CN111868405A - Clutch lubrication structure - Google Patents
Clutch lubrication structure Download PDFInfo
- Publication number
- CN111868405A CN111868405A CN201980014298.2A CN201980014298A CN111868405A CN 111868405 A CN111868405 A CN 111868405A CN 201980014298 A CN201980014298 A CN 201980014298A CN 111868405 A CN111868405 A CN 111868405A
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- Prior art keywords
- oil
- clutch
- passage
- supply
- hub
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
Abstract
A clutch lubricating structure of a clutch device includes: a radial oil passage extending radially inside the hub; a branch oil passage that branches from the radial oil passage in the hub and extends in a plate arrangement direction of the clutch portion; and a plurality of supply oil passages including a plurality of far-side supply oil passages and a plurality of near-side supply oil passages provided at positions closer to the radial oil passages than the plurality of far-side supply oil passages. The 1 st flow path area of the plurality of far-side supply oil paths is larger than the 2 nd flow path area of the plurality of near-side supply oil paths so that the 1 st oil supply amount supplied from the plurality of far-side supply oil paths and the 2 nd oil supply amount supplied from the plurality of near-side supply oil paths are close to each other.
Description
Technical Field
The present disclosure relates to a clutch lubrication structure, and more particularly, to a lubrication structure of a friction plate of a dual clutch device.
Background
In a general dual clutch device, wet multiple disc clutches are provided in power transmission paths of the two systems, respectively, and lubricating oil is supplied from an oil supply circuit to friction plates of the wet multiple disc clutches (see, for example, patent document 1).
Prior art documents
Patent document
Patent document 1: japanese laid-open patent publication No. 2005-133937
Disclosure of Invention
Technical problem to be solved by the invention
However, if the amount of lubricant supplied to each friction plate of the wet multiple disc clutch varies, the friction material will be unevenly worn in the friction plate with insufficient amount of lubricant.
The disclosed technology provides a clutch lubricating structure that efficiently supplies lubricating oil to each friction plate.
Technical solution for solving technical problem
According to the technique of the present disclosure, a clutch lubrication structure of a clutch device provided with a clutch portion including a plurality of friction plates on a hub rotatable integrally with an input shaft includes: a radial oil passage extending radially within the hub; a branch oil passage that branches from the radial oil passage in the hub and extends in a plate arrangement direction of the clutch portion; and a plurality of supply oil passages including a plurality of far-side supply oil passages and a plurality of near-side supply oil passages provided at positions closer to the radial oil passages than the plurality of far-side supply oil passages. The 1 st flow path area of the plurality of far-side supply oil paths is larger than the 2 nd flow path area of the plurality of near-side supply oil paths so that the 1 st oil supply amount supplied from the plurality of far-side supply oil paths and the 2 nd oil supply amount supplied from the plurality of near-side supply oil paths are close to each other.
In addition, the clutch device may be a dual clutch device provided with a 1 st clutch part and a 2 nd clutch part each including a plurality of friction plates on the hub;
as the branch oil passage, there is a 1 st branch oil passage and a 2 nd branch oil passage, the 1 st branch oil passage branching from the radial oil passage in the hub and extending in the plate arrangement direction of the 1 st clutch portion, the 2 nd branch oil passage branching from the radial oil passage in the hub and extending in the plate arrangement direction of the 2 nd clutch portion;
as the plurality of supply oil passages, there are a plurality of 1 st supply oil passages and a plurality of 2 nd supply oil passages, the 1 st supply oil passage extending from the 1 st branch oil passage to the 1 st clutch portion in the hub and supplying the oil flowing in from the 1 st branch oil passage to the 1 st clutch portion, the second supply oil passage extending from the 2 nd branch oil passage to the 2 nd clutch portion in the hub and supplying the oil flowing in from the 2 nd branch oil passage to the 2 nd clutch portion; the plurality of 1 st supply oil passages and the plurality of 2 nd supply oil passages are respectively provided with the far side supply oil passage and the near side supply oil passage; the 1 st flow path area of the plurality of distal-side supply oil paths is larger than the 2 nd flow path area of the plurality of proximal-side supply oil paths so that the oil supply amount to the 1 st clutch portion and the oil supply amount to the 2 nd clutch portion approach each other.
