JP5773898B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission having a variable amount of lubrication.

  Conventionally, in Patent Document 1, when the amount of lubrication is switched, a switching valve is provided in the control valve unit, and the amount of lubrication is controlled by switching the switching valve according to the running state.

JP 2004-324819 A

However, in the apparatus described in Patent Document 1, a new switching valve, a solenoid for controlling the switching valve, etc. must be mounted in the control valve unit, and the number of design change points increases and is adopted. It was difficult.
The present invention has been made paying attention to the above-described problems, and an object thereof is to provide an automatic transmission capable of easily changing the amount of lubrication.

In order to achieve the above object, according to the present invention, an automatic transmission case comprising a case housing a transmission mechanism of an automatic transmission, a housing connected to the case and a prime mover, and an automatic transmission case are formed. A fastening pressure supply oil passage for supplying a fastening pressure to the friction fastening element, a lubricating oil supply oil passage formed in the automatic transmission case for supplying the lubricating oil to the lubricated element, and the housing When the frictional engagement element is fastened and is operated according to the fastening pressure, the flow resistance of the lubricating oil supply oil passage is made larger than when the frictional fastening element is not fastened. And a lubricating oil amount changing means.

  Therefore, the amount of lubricating oil can be changed using the fastening pressure, and the lubricating flow rate can be controlled with a simple configuration without changing the design of the hydraulic control valve unit or the like.

1 is a schematic diagram showing a power train of Example 1. FIG. 1 is a hydraulic circuit diagram of an automatic transmission according to a first embodiment. 1 is a cross-sectional view of a power train of Example 1. FIG. 3 is an enlarged cross-sectional view of the vicinity of an output shaft support portion in the power train of Embodiment 1. FIG. 3 is an enlarged cross-sectional view of the vicinity of an output shaft support portion in the power train of Embodiment 1. FIG.

  FIG. 1 is a schematic diagram showing a power train according to a first embodiment on which the control device for an automatic transmission according to the present invention is mounted. FIG. 3 is a cross-sectional view of the power train according to the first embodiment. The power train of the first embodiment includes an engine 1 that is a drive source, a torque converter 2 that is drivingly coupled to the engine 1, an automatic transmission 4 that is drivingly coupled to the torque converter 2 via a speed reduction mechanism 3, A final drive gear mechanism 6 that is drive-coupled via a transmission output shaft (propeller shaft) 5 of the automatic transmission 4, and wheels 7 through which the power from the automatic transmission 4 is output via the final drive gear mechanism 6. And have. The automatic transmission 4 includes a continuously variable transmission mechanism 8 and an auxiliary transmission mechanism 9.

  The continuously variable transmission mechanism 8 has a drive pulley 8a connected to the output shaft of the speed reduction mechanism 3 and a secondary pulley 8b connected to the input shaft 9a of the auxiliary transmission mechanism 9, and a belt 8c is hung between them. It is an existing belt type continuously variable transmission mechanism. Oil is supplied to each of the drive pulley 8a and the secondary pulley 8b, and the pulley width can be freely changed according to the oil pressure. Thereby, the continuously variable transmission mechanism 8 can change the gear ratio steplessly by controlling the supply pressure to the drive pulley 8a and the supply pressure to the secondary pulley 8b.

  The sub-transmission mechanism 9 receives the sun gear 9b as an input by drivingly coupling the secondary pulley 8b to the composite sun gear 9b of the Ravigneaux planetary gear mechanism, while driving the carrier 9c to the transmission output shaft 5 and thereby the carrier 9c. Is a step-variable transmission mechanism. The sun gear 9b is fixed to the case portion HG2 via the low brake L / B, and the carrier 9c is drivingly coupled to the ring gear 9d via the high clutch H / C. Furthermore, the ring gear 9d is fixed to the case portion HG2 via a reverse brake R / B.

