CN116592108A - Torque converter for vehicle - Google Patents

Abstract

The present invention relates to a torque converter in which a cover hub is integrally coupled to a front center of the cover to minimize or eliminate an axial load applied to an engine side by the cover, and an annular thrust washer is provided between the cover hub and an output member in an axial direction. The output member has a first oil circulation hole, the cover hub has a second oil circulation hole, and the thrust washer has a guide groove communicating the first oil circulation hole and the second oil circulation hole. The front surface of the cover hub engages the rear surface of the front cover. The second oil circulation hole is provided with an axial oil hole and a radial oil hole connected with the axial oil hole, and the diameter of the radial oil hole is larger than that of the axial oil hole or is in a gap shape. A part of the circumference of the radial oil hole is opened to the front surface of the cover hub, and a center angle (A1) corresponding to the opened circumference part is smaller than a center angle (A2) corresponding to the unopened circumference part.

Description

Torque converter for vehicle

Technical Field

The present invention relates to a torque converter for a vehicle, and in particular, to a torque converter that minimizes or eliminates axial load of a cover on an engine side.

Background

Typically, a torque converter may be installed between an engine and a transmission of a vehicle, and utilizes fluid to transfer driving force of the engine to the transmission. Such a torque converter may be a fluid transmission mechanism that transmits driving force from an engine to a transmission by increasing the driving force.

The torque converter has an annulus that transfers rotational input to output through a fluid coupling. The annulus includes an impeller, a turbine, and a reactor supported by a fixed end through a one-way clutch. As power is transferred through the force of the fluid (ATF; automatic transmission fluid), torque converter Slip (Slip) will occur and power losses will inevitably occur.

To compensate for this and improve the power transmission efficiency, a Lock-Up Clutch (Lock-Up Clutch) is applied to the torque converter. The torque converter directly connects the input and output to recover the power transmission losses through the fluid coupling.

Also, the torque converter has a torsion Damper (Torsional Damper) so that the shock can be reduced when directly connected. The input of the engine has fluctuations in torque, so that a torsional damper and/or a pendulum (pendulum) can also be provided in the power transmission system via the lockup clutch.

The lockup clutch applied to such a torque converter includes a Single-sided clutch (Single-clutch) to which one piece of friction material is applied, and a multiple-sided clutch (Multi-clutch) composed of two or more pieces of friction material and a clutch assembly.

Typically, in the case of multiple facets, the clutch assembly is located in the cyclic pressure region of the lockup clutch.

Referring to fig. 1, the output member 60 of the torque converter 1 is disposed rearward of the cover hub 13, and the output member 60 and the cover hub 13 have a first oil circulation hole 63 and a second oil circulation hole 135 to guide the flow of oil for cooling the clutch assembly 33. However, since the cover hub 13 is disposed to be axially spaced from the output member 60, the pressure of the oil flowing in the space between the cover hub 13 and the output member 60 applies pressure to the rear surface of the cover hub 13 in the forward direction. Accordingly, the cap hub 13 and the cap 10 receive a thrust load in the axial forward direction. This phenomenon causes a large thrust load between the engine and the torque converter 1, and causes deformation of the cover 10. Therefore, the strength can be ensured only by manufacturing the cover 10 using a higher strength material, or by manufacturing the cover 10 thicker, which results in an increase in the manufacturing cost of the cover and an increase in the weight of the torque converter 1.

In the second oil circulation hole 135 of the cover hub 13 shown in fig. 1, the radial oil hole 1353 has a smaller flow cross-sectional area than the axial oil hole 1351, and thus oil cannot smoothly flow.

Disclosure of Invention

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 in which a thrust load applied to a cover hub of the torque converter in an axial direction is minimized or eliminated so that a lockup clutch is positively operated, and a material selection and a design for improving the strength of the cover are not required.

Further, another object of the present invention is to provide a torque converter in which oil can smoothly flow through an oil circulation hole provided in a cover hub.

The technical problems to be solved by the present invention are not limited to the above-mentioned objects, and other objects and advantages of the present invention, which are not mentioned, can be understood by the following description, or can be more clearly understood by the embodiments of the present invention. Moreover, it is apparent that the objects and advantages of the invention can be realized by the means set forth in the appended claims and combinations thereof.

In order to solve the above problems, a torque converter for a vehicle according to the present invention includes: a cover receiving a rotational force of the engine from the front; a ring surface disposed in the cover and connected to the rear part of the cover; a lock-up clutch disposed inside the cover and connected to a front portion of the cover; and an output member connected to the annular surface and connected to the lockup clutch, and configured to transmit a rotational force to the transmission in a rearward direction.

The cover may include a front cover and a rear cover.

The lockup clutch may be provided in the front cover.

The annular surface may be provided on the rear cover.

A cover hub is integrally coupled to the center of the front cover.

The end of the back cover may be connected to the pump input.

The output member may be disposed rearward of the cover hub.

The torus may include: an impeller disposed on the rear cover; a turbine arranged in front of the impeller; and a reactor disposed between the impeller and the turbine.

The turbine may be provided on a turbine plate. The turbine plate may be connected to the output member.

The reactor can be arranged at the fixed end through a one-way clutch.

The fixed end may be disposed axially between the output member and the rear cover.

A first bearing may be provided between the rear cover and the reactor, and a second bearing may be provided between the reactor and the output member.

The lockup clutch may be connected to the output member through a torsional damper.

The torsion damper may be configured such that the first torsion damper is connected in series with the second torsion damper.

The lockup clutch may include a clutch assembly.

One side of the clutch assembly may be coupled to an input drum provided at the front cover.