Further, the 1 st clutch part and the 2 nd clutch part may be arranged in series in the direction of the rotation axis of the hub, and the radial oil passage may be formed in an annular partition wall that partitions a 1 st hydraulic pressure canceller chamber corresponding to the 1 st clutch part and a 2 nd hydraulic pressure canceller chamber corresponding to the 2 nd clutch part.
The flow path area of 1 of the plurality of distal-side supply oil passages may also be formed larger than the flow path area of 1 of the proximal-side supply oil passages. The number of the plurality of distal-side supply oil passages may be larger than the number of the plurality of proximal-side supply oil passages.
Effects of the invention
According to the technique of the present disclosure, the lubricating oil can be efficiently supplied to each friction plate.
Drawings
Fig. 1 is a schematic cross-sectional view of a clutch device including a clutch lubrication structure according to the present embodiment.
Fig. 2 is a schematic view of the guide member of the present embodiment as viewed from the radial direction.
Fig. 3 is a schematic view of the clutch hub of the present embodiment as viewed from the radial direction.
Fig. 4 is a schematic view of other embodiments of the clutch hub as viewed from the radial direction.
Detailed Description
Hereinafter, a clutch lubricating structure according to the present embodiment will be described with reference to the drawings. The same components are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.
Fig. 1 is a schematic cross-sectional view of a clutch device 10 including a clutch lubrication structure according to the present embodiment. As shown in the drawing, the clutch device 10 of the present embodiment is a dual clutch device including a 1 st wet multiple disc clutch C1 and a 2 nd wet multiple disc clutch C2.
Specifically, the clutch device 10 is provided between a crankshaft 11 (input shaft) of the engine E and the 1 st shaft 12A and the 2 nd shaft 12B of the transmission T, and is configured to be able to selectively transmit power of the engine E to the 1 st shaft 12A or the 2 nd shaft 12B. The crankshaft 11, the 1 st shaft 12A, and the 2 nd shaft 12B are coaxially disposed, and the 2 nd shaft 12B is rotatably inserted into a hollow shaft of the 1 st shaft 12A.
The clutch device 10 includes a clutch hub 13 (one example of a hub) that is rotatable integrally with the crankshaft 11. The clutch hub 13 is formed in a substantially cylindrical shape as a whole, and integrally includes an inner annular portion 13A, an inner cylindrical portion 13B, an intermediate annular portion 13C (partition wall portion), an outer cylindrical portion 13D, and an outer annular portion 13E in this order from the rotation axis center side.
The inner annular portion 13A has an inner diameter substantially equal to the outer diameter of the crankshaft 11, and is fitted to the outer peripheral surface of the crankshaft 11 on the output end side by spline or welding. The inner cylindrical portion 13B is provided to extend in the axial direction from the outer circumferential side of the inner annular portion 13A toward the engine E. The inner cylindrical portion 13B is formed with 4 oil introduction ports 90 to 93 and an inlet portion of the radial oil passage 60, which will be described in detail later. A substantially cylindrical support hub 50 is interposed between the inner circumferential surface of the inner cylindrical portion 13B and the outer circumferential surface of the crankshaft 11, and the support hub 50 rotatably supports the inner cylindrical portion 13B and the crankshaft 11. The support hub 50 is provided with oil supply lines 75, 76, 81, 82, 83 described in detail below.
The intermediate annular portion 13C extends radially outward from substantially the center of the inner cylindrical portion 13B in the axial direction, and separates a 1 st centrifugal hydraulic pressure canceller chamber 24 and a 2 nd centrifugal hydraulic pressure canceller chamber 27, which will be described later. A radial oil passage 60, which will be described in detail later, is provided in the intermediate annular portion 13C over substantially the entire length in the radial direction.
The outer cylindrical portion 13D is provided such that an inner cylindrical surface thereof extends substantially parallel to an outer cylindrical surface of the inner cylindrical portion 13B. The outer annular portion 13E is provided to extend radially outward from substantially the center of the outer cylindrical portion 13D in the cylinder axial direction.