  The low brake L / B, the high clutch H / C, and the reverse brake R / B can each be supplied with oil, and can be freely engaged and released according to the oil pressure. Thereby, the subtransmission mechanism 9 can select the first forward speed, the second forward speed, and the reverse speed by controlling the supply pressure to the low brake L / B, the high clutch H / C, and the reverse brake R / B. it can.

In the case of selecting the first forward speed, the low brake L / B is engaged and the high clutch H / C is released. When selecting the second forward speed, the low brake L / B is released and the high clutch H / C is engaged. In addition, the detail about the relationship of the fastening and release | release in the control of the subtransmission mechanism 9 is as showing below.
Forward first speed: Only the low brake L / B is engaged, otherwise released Forward second speed: Only the high clutch H / C is engaged, otherwise released Reverse: Only the reverse brake R / B is engaged, otherwise Release These lubricants are supplied to the released brakes and clutches or Ravigneaux planetary gear mechanisms.

  The vehicle according to the first embodiment includes a transmission controller 100 for controlling the shift of the automatic transmission 4. The transmission controller 100 calculates a target input rotational speed of the automatic transmission 4 and, based on the target input rotational speed, a continuously variable transmission control unit 101 that continuously controls the transmission ratio of the continuously variable transmission mechanism 8; A stepped shift control unit 102 that calculates a target shift stage of the transmission mechanism 9 and controls to the target shift stage is provided. That is, for the automatic transmission 4 as a whole, the target speed ratio is realized by coordinating the speed change control of the continuously variable transmission mechanism 8 and the speed change control of the auxiliary transmission mechanism 9.

  The continuously variable transmission mechanism 8 performs ON / OFF control of a plurality of solenoid valves built in the hydraulic control valve unit 10 to supply pressure to the drive pulley 8a and the secondary pulley 8b (usually, supply to the drive pulley 8a). Pressure only) is controlled. As a result, the gear ratio can be changed steplessly. Similarly, the sub-transmission mechanism 9 also controls ON / OFF of a plurality of solenoid valves built in the hydraulic control valve unit 10 so that the low brake L / B, high clutch H / C, and reverse brake R / B are controlled. The supply pressure is controlled, and the first forward speed or the second forward speed is selected.

  FIG. 2 is a hydraulic circuit diagram of the automatic transmission according to the first embodiment. The oil pumped up by the oil pump O / P is introduced into the hydraulic control valve unit 10. In the hydraulic control valve unit 10, a plurality of valves, electromagnetic valves, and the like are incorporated. Further, the oil drained from each valve is supplied to an oil cooler 57 installed outside the hydraulic control valve unit 10. After the oil supplied to the oil cooler 57 is cooled, it is recirculated to the hydraulic control valve unit 10 and supplied as lubricating oil.

  Connected to the hydraulic control valve unit 10 is an opening portion through which an oil passage 70 is opened and a case-side lubricating oil supply oil passage 71 formed in the housing portion HG1. The case-side lubricating oil supply oil passage 71 lubricates the sub-transmission mechanism 9 and each sliding portion (power train lubrication) via a lubricating oil amount changing means 80 that changes the passage resistance, and the belt 8c and each pulley. Lubricate the friction surface with 8a, 8b (belt lubrication). Here, the to-be-lubricated elements that require lubrication are the elements that make up the subtransmission mechanism 9 and include the clutches and brakes that are engaged, the Ravigneaux planetary gears, etc., including the released clutches and brakes. . Details of the reason for changing the amount of lubricating oil applied to these elements to be lubricated will be described later.

  FIG. 3 is a sectional view of the automatic transmission according to the first embodiment. This sectional view is a developed sectional view passing through the center of each rotating shaft, and the positional relationship of each rotating shaft is different from the actual one. The automatic transmission is attached to an engine (not shown) and houses a housing portion HG1 that houses the torque converter 2, and a case portion that is attached to the housing portion HG1 and houses the continuously variable transmission 8 and the auxiliary transmission mechanism 9 inside. HG2 and a cover portion HG3 which is attached to the case portion HG2 and has a bearing or the like for supporting each rotating shaft.

