CN1005788B - Speed-changing device for hydraulic mechanism - Google Patents
Speed-changing device for hydraulic mechanism Download PDFInfo
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- CN1005788B CN1005788B CN85107332.8A CN85107332A CN1005788B CN 1005788 B CN1005788 B CN 1005788B CN 85107332 A CN85107332 A CN 85107332A CN 1005788 B CN1005788 B CN 1005788B
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Abstract
The present invention relates to a hydraulic mechanical speed changing device for automobiles, which combines a hydraulic transmission mechanism with a differential gear mechanism, changes the speed of the revolving output of an engine, etc., and transmits the revolving output to wheels. When the device is changed from a low speed state to a high speed state, because of the fluid leakage of the hydraulic transmission mechanism and elastic influence, the rotary speed during transmission conversion is unequal, and thereby, impact is produced. In order to preventing the phenomenon, the rotary speed and the torque of each transmission conversion end are detected and are used for correcting the variable speed ratio of the hydraulic transmission mechanism, the speed and the torque of two transmission ends equal to each other respectively, and the conversion is carried out after equalization.
Description
The present invention is the relevant hydraulic-mechanical speed variator that can be used for various industrial fields as the stepless speed variator of high efficiency.
Adopt hydraulic pump/motor known as the so-called hydraulic transmission (HST) of stepless speed variator.Yet though the stepless change performance of this device is good, the low and slewing range of efficient can not meet the demands.Yan Zhi And has announced by this HST and differential gear train Zu He And are used for this reason, make HST and differential gear train share the transmission of power, thereby make the good stepless change characteristic of above-mentioned HST and the hydraulic-mechanical speed variator (HMT) that gear-driven high efficiency is brought into play simultaneously (reference: oil pressure engineering (stone former intelligence man compile towards the study, storehouse), PVC ス ト Application Port Application プ モ-タ theory and actual (the outstanding コ ロ of the former loyal man of stone
Society)) promptly, this device is made of following several parts: differential attachment, have first, second and the 3rd input/output terminal and formation by the low speed side mechanical type power train between this first input/output terminal and second input/output terminal, and by the high-speed side mechanical type power train between first input/output terminal and the 3rd input/output terminal; The input and output shaft of one group of hydraulic pump/motor is connected with second input/output terminal of above-mentioned differential attachment, the input and output shaft of another group hydraulic pump/motor is connected with the 3rd input/output terminal of above-mentioned differential attachment, the fluid drive mechanism that the variable speed hydraulic transmission that is made of these two pump/motors is; Make the driving end and the low speed clutch that is located at the shared turning member clutch of input side or outlet side of the mechanical type power train of above-mentioned low speed side, make the driving end of mechanical type power train of above-mentioned high-speed side and the high speed clutch of above-mentioned shared turning member clutch, by to the reciprocal switching of above-mentioned two clutches, can choose lower-speed state or fast state wantonly.
Yet, in the device of this constituted mode, easily produce the problem of impacting when existing state exchange.That is to say that in this device, a part of input power is directly delivered to outlet side by the mechanical type power train that is made of gear etc.; Simultaneously, the hydraulic transmission system that then is made up of above-mentioned hydraulic pump/motor of remaining power power that is delivered to outlet side ， And and above-mentioned mechanical type power train converges.In this case, when above-mentioned hydraulic transmission frenulum had load, owing to the leakage of the working fluid of above-mentioned hydraulic pump/motor inside and the reasons such as flexible influence of oil hydraulic circuit, its gyroscopic output had the tendency that lags behind than mechanical type power train.
As following introduction, in the state exchange stage, because a pair of hydraulic pump/motor is a co-conversion mutually as pump and effect as motor, therefore the influence that is produced by above-mentioned hysteresis will have the opposite effect.Like this, for example, be transformed into from lower-speed state the process of fast state, just or afterwards in moment that the rotating speed of the mechanical type power train driving end of high-speed side equates with the rotating speed of the mechanical type power train driving end of low speed side, through stage regular hour, just when above-mentioned low speed unclamps with clutch, make and use the clutch combination at a high speed, therefore just interrupt suddenly to the state of shared turning member transmitting torque from the mechanical type power train of low speed side, after with the regional instantaneous absorption of the indefinite idle running of whole system reverse impact character, just change over to from the mechanical type power train of high-speed side state to shared turning member transmitting torque.Therefore when this conversion, usually can produce big mechanical shock in moment.
