JP2011174588A - Torque converter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque converter that has a structure for increasing a torque capacity. <P>SOLUTION: The torque converter 2 includes a pump impeller 8 and a turbine runner 10. The pump impeller 8 includes a pump shell 8s, a plurality of pump blades 8b radially arranged around the rotation axis line O of the pump impeller 8 on the inner surface of the pump shell 8s, and a pump core ring 8r to which the base ends 8be on the side of the rotation axis line O are fixed. The turbine runner 10 includes a turbine shell 10s, a plurality of turbine blades 10b radially arranged around the rotation axis line O on the inner surface of the turbine shell 10s, and a turbine core ring 10r to which the base ends 10be on the side of the rotation axis line O of the turbine blades 10b are fixed. A plurality of through-holes 30a, 30b are provided at the part of the pump core ring 8r, sandwiched between the two adjacent pump blades 8b so as to be circumferentially spaced-apart at an interval. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a torque converter that uses a fluid to transmit rotational force.

  2. Description of the Related Art Conventionally, there has been known a torque converter that includes three elements of a pump impeller, a turbine runner, and a stator and amplifies a rotational force (torque) from a power source such as an engine and transmits the amplified torque to an automatic transmission. The torque converter has a fluid that circulates between the pump impeller and the turbine runner, and torque from the power source is transmitted to the automatic transmission by this fluid.

  An example of such a torque converter is shown in FIG. In the figure, when the fluid circulates from the stator 103 to the pump impeller 101 while rotating the turbine runner 102 by the rotation of the pump impeller 101, the stator core ring 103c at the outlet of the stator 103 and the pump core ring 101c partially overlap each other. Therefore, a part of the fluid flowing along the pump core ring 101c is disturbed (separation of fluid).

  As described above, when a part of the fluid is disturbed, the torque capacity of the torque converter transmitted from the power source to the automatic transmission is reduced. For this reason, a torque converter has been proposed that increases or reduces the torque capacity by reducing or suppressing fluid disturbance when flowing from the stator into the pump impeller (see Patent Document 1). This is because the flow path cross-section is formed at the inlet section of the pump impeller so that the flow path cross section is equal to or less than the maximum flow path cross section of the stator, thereby reducing or suppressing the disturbance of the fluid flowing from the stator to the pump impeller (separation). Is reduced).

JP-A-8-21509

  The torque converter as described above is desired to be small because a space for mounting the torque converter in a vehicle is limited. Therefore, it is preferable that the torque converter be formed so that the thickness in the direction of the rotation axis located at the center thereof is reduced. An index representing the shape of such a torque converter is an aspect ratio. As shown in FIG. 16, the flatness is such that the dimension in the direction perpendicular to the rotation axis O of the torque converter 100 is H and the rotation axis O is parallel to the cross section of the flow path constituted by the pump impeller 101 and the turbine runner 102. The dimension in a simple direction is defined as W / H where W is a dimension. Therefore, the smaller the flatness ratio is, the smaller the thickness of the torque converter in the direction of the rotation axis is.

  However, in the torque converter shown in FIG. 16, if the flatness is 0.65 or less, for example, the pump shell 101s and the pump blade 101b constituting the pump impeller 101 are greatly bent, and it is difficult to prevent fluid separation. become. Therefore, even if the flow path reduction portion 103c is formed as in Patent Document 1, it is difficult to increase the torque capacity.

  It is an object of the present invention to provide a torque converter that can reduce the separation of fluid and increase the torque capacity even if the flatness is reduced.

  The present invention provides a torque converter that transmits a rotational force input to a pump impeller to the turbine runner using a fluid circulating between the pump impeller and the turbine runner as a transmission medium. A formed pump shell, a plurality of pump blades arranged radially around the rotation axis of the pump impeller on the inner surface of the pump shell, and a pump core in which a proximal end portion on the rotation axis side of the pump blade is fixed A turbine shell formed in a bowl shape, a plurality of turbine blades radially disposed around an axis of rotation of the turbine runner on an inner surface of the turbine shell, and the turbine blade And a turbine core ring to which the base end portion on the rotation axis side is fixed. A plurality of through-holes are formed in the pump core ring or the turbine core ring in at least one of the pump core ring part sandwiched between the turbine cores or the turbine core ring part sandwiched between two adjacent turbine blades. It is characterized by being provided at intervals in the circumferential direction.