  In the shaft of the input shaft 9a, a lubricating shaft center oil passage 9a1 for supplying lubricating oil to the belt 8c and the auxiliary transmission mechanism 9 is formed so as to penetrate therethrough. A plurality of radial oil passages 9a2 are formed in the lubricating shaft oil passage 9a1, and the lubricating oil is supplied to the rotating elements and friction elements of the auxiliary transmission mechanism 9 disposed on the outer periphery of the input shaft 9a. In the shaft of the transmission output shaft 5 fitted to the input shaft 9a, lubricating oil is supplied to a fastening pressure supply oil passage 5a for supplying a fastening pressure to the high clutch H / C and a lubricating shaft oil passage 9a1. A lubricating oil supply oil passage 5b is formed. The transmission output shaft 5 is rotatably supported via a bearing in an output shaft support portion C1 formed in the housing portion HG1 and bulging in the axial direction.

FIG. 4 is an enlarged cross-sectional view of the vicinity of the output shaft support portion in the power train of the first embodiment. The output shaft support portion C1 has a high diameter from the high clutch oil passage 63 in the hydraulic control valve unit 10 through the case side high clutch pressure oil passage 63a formed in the housing portion HG1 to the fastening pressure supply oil passage 5a from the radial direction. An engagement pressure supply unit C10 for supplying clutch pressure is formed. A bush C11 is supported on the inner periphery of the fastening pressure supply unit C10. The bush C11 is a cylindrical member having excellent wear resistance, and a radial oil passage C11a is formed at a position communicating with the case-side high clutch pressure oil passage 63a.
An annular groove 5d is formed on the outer periphery of the end portion of the transmission output shaft 5 and overlapping with the radial oil passage C11a when viewed from the radial direction. The fastening pressure supply oil passage 5a is formed in the groove 5d. A radial oil passage 5e that opens toward the center is formed. Further, seal members 5c are attached to both sides in the axial direction of the groove 5d and are in sliding contact with the inner periphery of the bush C11 to ensure liquid tightness.

The output shaft support portion C1 passes through a case-side lubricating oil supply oil passage 71 formed in the housing portion HG1 from the oil passage 70 in the hydraulic control valve unit 10 outside the fastening pressure supply portion C10 in the axial direction. A lubricating oil supply portion C12 that supplies lubricating oil to the lubricating oil supply oil passage 5b is formed. The lubricating oil supply part C12 is formed with a bottomed cylindrical hollow part C12a that is formed in the radial direction of the transmission output shaft 5. The hollow portion C12a is connected to the case-side lubricating oil supply oil passage 71 at the bottom, a first cylindrical portion C12a1 in which the bottom portion is formed, a second cylindrical portion C12a2 having a larger diameter than the first cylindrical portion C12a1, A third cylindrical portion C13a3 having a diameter larger than that of the second cylindrical portion C12a2 and a fourth cylindrical portion C13a4 having a diameter larger than that of the third cylindrical portion C13a3 and having a thread groove formed on the inner periphery thereof. The plug member C12b is screwed into the fourth cylindrical portion C13a4 to close the lubricating oil supply portion C12.

