CN112049913A - Torque converter - Google Patents
Torque converter Download PDFInfo
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- CN112049913A CN112049913A CN202010391579.4A CN202010391579A CN112049913A CN 112049913 A CN112049913 A CN 112049913A CN 202010391579 A CN202010391579 A CN 202010391579A CN 112049913 A CN112049913 A CN 112049913A
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- output
- input
- damper
- side damper
- torque converter
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/04—Combined pump-turbine units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
- F16H41/30—Details relating to venting, lubrication, cooling, circulation of the cooling medium
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The invention provides a torque converter, which prevents the abrasion of the front end parts of an input side damping sheet and an output side damping sheet of a stop mechanism and restrains the performance reduction of the stop mechanism. The solution of the present invention is a torque converter (100) provided with a lock device (110) that directly couples a torque converter cover (101) provided with a pump impeller (102) and a turbine rotor (104) coupled to an output shaft (107) via a turbine hub (122). The lockup device (110) is provided with an input-side damper plate (111) that is in contact with or separated from a torque converter cover (101) by a clutch mechanism (130), and an output-side damper plate (115) that is disposed opposite to the input-side damper plate (111) with an outer damper spring (113) therebetween. The output side damper plate (115) is assembled to the center damper plate (120) with the inner damper spring (121) interposed therebetween, and the turbine hub (122) is connected to the center damper plate (120).
Description
Technical Field
The present invention relates to a torque converter that uses hydraulic oil to reinforce the driving force from an engine and transmits the driving force to an output shaft side.
Background
Conventionally, in a self-propelled vehicle (so-called AT vehicle) mainly provided with an automatic transmission, a torque converter is provided between an engine and the transmission. The torque converter is a mechanical device that transmits drive force from an engine to an output shaft side while reinforcing the drive force by circulating hydraulic oil between a pump impeller and a turbine rotor disposed to face each other. The torque converter is provided with a damper mechanism including a coil spring for reducing a variation in rotational driving force of the engine (also referred to as "torque variation").
In this case, the damper mechanism may be provided with a stopper mechanism in order to limit input of an excessive load to the coil spring and prevent excessive contraction of the coil spring. For example, patent documents 1 and 2 listed below disclose a stopper mechanism in which outer edge portions of an output-side damper plate (damper plate 94, intermediate plate 23) accommodating a coil spring and an input-side damper plate (friction plate 152, input plate 21) disposed opposite to the output-side damper plate are fitted to each other in a circumferential direction.
Documents of the prior art
Patent document 1: japanese patent laid-open No. 2000-88081
Patent document 2: japanese patent laid-open No. 2001-317610
However, in the stopper mechanisms of the torque converters described in patent documents 1 and 2, respectively, the input-side damper plate is configured to be movable in the axial direction of the output shaft with respect to the output-side damper plate, and therefore, there is a problem that: the respective front end portions of the input-side damper piece and the output-side damper piece constituting the stopper mechanism are worn by sliding contact with each other, and the performance of the stopper mechanism is degraded.
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a torque converter capable of preventing wear of the tip end portions of an input-side damper plate and an output-side damper plate constituting a stopper mechanism, and suppressing a decrease in the performance of the stopper mechanism.
Disclosure of Invention
To achieve the above object, the present invention is characterized by comprising: a torque converter cover body which forms an accommodation space for accommodating working oil, has a pump impeller for flowing the working oil in the accommodation space, and is driven to rotate together with the pump impeller by the driving force of an engine; a turbine rotor disposed opposite to the pump impeller and rotationally driven by a flow of the working oil to rotationally drive the output shaft; a turbine hub integrally connecting the turbine rotor and the output shaft and transmitting a rotational driving force of the turbine rotor to the output shaft; an input-side damper plate which is rotatably provided in the accommodation space by a clutch mechanism that transmits or disconnects a rotational driving force of the torque converter cover and has a disc shape in plan view; an output-side damper plate which is provided rotatably relative to the input-side damper plate and has a disk shape in plan view; a damping spring elastically connecting the input side damping fin and the output side damping fin; and a stopper mechanism formed by outer edge portions of the input-side damper piece and the output-side damper piece, and restricting a relative rotation amount of the input-side damper piece and the output-side damper piece; wherein the stopper mechanism is composed of an input side protrusion and an output side protrusion, which are formed to protrude from outer edge portions of the input side damper blade and the output side damper blade, and are brought into contact with or separated from each other by relative displacement of the input side damper blade and the output side damper blade in a circumferential direction; the input-side damper plate and the output-side damper plate are in direct or indirect contact with the turbine hub, and are restricted from moving in the axial direction of the output shaft.
According to the feature of the present invention configured as described above, since the input-side damper plate and the output-side damper plate of the torque converter, which are provided with the stopper mechanism, are respectively coupled to the turbine hub and the movement of the torque converter in the axial direction of the output shaft is respectively restricted, it is possible to prevent the wear of the input-side protruding portion and the output-side protruding portion that constitute the stopper mechanism and to suppress the performance degradation of the stopper mechanism; the stopper mechanism is formed at the front end of each of the input-side damper plate and the output-side damper plate.