The other side of the clutch assembly may be connected to an output drum provided in the torsional damper.

The input drum may be disposed radially inward of the clutch assembly, and the output drum may be disposed radially outward of the clutch assembly.

A piston plate for pressing or releasing the clutch assembly may be disposed at the rear of the clutch assembly.

The radially inner end of the piston plate is slidably disposed on the outer peripheral surface of the cover hub.

A cylinder plate may be provided behind the piston plate.

The radially inner end of the cylinder plate may be fixed to the cover hub.

The radially outer end of the cylinder plate is slidably connected to the radially outer end of the piston plate.

The space between the piston plate and the cylinder plate may form a fluid (oil) filled working chamber to move the piston plate in a direction to press the clutch assembly.

The cover hub may be provided with a piston oil hole to supply oil to the working chamber.

The piston oil hole may be in a form extending in a radial direction.

The oil supplied to the radially inner side of the cap hub may be supplied to the working chamber through the piston oil hole.

The front end of the output member may be opposed to the inner peripheral surface of the cover hub on the radially inner side than the inner peripheral surface of the cover hub. A seal ring may be provided between an inner circumferential surface of the cap hub and an outer circumferential surface of the output member facing the cap hub in a radial direction, so as to prevent leakage of oil supplied to the working chamber through a space between the output member and the cap hub.

The torsional damper may be connected to the output member through a space between the cylinder plate and the turbine plate.

An annular thrust washer may be axially disposed between the cover hub and the output member.

The thrust washer may be in contact with a rear surface of the cover hub and with a front surface of the output member. Therefore, the seal ring can be omitted.

The output member has a first oil circulation hole for guiding an oil flow rearward of the output member toward a forward of the output member.

The cover hub has a second oil circulation hole, and the oil flowing forward of the output member through the first oil circulation hole is introduced.

The thrust washer has a guide groove communicating the first oil circulation hole and the second oil circulation hole. Therefore, the fluid flowing through the first oil circulation hole may be supplied to the second oil circulation hole without leaking elsewhere.

The thrust washer may include: an inner wheel; an outer ring located radially outwardly of the inner ring and spaced apart from the inner ring; and a connecting member extending in a radial direction and connecting the inner wheel and the outer wheel.

The guide groove is defined by the inner wheel, the outer wheel and the connecting member.

The outer and inner rings may not block the second oil circulation hole exposed to the rear of the cover hub and the first oil circulation hole exposed to the front of the output member.

Therefore, the inner peripheral surface of the outer ring is disposed radially outward of the second oil hole exposed to the rear of the cover hub and the first oil hole exposed to the front of the output member, and the outer peripheral surface of the inner ring is disposed radially inward of the second oil hole exposed to the rear of the cover hub and the first oil hole exposed to the front of the output member.

The guide groove may extend in a circumferential direction by a length greater than or equal to a circumferential width of the connection member. The thrust washer is assembled to the cover hub and rotates relative to the output member. According to circumstances, the thrust washer may be assembled to the output member and relatively rotated with the cover hub. Therefore, the connecting member may block the first oil circulation hole and/or the second oil circulation hole. The circumferential width of the connecting member may affect the flow of oil and may affect the thrust load applied to the cap hub by the oil. Therefore, the width of the connecting member is preferably optimized in consideration of smoothness of oil flow within a range allowed for securing rigidity of the thrust washer.

At least one side of the rear surface of the cover hub or the front surface of the output member may be provided with an annular groove that axially accommodates a portion of the thrust washer. And, the thrust washer may be received in the annular groove with its axes aligned.

The first oil circulation hole may extend in an axial direction. The first circulating oil extends in a radially outward direction and is inclined more and more in the axial direction. Therefore, the flow of oil can be made smoother by centrifugal force.

The second oil circulation hole may have an axial oil hole extending forward from a rear direction of the cover hub and a radial oil hole connected to a front end portion of the axial oil hole and extending radially outward.

The second oil circulation hole may be provided at a position not overlapping the piston oil hole in a circumferential direction.

In particular, the axial oil hole may be provided at a position not overlapping the piston oil hole in the circumferential direction.

The axial oil hole may be inclined radially outward as it extends in a direction parallel to the axial direction or as it extends from the rear to the front.

If the first oil circulation hole is inclined, the oil smoothly flows even if the axial oil hole extends parallel to the axial extension.

In one example, the diameter of the radial oil hole may be equal to the diameter of the axial oil hole.

In another example, the diameter of the radial oil hole may be larger than the diameter of the axial oil hole. Therefore, in the radial oil hole, the flow of oil may become smoother.

In one example, the radial oil hole may have a flow cross-sectional area smaller than or equal to a flow cross-sectional area of the axial oil hole.

In another example, the radial oil hole may have a larger flow cross-sectional area than the axial oil hole. Therefore, in the above-described radial oil hole, the flow of oil may become smoother.

A part of the circumference of the radial oil hole may be opened to the front surface of the cover hub. Therefore, the processing of the radial oil hole can be made easier.

The center C of the radial oil hole may be offset rearward from the front surface of the cover hub. Therefore, the oil pressure acting on the front cover can be minimized.

In the circumference of the radial oil hole, a width of a circumferential portion opened to the front surface of the cover hub may be smaller than a diameter of the radial oil hole. Therefore, the oil pressure acting on the front cover can be minimized.

In the circumference of the radial oil hole, a center angle A1 corresponding to a circumferential portion opened to the front surface of the cover hub may be smaller than a center angle A2 corresponding to an unopened circumferential portion. Therefore, the oil pressure acting on the front cover can be minimized.