  A bottomed cylindrical sleeve D1 is inserted into the hollow portion C12a. The sleeve D1 has an outer periphery whose outer periphery is substantially the same diameter as the inner periphery of the second cylindrical portion C12a2. Moreover, it has the small diameter sleeve D2 which has an outer periphery substantially the same diameter as the 1st cylindrical part C12a1 inner periphery of the hollow part C12a. A communication hole D4 that opens to the case-side lubricating oil supply oil passage 71 is formed at the bottom of the sleeve D1. Further, in the radial direction of the small diameter sleeve D2, there is a through hole that communicates the inner peripheral side of the sleeve D1 and the small diameter sleeve D2, and the space formed between the outer periphery of the small diameter sleeve D2 and the second cylindrical portion C12a2. A hole D3 is formed. Further, a seal member g1 for sealing between the sleeve D1 and the second cylindrical portion C12a2 is provided. Further, a third cylindrical portion C12a3 of the hollow portion C12a is formed on the outer periphery on the plug member C12b side of the seal member g1 of the sleeve D1, and between the outer periphery of the sleeve D1 and the inner periphery of the third cylindrical portion C12a3. A gap is formed. An oil passage F1 communicating with the case side high clutch pressure oil passage 63a is formed in the gap. In other words, when the oil pressure is supplied to the case side high clutch pressure oil passage 63a, the oil pressure is introduced to the inner peripheral side of the third cylindrical portion C12a3 via the oil passage F1.

A spool valve E1 is accommodated in the sleeve D1 so as to allow a stroke in the sleeve D1. The spool valve E1 includes a plug-side convex portion E21 projecting from the plug-side pressure receiving surface E22 on the plug member C12b side, and an oil passage-side convex portion E3 projecting from the oil-side pressure receiving surface E31 on the case-side lubricating oil supply oil passage 71 side. Have A return spring 82 is inserted between the oil passage side pressure receiving surface E31 and the bottom of the sleeve D1 to urge the spool valve E1 toward the plug member C12b.
Here, there is a predetermined gap F2 between the plug-side end of the sleeve D1 and the plug member C12b, and the height in the protruding direction of the plug-side protrusion E21 is substantially the same as the gap F2. Thereby, the hydraulic pressure introduced through the oil passage F1 can surely act on the plug-side pressure receiving surface E22 of the spool valve E1. On the other hand, on the top surface E5 of the oil passage side convex portion E3, a communication hole D4 and a small diameter orifice E6 smaller than the opening diameter of the communication hole D3 are formed. Further, a radial through hole E4 penetrating in the radial direction is formed in the side surface of the oil passage side convex portion E3, and the small diameter orifice E6 and the radial through hole E4 are formed in communication with each other.

  The outer diameter of the top surface E5 is larger than the inner diameter of the through hole D4 formed in the sleeve D1. As a result, when the spool valve E1 is pressed against the case-side lubricating oil supply oil passage 71 side, the top surface E5 and the bottom surface of the sleeve D1 come into contact (or close to each other to form a very small gap). The lubricating oil supplied from the side lubricating oil supply oil passage 71 passes through the small-diameter orifice E6. In this way, the state in which the communication hole D4 and the through hole D3 communicate with each other and the state in which the lubricant flows between the communication hole D4 and the through hole D3 through the small diameter orifice E6 by switching the spool valve E1 are switched. Thus, the lubricating oil amount changing means is configured.

  Next, the effect | action which concerns on the lubricating oil amount change based on the said structure is demonstrated. In the power train of the first embodiment, during forward traveling, the vehicle runs while either the low brake L / B or the high clutch H / C is engaged. When the forward first speed is selected, only the low brake L / B is engaged, and the others are released. Therefore, the Ravigneaux planetary gear mechanism in the subtransmission mechanism 9 is configured so that each rotating element rotates relative to the input shaft. The rotation of the transmission output shaft 5 is slower than the rotation of 9a. Thus, when relative rotation is occurring, a large amount of lubricating oil is required for each rotating element. On the other hand, when the forward second speed is selected, only the high clutch H / C is engaged, and the others are released. Therefore, the Ravigneaux planetary gear mechanism in the auxiliary transmission mechanism 9 has each rotating element integrally rotated, The input shaft 9a and the transmission output shaft 5 rotate together. In this way, when there is no relative rotation, a large amount of lubricating oil is not required for each rotating element. If the amount of lubricating oil is too large, drag torque in the low brake L / B and reverse brake R / B on the contrary. Is unfavorable because it increases. When the second forward speed is selected, the secondary pulley side is accelerated by the continuously variable transmission mechanism 8, and the auxiliary transmission mechanism 9 installed on the secondary pulley side is particularly high in rotation. Also, there is a problem that drag torque due to unnecessary lubricating oil tends to cause deterioration of fuel consumption.