In addition, as prior art, as No. 3988949 representative of U. S. Patent, the two is made up with gear type mechanical transmission and hydraulic transformer, and " hydraulic-mechanical speed variator (HMT) is known.This patent is called as the ORSHANSKY mode, and it can realize stepless change in high speed field and low speed field by the function of mechanical speed change and hydraulic speed-changing.
The present invention is improvements over the prior art.
The objective of the invention is to the shock problem that produces when solving state exchange really with simpler structure.
The invention is characterized in, in order to achieve the above object, in the hydraulic-mechanical speed variator that has adopted above-mentioned the sort of state exchange mode, possesses the speed detector that detects above-mentioned two mechanical type power train driving end rotating speeds, detect the torque detecting apparatus of above-mentioned two driving end moment of torsion transmit modes, and control gear, when this control gear equates at the rotating speed by above-mentioned each driving end that above-mentioned speed detector detected, with above-mentioned two clutch combinations, simultaneously, before the moment of torsion transmit mode that is detected by above-mentioned torque detecting apparatus is changed mutually, the gear ratio of above-mentioned hydraulic gear is carried out Correction and Control always; Making not when this correction finishes, the clutch of transmitting torque side unclamps.
When lower-speed state, with clutch the driving end through the mechanical type power train of first input/output terminal of differential attachment and the low speed side between second input/output terminal is connected by low speed with the shared turning member that is located at outlet side or input side, a part of power of importing is directly exported by this mechanical type power train.The power of remaining part then is passed to outlet side by the fluid transmission of being made up of fluid drive mechanism; In this case, one group of hydraulic pump/motor is being worked as motor, and simultaneously, another group hydraulic pump/motor possesses the function of pump.
In addition, when fast state, driving end by first input/output terminal of differential attachment and the high-speed side mechanical type power train between the 3rd input/output terminal is connected with the shared turning member that is located at outlet side or input side, and part input power is directly exported by this mechanical type power train.The power of remaining part then is passed to outlet side by the hydraulic transmission system that is made of the fluid driving mechanism, and in this case, above-mentioned each hydraulic pump/motor plays the situation of pump or motor effect with opposite just now.
Like this, from lower-speed state when fast state is changed, play following effect, promptly, at first, having only low-speed clutch to be under the situation of bonding state, when the mechanical transmission of high-speed side is the rotating speed of driving end when equating with the rotating speed of low speed side mechanical type power train driving end, not only low-speed clutch but also high-speed clutch all are in bonding state.Then, low speed disappears with the state of transmitting torque between mechanical type power train and the shared turning member, carry out between by high speed machine formula power train and above-mentioned shared turning member the gear ratio of hydraulic transmission system being revised before moment of torsion transmits, then make the low-speed clutch disengagement.When lower-speed state was changed, its effect situation was opposite from fast state.
Fig. 1 is the system diagram of one embodiment of the invention.Fig. 2 is embodiment's Action Specification figure.
Below, see figures.1.and.2 and introduce one embodiment of the present invention.The present invention is a hydraulic-mechanical speed variator, overview as shown in Figure 1 is such, being constructed as follows of this speed changer: have first, second and the 3rd input/output terminal 1,2,3 And by by the low speed side mechanical type power train a between this first input/output terminal 1 and second input/output terminal 2, and the differential attachment of forming by the high-speed side mechanical type power train b between this first input/output terminal 1 and the 3rd input/output terminal 34; The variable speed hydraulic transmission of being made up of two groups of pump/motors 5,7 is that A, B constitute fluid drive mechanism 8, wherein, the input and output shaft 5a of quantitative hydraulic pump/motor 5 is connected with second input/output terminal 2 of this differential attachment 4, and the input and output shaft 7a of volume adjustable hydraulic pump/motor 7 is connected with above-mentioned the 3rd input/output terminal 3; Can by above-mentioned low speed side mechanical type power train a with input side and the direct-connected lower-speed state of outlet side with by choose any one kind of them in input side and the direct-connected fast state of the outlet side switching mechanism 9 of state of above-mentioned high-speed side mechanical type power train b.
