53.

  The discharge port 72 is located in each contraction region 42b, 42d. Therefore, the hydraulic oil in the pump chamber 41 is discharged to the high pressure chamber 53 through the discharge port 72 when the pump chamber 41 passes through the contraction regions 42b and 42d.

  The first side plate 70 is also formed with two back pressure passages 73 that guide hydraulic oil from the high pressure chamber 53 to the back pressure chamber 24. The back pressure passage 73 passes through the first side plate 70 and opens toward the high pressure chamber 53 and the back pressure chamber 24.

  The back pressure passage 73 has an arc shape centered on the hole 71 and is located in the expansion regions 42a and 42c. Therefore, hydraulic oil is guided from the high pressure chamber 53 to the back pressure chamber 24 that passes through the expansion regions 42 a and 42 c. As a result, the vane 30 passing through the expansion regions 42a and 42c is pressed in a direction protruding from the slit 22 (see FIG. 2) by the pressure in the back pressure chamber 24.

  In this manner, the vane 30 is pressed in the direction of protruding from the slit 22 by the pressure in the back pressure chamber 24 and the centrifugal force generated by the rotation of the rotor 20.

  Refer to FIG. 1 again. The housing recess 51 of the pump body 50 is formed larger than the cam ring 40, and a passage 54 is defined by the cam ring 40 and the pump body 50. The passage 54 extends from the outer periphery of the second side plate 80 to the outer periphery of the first side plate 70.

  The opening of the housing recess 51 is sealed by the pump cover 60. The pump cover 60 is fastened to the pump body 50 by bolts (not shown). A second side plate 80 is disposed between the pump cover 60 and the cam ring 40.

  The pump cover 60 forms a low pressure chamber 61 connected to the tank 2. The low pressure chamber 61 communicates with the pump chamber 41 through the passage 54 and the suction port 74 provided in the first side plate 70, and communicates with the pump chamber 41 through the suction port 81 provided in the second side plate 80.

  The suction port 74 and the suction port 81 will be described in detail.

  First, the structure of the suction port 74 will be described in more detail with reference to FIGS. FIG. 5 is a perspective view of the rotor 20, the vane 30, the cam ring 40, and the first side plate 70. FIG. 6 is a plan view of the rotor 20, the vane 30, the cam ring 40, and the first side plate 70 as viewed from the pump cover 60 side.

  The first side plate 70 has two depressions 75 formed on the side surface 70a. The recess 75 faces the end surface 40b of the cam ring 40. The recess 75 opens to the outer peripheral surface 70 b of the first side plate 70 and communicates with the passage 54.

  A part of the side wall 75 a of the recess 75 is located on the radially inner side of the inner circumferential cam surface 40 a of the cam ring 40. That is, the recess 75 opens toward the pump chamber 41 and communicates with the pump chamber 41.

  Moreover, the hollow part 75 is located in each expansion | swelling area | region 42a, 42c. Therefore, when the pump chamber 41 passes through the expansion regions 42 a and 42 c, the hydraulic oil is guided from the low pressure chamber 61 to the pump chamber 41 through the passage 54 and the recess 75.

  In this way, the suction port 74 is partitioned by the recess 75 and the end surface 40b of the cam ring 40 facing the recess 75, and the hydraulic oil is pumped from the passage 54 toward the radially inner side. Lead to 41.

  The suction port 74 is not limited to the form defined by the recessed part 75 and the end face 40b of the cam ring 40, and may be a form including a hole penetrating the first side plate 70, for example.

  Each of the suction ports 74 is provided with three fins 76a, 76b, and 76c in this order in the rotation direction as guide portions for guiding the hydraulic oil guided from the passage 54 to the pump chamber 41. The fins 76a, 76b, and 76c are formed to protrude from the bottom surface 75b of the recess 75.

  The fins 76a, 76b, and 76c are preferably as thin as possible. Moreover, the space | interval between fin 76a, 76b, 76c can be set arbitrarily.

  The fin 76 b has a height substantially equal to the depth of the recess 75 (refers to the axial dimension of the recess 75), and is in contact with the end surface 40 b of the cam ring 40. The fins 76 a and 76 c are lower than the depth of the recess 75 and have a gap between the end surface 40 b of the cam ring 40. Further, the fins 76 a, 76 b, 76 c have a gap between them and the side wall 75 a of the recess 75.