In the circumference of the radial oil hole, a width of a circumferential portion opened to the front surface of the cap hub may be smaller than a diameter of the axial oil hole. Therefore, the oil pressure acting on the front cover can be minimized.

The front surface of the cover hub may be closely adhered to the rear surface of the front portion of the cover.

The radially inner corner portion of the front surface of the cover hub may be welded to the cover.

The welding may be laser welding.

The welding may be metal inert gas (MIG, metal inert gas Welding).

The plurality of axial oil holes may be arranged adjacent to each other in the circumferential direction and formed in groups.

The radial oil holes may be formed in a slit shape formed in a circumferential direction so as to communicate with the group of the axial oil holes.

The axial oil holes are provided with a plurality of groups, and one radial oil hole can be communicated with a plurality of groups of the axial oil holes. Of course, according to this structure, the radial oil hole and the piston oil hole may be disposed at non-overlapping positions in the axial direction.

The slit may be formed 360 degrees in the circumferential direction. Of course, according to this structure, the radial oil hole and the piston oil hole may be disposed at non-overlapping positions in the axial direction.

According to the present invention, the area where the oil pressure existing behind the cover hub applies pressure to the front of the cover hub can be minimized by placing the thrust washer in the gap between the cover hub and the output member. Therefore, malfunction of the lock-up clutch can be prevented by preventing deformation of the cover hub and the cover.

According to the present invention, not only can the oil flowing through the oil circulation hole provided in the cover hub smoothly flow, but also the oil flowing from the axial oil hole to the radial oil hole can change the flow direction and cancel the pressure applied to the cover in the forward direction, thereby preventing the cover from being deformed.

According to the present invention, the thrust force of the circulating oil applied to the cover hub and the cover can be reduced by the thrust washer and the oil circulating hole, and thus, the selection and design for improving the strength of the cover are not required. Therefore, the manufacturing cost can be reduced and the dead weight of the torque converter can be reduced.

In addition to the above effects, specific effects of the present invention will be described together in the process for carrying out specific matters of the following invention.

Drawings

Fig. 1 is a cross-sectional view schematically showing a torque converter for a vehicle.

Fig. 2 is a cross-sectional view schematically showing a vehicular torque converter of the embodiment.

Fig. 3 is a perspective view of a cover hub of the torque converter of fig. 2 viewed from the front.

Fig. 4 is a perspective view of a thrust washer of the torque converter of fig. 2.

Fig. 5 is a perspective view of an output member of the torque converter of fig. 2.

Fig. 6 is a rear perspective view showing a state in which a thrust washer is mounted on a cover hub of the torque converter of fig. 2.

Fig. 7 is an expanded view of a connection portion between a cover hub and a front cover of the torque converter for a vehicle of the embodiment as viewed in the radial direction.

Fig. 8 is an expanded view of a connection portion between a cover hub and a front cover of a torque converter for a vehicle according to a modification.

Description of the reference numerals

1: torque converter 10: cover 11: front cover

13: cover hub 131: annular groove 1311: inner peripheral wall

1313: outer peripheral wall 133: joint surface 135: second oil circulation hole

1351: axial oil hole 1353: radial oil hole 137: piston oil hole

15: rear cover 151: pump input 20: annular surface

21: impeller 23: turbine 231: turbine plate

25: reactor 27: one-way clutch 29: fixed end

30: lockup clutch 31: input drum 33: clutch assembly

35: output drum 41: piston plate 43: cylinder plate

45: working chamber 50: torsional damper 51: first torsional damper

52: a second torsional damper 60: damping hub (output component)

61: flange 611: rivet hole 63: first oil circulation hole

65: sealing ring B1: first bearing B2: second bearing

70: thrust washer 71: outer wheel 73: inner wheel

75: the connecting member 77: guide groove We: welding part

A1, A2: center angle

Detailed Description

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

The present invention is not limited to the embodiments disclosed below, and can be implemented in various forms with various modifications. This embodiment is provided only for completeness of the disclosure of the present invention and to fully understand the scope of the present invention by those of ordinary skill in the art. Therefore, it is to be understood that the invention is not limited to the embodiments disclosed below, which include not only the mutual replacement or addition between the structure of one embodiment and the structure of another embodiment, but also all modifications, equivalent technical solutions and alternative technical solutions within the technical spirit and scope of the present invention.

The drawings are only for the convenience of understanding the embodiments disclosed in the present specification, and the technical ideas disclosed in the present specification are not limited to the drawings, but should be understood to include all modifications, equivalents, and alternatives falling within the spirit and technical scope of the present invention. In the drawings, the size or thickness of the structural elements may be enlarged or reduced for easy understanding, and the scope of the present invention should not be construed as being limited.

The terminology used in the description presented herein is for the purpose of describing particular examples or embodiments only and is not intended to be limiting of the invention. Also, unless the context clearly indicates otherwise, singular expressions include plural expressions. In the present specification, terms such as "comprising" and "consisting of" mean that the feature, number, step, operation, structural element, component, or combination thereof described in the present specification is present. That is, in the description, it should be understood that the terms "comprises" and "comprising," and the like, do not preclude the presence or addition of one or more other features, numbers, steps, operations, structural elements, components, or groups thereof.

Terms including ordinal numbers such as first, second, etc., may be used to describe various structural elements, but the structural elements are not limited to the above terms. The above terms are used only to distinguish between two structural elements.

When a structural element is referred to as being "connected" or "coupled" to another structural element, it can be directly connected or coupled to the other structural element, but it should be understood that other structural elements may be present in the middle. Conversely, when a structural element is referred to as being "directly connected" or "directly coupled" to another structural element, it should be understood that there are no other structural elements in between.