  That is, it is understood that it is desirable to change the amount of lubricating oil between the first forward speed and the second forward speed during forward travel. Therefore, in order to change the amount of lubricating oil according to the selected gear position, it is conceivable to provide a switching valve or the like having a different orifice diameter in the hydraulic control valve unit 10 and switch according to the high clutch pressure or the like.

  Here, the hydraulic control valve unit 10 forms a complicated groove in a box-shaped aluminum member, and forms an oil passage by combining these aluminum members. The hydraulic control valve unit 10 designed in accordance with such a design procedure is an element designed with sufficient consideration of the oil path resistance and the necessary thickness between the adjacent oil paths, It is very difficult to change the oil passage configuration easily. In addition, when adding a valve, the high clutch pressure must be routed near the oil passage for lubrication, and the handling of the oil passage becomes more complicated, and although a switching valve is simply added, the hydraulic control valve unit 10 affects the whole, not easy.

  Therefore, in the first embodiment, paying attention to the fact that the fastening pressure supply oil passage 5a and the lubricating oil supply oil passage 5b are adjacent to each other in the shaft center of the transmission output shaft 5, the hydraulic control valve unit 10 In the configuration, the amount of lubricating oil is changed without any particular design change.

FIG. 4 is a sectional view showing the operation when the first forward speed is selected in the power train of the first embodiment, and FIG. 5 shows the operation when the second forward speed is selected in the power train of the first embodiment. It is sectional drawing to represent. The flow of oil is indicated by arrows in FIGS.
When the forward first speed is selected, the engagement pressure is supplied to the low brake L / B, and no engagement pressure is supplied to the high clutch H / C. There is no pressure and no oil flow. In this case, since only the urging force by the return spring 82 is acting on the spool valve E1, the communication hole D4 and the through hole D3 are in a state of being communicated without particularly passing through an orifice or the like. At this time, the oil supplied from the case-side lubricating oil supply oil passage 71 flows from the communication hole D4 through the through hole D3 into the lubricating oil supply oil passage 5b, so that a large flow rate is supplied as the lubricating flow rate.

  When the forward second speed is selected, the engagement pressure is supplied to the high clutch H / C. Therefore, the engagement pressure acts on the case-side high clutch pressure oil passage 63a, and the groove 5d extends from the radial oil passage C11a. And is supplied to the radial oil passage 5e, and the high clutch pressure is supplied to the engagement pressure supply oil passage 5a. At this time, a high clutch pressure is applied to the spool valve E1, and the spool valve E1 is pushed upward in FIG. 5 to move against the urging force of the return spring 82. E5 seals the communication hole D4. Then, the oil supplied from the case-side lubricating oil supply oil passage 71 flows from the small diameter orifice E6 through the radial through hole E4 into the lubricating oil supply oil passage 5b through the through hole D3. The flow path resistance of the path 5b increases, and a small flow rate is supplied as the lubrication flow rate.

In this way, when the engagement pressure is supplied to the high clutch H / C, the supply path of the lubricating oil is changed so as to pass through the small-diameter orifice E6 according to the hydraulic pressure, and therefore the flow path of the lubricating oil supply oil path 5b. The resistance is also changed, and the amount of lubricating oil is changed. The change of the lubricating oil amount is achieved by the lubricating oil amount changing means 80 constituted by the spool valve E1 and the return spring 82 provided in the shaft of the transmission output shaft 5, so that the hydraulic control valve unit There is no need to change any of the components in the housing 10, and design changes in the housing part HG1 are negligible.
Here, for example, a case is assumed in which lubricating oil amount changing means is provided in the case part HG2 which is a common part basically regardless of the engine specifications. At this time, if it is desired to make an automatic transmission that does not have the spool valve E1 for some models in order to reduce costs, it is necessary to newly design the case part HG2, and the model that does not substantially have the lubricating oil amount changing means 80 Setting is difficult. Similarly, there is no degree of freedom in selecting a structure in which the lubricating oil amount changing means 80 is provided in the transmission output shaft 5 which is a common part regardless of the model. On the other hand, by providing the lubricating oil amount changing means in the housing part HG1 having a different shape for each specification as in the first embodiment, the degree of freedom in selecting whether or not to provide the spool valve E1 for each model of the automatic transmission can be increased. Can be spread.