  The fins 76a, 76b, and 76c are formed integrally with the first side plate 70 by, for example, sintering. Since the suction port 74 is defined by the recess 75 and the end surface 40b of the cam ring 40, the bottom surface 75b of the recess 75 is exposed in a state where the cam ring 40 and the first side plate 70 are separated. Therefore, advanced technology is not required to form the fins 76a, 76b, and 76c on the bottom surface 75b of the recess 75. Therefore, the vane pump 100 can be manufactured easily.

  The fins 76 a, 76 b, and 76 c are not limited to a form integrally formed with the first side plate 70 by sintering, and may be formed separately from the first side plate 70 and attached to the first side plate 70. Good.

  The fins 76a are formed to be inclined with respect to the radial direction so that the flow of hydraulic oil is directed forward in the rotational direction. Specifically, the fin 76a is positioned so that the downstream end (radially inner end) 77a of the fin 76a is positioned forward of the upstream end (radially outer end) 77b of the fin 76a in the rotational direction. Is inclined with respect to the radial direction. The fins 76b and 76c are formed so as to be inclined with respect to the radial direction so that the flow of hydraulic oil is directed forward in the rotational direction, like the fins 76a.

  Since the fins 76 a, 76 b, 76 c direct the flow of hydraulic oil guided from the suction port 74 to the pump chamber 41 in the rotational direction, the hydraulic fluid in the suction port 74 is pumped into the pump chamber 41 when sucked into the pump chamber 41. 41 flows into the front in the rotational direction. Therefore, the suction characteristics of the vane pump 100 are improved, and the working oil is distributed to the front part in the rotational direction of the pump chamber 41. Since a sufficient amount of hydraulic oil is guided to the pump chamber 41, a decrease in pressure in the pump chamber 41 can be prevented, and the occurrence of cavitation can be prevented.

  Further, the fin 76a is formed in a curved shape so as to be inclined at a larger angle with respect to the radial direction at a portion closer to the downstream end 77a. The fins 76b and 76c are formed in a curved shape like the fin 76a. By forming the fins 76a, 76b, and 76c in a curved shape, the direction of the flow of the hydraulic oil guided from the suction port 74 to the pump chamber 41 changes gently. Therefore, the flow resistance at the suction port 74 is reduced, and the suction characteristics of the vane pump 100 can be further improved.

  The fin 76a has a radially inner end 77a that is directed forward in the rotational direction of the pump from the radially outer end 77b. More specifically, the radially inner end 77a of the fin 76a is formed so as to extend in a direction substantially orthogonal to the vane 30 positioned forward in the rotational direction of the pump chamber 41 in the expansion regions 42a and 42c. . Therefore, the direction of the flow of the hydraulic oil guided by the fins 76 a is substantially orthogonal to the vane 30 that is positioned forward in the rotational direction of the pump chamber 41 when being sucked into the pump chamber 41.

  By making the flow direction of the hydraulic oil in the suction port 74 substantially orthogonal to the vane 30, the hydraulic oil can easily flow toward the front part in the rotational direction of the pump chamber 41. Therefore, the hydraulic oil is filled by the front portion in the rotational direction of the pump chamber 41, and the suction characteristics of the vane pump 100 are further improved. As a result, a sufficient amount of hydraulic oil is guided to the pump chamber 41, so that a decrease in pressure in the pump chamber 41 can be prevented, and the occurrence of cavitation can be prevented.

  7A is a cross-sectional view taken along line VIIA-VIIA in FIG. As shown in FIG. 7A, in the present embodiment, the fins 76b are formed with a substantially uniform height. Similarly, the fins 76a and 76c may be formed with a substantially uniform height, and may be inclined as shown in FIGS. 7B and 7C described later.

  FIG. 7B is a cross-sectional view illustrating another example of the first side plate 70 corresponding to FIG. 7A. As shown in FIG. 7B, the fin 76b may be formed to be inclined so as to become lower inward in the radial direction, and the radial inner end 77a of the fin 76b may be lower than the radial outer end 77b. In this case, the flow resistance of the hydraulic oil generated by the fins 76b can be reduced. Similarly, the fins 76a and 76c may be formed so as to become lower inward in the radial direction, and even if the height is uniform as shown in FIG. 7A described above, they are inclined as shown in FIG. 7C described later. May be.