In the torque converter, the input-side projecting portion and the output-side projecting portion are formed to project convexly from the outer edge portions of the input-side damper plate and the output-side damper plate, respectively.
According to another feature of the present invention configured as described above, since the input-side projecting portion and the output-side projecting portion are formed to project from the outer edge portions of the input-side damper plate and the output-side damper plate, respectively, the torque converter can be configured in an efficient layout as described below: the input side protruding portion and the output side protruding portion are respectively arranged in the concave portion, and the concave portion is the input side protruding portion and the output side protruding portion which are adjacent to each other and protrude convexly.
In the torque converter, the input-side damper plate and the output-side damper plate are provided on the opposite side of the turbine rotor from the pump impeller, and the stopper mechanism is provided on the turbine rotor side of the damper spring.
According to another feature of the present invention configured as described above, since the stopper mechanism is provided on the turbine rotor side with respect to the damper spring, the working oil flowing out from the pump impeller and the turbine rotor can flow in quickly and smoothly, and the stopper mechanism can be lubricated quickly.
In the torque converter, a portion of the input-side damper blade that is located inward of the outer edge portion is bent toward the turbine rotor and opens toward the turbine rotor, and the torque converter further includes a spring accommodating portion that accommodates the damper spring.
According to another feature of the present invention configured as described above, the torque converter includes the spring housing portion for housing the damper spring by bending the portion of the input-side damper that is located further inward than the outer edge portion toward the turbine rotor and opening the turbine rotor side, so that the working oil that flows out from the pump impeller and the turbine rotor can flow into the spring housing portion quickly and smoothly, the spring housing portion and the damper spring can be lubricated quickly, and vibration due to intermittent expansion and contraction of the damper spring can be suppressed.
In the torque converter, the output side protrusion is disposed opposite to the damper spring in the spring housing, and a side surface facing the turbine rotor is formed in a flat shape.
According to another feature of the present invention configured as described above, since the output-side protrusion is disposed to face the damper spring in the spring housing and the side surface facing the turbine rotor is formed in a planar shape, the working oil flowing out from the pump impeller and the turbine rotor is pressed in a planar manner through the planar side surface of the output-side protrusion, and vibration of the output-side protrusion can be suppressed compared to a case where the side surface is formed in a curved surface.
In the torque converter, the input-side damper plate is restricted from moving toward the output-side damper plate in the axial direction of the output shaft by the output-side damper plate.
According to another feature of the present invention configured as described above, since the movement of the input-side damper plate in the axial direction of the output shaft toward the output-side damper plate is restricted by the output-side damper plate, and the output-side damper plate also serves as a component for restricting the movement of the input-side damper plate toward the output-side damper plate, the torque converter can be downsized with a reduced number of components.
Drawings
Fig. 1 is a front view schematically showing the structure of a lock-up device in a torque converter according to the present invention.
Fig. 2 is a sectional view schematically showing the structure of the torque converter including the lock-up device as viewed from the line 2-2 shown in fig. 1.
Fig. 3 is a sectional view schematically showing the structure of the torque converter including the lock-up device as viewed from the line 3-3 shown in fig. 1.
Fig. 4 (a) and (B) show the external appearance of the input-side damper plate in the locking device shown in fig. 1 to 3, respectively, fig. 4 (a) is a front view of the input-side damper plate, and fig. 4 (B) is a cross-sectional view of the input-side damper plate as viewed from the line B-B shown in fig. 4 (a).
Fig. 5 (a) and (B) show the external appearance of the output damper in the lock-up device shown in fig. 1 to 3, respectively, fig. 5 (a) is a front view of the output damper, and fig. 5 (B) is a cross-sectional view of the output damper as viewed from the line B-B shown in fig. 5 (a).
Fig. 6 (a) and (B) show the external appearance of the central damper in the locking device shown in fig. 1 to 3, respectively, fig. 6 (a) is a front view of the central damper, and fig. 6 (B) is a cross-sectional view of the central damper as viewed from the line B-B shown in fig. 6 (a).
Fig. 7 is a front view showing a state where the input-side damper is rotated counterclockwise in the drawing in the locking device shown in fig. 1.
Detailed Description
Hereinafter, an embodiment of a torque converter according to the present invention will be described with reference to the drawings. Fig. 1 is a front view schematically showing the structure of a lock-up device 110 in a torque converter 100 according to the present invention. Fig. 2 is a sectional view schematically showing the structure of the torque converter 100 including the lock-up device 110, as viewed from the 2-2 line shown in fig. 1. Fig. 3 is a sectional view schematically showing the structure of the torque converter 100 including the lock-up device 110, as viewed from the line 3-3 shown in fig. 1. This torque converter 100 is a mechanical device that is provided between an engine and a transmission in an automobile mainly including an automatic transmission (so-called AT vehicle or CVT vehicle) and reinforces the driving force of the engine and transmits the driving force to the transmission.