  As described above, the effects listed below can be obtained in the first embodiment.

(1) Formed in the housing part HG1 (automatic transmission case) and formed in the housing part HG1 and the fastening pressure supply oil passage 5a for supplying the fastening pressure to the high clutch H / C (friction fastening element). , A lubricating oil supply oil passage 5b for supplying lubricating oil to the lubricated elements such as the clutch, brake, belt 8c or planetary gear, and the fastening pressure in the fastening pressure supply oil passage 5a provided in the housing portion HG1. When the high clutch H / C is engaged, the lubricating oil that increases the flow resistance of the lubricating oil supply oil passage 5b is greater than when the high clutch H / C is not engaged. And a quantity changing means.
Therefore, when the relative rotation is small and the amount of lubricating oil may be small as in the case of engaging the high clutch H / C, the lubricating flow rate is increased by using the high clutch pressure. Therefore, the lubrication flow rate can be controlled with a simple configuration without changing the design of the hydraulic control valve unit or the like.

  Here, the operational effect based on the difference between the case where the spool is provided in the transmission output shaft 5 (hereinafter referred to as a comparative example) and the case where the spool valve E1 is provided in the housing portion HG1 as in the first embodiment will be described. To do. In the case of the comparative example, when the spool is arranged at a position eccentric with respect to the rotation center of the transmission output shaft 5, the sliding resistance of the spool due to centrifugal force increases as the number of rotations of the transmission output shaft 5 increases. In addition, it is difficult to ensure the operability of the spool. On the other hand, by providing the spool valve E1 in the housing part HG1 as in the first embodiment, stable spool operability can be ensured regardless of the rotational speed.

(2) The automatic transmission case includes a case portion HG2 that houses the transmission mechanism of the automatic transmission, and a housing portion HG1 (housing) that is connected to the case portion HG2 and the engine (prime mover). The changing means is provided in the housing part HG1.
Since the housing portion HG1 connected to the engine has a different shape for each engine specification, the degree of freedom in selecting whether or not to provide the spool valve E1 for each model of the automatic transmission can be expanded.

(3) The element to be lubricated includes a Ravigneaux planetary gear mechanism (planetary gear), and this planetary gear rotates integrally by engaging the high clutch H / C.
That is, the Ravigneaux planetary gear mechanism of the auxiliary transmission mechanism 9 that is the element to be lubricated rotates integrally with the engagement of the high clutch H / C, and therefore the amount of lubrication may be small. Therefore, by increasing the flow resistance of the lubricating oil supply oil passage according to the fastening pressure of the high clutch H / C that integrally rotates the Ravigneaux planetary gear by fastening, the drag torque can be reduced without impairing the durability of the lubricated element. Can be reduced, and fuel consumption can be improved.

(4) The lubricating oil amount changing means has a spool valve E1 (spool valve) provided in the lubricating oil supply oil passage, and the fastening pressure of the high clutch H / C acts on one end side of the spool valve E1. By doing so, the spool valve E1 reduces the cross-sectional area of the lubricating oil supply oil passage when it slides to the other end side, thereby increasing the passage resistance. In other words, the flow path resistance is increased by passing through the small-diameter orifice E6.
As a result, the lubricating oil amount can be changed only by changing the design of only a part of the housing portion HG1, and the lubricating oil amount can be controlled at a low cost.