When referring to a structural element as being "on" or "under" another structural element, it is to be understood that other structural elements may be present in the middle as well as directly above the other structural element.

Unless defined otherwise, all terms used herein, including technical or scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The meaning of terms defined in commonly used dictionaries is the same as in the context of the relevant art and should not be interpreted in an idealized or overly formal sense unless expressly so defined herein.

Since the torque converter of the embodiment is symmetrical with respect to the axis, only half is shown based on the axis for ease of drawing. For convenience of explanation, a direction along a longitudinal direction of a shaft forming a rotation center of the torque converter will be referred to as an axial direction. That is, the front-rear direction or the axial direction is a direction parallel to the rotation shaft, the front (front side) means a direction of the power source, that is, a direction toward the engine side, and the rear (rear side) means another direction, that is, a direction toward the transmission. Thus, the front surface (front) refers to the front-facing surface, and the rear surface (rear) refers to the rear-facing surface.

The radial direction or radial direction means a direction approaching the center or a direction separating from the center along a straight line passing through the center of the rotation axis on a plane perpendicular to the rotation axis. The direction away from the center in the radial direction is referred to as the centrifugal direction, and the direction toward the center is referred to as the centripetal direction.

The circumferential or circumferential direction refers to a direction around the circumference of the above-described rotation axis. The outer circumference refers to the outer circumference and the inner circumference refers to the inner circumference. Accordingly, the outer peripheral surface refers to a surface facing away from the rotation axis direction, and the inner peripheral surface refers to a surface facing the rotation axis direction.

The circumferential side surface means a surface whose normal line is directed in the circumferential direction.

Hereinafter, a torque converter for a vehicle according to an embodiment of the present invention will be described.

Referring to fig. 2, the torque converter 1 of the embodiment of the invention includes a cover 10 filled with fluid (oil) inside. The cover 10 is rotatable by receiving an input from an engine from the front.

The cover 10 includes: a cover hub 13 disposed in front; a front cover 11 extending radially outward and rearward from the cover hub 13; and a rear cover 15 connected to a rear end of the front cover 11. The rear cover 15 extends rearward from the front cover and radially inward.

The rear cover 15 has a pump inlet end 151 extending rearward at a radially inner end thereof. Accordingly, the rotational force of the cover 10 rotated by receiving the rotational force of the front engine (not shown) is transmitted to the rear oil pump (not shown), and therefore, the transmission oil can be supplied to the inside of the cover.

A torus 20 is connected to the front of the rear cover 15. The torus 20 includes an impeller 21, a turbine 23, and a reactor 25 disposed therebetween.

The impeller 21 is fixed to the inner surface (front surface) of the rear cover. The turbine 23 is disposed in front of the impeller 21 so as to face the impeller 21. The reactor 25 is disposed between the impeller 21 and a radially inner portion of the turbine 23. The reactor 25 is rotatably supported by a fixed end 29 through a one-way clutch 27.

The fixed end 29 is disposed radially inward of the front of the pump input end 151. A first bearing B1 is provided between the reactor 25 and the pump input 151 to support relative rotation therebetween.

A turbine plate 231 supporting the turbine 23 extends radially inward from the turbine 23 and is connected to the output member 60. The output member 60 is connected to the torsional damper 50 described later, and functions as a damper hub. The output member 60 has a flange 61 extending in the radial direction, and the turbine plate 231 and the torsional damper 50 described later are integrally fixed by caulking with a rivet hole 611 (see fig. 5) of the flange 61.

The output member 60 is disposed radially inward of the front of the fixed end 29. The second bearing B2 is interposed between the fixed end 29 and the output member 60 to support relative rotation therebetween.

The output member 60 is disposed radially inward of the rear of the cover hub 13. That is, the torque converter 1 includes, in order from the front to the rear along the rotation center thereof, a cover hub 13, an output member (damper hub) 60, a fixed end 29, and a pump input end 151.

The space between the rear cover 15 and the reactor 25 and the space between the reactor 25 and the output member 60 may provide a passage through which fluid (oil) circulates to cool the fluid coupling of the annulus 20.

The lockup clutch 30 is provided on an inner surface (rear surface) of the front cover 11. In the present embodiment, as the lockup clutch 30, a clutch pack 33 having a multiplate clutch structure is illustrated.

The lockup clutch 30 includes: an input drum 31 integrally connected to the front cover 11 and extending rearward; a clutch assembly 33 connected to the radially outer side of the input drum 31; an output drum 35 connected to the radially outer side of the clutch assembly 33; and a piston plate 41 for pressing or releasing the clutch assembly 33 at the rear of the clutch assembly 33.

The output drum 35 is connected to the output member 60 via a torsional damper 50.

The torsion damper 50 is formed by connecting a first torsion damper 51 and a second torsion damper 52 in series. The torsional damper 50 is disposed axially rearward of the piston plate 41 and forward of the turbine plate 231.

A cylinder plate 43 is disposed axially between the piston plate 41 and the torsional damper 50. The torsional damper 50 may be connected to the output member 60 through a space between the cylinder plate 43 and the turbine plate 231.

The radially inner end of the cylinder plate 43 may be fixed to the outer circumferential surface of the cover hub 13. The radially outer end of the cylinder plate 43 may be in contact with the radially outer end of the piston plate 41.

The radially outer end portion of the piston plate 41 extends in the axial direction, and the inner peripheral surface thereof slidably contacts the outer peripheral surface of the cylinder plate 43. The radially inner end of the piston plate 41 slidably contacts the outer peripheral surface of the cover hub 13. Accordingly, the piston plate 41 is axially slidable with respect to the cover hub 13 and the cylinder plate 43.