A 1 st guide member 37 (an example of a hub) is inserted into the cylinder on the engine E side of the outer cylinder portion 13D so as to be rotatable integrally therewith. Further, a 2 nd guide member 38 (one example of a hub) is inserted into the tube on the transmission T side of the outer cylindrical portion 13D so as to be integrally rotatable. Each of the guide members 37 and 38 is formed in a cylindrical shape having a substantially L-shaped cross section, and has an outer cylindrical surface in contact with the inner circumferential surface of the outer cylindrical portion 13D and a cylindrical end surface in contact with the side surface of the intermediate annular portion 13C. Downstream side flow path portions 63 and 67 of axial oil paths 61 and 65, which will be described in detail later, are recessed in outer peripheral portions of the guide members 37 and 38, respectively.
A substantially annular 1 st cover member 20 is interposed between the inner cylindrical portion 13B and the respective guide members 37 and 38 at the end on the engine E side, and a substantially annular 2 nd cover member 21 is interposed at the end on the transmission T side. That is, the 1 st piston chamber 22 and the 2 nd piston chamber 25 are defined by the outer cylindrical surface of the inner cylindrical portion 13B, the inner cylindrical surfaces of the guide members 37 and 38, both side surfaces of the intermediate annular portion 13C, and the inner side surfaces of the cover members 20 and 21, respectively.
In the 1 st piston chamber 22, a 1 st hydraulic chamber 23 on the 1 st cover member 20 side and a 1 st centrifugal hydraulic pressure canceller chamber 24 on the intermediate annular portion 13C side are defined by a 1 st piston 17 slidably housed in the cylinder axial direction. In the 2 nd piston chamber 25, a 2 nd hydraulic chamber 26 on the 2 nd cover member 21 side and a 2 nd centrifugal hydraulic pressure canceller chamber 27 on the intermediate annular portion 13C side are partitioned by a 2 nd piston 18 slidably housed in the cylinder axis direction.
The working oil is supplied from the oil supply circuit 70 to the 1 st hydraulic chamber 23 and the 2 nd hydraulic chamber 26, and the cancellation oil is supplied from the oil supply circuit 70 to the 1 st centrifugal hydraulic pressure cancellation chamber 24 and the 2 nd centrifugal hydraulic pressure cancellation chamber 27. Details of these oil supply paths will be described later. Further, a 1 st return spring 28 that biases the 1 st piston 17 in a direction away from the intermediate annular portion 13C is housed in the 1 st centrifugal hydraulic pressure canceller chamber 24, and a 2 nd return spring 29 that biases the 2 nd piston 18 in a direction away from the intermediate annular portion 13C is housed in the 2 nd centrifugal hydraulic pressure canceller chamber 27.
The 1 st clutch drum 15 has a substantially bottomed cylindrical shape with the engine E side open, and has a cylindrical inner diameter larger than the clutch hub 13. The 1 st clutch drum 15 is fixed to the outer peripheral surface of the 1 st shaft 12A so that the end portion on the transmission T side is integrally rotatable by spline fitting or the like.
The 2 nd clutch drum 16 is a substantially bottomed cylindrical shape with the engine E side open, and has a cylindrical inner diameter formed larger than the clutch hub 13 and a cylindrical outer diameter formed smaller than the 1 st clutch drum 15. The 2 nd clutch drum 16 is fixed to the outer peripheral surface of the 2 nd shaft 12B by spline fitting or the like so that the end portion on the transmission T side is integrally rotatable.
The 1 st wet multiple disc clutch C1 includes: a plurality of the 1 st partition plates 31; a plurality of 1 st friction plates 32 alternately arranged between the 1 st partition plates 31; and a 1 st pressure contact plate 33 (hereinafter, the 1 st partition plate 31 and the 1 st friction plate 32 are also simply referred to as a 1 st friction plate part 30).
The 1 st partition plate 31 and the 1 st pressure contact plate 33 are spline-fitted to the outer cylindrical surface of the outer cylindrical portion 13D on the engine E side of the outer annular portion 13E of the clutch hub 13, and are attached so as to be movable in the axial direction. The 1 st friction plate 32 is spline-fitted to an inner cylindrical surface of the 1 st clutch drum 15 facing the outer cylindrical portion 13D, and is attached in a movable state in the axial direction. The 1 st pressure contact plate 33 is a substantially annular plate-shaped member, and the 1 st piston 17 is arranged on the engine E side surface thereof so as to be contactably opposed thereto.