  Although the first embodiment has been described above, the present invention is not limited to the above-described configuration, and may have other configurations. In the first embodiment, the configuration including the belt-type continuously variable transmission 8 and the auxiliary transmission mechanism 9 is shown. However, the present invention can also be applied to a case where the amount of lubricating oil is desired to be changed in a stepped automatic transmission. Moreover, even if it is not the structure provided with the subtransmission mechanism 9, it is effective even if it applies only to the structure provided with the forward / reverse switching mechanism. That is, in the case of a forward / reverse switching mechanism that rotates integrally by fastening the fastening element at the time of forward movement or the like, the amount of lubricating oil at the time of forward movement may be small. Because there is a need to do more.

  Further, in the first embodiment, the spool valve E1 moves through the small-diameter orifice E6. However, the present invention is not limited to opening and closing the orifice, and the spool has a port connected to a lubricating oil passage, and the spool moves. It is good also as a structure from which flow-path resistance changes by setting an opening degree according to.

  In the first embodiment, an example in which the spool valve E1 is provided in the housing part HG1 in the automatic transmission case is shown, but the present invention is not limited to this. For example, the transmission output from the housing part HG1 A sleeve may be fitted to the transfer portion of the oil passage to the shaft 5, thereby constituting the lubricating oil amount changing means.

DESCRIPTION OF SYMBOLS 1 Engine 2 Torque converter 3 Deceleration mechanism 4 Automatic transmission 5 Transmission output shaft 5a Fastening pressure supply oil path 5b Lubricating oil supply oil path 8 Continuously variable transmission mechanism 8c Belt 9 Subtransmission mechanism 9a Input shaft 9a1 Lubrication shaft center Oil path 9a2 Radial oil path 10 Hydraulic control valve unit 63 High clutch oil path 63a Case side high clutch pressure oil path 71 Case side lubricating oil supply oil path 82 Return spring 100 Transmission controller C1 Output shaft support C10 Fastening pressure supply Part C11 Bush C11a Radial oil passage C12 Lubricating oil supply part C12a Hollow part E1 Spool valve E6 Small diameter orifice H / C High clutch
HG1 housing
HG2 case section
HG3 Cover L / B Low brake O / P Oil pump R / B Reverse brake

Claims (4)

An automatic transmission case comprising a case for housing a transmission mechanism of an automatic transmission, and a housing coupled to the case and a prime mover;
An oil passage for fastening pressure supply formed in the automatic transmission case and supplying fastening pressure to the friction fastening element;
A lubricating oil supply oil passage formed in the automatic transmission case for supplying lubricating oil to the lubricated element;
When the friction engagement element is fastened and provided in the housing and operates according to the fastening pressure, the flow path of the lubricating oil supply oil path is greater than when the friction engagement element is not fastened. Lubricating oil amount changing means for increasing resistance,
An automatic transmission characterized by comprising: The automatic transmission according to claim 1, wherein
The lubricated element includes a planetary gear,
It said friction engagement element, the automatic transmission according to claim Rukoto is integrally rotated with the planetary gear by engagement of the frictional engagement element. The automatic transmission according to claim 1 or 2,
The lubricating oil amount changing means has a spool valve provided in the lubricating oil supply oil passage,
The spool valve slides to the other end side when the fastening pressure acts on one end side, and when the spool valve slides to the other end side, the spool valve reduces the cross-sectional area of the lubricating oil supply oil passage. An automatic transmission characterized in that the flow path resistance is increased . The automatic transmission according to any one of claims 1 to 3,
An output shaft rotatably supported by the housing and driven and fastened to the lubricated element;
In the output shaft, an in-shaft fastening pressure supply oil passage that communicates with the fastening pressure supply oil passage and an in-shaft lubricating oil supply oil passage that communicates with the lubricating oil supply oil passage,
An automatic transmission characterized in that the lubricating oil amount changing means is provided in a support portion for supporting the output shaft of the housing .

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