The space between the piston plate 41 and the cylinder plate 43 constitutes a working chamber 45. The piston plate 41 applies a pressure corresponding to a difference between a pressure of the fluid filled in the working chamber 45 and an external pressure to the clutch assembly 33.

The cover hub 13 is provided with a piston oil hole 137, and the working chamber 45 communicates with the piston oil hole 137. The piston oil hole 137 extends radially from the inner peripheral surface to the outer peripheral surface of the annular cap hub 13. Referring to fig. 3, in the embodiment, a structure in which two piston oil holes 137 are formed at three positions, respectively, is illustrated.

At least a part of the inner peripheral surface of the cover hub 13 is disposed so as to face the outer peripheral surface of the output member 60. The piston oil hole 137 opened to the inner circumferential surface of the cap hub 13 is opposite to the outer circumferential surface of the output member 60.

The piston oil hole 137, which opens to the outer circumferential surface of the cover hub 13, is disposed axially between the piston plate 41 and the cylinder plate 43. The oil in the space facing the inner circumferential surface of the cap hub 13 flows radially outward through the piston oil hole 137 and fills the working chamber 45.

The front region of the output member 60 faces the inner peripheral surface of the cover hub 13. A seal 65 may be provided between the inner peripheral surface of the cap hub 13 and the outer peripheral surface of the output member 60, rearward of the piston oil hole 137 that opens to the inner peripheral surface of the cap hub 13. The seal 65 prevents oil supplied to the working chamber 45 from leaking through a space between the output member 60 and the cover hub 13.

An annular thrust washer 70 is provided axially between the cover hub 13 and the output member 60.

The thrust washer 70 may be in contact with the rear surface of the cover hub 13 and in contact with the front surface of the output member 60. Thus, the thrust washer 70 may block or prevent oil from flowing in a radial direction through the space between the cover hub 13 and the output member 60. The thrust washer 70 functions as a thrust bearing between the cover hub 13 and the output member 60.

Referring to fig. 4, the thrust washer 70 has a flat annular shape. The thrust washer 70 is formed with a guide groove 77 in the circumferential direction. In the present embodiment, three guide grooves 77 are uniformly arranged in the circumferential direction of the thrust washer 70.

An outer wheel 71 is provided radially outward of the guide groove 77, and an inner wheel is provided radially inward. A connecting member 75 is provided between two adjacent guide grooves 77 in the circumferential direction. The connection member 75 may be formed to extend in a radial direction and connect the inner ring 73 and the outer ring 71.

The connection member 75 may block the first and/or second oil circulation holes 63 and 135 according to circumstances. From this point of view, the longer the length of the guide groove 77 in the circumferential direction is, the smaller the width of the connecting member 75 in the circumferential direction is, the better. The thickness of the connection member 75 may be set to a thickness capable of securing the minimum rigidity required for the thrust washer 70.

Conversely, if the circumferential width of the connecting member 75 becomes smaller, the area of the rear surface of the cover hub 13 exposed to the oil flow path increases. This may cause the oil pressure to press the cover hub 13 forward to increase the thrust load. Therefore, the circumferential width of the connecting member 75 may be set to an optimum value in consideration of ensuring smoothness of oil flow and thrust load applied to the rear surface of the cover hub 13 by the oil.

The outer peripheral surface of the outer ring 71 is circular, and the inner peripheral surface of the inner ring 73 is circular. Accordingly, the thrust washer 70 may be rotated relative to the cover hub 13 or the output member 60.

The outer circumferential surface of the outer wheel 71 is in contact with the cover hub 13 and/or the output member 60, and/or the inner circumferential surface of the inner wheel 73 is in contact with the cover hub 13 and/or the output member 60, whereby the center of the thrust washer 70 can be aligned with respect to the cover hub 13 and/or the output member 60.

An annular groove that accommodates a part of the thrust washer 70 in the axial direction may be provided on at least one side of the rear surface of the cover hub 13 or the front surface of the output member 60. Further, the thrust washer 70 may be received in the annular groove such that its axes are aligned. Specifically, the outer peripheral surface of the outer ring 71 contacts the outer peripheral wall 1313 of the annular groove 131 of the hub 13, and the inner peripheral surface of the inner ring 73 contacts the inner peripheral wall 1311 of the annular groove 131.

Referring to fig. 6, in the present embodiment, an annular groove 131 recessed forward is formed on the rear surface of the cover hub 13, and a part of the thrust washer 70 is accommodated in the annular groove 131 in the axial direction.

Referring to fig. 2 and 5, the output member 60 has a first oil circulation hole 63 to guide the oil flowing rearward of the output member 60 to the front of the output member 60.

The first oil circulation hole 63 may extend forward from the rear and incline outward in the radial direction. A plurality of the first oil circulation holes 63 may be provided at equal intervals along the Zhou Xiangan of the output member 60. In the embodiment, a structure in which 12 first oil circulation holes 63 are arranged at intervals of 30 ° is exemplified.

The output member 60 rotates rapidly, and thus the oil flowing into the first oil circulation hole 63 from the rear of the output member 60 can flow forward more smoothly by centrifugal force.

The front end of the first oil circulation hole 63 is open to the guide groove 77.

The outer and inner rings 71 and 73 do not block the first oil circulation hole 63. That is, the inner peripheral surface of the outer ring 71 is disposed radially outward of the front opening of the first oil hole 63, and the outer peripheral surface of the inner ring 73 is disposed radially inward of the front opening of the first oil hole 63. Therefore, the flow of the oil moving from the rear to the front of the output member 60 through the first oil circulation hole 63 is not hindered.