  According to the present invention, the pump blade rotates about the rotation axis of the pump impeller by the rotational force input to the pump impeller. At this time, the pressure of the fluid increases near the pressure side (positive pressure side) surface (hereinafter referred to as pressure surface) of the pump blade, and near the suction side (negative pressure side) surface (hereinafter referred to as suction surface) of the pump blade. Then, the pressure of the fluid decreases.

  Here, it is a part of the pump core ring sandwiched between two adjacent pump blades, and when a plurality of through holes are provided in the pump core ring at intervals in the circumferential direction, The fluid sandwiched between the pump blades flows into the turbine coring side of the pump coring from the through hole provided near the pressure surface, and the fluid on the turbine coring side of the pump coring is provided near the suction surface. It flows from the through hole to the pump blade side of the pump core ring. Therefore, compared with the case where there is no through hole, the pressure difference of the fluid between the vicinity of the through hole near the pressure surface of the pump blade and the vicinity of the through hole near the suction surface becomes small. Thereby, since the disturbance of the fluid caused by the pressure difference of the fluid is reduced or suppressed, the torque capacity is increased.

  Alternatively, a portion of the turbine core ring sandwiched between two adjacent turbine blades, and when a plurality of through holes are provided in the turbine core ring at intervals in the circumferential direction, a plurality of through holes are provided in the pump blade. Similar to the case where the holes are provided, the fluid pressure difference between the vicinity of the through hole near the pressure surface of the turbine blade and the vicinity of the through hole near the suction surface is smaller than in the case where the through hole is not provided. Thereby, since the disturbance of the fluid caused by the pressure difference of the fluid is reduced or suppressed, the torque capacity is increased.

  Further, a plurality of through holes may be provided in both a pump core ring portion sandwiched between two adjacent pump blades and a turbine core ring portion sandwiched between two adjacent turbine blades. In that case, the pressure difference of the fluid between the vicinity of the through hole near the pressure surface of the pump blade and the vicinity of the through hole near the suction surface is reduced, and the vicinity of the through hole near the pressure surface of the turbine blade and the penetration near the suction surface The pressure difference between the fluid and the vicinity of the hole is reduced. Therefore, the fluid turbulence generated in the pump impeller and the fluid turbulence generated in the turbine runner are alleviated or suppressed. Therefore, the torque capacity increases as compared with the case where the through-hole is provided only in the pump coring or the case where the through-hole is provided only in the turbine coring.

  The pump impeller and the turbine runner are arranged so that the pump core ring and the turbine core ring face each other, and a stator having a plurality of radially extending stator blades is provided between the pump impeller and the turbine runner, and the stator blade It is preferable that a stator core ring is provided between the pump core ring and the turbine core ring. The stator core ring is connected in a ring shape and extends to a position corresponding to the through hole.

  According to this, when a plurality of through holes are provided at intervals in the circumferential direction in the portion of the pump core ring sandwiched between two adjacent pump blades, the through holes close to the pressure surface from between the pump blades. The fluid flowing into the inner periphery of the pump core ring through the hole is guided to the through hole near the suction surface under the influence of the stator core ring extending to the position corresponding to the through hole, and penetrates near the suction surface. It flows from the hole between the pump blades. Therefore, the flow of fluid from the pressure side to the suction side is promoted, and the fluid pressure difference between the vicinity of the through hole near the pressure surface of the turbine blade and the vicinity of the through hole near the suction surface is reduced, and fluid disturbance is alleviated. Or suppressed. Therefore, the torque capacity is further increased as compared with the case where the stator core ring is not provided between the pump core ring and the turbine core ring.

  In addition, when a plurality of through holes are provided in the turbine core ring portion sandwiched between two adjacent turbine runners at intervals in the circumferential direction, the through holes near the pressure surface are interposed between the turbine blades. The fluid flowing into the inner peripheral side of the turbine core ring is guided to the through hole near the suction surface under the influence of the stator core ring, and flows between the turbine blades through the through hole near the suction surface. Therefore, as in the case where a plurality of through holes are formed in the pump core ring, the fluid turbulence is mitigated or suppressed, and compared with the case where the stator core ring is not provided between the pump core ring and the turbine core ring. Thus, the torque capacity further increases.