(constitution of torque converter 100)
The torque converter 100 includes a torque converter cover 101. The torque converter cover 101 is a component rotationally driven by a driving force from an engine of a vehicle, not shown, and is mainly composed of an input-side half body 101a and a pump-side half body 101 b. The input side half body 101a is a component constituting a part of the torque converter cover 101, and is formed in a substantially cup shape in which an outer edge portion of a metallic disk is bent and extended. The input-side half body 101a has a rear surface (right side surface in the figure) to which a crankshaft (not shown) extending from the engine is coupled by a coupling member 101c, and a pump-side half body 101b is coupled to the curved outer edge portion.
The pump side half body 101b is a metal component constituting another part of the torque converter cover 101, and is formed in a cylindrical shape having a substantially cup-shaped portion into which the input side half body 101a is fitted. A pump impeller 102 is provided on an inner wall surface of the pump side half body 101 b.
The pump impeller 102 is an impeller that is rotationally driven integrally with the torque converter cover 101 and transfers working oil, not shown, to the turbine rotor 104, and is radially formed on an inner wall surface of the pump side half body 101 b. Then, the pump side half body 101b is fixedly attached to the input side half body 101a in a fitted state, so that an accommodation space 103 for accommodating the working oil and the pump impeller 102 is formed between the input side half body 101a and the pump side half body 101b, and the pump side half body and the input side half body 101a rotate integrally. In addition to the working oil and the pump impeller 102, the housing space 103 is provided with a turbine rotor 104, a stator 105, a lock device 110, and a clutch mechanism 130.
The turbine rotor 104 is an impeller that rotates by the flow of the working oil caused by the rotational driving of the pump impeller 102, and is provided in a state of facing the pump impeller 102 and being relatively rotatable. More specifically, the turbine rotor 104 is an output shaft 107 extending from a transmission (gear box), not shown, and coupled to a turbine hub 122 via a central damper 120, which will be described later.
The stator 105 is an impeller that rectifies the flow of the working oil that flows back from the turbine rotor 104 and transfers the working oil to the pump impeller 102, and is attached to an output shaft 107 via a one-way clutch 106. The one-way clutch 106 is a component that supports the stator 105 so as to be rotatable only in the same direction as the rotation direction of the turbine rotor 104, and is spline-fitted to the output shaft 107 via a bearing.
The lock device 110 is a mechanical device for directly connecting the pump impeller 102 and the turbine rotor 104 without interposing hydraulic oil therebetween, and includes an input-side damper blade 111. As shown in fig. 4, the input-side damper plate 111 is a component that is rotationally driven by a rotational driving force transmitted from the input-side half body 101a of the torque converter cover 101 through the clutch mechanism 130, and has a planar annular portion and is formed in an annular shape in plan view.
The input-side damper plate 111 has a radially outer portion of an inner edge portion bent toward the clutch mechanism 130 to form a clutch plate holding portion 111a, and a radially inner portion of an outer edge portion bent at a right angle toward the turbine rotor 104 to form a spring accommodating portion 111 b. The clutch plate holding portion 111a is a portion that can displace a driven-side clutch plate 135, which will be described later, in the axial direction of the input-side damper plate 111, and holds a state in which the driven-side clutch plate is rotatable integrally with the input-side damper plate 111, and is formed of an external gear-shaped spline.
The spring housing portion 111b is a portion that houses the outer damper spring 113, and is formed along the circumferential direction of the input-side damper blade 111. The depth of the spring receiving portion 111b is formed to be substantially the same as the outer diameter of the outer damping spring 113. An input-side projecting portion 112 is formed at an outer edge portion of the input-side damper plate 111 constituting the spring housing portion 111 b.
The input-side projecting portion 112 is a portion that restricts relative displacement of the input-side damper plate 111 and the output-side damper plate 115 in the circumferential direction by coming into contact with an output-side projecting portion 116 described later, and is formed to project convexly from the outer edge portion of the input-side damper plate 111 in a direction parallel to the axial direction of the input-side damper plate 111. Thereby, the input side protrusion 112 is formed on the turbine rotor 104 side with respect to the outer damper spring 113 provided in the spring housing 111 b.
A plurality of (6 in the present embodiment) input-side protrusions 112 are formed at regular intervals along the circumferential direction of the input-side damper 111. The protruding amount of the input-side protruding portion 112 is formed to be the same as the thickness of the output-side protruding portion 116, or slightly larger than the thickness.
The outer damper spring 113 is a component that transmits the rotational driving force (torque) transmitted from the engine through the torque converter cover 101 to the output side damper plate 115 while reducing the fluctuation, and is formed of a steel coil spring. The number of the outer damping springs 113 is 6 in the circumferential direction in the spring housing 111b by the spring holder 114.
The spring holder 114 is a metal component that is held in the spring housing portion 111b and presses the outer damper springs 113 together with the rotational drive of the input-side damper plate 111, and has a planar annular portion and is formed in an annular shape in plan view, more specifically, the spring holder 114 has pressing portions 114a that radially protrude at 6 positions on the outer edge portion, and support portions 114b are formed between the pressing portions 114 a.
The pressing portion 114a is a portion that presses one end portion of the outer damper spring 113 in the spring housing portion 111b, and is formed by bending in a U shape. The support portion 114b is a portion that supports the radially inner portion of the outer damper spring 113 disposed in the spring housing portion 111b, and is formed by bending the outer edge portion of the spring holder 114 along the arc shape of the outer damper spring 113.