  FIG. 7C is a cross-sectional view showing another example of the first side plate 70 corresponding to FIG. 7A. As shown in FIG. 7C, the fins 76b are formed to be inclined so as to increase inward in the radial direction, and the radial inner end 77a of the fin 76b is preferably higher than the radial outer end 77b. In this case, the flow resistance of the hydraulic oil generated by the fins 76b can be reduced, and the hydraulic oil can be guided efficiently. Similarly, the fins 76a and 76c may be formed so as to increase inward in the radial direction. Even if the height is uniform as shown in FIG. 7A, the fins 76a and 76c are inclined as shown in FIG. 7B. May be.

  FIG. 8 is an enlarged view of the periphery of the suction port 74 located in the expansion region 42c. As shown in FIG. 8, the inclination angle β with respect to the radial direction of the fin 76b is smaller than the inclination angle α with respect to the radial direction of the fin 76a. Therefore, the flow Fb of hydraulic fluid guided by the fins 76b is directed more radially inward than the hydraulic fluid flow Fa guided by the vanes 30 by the fins 76a.

  Since the flow Fb is directed more radially inward than the flow Fa, the time from when the vane 30 passes through the fins 76b until it is orthogonal to the direction of the flow Fb is after the vane 30 passes through the fins 76a. It is longer than the time until it is orthogonal to the direction of the flow Fa. That is, the vane 30 is orthogonal to the direction of the flow Fb at a later timing.

  The inclination angle γ with respect to the radial direction of the fins 76c is smaller than the inclination angle β. Therefore, the flow Fc of hydraulic oil guided by the fins 76c is directed more radially inward than the flow Fb. Therefore, the vane 30 is orthogonal to the flow Fc at a later timing.

  Thus, in this embodiment, since the inclination angles α, β, and γ are different, the flow of hydraulic oil in the suction port 74 is orthogonal to the vane 30 at various timings during the operation of the vane pump 100. Therefore, the hydraulic oil is unlikely to stay in the rear portion of the pump chamber 41 in the rotation direction, and the suction characteristics of the vane pump 100 are further improved.

  The fin 76 b has a height that is substantially equal to the depth of the recess 75, and is in contact with the cam ring 40. For this reason, even if the first side plate 70 is pressed against the cam ring 40, the recess 75 is not easily deformed. Therefore, the magnitude | size of the suction port 74 can be maintained and the fall of the suction characteristic of the vane pump 100 can be prevented.

  Further, the fins 76 a and 76 c are lower than the depth of the recessed portion 75, and have a gap between the end surface 40 b of the cam ring 40. Therefore, hydraulic oil flows from the suction port 74 into the pump chamber 41 through this gap. Therefore, the suction characteristics of the vane pump 100 are further improved.

  In the present embodiment, the fins 76b prevent the recess 75 from being deformed, and the hydraulic oil passage is sufficiently secured by the gaps between the fins 76a and 76c and the cam ring. Therefore, the suction characteristics of the vane pump 100 are further improved.

  If the fins 76a, 76b, and 76c have a height substantially equal to the depth of the recess 75, the vane 30 passes through the vicinity of the fins 76a, 76b, and 76c. Therefore, friction occurs between the vane 30 and the fins 76a, 76b, and 76c, and the resistance of the vane 30 may increase. Further, when the fins 76a, 76b, and 76c are lower than the depth of the recess 75, the recess 75 is deformed when the first side plate 70 is pressed against the cam ring 40, and the suction characteristics of the vane pump 100 may be deteriorated. .

  In the present embodiment, since the fins 76 a and 76 c are lower than the depth of the recess 75, the friction generated between the fins 76 a and 76 c and the vane 30 is small. Therefore, an increase in the resistance of the vane 30 can be prevented. Further, since the fins 76b have a height substantially equal to the depth of the recess 75, the recess 75 is not easily deformed even when the first side plate 70 is pressed against the cam ring 40. Therefore, it is possible to prevent the suction characteristics of the vane pump 100 from being deteriorated.