The 2 nd wet multiple disc clutch C2 includes: a plurality of 2 nd partition plates 41; a plurality of 2 nd friction plates 42 alternately arranged between the 2 nd partition plates 41; and a 2 nd pressure contact plate 43 (hereinafter, the 2 nd partition plate 41 and the 2 nd friction plate 42 are also simply referred to as a 2 nd friction plate portion 40).
The 2 nd partition plate 41 and the 2 nd pressure contact plate 43 are spline-fitted to the outer cylindrical surface of the outer cylindrical portion 13D on the transmission T side of the outer annular portion 13E of the clutch hub 13, and are attached in a state of being movable in the axial direction. The 2 nd friction plate 42 is spline-fitted to an inner cylindrical surface of the 2 nd clutch drum 16 facing the outer cylindrical portion 13D, and is attached in a movable state in the axial direction. The 2 nd press contact plate 43 is a substantially annular plate-shaped member, and the 2 nd piston 18 is arranged on the transmission T side surface thereof so as to be contactably opposed thereto.
The oil supply circuit 70 includes: an oil filter 72 immersed in oil pan 71; an upstream supply line 73 connected to the oil filter 72; a 1 st downstream supply line 74 branched from the upstream supply line 73; and a 2 nd downstream supply line 80 branched from the upstream supply line 73. An oil pump OP driven by the power of the engine E is provided on the upstream supply line 73.
The 1 st downstream supply line 74 is branched into a 1 st hydraulic oil supply line 75 for supplying hydraulic oil to the 1 st hydraulic chamber 23, and a 2 nd hydraulic oil supply line 76 for supplying hydraulic oil to the 2 nd hydraulic chamber 26. The downstream side of each of the hydraulic oil supply lines 75 and 76 extends in the axial direction inside the support hub 50. Specifically, the downstream end of the 1 st working oil supply line 75 is connected to the 1 st working oil introduction port 90, and the downstream end of the 2 nd working oil supply line 76 is connected to the 2 nd working oil introduction port 91. Further, solenoid valves 77 and 78 capable of switching supply and stop of the hydraulic oil are provided upstream of the hydraulic oil supply lines 75 and 76, respectively.
When the working oil is supplied from the 1 st working oil supply line 75 to the 1 st hydraulic chamber 23 and the oil pressure in the 1 st hydraulic chamber 23 rises, the 1 st piston 17 makes a stroke movement in the axial direction toward the 1 st friction plate 30 side to press the 1 st partition plate 31 and the 1 st friction plate 32 against each other (1 st wet multiple plate clutch C1: engaged). In the pressure contact state, the power of the engine E is transmitted to the 1 st shaft 12A via the crankshaft 11, the clutch hub 13, the 1 st friction plate 30, and the 1 st clutch drum 15.
On the other hand, when the supply of the hydraulic oil to the 1 st hydraulic chamber 23 is stopped and the hydraulic pressure in the 1 st hydraulic chamber 23 decreases, the 1 st piston 17 moves in a direction away from the 1 st friction plate 30 by the biasing force of the 1 st return spring 28, and the pressure-contact state of the 1 st partition plate 31 and the 1 st friction plate 32 is released (the 1 st wet multiple disc clutch C1: OFF).
Similarly, when the working oil is supplied from the 2 nd working oil supply line 76 to the 2 nd hydraulic chamber 26 and the oil pressure in the 2 nd hydraulic chamber 26 rises, the 2 nd piston 18 moves in the axial direction toward the 2 nd friction plate 40 side to press the 2 nd partition plate 41 and the 2 nd friction plate 42 against each other (2 nd wet multiple plate clutch C2: engaged). In the pressure contact state, the power of the engine E is transmitted to the 2 nd shaft 12B via the crankshaft 11, the clutch hub 13, the 2 nd friction plate portion 40, and the 2 nd clutch drum 16.
On the other hand, when the supply of the hydraulic oil to the 2 nd hydraulic chamber 26 is stopped and the hydraulic pressure in the 2 nd hydraulic chamber 26 decreases, the 2 nd piston 18 moves in a direction away from the 2 nd friction plate portion 40 by the biasing force of the 2 nd return spring 29, and the pressure-contact state of the 2 nd partition plate 41 and the 2 nd friction plate 42 is released (the 2 nd wet multiple disc clutch C2: off).