  The stator core ring is preferably provided with a recess facing the through hole. According to this, the fluid that has flowed into the inner peripheral side of the pump core ring through the through hole near the pressure surface provided between the pump blades is affected by the recess provided in the stator core ring and is close to the suction surface. It is guided by the through-hole of this and flows into between pump blades from the through-hole near the suction surface. Therefore, the flow of fluid from the pressure side to the suction side is promoted, the pressure difference between the fluid near the through hole near the pressure surface and the fluid near the suction surface is reduced, and fluid turbulence is reduced or suppressed. The Therefore, the torque capacity is further increased as compared with the case where the stator core ring not provided with the recess facing the through hole is provided between the pump core ring and the turbine core ring.

  Further, when a plurality of through holes are provided at intervals in the circumferential direction in a portion of the turbine core ring sandwiched between two adjacent turbine runners, the penetration near the pressure surface provided between the turbine blades. The fluid that has flowed into the inner peripheral side of the turbine coring through the hole is guided to the through hole near the suction surface due to the influence of the recess provided in the stator coring blade, and the turbine blade from the through hole near the suction surface Flows in between. Therefore, similarly to the case where a plurality of through holes are formed in the pump core ring, the disturbance of the fluid is mitigated or suppressed, and the stator core ring not provided with the recess facing the through hole is formed between the pump core ring and the turbine core ring. Compared with the case where it is provided in between, the torque capacity further increases.

  Moreover, it is preferable that the through hole is provided on the outer peripheral side of the pump core ring. According to this, since the fluid flows from the inner peripheral side of the pump impeller to the outer peripheral side when the pump impeller rotates, the pressure of the fluid increases on the outer peripheral side of the pump impeller. For this reason, the difference between the pressure of the fluid in the through hole provided near the pressure surface and the pressure of the fluid in the through hole provided near the suction surface is increased, and the fluid flows from the pressure side to the suction side. Promoted. Therefore, the difference in fluid pressure between the vicinity of the through hole near the pressure surface and the vicinity of the through hole near the suction surface is reduced, and the turbulence of the fluid is reduced or suppressed, so that the torque capacity is further increased.

  Moreover, it is preferable that the through hole is provided on the inner peripheral side of the turbine core ring. According to this, since the fluid flows from the outer peripheral side of the turbine runner to the inner peripheral side when the turbine runner rotates, the fluid pressure increases on the inner peripheral side of the turbine runner. For this reason, the difference between the pressure of the fluid in the through hole provided near the pressure surface and the pressure of the fluid in the through hole provided near the suction surface is increased, and the fluid flows from the pressure side to the suction side. Promoted. Therefore, the difference in fluid pressure between the vicinity of the through hole near the pressure surface and the vicinity of the through hole near the suction surface is reduced, and the turbulence of the fluid is reduced or suppressed, so that the torque capacity is further increased.

Sectional drawing of the torque converter of 1st Embodiment. FIG. 2 is a cross-sectional perspective view of a pump impeller along the line II-II in FIG. 1. FIG. 3 is a partial cross-sectional view of a pump impeller along line III-III in FIG. 1. The graph which shows the torque converter characteristic of 1st Embodiment. Sectional drawing of the torque converter of 2nd Embodiment. FIG. 6 is a cross-sectional perspective view of the turbine runner along line VI-VI in FIG. 5. Sectional drawing of the torque converter of 3rd Embodiment. The partial side view of the stator of 3rd Embodiment. FIG. 8 is a partial cross-sectional view of the pump impeller and the stator along the line IX-IX in FIG. 7. The graph which shows the torque converter characteristic of 3rd Embodiment. Sectional drawing of the torque converter of 4th Embodiment. The partial side view of the stator of 4th Embodiment. FIG. 12 is a partial cross-sectional view of the pump impeller and the stator, showing a cross-section XIII-XIII in FIG. (A) is a fragmentary sectional view of the pump impeller of 5th Embodiment, (b) is a fragmentary sectional view of the turbine runner of 6th Embodiment. Sectional drawing of the pump impeller of 5th Embodiment. Sectional drawing of the tor converter of a prior art.

[First Embodiment]
The torque converter 2 according to the present invention is configured as shown in FIG. The torque converter 2 is in the vicinity of an annular pump impeller 8 attached to a flywheel 6 connected to a drive shaft 4 (engine crankshaft) to which engine output is transmitted, and an annular fluid discharge port of the pump impeller 8. An annular turbine runner 10 having an annular fluid inlet arranged and coupled to a speed change mechanism, and a stator 12 for deflecting the flow of fluid returning from the turbine runner 10 to the pump impeller 8 are provided.