  The present embodiment is not limited to a form in which only the fins 76 b have a height equal to the depth of the recessed portion 75 and only the fins 76 a and 76 c are lower than the depth of the recessed portion 75. For example, the fins 76 a and 76 b may have a height equal to the depth of the recess 75 and the fin 76 c may be lower than the depth of the recess 75. In other words, some of the fins 76 a, 76 b, 76 c have a height equal to the depth of the recess 75, and the other fins of the fins 76 a, 76 b, 76 c are compared with the depth of the recess 75. And it should be low.

  In the present embodiment, the fins 76 a, 76 b, and 76 c have a gap with the side wall 75 a of the recess 75. Therefore, even when the vane 30 passes near the fins 76a, 76b, and 76c, the hydraulic oil in the suction port 74 is sucked into the pump chamber 41 through this gap. That is, the flow of the hydraulic oil is hardly inhibited by the fins 76a, 76b, and 76c. Therefore, the suction characteristics of the vane pump 100 can be further improved.

  Next, the structure of the suction port 81 will be described in more detail with reference to FIG. 3, FIG. 9, and FIG. 9 is a view of the second side plate 80 as viewed from the cam ring 40 side, and FIG. 10 is a view of the second side plate 80 and the cam ring 40 as viewed from the outside in the radial direction.

  The second side plate 80 has two recessed portions 82 formed on the outer peripheral surface 80b. The recess 82 opens to the side surface 80 a of the second side plate 80 and communicates with the pump chamber 41. The recessed portion 82 opens to the side surface 80 c of the second side plate 80 opposite to the side surface 80 a and communicates with the low pressure chamber 61.

  The recessed part 82 is located in each expansion | swelling area | region 42a, 42c. Therefore, when the pump chamber 41 passes through the expansion regions 42 a and 42 c, the working oil is guided from the low pressure chamber 61 to the pump chamber 41 through the recess 82.

  Thus, the suction port 81 is partitioned by the recess 82 and the end surface 40c of the cam ring 40 facing the recess 82, and the flow of hydraulic oil from the low pressure chamber 61 is axially directed (from the second side plate 80 to the cam ring). Toward the pump chamber 41).

  The suction port 81 is not limited to the form defined by the recessed part 82 and the end face 40c of the cam ring 40. For example, the suction port 81 may be formed by a hole penetrating the second side plate 80.

  The suction port 81 is provided with fins 83a, 83b, and 83c as guide portions for guiding the flow of hydraulic oil guided from the low pressure chamber 61 to the pump chamber 41. The fins 83a, 83b, 83c are formed so as to protrude from the bottom surface 82a of the recess 82.

  The fin 83a is formed to be inclined with respect to the axial direction so that the flow of hydraulic oil is directed forward in the rotational direction. Specifically, the downstream end portion (end portion on the pump chamber 41 side) 84a of the fin 83a is more forward in the rotational direction of the rotor 20 than the upstream end portion (end portion on the low pressure chamber 61 side) 84b of the fin 83a. The fin 83a is inclined with respect to the axial direction so as to be positioned. The fins 83b and 83c are formed to be inclined with respect to the axial direction so that the flow of hydraulic oil is directed forward in the rotational direction, similarly to the fin 83a.

  Since the fins 83 a, 83 b, 83 c direct the flow of hydraulic oil guided from the suction port 81 to the pump chamber 41 in the rotational direction, the hydraulic oil in the suction port 81 is pumped into the pump chamber 41 when sucked into the pump chamber 41. The front part of the rotation direction 41 is filled. Therefore, the suction characteristics of the vane pump 100 are improved, and the occurrence of cavitation can be prevented.

  Similarly to the fins 76a (see FIG. 4 and the like), the fins 83a are formed in a curved shape so as to be inclined at a larger angle with respect to the axial direction at a portion closer to the downstream end portion 84a. The fins 83b and 83c are formed in a curved shape like the fin 83a. The suction characteristics of the vane pump 100 can be further improved by forming the fins 83a, 83b, and 83c in a curved shape.

  The fins 83a, 83bb, and 83c are formed so as to extend in a direction orthogonal to the vane 30 that is positioned forward in the rotational direction of the pump chamber 41 in the expansion regions 72a and 72c. Therefore, the hydraulic oil easily flows toward the front part in the rotational direction of the pump chamber 41. Therefore, the suction characteristics of the vane pump 100 are further improved, and the occurrence of cavitation can be prevented.