However, although the connection member 75 may temporarily block a portion of the first oil circulation hole 63 by the relative rotation of the output member 60 and the thrust washer 70, as described above, the circumferential width of the connection member 75 has an optimal size within an allowable range, thereby minimizing the obstruction to the oil flow.

The outer wheel 71 and the inner wheel 73 prevent oil from flowing in a radial direction through the space between the output member 60 and the cover hub 13. Therefore, the oil flowing into the guide groove 77 through the first oil circulation hole 63 does not flow out in the radial direction.

In the above embodiment, the thrust washer 70 has the outer wheel 71, the inner wheel 73, and the connecting member 75 connecting them as one member.

However, the connection member 75 may be omitted from the thrust washer 70, and the outer ring 71 and the inner ring 73 may be used together as separate members to form the thrust washer 70. Even if the connecting member 75 is omitted, the outer ring 71 and the inner ring 73 block a predetermined area of the rear surface of the cover hub 13, thereby reducing an area of the rear surface of the cover hub 13 exposed to a path of oil flow. Accordingly, the thrust load applied to the cover hub 13 forward by the hydraulic pressure can be reduced.

Further, since the outer peripheral surface of the outer ring 71 is in contact with the outer peripheral wall 1313 of the annular groove 131 of the cover hub 13 and the position thereof is limited, and the inner peripheral surface of the inner ring 73 is in contact with the inner peripheral wall 1311 of the annular groove 131 and the position thereof is limited, the inner ring 73 and the outer ring 71 can be assembled to the push washer 70 even if they are used as separate members without the connecting member 75.

As described above, in the case where the thrust washer 70 is applied in two pieces of the outer wheel 71 and the inner wheel 73, an annular guide groove may be formed in the radial direction through the space between the outer wheel 71 and the inner wheel 73.

The cover hub 13 has a second oil circulation hole 135 to allow oil flowing forward of the output member 60 through the first oil circulation hole 63 to flow in. The second oil circulation hole 135 does not intersect the piston oil hole 137. For this, the piston oil hole 137 and the second oil circulation hole 135 are formed at different positions in the circumferential direction.

The second oil circulation hole 135 has a rear opening and is provided on the rear surface of the cover hub 13. The rear opening of the second oil hole 135 faces the guide groove 77.

The outer and inner rings 71 and 73 do not block the second oil circulation hole 135. That is, the inner peripheral surface of the outer ring 71 is disposed radially outward of the rear opening of the second oil hole 135, and the outer peripheral surface of the inner ring 73 is disposed radially inward of the rear opening of the second oil hole 135. Therefore, the oil in the guide groove 77 is not blocked from flowing into the second oil circulation hole 135.

However, although the connection member 75 may temporarily block a portion of the second oil circulation hole 135 by the relative rotation of the cover hub 13 and the thrust washer 70, as described above, the circumferential width of the connection member 75 has an optimal size within an allowable range, thereby minimizing the obstruction to the oil flow.

As a result, the thrust washer 70 communicates the first oil circulation hole 63 with the second oil circulation hole 135. The thrust washer 70 allows the fluid flowing through the first oil circulation hole 63 to flow into the second oil circulation hole 135 without leaking to other places.

The first oil circulation hole 63 may extend in the axial direction. The first oil circulation hole 63 extends in a radially outward direction and gradually inclined toward the axial front. Therefore, the flow of oil can be made smoother by centrifugal force.

The second oil circulation hole 135 may have an axial oil hole 1351 extending forward from the rear of the cover hub 13 and a radial oil hole 1353 connected to the front end of the axial oil hole 1351 and extending radially outward.

The second oil circulation hole 135 is provided at a position not overlapping the piston oil hole 137 in the circumferential direction of the cap hub 13. The piston oil hole 137 is axially provided at the rear of the piston plate 41 to supply oil to the working chamber 45, and the radial oil hole 1353 is axially provided at the front of the piston plate 41 to supply oil to the front space of the piston plate 41. Therefore, in the second oil circulation hole 135, the radial oil hole 1353 is formed so as to easily avoid the piston oil hole 137.

In contrast, the axial oil hole 1351 must extend in the axial direction, and thus, is formed at a different circumferential position from the piston oil hole 137.

The axial oil hole 1351 may be inclined radially outward as it extends in a direction parallel to the axial direction of the torque converter, or as it extends forward from the rear. In the illustrated embodiment, the axial oil holes 1351 are formed in parallel, three axial oil holes 1351 are formed in one group, and the three groups are arranged at intervals of 120 degrees. This position is a position where two piston oil holes 137 form one group and are offset by 60 degrees from a structure in which three groups are arranged at 120 degree intervals.

According to the present invention, the thrust washer 70 interposed between the cover hub 13 and the output member 60 guides the entire oil flowing out of the first oil circulation hole 63 to flow into the second oil circulation hole 135. Accordingly, in the first oil circulation hole 63, the flow pressure of the oil generated by the centrifugal force is directly transmitted to the second oil circulation hole 135. Therefore, if the first oil circulation hole 63 is inclined, oil can smoothly flow through the axial oil hole 1351 extending parallel to the axial direction.

According to an embodiment, the front surface of the cover hub 13 is in contact with the rear surface of the front cover 11, and the corner portion of the lower end portion of the front surface of the cover hub 13 may be welded to the front cover 11 by laser welding, melt electrode inert gas welding, or the like.

The welding of the front cover 11 and the cover hub 13 is performed after the piston oil hole 137 and the second oil circulation hole 135 are formed in the cover hub 13.

The axial oil hole 1351 is parallel to the axial direction, thereby facilitating processing. Further, since the front surface of the cover boss 13 is fixed in close contact with the rear surface of the front cover 11, the axial oil hole 1351 may be formed so as to pass through the front surface of the cover boss 13. This makes it easier to machine the axial oil hole 1351.