Differential attachment 4 is a plurality of planet wheel 4a of five equilibrium ground configuration on the Zhou Fangxiang of garden, its inboard and sun gear 4b engagement, its outside and gear ring 4c planet gear meshed mechanism simultaneously.And and, the central part of the gear retainer 4d of planetary gear bearing 4a as the above-mentioned first input output axle head 1, is provided with input shaft 13 at this input/output terminal 1 place.The supporting axle 4e of above-mentioned sun gear 4b as above-mentioned second input/output terminal 2, is being installed gear 14 at these input/output terminal 2 places, the 4f of hub portion of above-mentioned gear ring 4c as above-mentioned the 3rd input/output terminal 3, is being provided with gear 15 at these input/output terminal 3 places.
In above-mentioned fluid drive mechanism 8, with common HST(hydraulic transmission) the same be above-mentioned quantitative hydraulic pump/motor 5 directly to be connected with volume adjustable hydraulic pump/motor 7 by oil hydraulic circuit 16 in series; The input and output shaft 5a of above-mentioned quantitative hydraulic pump/motor 5 directly is connected on the supporting axle 4e of above-mentioned sun gear 4b; Simultaneously, be connected with above-mentioned gear ring 4c by the input and output shaft 7a of gear 17 above-mentioned hydraulic pump/motor 7.
In addition, in above-mentioned state exchange mechanism 9, with gear 14 engagements of above-mentioned second input/output terminal 2 and the low speed gear 18 that is a driving end as above-mentioned low speed side mechanical transmission, and between the output shaft 19 as shared turning member, be provided with the low speed clutch.
In this speed changer, also be provided with detection as the speed detector 24 of the low speed gear 18 of above-mentioned two mechanical type power train a, b driving end and high gear 22 rotating speeds, detect the torque detecting apparatus 25 of moment of torsion transmit mode in above-mentioned two gears 18,22, and control gear 26, when the latter equates at the rotating speed by above-mentioned speed detector 24 detected above-mentioned each gear 18,22, make 21,23 combinations of above-mentioned two clutches; Before the mutual conversion of moment of torsion transmit mode that detects by above-mentioned torque detecting apparatus 25, the gear ratio of above-mentioned fluid drive mechanism 8 is carried out Correction and Control simultaneously always, when this correction is over, be with the not clutch 21 or 23 disengagements of transmitting torque side.
Be illustrated in down in detail.Speed detector 24 has paired velocity transducer 24a, 24b, and velocity transducer 24a and another velocity transducer 24b detect the rotating speed of low speed gear 18 respectively and the Zhuan Su And of high gear 22 is transformed to electrical signal with it.
In addition, torque detecting apparatus 25 has paired pressure transducer 25a, 25b.A pressure transducer 25a is used for the high tension loop part 16a(in the oil hydraulic circuit 16 of above-mentioned fluid drive mechanism 8 promptly, becomes the high pressure side loop feature when selecting lower-speed state) Pressure testing Chu Lai And convert electrical signal to.The high tension loop part 16b(of another pressure transducer 25b during with the oil hydraulic circuit 16b high speed of above-mentioned hydraulic gear 8 becomes the high pressure side loop feature when selecting fast state) Pressure testing Chu Lai And be transformed into electrical signal.