  The pump impeller 8 includes a pump shell 8s formed in a bowl shape, a plurality of pump blades 8b arranged radially around the rotation axis O of the drive shaft 4 on the inner surface of the pump shell 8s, and a rotation axis of the pump blade 8b. A pump core ring 8r is provided that has a base end 8be on the O side fixed at intervals along the circumference. The pump impeller 8 is formed in an annular shape and rotates along the rotation axis O. An outer peripheral end of the pump impeller 8 is attached to a converter cover 14 connected to the drive shaft 4. The inner peripheral end of the pump impeller 8 is fixed to the pump hub 15.

  An output shaft 16 is disposed in the pump hub 15 so as to be rotatable about the rotation axis O.

  The turbine runner 10 includes a turbine shell 10s formed in a bowl shape, a plurality of turbine blades 10b arranged radially around the rotation axis O on the inner surface of the turbine shell 10s, and a base on the rotation axis O side of the turbine blade 10b. And a turbine core ring 10r having ends fixed at intervals along the circumference.

  The stator 12 is disposed so as to be sandwiched between the pump impeller 8 and the turbine runner 10. The stator 12 includes a plurality of stator blades 12b extending radially around the rotation axis O, an annular stator core ring 12c that fixes the outer peripheral side of each stator blade 12b, and a stator that fixes the inner peripheral side of each stator blade 12b. And a ring 12r. The stator 12 is supported via a fixed shaft 17 and a one-way clutch 18 that are non-rotatably supported by a housing (not shown).

  The converter cover 14 is formed in a disk shape, and its outer peripheral end 14a is formed so as to protrude toward the pump impeller 8 side. A plurality of nuts 19 a are fixed to the outer surface of the torque converter cover 14 along the circumferential direction. The bolt 19b attached to the flywheel 6 is screwed into the nut 19a, and the flywheel 6 and the converter cover 14 are connected.

  The one-way clutch 18 includes an inner ring 18i that is spline-fitted to the fixed shaft 17, an outer ring 18o that is disposed around the inner ring 18i, and an engagement body 18c that is provided between the inner ring 18i and the outer ring 18o. Yes.

  Next, the fluid circulating between the pump impeller 8 and the turbine runner 10 will be described. The fluid that circulates between the pump impeller 8 and the turbine runner 10 includes oil. This oil is supplied into the torque converter 2 through an oil passage 20 from an oil pump (not shown). When the rotation of the engine is transmitted from the converter cover 14 to the pump impeller 8, a flow is generated in the oil in the torque converter 2 by the rotation of the pump impeller 8.

  The turbine runner 10 generates torque by the flow of oil, and the generated torque is transmitted to the transmission mechanism via the clutch hub 22 and the output shaft 16. During this operation, the stator 12 functions to change the oil flow and amplify the torque transmitted from the pump impeller 8 to the turbine runner 10. Therefore, the fluid, which is oil, corresponds to a torque transmission medium that circulates between the pump impeller 8 and the turbine runner 10.

  Next, the configuration of the pump impeller that is a characteristic configuration of the first embodiment of the present invention will be described with reference to FIGS. 1 and 2. The two through holes 30a and 30b are portions on the outer peripheral side of the pump core ring 8r sandwiched between two adjacent pump blades 8b, and are provided at intervals in the circumferential direction of the pump core ring 8r. Yes. The fluid sandwiched between the two adjacent pump blades 8b, the pump core ring 8r, and the pump shell 8s is a fluid sandwiched between the pump core ring 8r and the turbine core ring 10r through the through holes 30a and 30b. Communicate.

  Next, the operation of the fluid in the vicinity of the through holes 30a and 30b will be described with reference to FIGS. When the output of the engine is transmitted to the pump impeller 8, the pump impeller 8 rotates and the fluid is pushed by the pump blade 8b. Therefore, the fluid pressure increases near the pressure surface 8bp of the pump blade 8b, and the fluid pressure decreases near the suction surface 8bs of the pump blade 8b. At this time, fluid disturbance occurs near the suction surface 8bs of the pump blade 8b, and the torque capacity decreases.

  Since the through holes 30a and 30b are provided in the circumferential direction of the pump core ring 8r, the through hole 30a is close to the pressure surface 8bp of the pump blade 8b, and the through hole 30b is close to the suction surface 8bs of the pump blade 8b. ing. Therefore, the fluid sandwiched between the adjacent pump blades 8b flows into the turbine core ring 10r side of the pump core ring 8r from the through hole 30a, and the fluid on the turbine core ring 10r side of the pump core ring 8r passes through the through hole 30b. It flows into the pump blade 8b side of the pump core ring 8r.