  The inclination angles with respect to the axial direction of the fins 83a, 83b, 83c are different. Thereby, the suction | inhalation characteristic of the vane pump 100 improves more similarly to the fins 76a, 76b, and 76c.

  The vane pump 100 may include a suction port different from the suction ports 74 and 81. The suction ports different from the suction ports 74 and 81 are formed as through holes having openings on the outer peripheral surface 40d and the inner peripheral cam surface 40a of the cam ring 40, for example. Such a suction port is also preferably provided with a guide portion that directs the flow of hydraulic oil guided to the pump chamber 41 forward in the rotational direction of the rotor 20.

  Next, the operation of the vane pump 100 will be described with reference to FIGS. 1 to 3.

  When the power of the engine or the electric motor (not shown) is transmitted to the drive shaft 10, the rotor 20 rotates as the drive shaft 10 rotates. As the rotor 20 rotates, the vane 30 reciprocates with respect to the rotor 20, and the pump chamber 41 repeats expansion and contraction.

  The hydraulic oil in the tank 2 is guided to the pump chamber 41 passing through the expansion regions 42 a and 42 c through the low pressure chamber 61, the passage 54 and the suction port 74, and through the low pressure chamber 61 and the suction port 81.

  The flow of hydraulic oil guided to the pump chamber 41 through the suction port 74 is directed forward in the rotational direction by the fins 76a, 76b, and 76c. Therefore, the hydraulic oil in the suction port 74 is filled in the front portion in the rotational direction of the pump chamber 41 when being sucked into the pump chamber 41. Therefore, the suction characteristics of the vane pump 100 are improved, and the occurrence of cavitation can be prevented.

  The flow of hydraulic oil guided to the pump chamber 41 through the suction port 81 is directed forward in the rotational direction by the fins 83a, 83b, and 83c. Therefore, the suction characteristics of the vane pump 100 are improved, and the occurrence of cavitation can be prevented.

  When the pump chamber 41 passes through the contraction regions 42 b and 42 d, the hydraulic oil in the pump chamber 41 is discharged to the high pressure chamber 53 and guided to the hydraulic device 1. Since the occurrence of cavitation is prevented, hydraulic oil having a higher pressure and a larger flow rate can be supplied to the hydraulic device 1.

  In the vane pump 100 described above, the fins 76a are formed in a curved shape, but the fins 76a may be formed in a straight line from the upstream end 77b to the downstream end 77a as shown in FIG. The fins 76b, 76c, 83a, 83b, and 83c may be formed in a straight line like the fin 76a.

  The vane pump 100 includes three fins 76 a, 76 b, 76 c in one suction port 74, but two or less, or four or more fins may be provided in one suction port 74. The number of fins provided in one suction port 81 is not limited to three.

  The guide portions such as the fins 76a, 76b, 76c, 83a, 83b, and 83c may be provided only on the first side plate 70 or only on the second side plate 80.

  The fins 76 a and 76 c may be in contact with the end surface 40 b of the cam ring 40. In this case, the deformation of the recess 75 is prevented by the three fins 76a, 76b, and 76c. Therefore, the size of the suction port 74 can be maintained, and the deterioration of the suction characteristics of the vane pump 100 due to the deformation of the recess 75 can be prevented more reliably.

  The fin 76b may have a gap between the end surface 40b of the cam ring 40. In this case, the hydraulic oil passage is sufficiently secured by the gaps between the three fins 76 a, 76 b, 76 c and the end surface 40 b of the cam ring 40. Therefore, it is possible to more reliably prevent the suction characteristics of the fin vane pump 100 from being reduced due to the narrow passage in the suction port 74.

  The fins 76a, 76b, and 76c may be in contact with the side wall 75a of the recess 75. In this case, it is desirable that the downstream end 77a of the fins 76a, 76b, and 76c is lower than the upstream end 77b of the fins 76a, 76b, and 76c in order to ensure a sufficient hydraulic fluid passage. By making the downstream end 77a lower than the upstream end 77b, a hydraulic oil passage is easily secured in the vicinity of the downstream end 77a. Therefore, it is possible to prevent the suction characteristics of the vane pump 100 from being deteriorated due to the fins 76a, 76b, and 76c coming into contact with the side wall 75a.