The spring holder 114 is in a state in which the pressing portions 114a are respectively arranged in the spring housing portion 111b and positioned at positions facing one end portion of each of the 6 outer damper springs 113, and the pressing portions 114a are fixedly attached to the input-side damper plate 111 by rivets 114 c. The spring holder 114 is held in a state where the inner edge portion is inserted between the output side damper 115 and the side disc 117.
The output-side damper plate 115 is a component rotationally driven by the rotational driving force transmitted from the input-side damper plate 111 via the outer damper spring 113 as shown in fig. 5, and is formed of an annular plate-like body. More specifically, the output-side damper sheet 115 has output-side protrusions 116 radially protruding from 6 positions on the outer edge portion thereof, and a pressing portion 115a is formed between each of the output-side protrusions 116. The output side damper sheet 115 has 6 spring openings 115b formed along the circumferential direction at positions radially inward of the output side protrusion 116 and the pressing portion 115 a.
The pressing portion 115a is a portion that presses the other end portion of the outer damper spring 113 in the spring housing portion 111b, and is formed by bending an L-shape of a portion formed by extending a part of the outer edge portion of the output side damper piece 115 radially outward. Thereby, the outer damper spring 113 is accommodated in the spring accommodating portion 111b in a state of being sandwiched by the pressing portion 114a and the pressing portion 115a of the spring holder 114; the pressing portion 114a is disposed on one end side of the outer damping spring, and the pressing portion 115a is disposed on the other end side of the outer damping spring.
The spring opening 115b is a portion that holds the inner damper spring 121 together with the side disc 117 and the center damper 120 described later, and is formed in a substantially rectangular elongated hole shape extending in the circumferential direction of the output side damper 115. In this case, the spring opening 115b is formed such that: the radially inner and outer side portions of the output-side damper 115 are each raised in a curved shape from the disk surface of the output-side damper 115 to hold the inner damper spring 121.
The output side protrusion 116 is a portion that restricts relative displacement of the input side damper blade 111 and the output side damper blade 115 in the circumferential direction by contacting the input side protrusion 112, and is formed in a plate shape that protrudes outward in the radial direction from the outer edge portion of the output side damper blade 115. The output-side protrusions 116 are formed at substantially the center between the 6 output-side protrusions 112 at regular intervals along the circumferential direction of the output-side damper 115.
The protruding amount of the output-side protruding portion 116 is formed by the protruding amount that faces the outer damper spring 113 housed in the spring housing portion 111b and extends to a position facing the outer edge portion of the input-side damper blade 111, and is substantially the same as the outer diameter of the input-side damper blade 111. That is, the output side protrusion 116 is formed extending in a direction perpendicular to the input side protrusion 112. In this case, a side surface 116a of the output side protrusion 116 facing the turbine rotor 104 is formed flat in the radial direction of the output side damper plate 115. The output side protrusion 116 is formed in a fan shape in plan view, with a width that increases from the radially inner side toward the radially outer side of the output side damper sheet 115. The lengths of the output side protrusion 116 and the input side protrusion 112 in the circumferential direction are set in accordance with the amount of relative rotational displacement between the input side damper plate 111 and the output side damper plate 115.
The output-side damper plate 115 is disposed on the turbine rotor 104 side with respect to a center damper plate 120 extending from a turbine hub 122, and is integrally assembled to a side disc 117 disposed on the input-side damper plate 111 side with respect to the center damper plate 120 by rivets 118a and 118 b. In this case, the output-side damper plate 115 is inserted with the inner edge portion thereof rotatably sliding between the one-way clutch 106 and the turbine hub 122, and the radial position thereof is restricted.
The side disc 117 is a component that is integrally assembled to the output side damper plate 115 via the center damper plate 120 and is rotationally driven, and is formed of an annular plate-like body. The side plate 117 has spring openings 117a formed at positions opposite to the spring openings 115b, the spring openings 115b being identical in shape.
The rivet 118a connects the output-side damper 115 and the side disc 117 via the center damper 120 near the outer edge of the side disc 117. On the other hand, the rivet 118b connects the turbine rotor 104 and the side disk 117 via the output-side damper plate 115 and the center damper plate 120 near the inner edge of the side disk 117. That is, the output-side damper 115 and the center damper 120 are rotationally driven integrally with the turbine rotor 104.
Between the output side damper 115 and the side disc 117 integrated with each other by these rivets 118a and 118b, as described above, the inner edge portion of the spring holder 114 is interposed therebetween, and the movement of the spring holder 114 and the input side damper 111 in the axial direction of the output shaft 107 is restricted. The inner damper spring 121 is provided between the output side damper plate 115 and the side disc 117 together with the center damper plate 120.
As shown in fig. 6, the center damper 120 is a component rotationally driven by the rotational driving force of the inner damper spring 121 from the output side damper 115, and is formed of an annular plate-like body. The center damper 120 is integrally fixed to the turbine boss 122 at its inner edge portion, and connects the output side damper 115 and the side disc 117 in a state where the output side damper 115 and the side disc 117 are relatively displaceable in the circumferential direction. Further, spring housing portions 120a protruding radially are formed at 6 positions on the outer edge portion of the central damper piece 120.