  For this reason, the pressure difference of the fluid becomes small between the pressure surface 8bp and the suction surface 8bs of the pump blade 8b, and the disturbance of the fluid caused by the pressure difference of the fluid is reduced or suppressed.

  The effect of providing the through holes 30a and 30b will be described below with reference to FIG. FIG. 4 shows the torque ratio κ, torque capacity τ and transmission efficiency η with respect to the speed ratio e, the solid line shows the case where the through holes 30a and 30b are provided in the pump core ring 8r, and the dotted line shows the pump core ring 8r. In this case, the through holes 30a and 30b are not provided.

  Here, the speed ratio e is the rotational speed of the output shaft 16 divided by the rotational speed of the input shaft 4, and the torque ratio κ is the torque of the output shaft 16 divided by the torque of the input shaft 4. The torque capacity τ is obtained by dividing the torque of the input shaft 4 by the square of the rotational speed of the input shaft 4, and the transmission efficiency η is obtained by dividing the rotational energy of the output shaft 16 by the rotational energy of the input shaft 4. It is. As is apparent from FIG. 4, when the through holes 30a and 30b are provided in the pump core ring 8r, the torque capacity τ increases in the region where the speed ratio e is about 0 to 0.8. did.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS. The first embodiment differs from the second embodiment only in that the through holes 30a and 30b provided in the pump core ring 8r become the through holes 30a and 30b provided in the turbine core ring 10r. Since the configuration is the same, the same components as those in the first embodiment are denoted by the same reference numerals and the description thereof is omitted.

  The structure of the turbine runner 10 which is a characteristic structure of 2nd Embodiment of this invention is demonstrated. The two through holes 30a and 30b are portions of the turbine core ring 10r sandwiched between two adjacent turbine blades 10b, and are provided at intervals in the circumferential direction on the inner peripheral side of the turbine core ring 10r. ing. The fluid sandwiched between the two adjacent turbine blades 10b, the turbine core ring 10r, and the turbine shell 10s is a fluid sandwiched between the pump core ring 8r and the turbine core ring 10r through the through holes 30a and 30b. Communicate.

  Next, the operation of the fluid in the vicinity of the through holes 30a and 30b will be described. When the output of the engine is transmitted to the pump impeller 8, the pump impeller 8 rotates, and the turbine runner 10 rotates due to the influence of the fluid flowing by this rotation. Therefore, the fluid is pushed by the turbine blade 10b, the pressure of the fluid increases near the pressure surface 10bp of the turbine blade 10b, and the pressure of the fluid decreases near the suction surface 10bs of the turbine blade 10b. At this time, fluid disturbance occurs near the suction surface 10bs of the turbine blade 10b, and the torque capacity decreases.

  Since the through holes 30a and 30b are provided in the circumferential direction of the turbine core ring 10r, the through hole 30a is close to the pressure surface 10bp of the turbine blade 10b, and the through hole 30b is close to the suction surface 10bs of the turbine blade 10b. ing. Therefore, the fluid sandwiched between the adjacent turbine blades 10b flows into the pump core ring 8r side of the turbine core ring 10r from the through hole 30a, and the fluid on the pump core ring 8r side of the turbine core ring 10r passes through the through hole 30b. It flows into the turbine blade 10b side of the turbine core ring 10r.

  For this reason, the pressure difference of the fluid is reduced between the pressure surface 10bp and the suction surface 10bs of the turbine blade 10b, and the disturbance of the fluid caused by the pressure difference of the fluid is reduced or suppressed.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS. In the first embodiment and the third embodiment, the stator core ring 12c extends to the outer peripheral side of the pump impeller 8, and is between the pump core ring 8r and the turbine core ring 10r, and in the through holes 30a and 30b. The only difference is that it extends to the corresponding position, and the other components are the same. Therefore, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  The configuration of the stator 12 that is a characteristic configuration of the third embodiment of the present invention will be described. The stator 12 includes a plurality of stator blades 12b extending radially around the rotation axis O, an annular stator core ring 12c that fixes the outer peripheral side of each stator blade 12b, and a stator that fixes the inner peripheral side of each stator blade 12b. And a ring 12r. An inner ring portion 12d having a width corresponding to the width of the stator blade 12b is formed on the inner peripheral side of the stator core ring 12c, and is fixed to each stator blade 12b.