Control gear 26 has the final controlling element 27 of the volume change that can make above-mentioned volume adjustable hydraulic pump/motor 7, and the computer 28 of control final controlling element 27 and above-mentioned each clutch 21,23.Final controlling element 27 is made of electrohydraudic servomechanism etc., and when above-mentioned hydraulic pump/motor was inclined disc type or clino-axis type, it can make the angle of this swash plate or inclined shaft change; When hydraulic pump/motor 7 is radial plunger type or special when opening the static balance formula that clear 58-77179 communique published, it will make the eccentric position of vertical shaft change.The conventional microcomputer system that aforementioned calculation machine 28 is made up of central processing unit (CPU) 29, various storage 30 and interface 31 constitutes; Signal from above-mentioned each rotary sensor 24a, 24b and above-mentioned pressure transducer 25a, 25b is input in this interface 31; Simultaneously, by this interface 31 command signal Shu Chu And is offered above-mentioned final controlling element 27 and clutch 21,23.And and, the program that will carry out is later on deposited among the part of storage 30 of this computer 28.Just, at first from have only low speed with clutch 21 in conjunction with the time lower-speed state, the rotating speed of high gear 22 moves closer to the rotating speed of low speed gear 18 at this moment, just send the combined command signal to high-speed clutch 23 in the moment that final consistent Shi And with this rotating speed obtains confirming, make two clutches all be in bonding state.Then, above-mentioned two pressure transducer 25a, 25b are temporarily stored in the above-mentioned storage 30 at checkout value P, the Q of this time point.Then, send the corrective action command signal, make the final controlling element action to final controlling element 27.And and, make this action last till above-mentioned two pressure transducer 25a25b detect out De And give the checkout value that deposits in earlier in the storage 30 when taking a turn for the worse till.Then,, above-mentioned final controlling element 27 is stopped, unclamping low-speed clutch 21 simultaneously, change fast state in the moment that this checkout value takes a turn for the worse.Equally, when fast state changes lower-speed state over to, also be order according to the above narration action that realizes clutch 21,23 conversions and final controlling element 27.
And, in the present embodiment, from the rotary motive power of motor etc. from being located at the input shaft input of the above-mentioned differential attachment 4 and first input/output terminal 1; Simultaneously, by above-mentioned state exchange mechanism 9, the output shaft 19 from being connected with the second or the 3rd input/output terminal 2,3 of above-mentioned differential attachment 4 passes to rotary motive power Shu Chu And the driving wheel of vehicle etc.
Introduce the action of present embodiment below.
Low-speed clutch 21 in conjunction with and under the lower-speed state that high-speed clutch 23 is thrown off, through by first input/output terminal 1 of above-mentioned differential attachment 4 and the low speed side mechanical type power train a between second input/output terminal 2, input side directly is connected with outlet side; The part power of input is directly passed to output shaft 19 by this mechanical type power train a.At this moment, as shown in Figure 2, above-mentioned volume adjustable hydraulic pump/motor 7 constitutes the function of pump, the then effect of formation motor of above-mentioned quantitative hydraulic pump/motor 5.Just, the rotary motive power of the 3rd input/output terminal 3 of above-mentioned differential attachment 4 by the hydraulic transmission A that forms, passes to above-mentioned output shaft 19 between above-mentioned volume adjustable hydraulic pump/motor 7 and above-mentioned quantitative hydraulic pump/motor.And, under this lower-speed state,, make rotating speed increase with the corresponding above-mentioned output shaft 19 of the rotating speed of above-mentioned input shaft 13 by increasing the capacity of above-mentioned volume adjustable hydraulic pump/motor 7.In other words, be under zero the situation at the capacity of above-mentioned volume adjustable hydraulic pump/motor 7, because the 3rd input/output terminal 3 of differential attachment 4 is in approximate idling conditions, 19 of output shafts that are connected with second input/output terminal 2 of this differential attachment 4 are in the approximate stall state.And along with the capacity of above-mentioned hydraulic pump/motor 7 increases, the rotating speed of above-mentioned the 3rd input/output terminal 3 reduces relatively, and the rotating speed of second input/output terminal 2 increases relatively.
When above-mentioned second input/output terminal 2 equates with the rotating speed of above-mentioned the 3rd input/output terminal 3, carry out following Zhuan Huan And and change fast state over to.