The 2 nd downstream supply line 80 is branched into 3 systems of oil supply lines 81, 82, 83 inside the support hub 50. The 1 st scavenge oil supply line 81 is connected to the 1 st scavenge oil introduction port 92, and the 2 nd scavenge oil supply line 82 is connected to the 2 nd scavenge oil introduction port 93. The lubricating oil supply line 83 is connected to the radial oil passage 60 of the clutch hub 13.
In the present embodiment, the seal rings 51 to 54 are interposed between the support hub 50 and the inner cylindrical portion 13B of the clutch hub 13, and are provided on the outer cylindrical surface of the support hub 50 and slidably contact the inner cylindrical surface of the inner cylindrical portion 13B to prevent oil leakage from the oil passages.
Specifically, the 1 st seal ring 51 is provided on the outer cylindrical surface of the support hub 50 on the engine E side of the 1 st hydraulic oil introduction port 90. The 2 nd seal ring 52 is provided on the outer cylindrical surface of the support hub 50 between the 1 st hydraulic oil introduction port 90 and the 1 st scavenge oil introduction port 92. The 3 rd seal ring 53 is provided on the outer cylindrical surface of the support hub 50 between the 2 nd relief oil introduction port 93 and the 2 nd hydraulic oil introduction port 91. The 4 th seal ring 54 is provided on the outer cylindrical surface of the support hub 50 on the transmission T side of the 2 nd hydraulic oil inlet port 91. That is, in the present embodiment, a total of 4 seal rings 51 to 55 are provided.
The radial oil passage 60 is provided with a plurality of radial oil passages (only 1 in the illustrated example) in the inner cylindrical portion 13B and the intermediate annular portion 13C of the clutch hub 13. Specifically, each radial oil passage 60 extends from the inner cylindrical portion 13B of the clutch hub 13 to the inside of the intermediate annular portion 13C over substantially the entire length in the radial direction. The number of the radial oil passages 60 and the diameter of the flow passage may be set as appropriate in accordance with the axial width of the intermediate annular portion 13C, the discharge capacity of the oil pump OP, and the like, within a range in which the strength of the clutch hub 13 can be secured.
The downstream end of the radial oil passage 60 is branched into a 1 st upstream side flow passage portion 62 of the 1 st axial oil passage 61 (1 st branch oil passage) and a 2 nd upstream side flow passage portion 66 of the 2 nd axial oil passage 65 (2 nd branch oil passage). The 1 st upstream flow path portion 62 extends axially from the radial oil path 60 toward the engine E at the radially outer end of the intermediate annular portion 13C. The 2 nd upstream flow path portion 66 extends axially from the radial oil path 60 to the transmission T side at the radially outer end of the intermediate annular portion 13C.
The 1 st downstream side flow path portion 63 of the 1 st axial oil passage 61 extends in the axial direction along the plate arrangement direction of the 1 st friction plate portion 30 between the 1 st guide member 37 and the outer cylindrical portion 13D. The 2 nd downstream side flow path portion 67 of the 2 nd axial oil passage 65 extends in the axial direction along the plate arrangement direction of the 2 nd friction plate portion 40 between the 2 nd guide member 38 and the outer cylindrical portion 13D.
Specifically, as shown in fig. 2, the 1 st downstream flow path portion 63 is formed by cutting the outer cylindrical surface of the 1 st guide member 37 into a concave shape toward the radially inner side, and extends in the axial direction from the cylindrical end surface 37A on the side of the intermediate annular portion 13C to the vicinity of the cylindrical end surface 37B on the side of the engine E. The 2 nd downstream flow path portion 67 is formed by cutting the outer cylindrical surface of the 2 nd guide member 38 into a concave shape facing radially inward, and extends in the axial direction from the cylindrical end surface 38A on the side of the intermediate annular portion 13C to the vicinity of the cylindrical end surface 38B on the side of the transmission T. The downstream flow path portions 63 and 67 may be provided on the inner cylindrical surface side of the outer cylindrical portion 13D (see fig. 1).