  Hereinafter, the configuration, operation, and effect of the embodiment of the present invention will be described together.

  The vane pump 100 accommodates the rotor 20 that is rotationally driven, the plurality of vanes 30 that are provided in the rotor 20 so as to be capable of reciprocating in the radial direction of the rotor 20, and the plurality of vanes 30 as the rotor 20 rotates. A cam ring 40 having an inner circumferential cam surface 40a with which the front end portion 31 is slidably contacted, and a rotor chamber 20 and a cam ring 40 are disposed therebetween, and a pump chamber 41 partitioned by a plurality of vanes 30 is defined between the rotor 20 and the cam ring 40. Suction ports 74, 81 that are provided in at least one of the first and second side plates 70, 80, the cam ring 40, the first side plate 70, and the second side plate 80, and guide the hydraulic oil to the pump chamber 41; And fins 76a, 76b, 76c, 83a, 83b, 83c provided on the suction ports 74, 81. And butterflies.

  In this configuration, since the fins 76 a, 76 b, 76 c, 83 a, 83 b, 83 c are provided in the suction ports 74, 81 that guide the hydraulic oil to the pump chamber 41, the hydraulic oil in the suction ports 74, 81 is transferred to the pump chamber 41. A large amount flows into the pump chamber 41 when sucked. Therefore, the suction characteristics of the vane pump 100 can be improved.

  Further, the vane pump 100 is characterized in that the radially inner ends 77a of the fins 76a, 76b, and 76c are directed forward in the rotational direction of the pump from the radially outer ends 77b.

  In this configuration, since the radially inner end 77a of the fins 76a, 76b, and 76c is directed forward in the rotational direction of the pump from the radially outer end 77b, the hydraulic oil is directed toward the rotationally forward portion of the pump chamber 41. Easy to flow. Therefore, more hydraulic oil is filled in the front portion of the pump chamber 41 in the rotation direction, and the suction characteristics of the vane pump 100 are further improved.

  In the vane pump 100, the first side plate 70 has a recess 75 formed in a side surface 70a that abuts the cam ring 40, and the suction port 74 is an end surface of the recess 75 and the cam ring 40 facing the recess 75. 40b, and the fins 76a, 76b, and 76c are provided on the bottom surface 75b of the recess 75.

  In this configuration, since the suction port 74 is defined by the recess 75 and the end surface 40b of the cam ring 40, the bottom surface 75b of the recess 75 is exposed when the cam ring 40 and the first side plate 70 are separated. Further, since the fins 76a, 76b, and 76c are provided on the bottom surface 75b of the recess 75, a high level of technology is not required for forming the fins 76a, 76b, and 76c. Therefore, the vane pump 100 can be manufactured easily.

  Further, the vane pump 100 is characterized in that the fins 76b are in contact with the end face 40b of the cam ring 40.

  In this configuration, since the fins 76b are in contact with the cam ring 40, even if the first side plate 70 is pressed against the cam ring 40, the recess 75 is not easily deformed. Therefore, the magnitude | size of the suction port 74 can be maintained and the fall of the suction characteristic of the vane pump 100 can be prevented.

  Further, the vane pump 100 has a side wall 75a in which the hollow portion 75 is located radially inward from the inner circumferential cam surface 40a of the cam ring 40, and the fins 76a, 76b, and 76c have a gap between the side wall 75a. It is characterized by.

  In this configuration, since the fins 76a, 76b, and 76c have a gap with the side wall 75a of the recess 75, even when the vane 30 passes in the vicinity of the fins 76a, 76b, and 76c, the operation in the suction port 74 is performed. Oil is sucked into the pump chamber 41 through this gap. Therefore, the suction characteristics of the vane pump 100 can be further improved.

  Further, the vane pump 100 is characterized in that the fins 76a, 76b, and 76c are inclined so as to become higher as they go radially inward.

  In this configuration, since the fins 76a, 76b, and 76c are inclined toward the inner side in the radial direction, the flow resistance of the hydraulic oil generated by the fins 76a, 76b, and 76c is reduced, and the hydraulic oil is efficiently guided. Therefore, the suction characteristics of the vane pump 100 can be further improved.

  Further, the vane pump 100 is characterized in that the fins 76 b have a height substantially equal to the depth of the recessed portion 75, and the fins 76 a and 76 c are lower than the depth of the recessed portion 75.