Referring to fig. 3, 6, 7 (a) and 7 (b), the radial oil hole 1353 may have a smaller flow cross-sectional area than the axial oil hole 1351.

The diameter of the radial oil holes 1353 may be equal to the diameter of the axial oil holes 1351.

Referring to fig. 3, 6 and 7 (c), the radial oil hole 1353 may have a larger flow cross-sectional area than the axial oil hole 1351.

The diameter of the radial oil holes 1353 may be larger than the diameter of the axial oil holes 1351. Therefore, the flow of oil can be made smoother by increasing the flow cross-sectional area of the radial oil holes 1353.

Also, since the diameter of the radial oil hole 1353 is larger than that of the axial oil hole 1351, the central axes do not intersect during the perforation process of the axial oil hole 1351 and the radial oil hole 1353, and even if there is a slight misalignment, the diameter of the axial oil hole 1351 can be included in the diameter of the radial oil hole 1353, so that the processing error allowance range of the second circulation oil hole 135 can be enlarged.

Referring to fig. 3, 6 and 7, a part of the radial oil hole 1353 may be opened toward the front of the cover hub 13. Alignment of these machining positions becomes easier during machining of the axial oil holes 1351 and the radial oil holes 1353.

As compared with the portion (a) of fig. 7, the center of the radial oil hole 1353 may be offset rearward from the front cover 11 as viewed in the portion (b) of fig. 7. That is, in the circumference of the radial oil hole 1353, the center angle A1 corresponding to the circumferential portion that is open to the front surface of the cover hub 13 is smaller than the center angle A2 corresponding to the non-open circumferential portion.

Accordingly, the width W of the circumferential portion opened to the front surface of the cover hub 13 may be smaller than the diameter of the radial oil hole 1353 in the circumference of the radial oil hole 1353. Therefore, the influence of the oil pressure existing in the radial oil hole 1353 on the front cover 11 can be reduced.

Referring to fig. 7 (b), the diameter of the radial oil hole 1353 is equal to the diameter of the axial oil hole 1351, but the flow cross-sectional area of the radial oil hole 1353 is slightly smaller than the flow cross-sectional area of the axial oil hole 1351. Therefore, it is possible to minimize the reduction in the flow cross-sectional area of the radial oil holes 1353 with respect to the axial oil holes 1351, and to reduce the influence exerted on the front cover 11 by the oil pressure present in the above-described radial oil holes 1353.

Referring to fig. 7 (c), the diameter of the radial oil hole 1353 is made larger than the diameter of the axial oil hole 1351, and the center of the radial oil hole 1353 is offset rearward from the front cover 11, so that the width W of the circumferential portion opened to the front surface of the cover hub 13 can be reduced in the circumference of the radial oil hole 1353.

Accordingly, the radial oil hole 1353 is made larger in flow cross-sectional area than the axial oil hole 1351, and in the circumference of the radial oil hole 1353, the width W of the circumferential portion opened to the front surface of the cap hub 13 may be made smaller than or equal to the diameter of the axial oil hole 1351. Therefore, not only the flow of the oil can be made smoother, but also the influence of the oil pressure existing in the radial oil hole 1353 on the front cover 11 can be reduced.

A plurality (three in the embodiment) of the axial oil holes 1351 may be arranged adjacent to each other in the circumferential direction to form a group.

Referring to fig. 8 (a) and 8 (b), as a modification of the radial oil holes 1353, the radial oil holes 1353 may be formed in a slit shape in the circumferential direction so as to communicate with a group of the axial oil holes. In fig. 8 (a), a structure in which one radial oil hole 1353 communicates with a group of axial oil holes 1351 is illustrated. In part (b) of fig. 8, a structure in which one radial oil hole 1353 communicates with two sets of axial oil holes 1351 is illustrated.

Although not shown, the cover hub 13 may be provided with a plurality of sets of the axial oil holes 1351, and one radial oil hole 1353 may be in communication with all of the plurality of sets of the axial oil holes 1351. This may be a slit pattern in which the radial oil holes 1353 may be formed in the circumferential direction over 360 degrees.

Hereinafter, the operation of the torque converter of the present invention will be described.

When the vehicle is initially driven, the rotational force of the engine is transmitted to the cover 10 in a state where the lockup clutch 30 is released. Accordingly, the pump input end 151 of the cap 10 supplies oil to the inside of the cap 10 by operating the pump. Oil is supplied from the transmission to the space between the output member 60 and the fixed end 29. Accordingly, a part of the oil supplied between the output member 60 and the fixed end 29 wets the one-way clutch 27 and the second bearing by centrifugal force and flows toward the annulus 20 side, and the remaining oil flows into the first oil circulation hole 63.

The oil flowing into the first oil circulation hole 63 flows out into the space between the output member 60 and the cover hub 13, and all of the oil flows into the second oil circulation hole 135 of the cover hub 13 under the guide of the thrust washer 70. Accordingly, the fluid flowing into the second oil circulation hole 135 is supplied to the front space of the piston plate 41 through the axial oil holes 1351 and the radial oil holes 1353.

The oil pressure supplied to the front of the piston plate 41 acts to push the piston plate 41 rearward so as to be away from the clutch assembly 33, and is supplied to the annulus 20 through a space where the clutch assembly 33 and the torsional damper 50 are disposed. The oil returns to the transmission through the space between the pump input 151 and the fixed end 29.

In the process, the rotational force of the cover 10 increases torque through the oil filled in the annulus 20 and is transmitted to the transmission through the output member 60.