Under this fast state, just having formed by first input/output terminal 1 of above-mentioned differential attachment system and the mechanical transmission between the 3rd input/output terminal 3 is b, and the part power of input is that b is directly passed to output shaft 19 by this mechanical transmission.At this moment, as shown in Figure 2, above-mentioned volume adjustable hydraulic pump/motor 7 constitutes the function of motor, and above-mentioned quantitative hydraulic pump/motor 5 then becomes pump work.Just, the rotary motive power of second input/output terminal 2 of above-mentioned differential attachment 4, the hydraulic transmission through forming between above-mentioned quantitative pump/motor 5 and above-mentioned variable pump/motor 7 is b, passes to above-mentioned output shaft 19.And, under fast state,, can make rotating speed increase with the corresponding above-mentioned output shaft 19 of the rotating speed of above-mentioned input shaft 13 by reducing the capacity of above-mentioned variable pump/motor 7.In other words, become the capacity of the above-mentioned hydraulic pump/motor 7 of motor face work, the rotating speed of the 3rd input/output terminal 3 is increased relatively, the rotating speed of second input/output terminal 2 is reduced relatively by minimizing.
At this, the working condition when lower-speed state is converted to fast state is explained.It is final when consistent with latter's rotating speed to move closer to the Zhuan Su And of low speed gear 18 at the rotating speed of high gear 22, and control gear 26 just sends combined command to high speed with clutch 23, so two clutches 21,23 just are in bonding state.And above-mentioned two pressure transducer 25a, checkout value P, the Q of 25b of this moment are temporarily stored in the storage 30.Then, in this stage, moment of torsion is that the low speed gear 18 of a is delivered to the output shaft 19 as shared turning member from the low speed side mechanical transmission just, and moment of torsion will be no longer be that the high gear 22 of b transmits to output shaft 19 from the mechanical transmission of high-speed side.Then, send the corrective action command signal to above-mentioned final controlling element 27, make above-mentioned two final controlling element 27 to the direction action that the pump/motor capacity is reduced by aforementioned calculation machine 28.And, till this action will last till the checkout value of above-mentioned two pressure transducer 25a, 25b always and give when taking a turn for the worse between the value that deposits in earlier in the storage 30.Just, from the checkout value of pressure sensing 25a is the P(high pressure), the checkout value of pressure transducer 25b is Q(low pressure) state-transition be the checkout value of Q, pressure transducer 25b when being P to the checkout value of pressure transducer 25a, all to revise the capacity of hydraulic pump/motor 7.And, in this process, above-mentioned hydraulic pump/motor 5,7 during as pump and motor role then exchanged fully; The moment of torsion of being passed to output shaft 19 by low speed gear 18 has disappeared, thereby is in by the state of high gear 22 to above-mentioned output shaft 19 transmitting torques.At this moment, the corrective action of above-mentioned final controlling element 27 stops, and low-speed clutch 21 is thrown off, and changes fast state over to.Equally, when fast state is transformed into lower-speed state, also be that the order by above introduction realizes the conversion of clutch 21,23 and the action of final controlling element.
Thereby if reach this situation, then at the state transition point place, rotating speed and moment of torsion are continually varyings, can realize shock-free level and smooth state exchange.And, because the timing of the switching of clutch 21,23 is controlled, just fluid drive mechanism 8 is carried out some Correction and Control simultaneously, thus relatively simple for structure, and it is also easy to implement.
In addition, differential attachment is not limited to planetary gear type; And, even if the employing planetary gear type, accomplish that mechanism's compactness also is easy to.
And fluid drive mechanism also is not limited to aforementioned person, for example, paired hydraulic pump/motor all can be selected for use variable displacement etc., only otherwise depart from essence spirit of the present invention, can adopt various distortion.
Also have, the formation of torque detecting apparatus also is not limited to above-mentioned those several modes, for example, adopts the direct detection effect of torque sensor good at the low speed gear and the moment of torsion on the high gear that as mechanical transmission are driving end; If adopt above-mentioned the sort of Pressure testing mode, can be simply and exactly the change over condition of torque drive state be detected.
Control gear also not necessarily must the employing electronic computer, adopts the fluid control device with the loop that meets the hydraulic pressure theory good.In addition, in the above-described embodiments, the input method of salary distribution device that only just differential attachment is configured in input side is explained; Yet this Fa Ming And not necessarily must be limited to this mode, for example, adopts being suitable for too of the output method of salary distribution.
The present invention is because by above-mentioned situation formation, so the hydraulic-mechanical speed variator that adopts fairly simple mechanism to make the function admirable that can not impact really when state exchange can be provided.