The spring housing portion 120a is a through hole for housing the inner damper spring 121, and is formed in a substantially rectangular long hole shape extending in the circumferential direction of the center damper piece 120. The spring housing portion 120a is formed to be curved toward the axial direction side along the circumferential direction of the center damper 120. These spring receiving portions 120a are formed at positions different from the positions where the outer damper springs 113 are arranged in the circumferential direction.
The inner damper spring 121 is a component that transmits the rotational driving force transmitted from the output side damper plate 115 to the center damper plate 120 while reducing the fluctuation, and is formed of a steel coil spring. In the present embodiment, the inner damping spring 121 is configured by overlapping 2 coil springs having different outer diameters by 2 layers, but may be configured by 1 coil spring. The inner damping spring 121 may have a different spring characteristic from the outer damping spring 113, or may have the same spring characteristic. Incidentally, in fig. 3, the inner damping spring 121 is shown by a two-point chain line.
The turbine hub 122 is a metal component that transmits the rotational driving force of the turbine rotor 104 and the central damper 120 to the output shaft 107, and is formed in a flange shape in which a circular plate body protrudes on the outer peripheral surface of a cylindrical body. The turbine boss 122 is formed with an internal gear spline on its inner peripheral portion and spline-fitted to the output shaft 107, and the inner edge portion of the central damper plate 120 is fixed to its outer peripheral portion.
The clutch mechanism 130 is a mechanical device that transmits and disconnects the rotational driving force transmitted from the engine to the torque converter cover 101 to the lock device 110. The clutch mechanism 130 includes a clutch plate holder 131.
The clutch plate holder 131 is a component that accommodates an outer edge portion of a clutch piston 136 (described later) and holds a plurality of (2 in the present embodiment) drive-side clutch plates 132 and stopper plates 133, respectively, and is formed by forming a metal material into a cylindrical shape. The clutch plate holder 131 is configured such that one end (right side in the drawing) is fixedly attached to an inner wall portion of the input-side half body 101a of the torque converter cover 101, and is rotationally driven integrally with the torque converter cover 101.
The clutch plate holder 131 is formed with an internal gear spline on its inner peripheral portion, and the plurality of drive-side clutch plates 132 and 1 of stopper plates 133 are held by this spline in a state displaceable in the axial direction of the clutch plate holder 131 and rotatable integrally with the clutch plate holder 131.
The driving-side clutch plate 132 is a flat annular member that presses a driven-side clutch plate 135, which will be described later, and is formed by annularly punching a thin plate material formed of an SPCC (cold-rolled steel sheet) material. In this case, an external gear-shaped spline described later is formed on the outer peripheral portion of the drive-side clutch plate 132: for fitting a spline formed on the inner peripheral portion of the clutch plate holder 131. The drive-side clutch plates 132 are disposed alternately with respect to the 2 driven-side clutch plates 135 in the clutch plate holder 131.
The stopper piece 133 is a member for sandwiching the driving side clutch plate 132 and the driven side clutch plate 135 with the clutch piston 136, and is formed by forming a metal material into a flat plate ring shape. The stopper piece 133 is disposed on the left side of the driving side clutch plate 132 and the driven side clutch plate 135 in the inner peripheral portion of the clutch plate holder 131, and its movement to the left side in the figure is restricted by a stopper 134 provided at the left end in the figure in the inner peripheral portion.
The driven-side clutch plate 135 is a flat annular member that presses the driving-side clutch plate 132, and is formed by annularly punching a thin plate material made of SPCC (cold-rolled steel plate) material. An internal gear-shaped spline described later is formed on the inner periphery of the driven clutch plate 135: a spline for fitting the clutch plate holding portion 111a formed in the input-side damper plate 111. That is, the clutch plate holding portion 111a constitutes a part of the clutch mechanism 130.
The clutch piston 136 is a metal component described later and is formed in a flange shape in which a circular plate body protrudes on the outer peripheral surface of a cylindrical body: in the clutch plate holder 131, the driving-side clutch plates 132 and the driven-side clutch plates 135 arranged alternately with each other are pressed against each other or separated from each other, thereby bringing the driving-side clutch plates 132 and the driven-side clutch plates 135 into close contact with each other or into separation from each other. The clutch piston 136 is supported by a cylindrical inner peripheral portion via a clutch hub 137 so as to be rotatable relative to the output shaft 107.
A gap S is secured between the clutch piston 136 and the inner wall portion of the input-side half body 101a of the torque converter cover 101, and the hydraulic oil is introduced into the gap S through the clutch hub 137 or flows out from the gap S, thereby moving closer to or away from the driving-side clutch plate 132 and the driven-side clutch plate 135. In this case, the hydraulic oil for operating the clutch piston 136 is supplied under control via the output shaft 107 by a supply device, not shown, provided outside the torque converter 100.