When the rotational speed of the turbine 23 approaches the rotational speed of the impeller 21, oil is supplied through a flow path provided radially inward of the output member 60, and such oil is supplied to the working chamber 45 through the piston oil hole 137 of the cap hub 13, thereby moving the piston plate 41 forward. The piston plate 41 presses the clutch assembly 33 to operate the lockup clutch. Then, the rotational force of the engine, which is transmitted to the transmission, is absorbed through the lockup clutch 30 and the torsional damper 50 and directly transmitted to the output member 60.

As described above, the present invention has been described with reference to the drawings as illustrated, but the present invention is not limited to the embodiments and drawings disclosed in the present specification, and various modifications are possible within the scope of the technical idea of the present invention, as will be apparent to those skilled in the art. In addition, even if the operational effects based on the constitution of the present invention are not explicitly described and explained in the process of explaining the embodiments of the present invention, effects predicted by the structure should be recognized.

Claims (17)

1. A torque converter, comprising: a cover (10) that receives the rotational force of the engine from the front; an annular surface (20) disposed inside the cover (10) and connected to the rear part of the cover (10); a lockup clutch (30) disposed inside the cover (10) and connected to the front part of the cover (10); and an output member (60) connected to the annular surface (20), connected to the lockup clutch (30), and transmitting rotational force to the transmission in the rear direction,

The torque converter described above is characterized in that,

a cover hub (13) is integrally connected to the front center of the cover (10),

the output member (60) is disposed behind the cover hub (13),

an annular thrust washer (70) is axially disposed between the cover hub (13) and the output member (60),

the output member (60) has a first oil circulation hole (63) for guiding the oil flow from the rear of the output member (60) to the front of the output member (60),

the cover hub (13) has a second oil circulation hole (135) for allowing oil flowing forward of the output member (60) through the first oil circulation hole (63) to flow in,

the thrust washer (70) has a guide groove (77) that communicates the first oil circulation hole (63) and the second oil circulation hole (135).

2. The torque converter of claim 1, wherein,

the thrust washer (70) includes:

an inner wheel (73);

an outer ring (71) located radially outward of the inner ring (73) and spaced apart from the inner ring (73); and

a connecting member (75) that extends in the radial direction and connects the inner ring (73) and the outer ring (71);

the guide groove (77) is defined by the inner ring (73), the outer ring (71), and the connecting member (75).

3. The torque converter of claim 2, wherein,

The inner peripheral surface of the outer ring (71) is disposed radially outward of the second oil circulation hole (135) exposed to the rear of the cover hub (13) and the first oil circulation hole (63) exposed to the front of the output member (60),

the outer peripheral surface of the inner ring (73) is disposed radially inward of the second oil circulation hole (135) exposed to the rear of the cover hub (13) and the first oil circulation hole (63) exposed to the front of the output member (60).

4. The torque converter according to claim 2, characterized in that the outer ring (71) and the inner ring (73) do not block the second oil circulation hole (135) exposed to the rear of the cover hub (13) and the first oil circulation hole (63) exposed to the front of the output member (60).

5. The torque converter according to claim 2, characterized in that the length of the guide groove (77) extending in the circumferential direction is greater than or equal to the circumferential width of the connecting member (75).

6. The torque converter of claim 1, wherein,

an annular groove (131) for receiving a part of the thrust washer (70) in the axial direction is provided on at least one side of the rear surface of the cover hub (13) or the front surface of the output member (60),

the thrust washer (70) is accommodated in the annular groove (131) such that the axes thereof are aligned.

7. The torque converter of claim 1, wherein,

the second oil circulation hole (135) includes:

an axial oil hole (1351) extending from the rear to the front of the cover hub (13); and

and a radial oil hole (1353) connected to the front end of the axial oil hole (1351) and extending radially outward.

8. The torque converter according to claim 7, wherein the axial oil hole (1351) is inclined radially outward as it extends in a direction parallel to the axial direction or as it extends forward from the rear.

9. The torque converter according to claim 7, characterized in that a diameter of the radial oil hole (1353) is larger than or equal to a diameter of the axial oil hole (1351).

10. The torque converter according to claim 7, characterized in that a part of the circumference of the radial oil hole (1353) is open to the front surface of the cover hub (13).

11. The torque converter according to claim 10, characterized in that, in the circumference of the radial oil hole (1353), a center angle (A1) corresponding to a circumferential portion that is open to the front surface of the cover hub (13) is smaller than a center angle (A2) corresponding to a circumferential portion that is not open.

12. The torque converter according to claim 10, characterized in that a center of the radial oil hole (1353) is offset rearward from a rear surface of a front portion of the cover (10).

13. The torque converter according to claim 10, characterized in that, of the circumferences of the radial oil holes (1353), a width (W) of a circumferential portion that is open to the front surface of the cover hub (13) is smaller than or equal to the diameter of the axial oil hole (1351).

14. The torque converter according to claim 10, characterized in that a front surface of the cover hub (13) is abutted against a rear surface of a front portion of the cover (10).

15. The torque converter according to claim 14, characterized in that a radially inner corner portion of a front surface of the cover hub (13) is welded to the cover (10).

16. The torque converter of claim 7, wherein,

the plurality of axial oil holes (1351) are arranged adjacent to each other in the circumferential direction and are formed in groups,

the radial oil holes (1353) are formed in a slit shape along the circumferential direction so as to communicate with the groups of axial oil holes (1351).

17. The torque converter of claim 16, wherein,

the axial oil holes (1351) are provided with a plurality of groups,

one radial oil hole (1353) communicates with a plurality of groups of the axial oil holes (1351).