Claims (1)
1, hydraulic-mechanical speed variator, by constituting: differential attachment with the bottom, this mechanism has first, second and the 3rd input/output terminal And forms by the low speed side mechanical type power train between first input/output terminal and second input/output terminal, and by the high-speed side mechanical type power train between first input/output terminal and the 3rd input/output terminal; Fluid drive mechanism, this mechanism is the hydraulic transmission system of the variable speed be made up of two groups of pump/motors, wherein the input and output shaft of one group of pump/motor is connected with second input/output terminal of this differential attachment, and simultaneously, the input and output shaft of another group pump/motor is connected with above-mentioned the 3rd input/output terminal; Make the driving end and the low speed clutch that is located at the shared turning member clutch of outlet side of above-mentioned low speed side mechanical type power train, and make the driving end of above-mentioned high-speed side mechanical type power train and the high speed clutch of above-mentioned shared turning member clutch, by the positive anti-switching of above-mentioned two clutches, can in fast state or lower-speed state, choose wantonly; It is characterized in that possessing the speed detector of the driving end rotating speed that detects above-mentioned two mechanical type power trains, detect the torque detecting apparatus of moment of torsion transmit mode on above-mentioned two driving ends, and control gear; When this control gear equates at the rotating speed of above-mentioned each driving end that is detected by above-mentioned speed detector, make above-mentioned two clutch combinations, simultaneously, before the moment of torsion transmit mode that is detected by above-mentioned torque detecting apparatus is changed mutually, gear ratio to above-mentioned fluid drive mechanism is carried out Correction and Control, and making not when this correction finishes, the clutch of transmitting torque one side unclamps.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN85107332.8A CN1005788B (en) | 1985-10-08 | 1985-10-08 | Speed-changing device for hydraulic mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN85107332.8A CN1005788B (en) | 1985-10-08 | 1985-10-08 | Speed-changing device for hydraulic mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN85107332A CN85107332A (en) | 1987-04-15 |
| CN1005788B true CN1005788B (en) | 1989-11-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN85107332.8A Expired CN1005788B (en) | 1985-10-08 | 1985-10-08 | Speed-changing device for hydraulic mechanism |
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| Country | Link |
|---|---|
| CN (1) | CN1005788B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101203399B (en) * | 2005-06-15 | 2011-07-20 | 沃尔沃拉斯特瓦格纳公司 | Vehicle |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6676557B2 (en) * | 2001-01-23 | 2004-01-13 | Black & Decker Inc. | First stage clutch |
| CA2363653A1 (en) * | 2001-11-22 | 2003-05-22 | Gerald Dyck | Hydro-mechanical continuously variable transmission |
| DE10310831A1 (en) * | 2002-04-10 | 2003-11-06 | Luk Lamellen & Kupplungsbau | Vehicle drive train, includes divided flywheel with relatively-rotating weights between crank shaft and input to gearbox |
| EP1499900B1 (en) * | 2002-04-10 | 2005-11-23 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Method for determining the rotational speed of a part |
| JP4632771B2 (en) * | 2004-02-25 | 2011-02-16 | 株式会社小松製作所 | Hydraulic steering type work vehicle |
| JP4789507B2 (en) * | 2005-05-24 | 2011-10-12 | 株式会社小松製作所 | Transmission |
| CN100448711C (en) * | 2005-05-30 | 2009-01-07 | 比亚迪股份有限公司 | Gear change mechanism, and speed changing method of motor vehicles |
| KR101078494B1 (en) * | 2005-07-22 | 2011-10-31 | 히다찌 겐끼 가부시키가이샤 | Shift control device for working vehicle |
| US8024925B2 (en) * | 2005-11-08 | 2011-09-27 | Caterpillar Inc. | Apparatus, system, and method for controlling a desired torque output |
| US8000863B2 (en) * | 2007-05-31 | 2011-08-16 | Caterpillar Inc. | Open-loop torque control with closed-loop feedback |
-
1985
- 1985-10-08 CN CN85107332.8A patent/CN1005788B/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101203399B (en) * | 2005-06-15 | 2011-07-20 | 沃尔沃拉斯特瓦格纳公司 | Vehicle |
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| Publication number | Publication date |
|---|---|
| CN85107332A (en) | 1987-04-15 |
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