The clutch hub 137 is a component that supports the clutch piston 136 in a relatively rotatable state on the output shaft 107, and is formed by forming a metal material into a cylindrical shape. The clutch hub 137 has an introduction hole for introducing and discharging the hydraulic oil for operating the clutch piston 136 into and from the gap S.
(operation of Torque converter 100)
Next, an operation of the torque converter 100 configured as described above will be described. This torque converter 100 is disposed between an engine and a transmission to function in a so-called AT vehicle or CVT vehicle. Specifically, the torque converter 100 first transmits the rotational driving force of the engine to the torque converter cover 101 by releasing the brake and depressing the accelerator pedal by the driver of the vehicle, and the torque converter cover 101 and the pump impeller 102 are rotationally driven integrally.
Then, the torque converter 100 circulates the working oil in the torque converter 100, and the turbine rotor 104 is rotationally driven. Thereby, the vehicle equipped with the torque converter 100 starts to run by transmitting the rotational driving force of the turbine rotor 104 to the output shaft 107 via the turbine hub 122.
Next, in the torque converter 100, the hydraulic oil is supplied to the gap S between the inner wall portion of the input-side half body 101a of the torque converter cover 101 and the clutch piston 136 by the accelerator operation performed by the driver, and the clutch piston 136 is brought into pressure contact with the driving-side clutch plate 132 and the driven-side clutch plate 135. Accordingly, the input-side damper plate 111 is integrally rotationally driven (in the direction of the dotted arrow in the drawing shown in fig. 7) by being coupled to the torque converter cover 101 by the clutch mechanism 130, and therefore the rotational driving force of the torque converter cover 101 is elastically transmitted to the output-side damper plate 115 via the outer damper spring 113.
The rotational driving force transmitted to the output-side damper 115 is transmitted to the side disc 117 via the rivets 118a and 118b, and is elastically transmitted to the center damper 120 via the inner damper spring 121. Thereby, the output shaft 107 is rotationally driven by the rotational driving force transmitted from the center damper 120 via the turbine boss 122.
That is, the torque converter 100 performs torque transmission via the fluid in the initial stage of increase in the rotational driving force from the engine, and then switches to torque transmission by the mechanical coupling, thereby continuously transmitting the rotational driving force from the engine to the output shaft 107; the torque transmission via the fluid is performed by the hydraulic oil flowing between the pump impeller 102 and the turbine runner 104, and the mechanical coupling is performed by the torque converter cover 101 via the clutch mechanism 130 and the lockup device 110, respectively.
The state of torque transmission in which the torque converter cover 101 is mechanically coupled to the output shaft 107 via the clutch mechanism 130 and the lock-up device 110 is referred to as a locked state. In this case, the lock device 110 transmits the rotational driving force from the engine to the output shaft 107 while reducing the fluctuation included in the rotational driving force by the outer damper spring 113 and the inner damper spring 121.
In this locked state, in the lock device 110, as shown in fig. 7, when the rotational driving force transmitted to the input side damper piece 111 becomes large and the relative rotation of the input side damper piece 111 and the output side damper piece 115 proceeds until the outer side damper spring 113 is in a compressed state near the compression limit, the input side protrusion 112 of the input side damper piece 111 contacts the output side protrusion 116 of the output side damper piece 115. Thereby, the lock device 110 is in a state in which the input-side damper plate 111 and the output-side damper plate 115 are in direct contact and the rotational driving force is transmitted, and prevents the outer damper spring 113 from being excessively compressed and deformed. That is, the input side protrusion 112 and the output side protrusion 116 correspond to the stopper mechanism of the present invention.
In this case, the turbine boss 122 is finally coupled to the input-side damper plate 111 and the output-side damper plate 115 via the components such as the center damper plate 120, and the movement in the axial direction of the output shaft 107 is restricted, so that the abrasion of the input-side projecting portion 112 and the output-side projecting portion 116 can be prevented, and the reduction in the stopping performance can be prevented. Incidentally, in this case, the movement of the input-side damper 111 in the axial direction of the output shaft 107 is restricted by the output-side damper 115 and the side disc 117 via the spring holder 114.
The stopper mechanism including the input-side protrusion 112 and the output-side protrusion 116 is formed on the turbine rotor 104 side with respect to the outer damper spring 113 provided in the spring housing 111 b. That is, the outer damping spring 113 corresponds to the damping spring of the present invention. Thereby, the stopper mechanism ensures smooth operation by the inflow of the working oil (see the dashed arrow in fig. 2) flowing out from between the pump impeller 102 and the turbine rotor 104.
In the locked state, the output side damper plate 115 vibrates due to frequent expansion and contraction of the outer damper spring 113 caused by a variation in the rotational driving force from the engine in the lock device 110. In this case, since the side surface 116a of the output side damper blade 115 facing the output side protrusion 116 of the turbine rotor 104 is formed in a planar shape, the entire side surface 116a is pressed toward the outer damper spring 113 by the hydraulic oil flowing out from between the pump impeller 102 and the turbine rotor 104, and vibration of the output side protrusion 116 can be suppressed.