  The outer peripheral side of the stator core ring 12c is between the pump core ring 8r and the turbine core ring 10r, extends to the outer peripheral side of the pump core ring 8r and the turbine core ring 10r, and corresponds to the through holes 30a and 30b. It extends to. Therefore, the stator core ring 12c is provided between the pump core ring 8r and the turbine core ring 10r.

  Next, the operation of the fluid in the vicinity of the through holes 30a and 30b will be described. When the pump impeller 8 rotates, the fluid is pushed by the pump blade 8b, the fluid pressure increases near the pressure surface 8bp of the pump blade 8b, and the fluid pressure decreases near the suction surface 8bs of the pump blade 8b. At this time, fluid disturbance occurs near the suction surface 8bs of the pump blade 8b, and the torque capacity decreases.

  The fluid sandwiched between the adjacent pump blades 8b flows into the turbine core ring 10r side of the pump core ring 8r from the through hole 30a. This fluid flows into the through hole 30b under the influence of the stator core ring 12c. Then, the fluid on the turbine core ring 10r side of the pump core ring 8r flows into the pump blade 8b side of the pump core ring 8r from the through hole 30b.

  For this reason, the pressure difference of the fluid becomes small between the pressure surface 8bp and the suction surface 8bs of the pump blade 8b, and the disturbance of the fluid caused by the pressure difference of the fluid is reduced or suppressed.

  The effect obtained by providing the stator core ring 12r between the pump core ring 8r and the turbine core ring 10r will be described below with reference to FIG. FIG. 10 represents the torque ratio κ, torque capacity τ, and transmission efficiency η with respect to the speed ratio e, and the solid line represents the case where the stator core ring 12c is provided between the pump core ring 8r and the turbine core ring 10r. A dotted line represents a case where the stator core ring 12c is not provided between the pump core ring 8r and the turbine core ring 10r.

  In this case, when the stator core ring 12c is provided between the pump core ring 8r and the turbine core ring 10r, the torque capacity τ may increase in the region where the speed ratio e is about 0 to 0.8. found.

[Fourth Embodiment]
Next, 4th Embodiment of this invention is described based on FIGS. The third embodiment is different from the fourth embodiment only in that the recess 12o is provided in the stator core ring 12c, and the other components are the same, and therefore the same components as those in the third embodiment. Are denoted by the same reference numerals, and description thereof is omitted.

  The structure of the stator 12 which is a characteristic structure of 4th Embodiment of this invention is demonstrated. The stator core ring 12c is provided with a recess 12o so as to face the through holes 30a and 30b provided in the pump core ring 8r. The concave portion 12o is formed in a semicircular shape, and an arc-shaped end portion and a linear end portion are opposed to the respective through holes 30a and 30b.

  Next, the operation of the fluid in the vicinity of the through holes 30a and 30b will be described. When the pump impeller 8 rotates, the fluid is pushed by the pump blade 8b, the fluid pressure increases near the pressure surface 8bp of the pump blade 8b, and the fluid pressure decreases near the suction surface 8bs of the pump blade 8b. At this time, fluid disturbance occurs near the suction surface 8bs of the pump blade 8b, and the torque capacity decreases.

  The fluid sandwiched between the adjacent pump blades 8b flows into the turbine core ring 10r side of the pump core ring 8r from the through hole 30a. Since this fluid is affected by the recess 12o of the stator core ring 12c, the flow direction is easily directed toward the through hole 30b. Then, more fluid on the turbine core ring 10r side of the pump core ring 8r flows into the pump blade 8b side of the pump core ring 8r from the through hole 30b.

  For this reason, the pressure difference of the fluid can be further reduced between the pressure surface 8bp and the suction surface 8bs of the pump blade 8b, and the disturbance of the fluid caused by the pressure difference of the fluid can be reduced or suppressed.

[Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIGS. The first embodiment and the fifth embodiment are different only in that there are three through holes 30 provided in the pump core ring 8r, and the other configurations are the same. The same components as those in the embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  The structure of the pump impeller 8 which is a characteristic structure of 5th Embodiment of this invention is demonstrated. The through holes 30a and 30b are portions of the pump core ring 8r sandwiched between two adjacent pump blades 8b, and are provided in the outer peripheral direction of the pump core ring 8r. The through hole 30c is a portion of the pump core ring 8r sandwiched between two adjacent pump blades 8b, and is provided in the inner peripheral direction of the pump core ring 8r.