Returning to fig. 1, the outer cylindrical portion 13D of the clutch hub 13 is provided with a plurality of 1 st and 2 nd supply oil passages 68, 69 formed to penetrate radially from the inner cylindrical surface to the outer cylindrical surface thereof. The 1 st supply oil passage 68 communicates the 1 st downstream side flow passage portion 63 of the 1 st axial oil passage 61 with the 1 st friction plate portion 30. The 2 nd supply oil passage 69 communicates the 2 nd downstream side flow passage portion 67 of the 2 nd axial oil passage 65 with the 2 nd friction plate portion 40.
That is, the lubricating oil pumped up from the oil pan 71 by the oil pump OP and fed under pressure is supplied from the upstream supply line 73 to the radial oil passage 60 via the 2 nd downstream supply line 80 and the lubricating oil supply line 83. The lubricating oil introduced into the radial oil passage 60 is supplied in the order of (1) the 1 st axial oil passage 61 → the 1 st supply oil passage 68 → the 1 st friction plate portion 30, and further in the order of (2) the 2 nd axial oil passage 65 → the 2 nd supply oil passage 69 → the 2 nd friction plate portion 40. The lubricating oil supplied to the friction plate portions 30 and 40 is returned to the oil pan 71 via a return line, not shown.
As shown in fig. 3, the supply oil passages 68 and 69 of the present embodiment are formed so that the flow passage diameters thereof become larger as the supply oil passages 68A and 69A are farther from the radial oil passage 60 (the intermediate annular portion 13C) (the flow passage diameters of the supply oil passages 68A and 69A > the flow passage diameters of the supply oil passages 68B and 69B > the flow passage diameters of the supply oil passages 68C and 69C). Namely, the present invention is configured to: the flow path area of the far-side supply oil path is larger than that of the near-side supply oil path provided at a position near the radial oil path, and the amount of oil supplied from the far-side supply oil path is close to that supplied from the near-side supply oil path. Thereby, the structure is as follows: the opening diameters of the supply oil passages 68A, 69A that are separated from the radial oil passage 60 and tend to decrease as the amount of lubricant fed under pressure increases toward the friction plate portions 30, 40 (see fig. 1). This makes it possible to equalize the amount of lubricating oil supplied to the friction plate portions 30 and 40, and to effectively prevent uneven wear of the friction material due to insufficient lubricating oil. Further, the cooling efficiency and durability can be effectively improved by making the amount of lubricating oil uniform in the friction plate portions 30 and 40.
Further, the apparatus is configured to: by making the lubricant oil supply paths to the friction plate portions 30 and 40 in the clutch hub 13 independent from the 1 st centrifugal hydraulic pressure canceller chamber 24 and the 2 nd centrifugal hydraulic pressure canceller chamber 27, the reduction in the cancellation capability of the respective hydraulic pressure canceller chambers 24 and 27 is effectively suppressed. Thus, the return springs 28 and 29 do not need to secure a strong biasing force, and the clutch device 10 can be downsized.
The present disclosure is not limited to the above-described embodiments, and can be implemented by appropriately modifying the embodiments without departing from the scope of the present disclosure.
For example, in the above-described embodiment, the case where the supply oil passages 68, 69 are formed so that the flow path diameters of the supply oil passages 68A, 69A farther from the radial oil passage 60 are larger has been described, but as shown in fig. 4, the supply oil passages 68A to 68C, 69A to 69C may be configured so that the flow path diameters of the respective supply oil passages are substantially the same and the number of the supply oil passages 68A, 69A farther from the radial oil passage 60 is increased.
Further, the case where the downstream side flow path portions 63 and 67 of the axial oil paths 61 and 65 are provided recessed in the outer cylindrical surfaces of the guide members 37 and 38 has been described, but in the case where the guide members 37 and 38 are formed integrally with the clutch hub 13, the axial oil paths 61 and 65 may be provided so as to penetrate the inside of the outer cylindrical portion 13D.
The application of the present embodiment is not limited to the clutch device 10 having the structure in which the 1 st clutch C1 and the 2 nd clutch C2 are arranged in series in the rotation axis direction of the clutch hub 13, but may be applied to a structure in which the 1 st clutch C1 and the 2 nd clutch C2 are arranged in parallel in the radial direction of the clutch hub 13. The application of the present embodiment is not limited to the double clutch device, and may be applied to a single clutch device including only one friction plate portion.