Further, since the spring housing portion 111b housing the outer damper spring 113 is formed so as to open on the turbine rotor 104 side, a part of the working oil flowing out from between the pump impeller 102 and the turbine rotor 104 flows into the spring housing portion 111b, so that the inside of the spring housing portion 111b and the outer damper spring 113 can be quickly lubricated, and vibration due to intermittent expansion and contraction of the outer damper spring 113 can be suppressed.
On the other hand, in the torque converter 100, when the rotational driving force of the engine is reduced by a deceleration operation such as a brake depression or an accelerator pedal release by a driver of the vehicle, the relative displacement amount in the circumferential direction of the input-side damper plate 111 and the output-side damper plate 115 is reduced, and the relative displacement amount in the circumferential direction of the output-side damper plate 115 and the central damper plate 120 is reduced. In the torque converter 100, the working oil in the gap S between the inner wall surface of the input-side half body 101a of the torque converter cover 101 and the clutch piston 136 flows out, and the clutch piston 136 separates from the driving-side clutch plate 132 and the driven-side clutch plate 135. Thereby, the torque converter 100 is unlocked and shifts to a torque transmission state of the fluid via the working oil flowing between the pump impeller 102 and the turbine rotor 104.
As can be understood from the above description of the operation, according to the above embodiment, since the input-side damper plate 111 and the output-side damper plate 115, which are formed with the stopper mechanism, are coupled to the turbine hub 122, respectively, and the movement in the axial direction of the output shaft 107 is restricted, respectively, the torque converter 100 can prevent the wear of the input-side protruding portion 112 and the output-side protruding portion 116 that constitute the stopper mechanism, and can suppress the performance degradation of the stopper mechanism; the stopper mechanism is formed at the tip end of each of the input-side damper plate 111 and the output-side damper plate 115.
The present invention is not limited to the above embodiments, and various modifications can be made without departing from the object of the present invention. Incidentally, in the description of each modified example, the same reference numerals are given to the same portions as those of the above embodiment.
For example, in the above embodiment, the stopper mechanism formed by the input-side protrusion 112 and the output-side protrusion 116 is formed on the turbine rotor 104 side with respect to the outer damper spring 113. However, the stopper mechanism may be formed on the clutch mechanism 130 side with respect to the outer damping spring 113. In this case, the output side protrusion 116 of the stopper mechanism can be formed at the tip end of the radially inner portion of the outer edge portion of the output side damper plate 115, which is bent toward the clutch mechanism 130. In the stopper mechanism, the input-side projecting portion 112 is formed in a straight shape with or without bending the outer edge portion of the input-side damper blade 111, and is formed at these fold portions.
In the above embodiment, the spring housing portion 111b is formed in a state of opening on the turbine rotor 104 side. However, the spring housing portion 111b may be formed so as to open on the clutch mechanism 130 side. Specifically, the spring housing 111b may be formed inside a bent portion of the output side damper 115, the bent portion being formed by bending a radially inner portion of the outer edge portion toward the clutch mechanism 130.
In the above embodiment, the output side protrusion 116 is formed in a planar shape with the side surface 116a facing the turbine rotor 104. However, the output side protrusion 116 may be formed in a curved surface shape in which a side surface 116a facing the turbine rotor 104 side protrudes convexly toward the turbine rotor 104 side. With this configuration, the output-side protrusion 116 can quickly guide the hydraulic oil flowing out from between the pump impeller 102 and the turbine rotor 104 to the radially outer side or the radially inner side of the output-side damper disk 115.
In the above embodiment, the movement of the input-side damper 111 toward the output-side damper 115 is restricted by the output-side damper 115 disposed opposite to the input-side damper. However, the movement of the input-side damper 111 toward the output-side damper 115 may be restricted by a component other than the output-side damper 115. For example, the input-side damper 111 can be fixed to the side disc 117 to restrict the movement in the axial direction of the output shaft 107; the movement in the axial direction of the output shaft includes the movement toward the output side damper 115.
In the above embodiment, the lock device 110 is configured to include the inner damping spring 121. However, in the lock device 110, when the output-side damper 115 is directly connected to the center damper 120 or the turbine hub 122, the inner damper spring 121 may be omitted.
In the above embodiment, the input-side damper 111 indirectly contacts the turbine boss 122 via a component such as the center damper 120, and the output-side damper 115 directly contacts (slides on) the turbine boss 122, whereby the movement in the axial direction of the output shaft 107 is restricted. That is, the input-side damper disk 111 and the output-side damper disk 115 are such that the input-side damper disk 111 is indirectly restricted from moving in the axial direction of the output shaft 107 by the turbine hub 122, and the output-side damper disk 115 is directly restricted from moving in the axial direction of the output shaft 107 by the turbine hub 122. However, the input-side damper plate 111 and/or the output-side damper plate 115 may be configured to be directly and/or indirectly in contact with or coupled to the turbine boss 122 so as to be restricted from moving in the axial direction of the output shaft 107, and may not be limited to the above-described embodiment.