  Next, the operation of the fluid in the vicinity of the through holes 30a, 30b, and 30c will be described. When the engine output is transmitted to the pump impeller 8, the pump impeller 8 rotates. Therefore, the fluid is pushed by the pump blade 8b, the fluid pressure increases near the pressure surface 8bp of the pump blade 8b, and the fluid pressure decreases near the suction surface 8bs of the pump blade 8b. In the pump core ring 8r, the fluid pressure increases on the outer peripheral side, and the fluid pressure decreases on the inner peripheral side. Therefore, the fluid pressure increases in the vicinity of the through hole 30a, and the fluid pressure decreases in the order in the vicinity of the through holes 30b and 30c.

  The fluid sandwiched between the adjacent pump blades 8b flows into the turbine core ring 10r side of the pump core ring 8r from the through hole 30a. Further, the fluid on the turbine core ring 10r side of the pump core ring 8r flows into the pump blade 8b side of the pump core ring 8r from the respective through holes 30b and 30c. Therefore, compared with the case where two through holes 30 are provided, the fluid flowing from the pump core ring 8r to the pump blade 8b side of the pump core ring 8r increases from the turbine core ring 10r side of the pump core ring 8r. The pressure difference of the fluid between the pressure surface 8bp and the suction surface 8bs is further reduced. Therefore, the fluid turbulence caused by the fluid pressure difference is reduced or suppressed.

[Sixth Embodiment]
Next, a sixth embodiment of the present invention will be described with reference to FIG. In the fifth embodiment and the sixth embodiment, the through holes 30a to 30c provided in the pump core ring 8r are provided in the turbine core ring 10r, and the through holes 30a and 30b are provided in the turbine core ring 10r. The other difference is that the through hole 30c is provided on the outer peripheral side, and the other components are the same. Therefore, the same components as those in the fifth embodiment are denoted by the same reference numerals and Description is omitted.

  The structure of the turbine runner 10 which is a characteristic structure of 6th Embodiment of this invention is demonstrated. Each through hole 30a, 30b is a portion of the turbine core ring 10r sandwiched between two adjacent turbine blades 10b, and is provided in the inner circumferential direction of the turbine core ring 10r. Further, the through hole 30c is a portion of the turbine core ring 10r sandwiched between two adjacent turbine blades 10b, and is provided in the outer peripheral direction of the turbine core ring 10r.

  Next, the operation of the fluid in the vicinity of the through holes 30a, 30b, and 30c will be described. When the output of the engine is transmitted to the pump impeller 8, the pump impeller 8 rotates, and the turbine runner 10 rotates due to the influence of the fluid flowing by this rotation. Therefore, the fluid is pushed by the turbine blade 10b, the pressure of the fluid increases near the pressure surface 10bp of the turbine blade 10b, and the pressure of the fluid decreases near the suction surface 10bs of the turbine blade 10b. Further, in the turbine coring 10r, the fluid pressure increases on the inner peripheral side, and the fluid pressure decreases on the outer peripheral side. Therefore, the fluid pressure increases in the vicinity of the through hole 30a, and the fluid pressure decreases in the order in the vicinity of the through holes 30b and 30c.

  The fluid sandwiched between the adjacent turbine blades 10b flows from the through hole 30a to the pump core ring 8r side of the turbine core ring 10r. Further, the fluid on the pump core ring 8r side of the turbine core ring 10r flows into the turbine blade 10b side of the turbine core ring 10r from the through holes 30b and 30c. Therefore, compared with the case where two through holes 30 are provided, the fluid flowing from the turbine core ring 10r to the turbine blade 10b side of the turbine core ring 10r increases from the pump core ring 8r side of the turbine core ring 10r. The pressure difference of the fluid between the pressure surface 10bp and the suction surface 10bs is further reduced. Therefore, the fluid turbulence caused by the fluid pressure difference is reduced or suppressed.