The present application is based on the japanese patent application filed on 20/2/2018 (japanese application 2018-.
Industrial applicability
According to the clutch lubricating structure of the present disclosure, lubricating oil can be efficiently supplied to each friction plate.
Description of the reference numerals
10 clutch device
11 crankshaft (input shaft)
13 Clutch hub (hub)
13A inner ring part
13B inner cylindrical part
13C middle ring part (partition wall)
13D outer cylinder part
13E outer ring part
17 st piston
18 nd 2 nd piston
24 st centrifugal oil pressure eliminating chamber
27 nd 2 centrifugal oil pressure eliminating chamber
C1 No. 1 wet type multiple plate clutch
30 st friction plate part
31 st divider plate
32 st friction plate
37 the 1 st guide member (hub)
38 the 2 nd guide member (hub)
C2 No. 2 wet type multiple plate clutch
40 nd 2 friction plate part
41 nd 2 nd partition plate
42 nd 2 nd friction plate
60 radial oil way
61 st axial oil passage
65 nd 2 axial oil path
68 1 st oil supply passage
69 nd 2 supply oil path
70 oil supply circuit
73 upstream supply line
80 nd 2 downstream supply line
83 lubricating oil supply line
OP oil pump
Claims (5)
1. A clutch lubrication structure of a clutch device provided with a clutch portion including a plurality of friction plates on a hub rotatable integrally with an input shaft, comprising:
A radial oil passage extending radially within the hub,
a branch oil passage that branches from the radial oil passage in the hub and extends in a plate arrangement direction of the clutch portion, and
a plurality of supply oil passages including a plurality of far-side supply oil passages and a plurality of near-side supply oil passages provided at positions closer to the radial oil passages than the plurality of far-side supply oil passages;
the 1 st flow path area of the plurality of far-side supply oil paths is larger than the 2 nd flow path area of the plurality of near-side supply oil paths so that the 1 st oil supply amount supplied from the plurality of far-side supply oil paths and the 2 nd oil supply amount supplied from the plurality of near-side supply oil paths are close to each other.
2. The clutch lubrication configuration of claim 1,
the clutch device is a double clutch device provided with a 1 st clutch part and a 2 nd clutch part which are provided with a plurality of friction plates on the hub;
as the branch oil passage, there is a 1 st branch oil passage and a 2 nd branch oil passage, the 1 st branch oil passage branching from the radial oil passage in the hub and extending in the plate arrangement direction of the 1 st clutch portion, the 2 nd branch oil passage branching from the radial oil passage in the hub and extending in the plate arrangement direction of the 2 nd clutch portion;
As the plurality of oil supply passages, there are a plurality of 1 st oil supply passages and a plurality of 2 nd oil supply passages, the 1 st oil supply passage extending from the 1 st oil branch passage to the 1 st clutch portion in the hub and supplying the oil flowing in from the 1 st oil branch passage to the 1 st clutch portion, the 2 nd oil supply passage extending from the 2 nd oil branch passage to the 2 nd clutch portion in the hub and supplying the oil flowing in from the 2 nd oil branch passage to the 2 nd clutch portion;
the plurality of 1 st supply oil passages and the plurality of 2 nd supply oil passages are respectively provided with the far side supply oil passage and the near side supply oil passage;
the 1 st flow path area of the plurality of distal-side supply oil paths is larger than the 2 nd flow path area of the plurality of proximal-side supply oil paths so that the oil supply amount to the 1 st clutch portion and the oil supply amount to the 2 nd clutch portion approach each other.
3. The clutch lubrication configuration of claim 2,
the 1 st clutch part and the 2 nd clutch part are arranged in series in a rotation axis direction of the hub;
the radial oil passage is formed in an annular partition wall portion that partitions a 1 st hydraulic pressure canceller chamber corresponding to the 1 st clutch portion and a 2 nd hydraulic pressure canceller chamber corresponding to the 2 nd clutch portion.
4. The clutch lubricating construction according to any one of claims 1 to 3,
the flow path area of 1 of the plurality of distal-side supply oil paths is larger than the flow path area of 1 of the plurality of proximal-side supply oil paths.