Description of the reference numerals
Gap between inner wall surface of input side half body of cover body of S torque converter and clutch piston
100 torque converter
101 torque converter cover
101a input side half body
101b pump side half body
101c connecting parts
102 pump impeller
103 accommodating space
104 turbine rotor
105 stator
106 one-way clutch
107 output shaft
110 locking device
111 input side damping fin
111a clutch plate holding part
111b spring housing
112 input-side projection
113 outside damping spring
114 spring support
114a pressing part
114b support part
114c rivet
115 output side damping fin
115a pressing part
115b spring opening
116 protruding from the output side
116a side surface
117 side plate
117a spring opening
118a, 118b rivet
120 central damping fin
120a spring housing
121 inner side damping spring
122 turbine hub
130 clutch mechanism
131 clutch plate holder
132 drive side clutch plate
133 stop tab
134 stop dog
135 driven side clutch plate
136 clutch piston
137 clutch hub
Claims (6)
1. A torque converter is characterized by comprising:
a torque converter cover body that forms an accommodation space for accommodating hydraulic oil, has a pump impeller for flowing the hydraulic oil in the accommodation space, and is rotationally driven together with the pump impeller by a driving force of an engine;
a turbine rotor disposed opposite to the pump impeller and rotationally driven by the flow of the working oil to rotationally drive an output shaft;
a turbine hub that integrally connects the turbine rotor and the output shaft and transmits a rotational driving force of the turbine rotor to the output shaft;
an input-side damper plate that is rotatably provided in the accommodation space through a clutch mechanism that transmits or disconnects a rotational driving force of the torque converter cover and has a disc shape in plan view;
an output-side damper plate which is provided to be rotatable relative to the input-side damper plate and has a disk shape in plan view;
a damping spring elastically connecting the input side damping fin and the output side damping fin; and
a stopper mechanism formed by outer edge portions of the input-side damper piece and the output-side damper piece, and configured to restrict a relative rotation amount of the input-side damper piece and the output-side damper piece;
wherein the stopper mechanism is constituted by an input-side protrusion and an output-side protrusion, which are formed to protrude from outer edge portions of the input-side damper blade and the output-side damper blade, and which are brought into contact with or separated from each other by relative displacement of the input-side damper blade and the output-side damper blade in a circumferential direction;
the input-side damper plate and the output-side damper plate are in direct or indirect contact with the turbine hub, and are each restricted from moving in the axial direction of the output shaft.
2. The torque converter of claim 1,
the input-side projecting portion and the output-side projecting portion are formed to project convexly from the outer edge portions of the input-side damper plate and the output-side damper plate, respectively.
3. The torque converter according to claim 1 or 2,
the input-side damper disk and the output-side damper disk are provided on the opposite side of the turbine rotor to the pump impeller,
the stopper mechanism is provided closer to the turbine rotor than the damper spring.
4. The torque converter according to claim 1 or 2,
the input-side damper blade is bent toward the turbine rotor and opened to the turbine rotor side at a portion inside the outer edge portion, and has a spring housing portion that houses the damper spring.
5. The torque converter of claim 4,
the output side protrusion is disposed opposite to the damper spring in the spring housing, and a side surface facing the turbine rotor side is formed in a planar shape.
6. The torque converter according to claim 1 or 2,
the movement of the input-side damper plate in the axial direction of the output shaft toward the output-side damper plate is restricted by the output-side damper plate.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019-106746 | 2019-06-07 | ||
| JP2019106746A JP2020200859A (en) | 2019-06-07 | 2019-06-07 | Torque converter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112049913A true CN112049913A (en) | 2020-12-08 |
Family
ID=73609100
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010391579.4A Pending CN112049913A (en) | 2019-06-07 | 2020-05-11 | Torque converter |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2020200859A (en) |
| CN (1) | CN112049913A (en) |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2783298B1 (en) * | 1998-09-10 | 2001-02-09 | Valeo | HYDROKINETIC COUPLING APPARATUS WITH COOLING GROOVE |
| JP3924395B2 (en) * | 1999-06-16 | 2007-06-06 | ヴァレオユニシアトランスミッション株式会社 | Torsional vibration damping device |
| JP3961740B2 (en) * | 2000-05-02 | 2007-08-22 | 株式会社エクセディ | Torque converter lockup device |
| DE102006028777A1 (en) * | 2006-06-23 | 2007-12-27 | Daimlerchrysler Ag | Hydrodynamic torque converter, has turbine, and torsion damper with three sheet plates, where extensions protruding via recesses of one sheet plate and turbine deform against each other between turbine sided axial stops and sections |
| JP5210038B2 (en) * | 2008-05-08 | 2013-06-12 | 本田技研工業株式会社 | Damper holding device for fluid transmission device |
| JP2011169419A (en) * | 2010-02-19 | 2011-09-01 | Honda Motor Co Ltd | Torsional damper device |
| US9322463B2 (en) * | 2014-04-25 | 2016-04-26 | Valeo Embrayages | Hydrokinetic torque coupling device with centered lock-up clutch friction disc, and method for assembling the same |
-
2019
- 2019-06-07 JP JP2019106746A patent/JP2020200859A/en active Pending
-
2020
- 2020-05-11 CN CN202010391579.4A patent/CN112049913A/en active Pending
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| Publication number | Publication date |
|---|---|
| JP2020200859A (en) | 2020-12-17 |
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Application publication date: 20201208 |
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