[Modification]
In addition, this invention is not limited only to embodiment mentioned above. For example, in the first embodiment, the through holes 30a and 30b are provided on the outer peripheral side of the pump core ring 8r, but one through hole 30b may be provided on the inner peripheral side of the pump core ring 8r. In this case, the through hole 30a is provided near the pressure surface 8bp, and the through hole 30b is provided near the suction surface 8bs. By doing so, the difference between the pressure of the fluid in the vicinity of the through hole 30a and the pressure of the fluid in the vicinity of the through hole 30b is further increased, and the fluid flowing into each of the through holes 30a and 30b is increased. Fluid turbulence caused by the fluid pressure difference is further mitigated or suppressed.

  In the second embodiment, the through holes 30a and 30b are provided on the inner peripheral side of the turbine core ring 10r. However, one through hole 30b may be provided on the outer peripheral side of the turbine core ring 10r. In this case, the through hole 30a is provided near the pressure surface 10bp, and the through hole 30b is provided near the suction surface 10bs. By doing so, the difference between the pressure of the fluid in the vicinity of the through hole 30a and the pressure of the fluid in the vicinity of the through hole 30b is further increased, and the fluid flowing into each of the through holes 30a and 30b is increased. Fluid turbulence caused by the fluid pressure difference is further mitigated or suppressed.

  In the third embodiment, the through holes 30a and 30b are provided in the pump core ring 8r. However, even if the through holes 30a and 30b are provided in the turbine core ring 10r, the pump core The same effect as when the through holes 30a and 30b are provided in the ring 8r can be obtained.

  Further, the shape of the recess 12o provided in the stator core ring is not limited to the semicircular shape shown in the fourth embodiment, and may be another shape. For example, in the fourth embodiment, the arc portion of the semicircular recess 12o faces the outer peripheral side, but the arc portion may face the inner peripheral side. Further, the recess 12o is not limited to a semicircular shape, and may be a circular shape.

[Effect of the embodiment]
As described above, according to the torque converters according to these embodiments, when the through holes 30a and 30b are provided in the circumferential direction of the pump core ring 8r, the vicinity of the through hole 30a of the pressure surface 8bp of the pump blade 8b. And the pressure difference of the fluid between the vicinity of the through hole 30b of the suction surface 8bs becomes small. For this reason, the fluid turbulence caused by the fluid pressure difference is alleviated or suppressed, and the torque capacity is increased.

  Further, when each through hole 30a, 30b is provided in the circumferential direction of the turbine core ring 10r, the pressure difference of fluid between the vicinity of the through hole 30a of the pressure surface 10bp of the turbine blade 10b and the vicinity of the through hole 30b of the suction surface 10bs Becomes smaller. For this reason, the fluid turbulence caused by the fluid pressure difference is alleviated or suppressed, and the torque capacity is increased.

  DESCRIPTION OF SYMBOLS 2 ... Torque converter, 8 ... Pump impeller, 8b ... Pump blade, 8be, 10be ... Base end part, 8r ... Pump coring, 8s ... Pump shell, 10 ... Turbine runner, 10b ... Turbine blade, 10r ... Turbine coring, 10s: Turbine shell, 30a, 30b: Through holes.

Claims (5)

In the torque converter that transmits the rotational force input to the pump impeller to the turbine runner using the fluid circulating between the pump impeller and the turbine runner as a transmission medium,
The pump impeller includes a pump shell formed in a bowl shape, a plurality of pump blades arranged radially around the rotation axis of the pump impeller on the inner surface of the pump shell, and the pump blade on the rotation axis side of the pump blade A pump core ring with a fixed base end,
The turbine runner includes a turbine shell formed in a bowl shape, a plurality of turbine blades arranged radially around the rotation axis of the turbine runner on an inner surface of the turbine shell, and the turbine blade on the rotation axis side of the turbine blade A turbine core ring with a fixed base end,
At least one of the portion of the pump coring sandwiched between two adjacent pump blades or the portion of the turbine coring sandwiched between two adjacent turbine blades, the pump coring or the turbine coring A torque converter characterized in that a plurality of through holes are provided at intervals in the circumferential direction. A stator having a plurality of stator blades extending radially between the pump impeller and the turbine runner;
The stator core ring is provided between the pump core ring and the turbine core ring, the stator core ring being connected to the outer periphery of the stator blade in an annular shape and extending to a position corresponding to the through hole. 1. The torque converter according to 1.   The torque converter according to claim 2, wherein the stator core ring is provided with a recess facing the through hole.   The torque converter according to claim 1, wherein the through hole is provided on an outer peripheral side of the pump core ring.   The torque converter according to claim 1, wherein the through hole is provided on an inner peripheral side of the turbine core ring.

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