5. The clutch lubricating construction according to any one of claims 1 to 3,
the number of the plurality of far-side supply oil passages is greater than the number of the plurality of near-side supply oil passages.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-028313 | 2018-02-20 | ||
| JP2018028313A JP7114924B2 (en) | 2018-02-20 | 2018-02-20 | Clutch lubrication structure |
| PCT/JP2019/006072 WO2019163763A1 (en) | 2018-02-20 | 2019-02-19 | Clutch lubrication structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111868405A true CN111868405A (en) | 2020-10-30 |
| CN111868405B CN111868405B (en) | 2022-03-22 |
Family
ID=67687784
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980014298.2A Active CN111868405B (en) | 2018-02-20 | 2019-02-19 | Clutch lubrication structure |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP7114924B2 (en) |
| CN (1) | CN111868405B (en) |
| WO (1) | WO2019163763A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018112131A1 (en) * | 2018-05-18 | 2019-11-21 | Gkn Automotive Ltd. | Double clutch unit and drive arrangement with such a dual clutch unit |
| JP7225461B1 (en) | 2022-06-30 | 2023-02-20 | 株式会社エフ・シー・シー | Clutch device and motorcycle |
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| JPH10169668A (en) * | 1996-12-10 | 1998-06-23 | Yanmar Diesel Engine Co Ltd | Lubricant supply mechanism of wet type multi-plate clutch |
| JP2004125098A (en) * | 2002-10-04 | 2004-04-22 | Tcm Corp | Lubricating part structure of wet multiple disc hydraulic clutch |
| JP2004347120A (en) * | 2003-05-24 | 2004-12-09 | Dr Ing H C F Porsche Ag | Clutch device and method for driving multiple disc clutch |
| JP2005133794A (en) * | 2003-10-29 | 2005-05-26 | Nsk Warner Kk | Hub for multiplate wet clutch |
| CN1763394A (en) * | 2004-09-08 | 2006-04-26 | 伊顿公司 | Coupling device and improved clutch lubrication arrangement therefor |
| US20130153355A1 (en) * | 2011-12-16 | 2013-06-20 | Eaton Corporation | Hydraulic clutch assembly |
| WO2016158887A1 (en) * | 2015-03-31 | 2016-10-06 | アイシン・エィ・ダブリュ株式会社 | Transmission device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2697455B2 (en) * | 1992-02-20 | 1998-01-14 | 株式会社豊田自動織機製作所 | Wet multi-plate clutch |
| JP3124493U (en) * | 2006-06-09 | 2006-08-17 | 株式会社ダイナックス | Wet dual clutch cooling structure |
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2018
- 2018-02-20 JP JP2018028313A patent/JP7114924B2/en active Active
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2019
- 2019-02-19 WO PCT/JP2019/006072 patent/WO2019163763A1/en active Application Filing
- 2019-02-19 CN CN201980014298.2A patent/CN111868405B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10169668A (en) * | 1996-12-10 | 1998-06-23 | Yanmar Diesel Engine Co Ltd | Lubricant supply mechanism of wet type multi-plate clutch |
| JP2004125098A (en) * | 2002-10-04 | 2004-04-22 | Tcm Corp | Lubricating part structure of wet multiple disc hydraulic clutch |
| JP2004347120A (en) * | 2003-05-24 | 2004-12-09 | Dr Ing H C F Porsche Ag | Clutch device and method for driving multiple disc clutch |
| JP2005133794A (en) * | 2003-10-29 | 2005-05-26 | Nsk Warner Kk | Hub for multiplate wet clutch |
| CN1763394A (en) * | 2004-09-08 | 2006-04-26 | 伊顿公司 | Coupling device and improved clutch lubrication arrangement therefor |
| US20130153355A1 (en) * | 2011-12-16 | 2013-06-20 | Eaton Corporation | Hydraulic clutch assembly |
| WO2016158887A1 (en) * | 2015-03-31 | 2016-10-06 | アイシン・エィ・ダブリュ株式会社 | Transmission device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2019163763A1 (en) | 2019-08-29 |
| CN111868405B (en) | 2022-03-22 |
| JP7114924B2 (en) | 2022-08-09 |
| JP2019143714A (en) | 2019-08-29 |
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