  In this configuration, since the fins 76 b have a height substantially equal to the depth of the recess 75, the recess 75 is not easily deformed even when the first side plate 70 is pressed against the cam ring 40. Further, since the fins 76 a and 76 c are lower than the depth of the recess 75, the friction generated between the fins 76 a and 76 c and the vane 30 is small. Therefore, the suction characteristics of the vane pump 100 can be prevented from being lowered, and the resistance of the vane 30 can be prevented from increasing.

  The vane pump 100 is characterized in that the fins 76a, 76b, 76c, 83a, 83b, and 83c are curved.

  In this configuration, since the fins 76a, 76b, 76c, 83a, 83b, and 83c are curved, the direction of the flow of the hydraulic oil guided from the suction ports 74 and 81 to the pump chamber 41 changes gently. Therefore, the flow resistance at the suction ports 74 and 81 is reduced, and the suction characteristics of the vane pump 100 can be further improved.

  Further, the vane pump 100 is characterized in that the inclination angles β and γ with respect to the radial direction of the fins 76 b and 76 c are smaller than the inclination angles α and β with respect to the radial direction of the fins 76 a and 76 b located at the rear in the rotation direction. .

  In this configuration, since the inclination angles α, β, γ of the fins 76 a, 76 b, 76 c are different, the flow of hydraulic oil in the suction port 74 is orthogonal to the vane 30 at various timings during the operation of the vane pump 100. To do. Accordingly, the hydraulic oil flows into the front portion in the rotational direction of the pump chamber 41, and the suction characteristics of the vane pump 100 are further improved.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  DESCRIPTION OF SYMBOLS 100 ... Vane pump, 20 ... Rotor, 30 ... Vane, 31 ... Tip part, 40 ... Cam ring, 40a ... Inner peripheral cam surface, 40b ... End surface, 41 ... Pump chamber, 70 ... first side plate (first side member), 70a ... side face, 74 ... suction port, 75 ... depression, 75a ... side wall, 75b ... bottom face, 76a, 76b, 76c... Fin (guide portion), 77a... Radially inner end, 77b .. radially outer end, 80 .. second side plate (second side member), 81 ... Suction port, 83a, 83b, 83c ... Fin (guide part), α, β, γ ... Inclination angle

Claims (8)

A rotor that is driven to rotate;
A plurality of vanes provided in the rotor so as to be capable of reciprocating in the radial direction of the rotor;
A cam ring that houses the rotor and has an inner circumferential cam surface with which the tips of the plurality of vanes slide in contact with rotation of the rotor;
A first side member and a second side member, which are arranged with the rotor and the cam ring interposed therebetween, and define a pump chamber partitioned by the plurality of vanes between the rotor and the cam ring;
A suction port that is provided in at least one of the cam ring, the first side member, and the second side member and guides the working fluid to the pump chamber;
A guide portion provided in the suction port ,
The first side member has a recess formed on a side surface that contacts the cam ring,
The suction port is partitioned by the recess and an end surface of the cam ring facing the recess,
The guide portion is a vane pump, characterized in Rukoto provided on the bottom surface of the recess portion.   2. The vane pump according to claim 1, wherein the guide portion has a radially inner end directed forward in a rotation direction of the pump from a radially outer end. The guide portion, the vane pump according to claim 1 or 2, characterized in that in contact with the end surface of the cam ring. The recess has a side wall located radially inward from the inner circumferential cam surface of the cam ring,
The vane pump according to any one of claims 1 to 3, wherein the guide portion has a gap between the side wall and the side wall. The vane pump according to any one of claims 1 to 4 , wherein the guide portion is inclined so as to become higher toward a radially inner side. A plurality of the guide portions;
Some of the plurality of guide portions have a height equal to the depth of the recessed portion, and the other guide portions of the plurality of guide portions are compared with the depth of the recessed portion. The vane pump according to claim 1 , wherein the vane pump is low. The vane pump according to any one of claims 1 to 6 , wherein the guide portion is curved. The vane pump according to any one of claims 1 to 7 , wherein an inclination angle with respect to a radial direction in the guide portion is smaller than an inclination angle with respect to the radial direction in the guide portion located rearward in the rotation direction. .

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