بســم الله الـرحمــن الرحيــم
اقدم لكم اكبر موسوعه كتب رياضيات فى الجبر فى العالم كله
================================================== ======
بدايه لضمان عدم حدوث مشاكل فى التحميل او فى تشغيل الكتب يرجى تحميل البرامج الاتيه:

1- برنامج انترنت دونلود مانجر اخر نسخه كاااامل مع الكراك
من هنا
http://www.seed-share.com/lrztx0cpjs37
او هنا
http://rapidshare.com/files/26926950...17new_full.rar
=================
2-برنامج adobe reader لقراءة الكتب الالكترونيه بصيغه pdf
من هنا
http://www.seed-share.com/5yu21rzx5dqh
او هنا
http://rapidshare.com/files/26646613...r910_en_US.exe
===============
3-برنامج لقراءة جميع الكتب بصيغه djiv هاااااااااااام جداااااااااااااااااا
من هنا
http://www.seed-share.com/bjkbepwtnr2s
او هنا
http://rapidshare.com/files/361120572/DJVU.rar
================================================== =======

قائمه بالكتب الموجوده فى الموسوعه


وصلنا لمرحله التحميل
الكتب جميعها مضغوطه و مقسمه الى خمس اجزاء
و مرفوعه على السيرفرات الاتيه
rapidshare.com
seed-share.com
و يمكن تحميل جزء من سيرفر و جزء من سيرفر اخر

download

seed-share.com -سريع جداااااااا و يدعم الاستكمال-

http://www.seed-share.com/g6zd2dvjpy2r
http://www.seed-share.com/asw5eddc4u45
http://www.seed-share.com/lllu1kvjyamj
http://www.seed-share.com/e36ceu1z97tw
http://www.seed-share.com/wi79znenkxaq


rapidshare.com
http://rapidshare.com/files/358660160/Algebra.part1.rar
http://rapidshare.com/files/358660156/Algebra.part2.rar
http://rapidshare.com/files/358660169/Algebra.part3.rar
http://rapidshare.com/files/358660166/Algebra.part4.rar
http://rapidshare.com/files/358660133/Algebra.part5.rar

الملفات المرفقة

Pump Power Calculator.mht.zip‏ (100.2 كيلوبايت)

وصف البرنامج


يعتبر هذا البرنامج من أقوى برامج صيانة وتشخيص أعطال السيارت حيث يحتوى على معلومات عن كافة أنواع السيارت والشاحنات من موديل 1982 وحتى 2009 .
1-يحتوى البرنامج على خرائط وصف دقيقة كهربية كانت أو ميكانيكة ومعلومات عن كل كبيرة وصغيرة بالسيارة.
2- كما يحتوى البرنامج على أكواد الخاصة بالأعطال الناتجة عن أجهزة الفحص وشرح طريقة صيانة هذة الأعطال بالتفصيل خطوة بخطوة معك حتى الوصول إلى حل المشكلة ياعنى بقيقولك الكود اللى طالع دة فين بالظبط .
3- يمكن عن طريق هذا البرنامج لكل دارسى ميكانيكا السيارات أن يختار نوع معين من السيارات ويدرس كل كبيرة وصغيرة عنة وبالتالى يكون قد تعود على الرموز والمصطلحات الخاصة بهذة الماركة وهو مما يأهله لأن يعمل فى توكيل مرسيدس أو بى أم مثلا .
4 - مما سبق يتضح لنا أن بهذا البرنامج لن يقف أمامك أى عطل كان ميكانيكى أى كهربى لأنه يعطيك الوصف الكامل بالصور والخرائط عن كل جزء بالسيارة مهما كان نوعها


وصف البرنامج من الشركة المصنعة بالغة الإنجليزية

Automotive repair shops that use the ALLDATA system have a clear differentiation from other repair facilities. ALLDATA-equipped shops can provide their customers with the most accurate repair estimates and proof of diagnostic and repair procedures. ALLDATA also includes factory-correct maintenance schedules that itemize additionally needed services. Moreover, ALLDATA helps shops build consumer confidence and loyalty.

Professional repair shops need current, factory-correct information to meet the complex repair demands of todays automotive industry. ALLDATA shops have fast access to the industrys best information for vehicles from 1982 to present including TSBs, maintenance schedules, manufacturer recall information, OE solutions, and factory images and diagrams.

ALLDATA DVD, the leading computer-based diagnostic, repair and estimating information system, can help you boost shop performance and build customer loyalty as you efficiently repair more makes and reduce comebacks.

1.The most comprehensive information for 1982 to present vehicles

2.OEM images, diagrams and diagnostic flow charts

3.Parts and labor information

4.Maintenance schedules

5.Manufacturer TSBs and Recalls

6.Integrated estimating software

7.OEM wiring diagrams with connector, ground, power distribution and splice information

8.A2Z Component Search - the fastest route available to component information

whether you measure productivity by the number of vehicles repaired in a day, the variety of vehicles youre able to work on, or the time spent on diagnosis and repair, using the right information and shop management tools is vital to the success of your business. ALLDATA can help you succeed in every way

Os: Win 98, WIN2000, WIN XP

محتوى البرنامج

DM1
DM2
DM3
DM4
DM5
DM6
IMPORT 01
IMPORT 02
IMPORT 03
IMPORT 04
IMPORT 05
IMPORT 06
IMPORT 07
IMPORT 08
IMPORT 09
IMPORT 10
IMPORT 11
IMPORT 12
IMPORT 13
IMPORT 14

20 DVD واسطوانة تركيب

حجم البرنامج كامل : 160 جيجا بيت

صور لإصدار البرنامج



لمزيد من التفاصيل عن مكونات ال 20 dvd وطريقة الحصول على البرنامج وتجربة البرنامج عرض تجريبى والمزيد من البرامج الأخرى

Cylinders find many applications, two of the most common categories being :
- fluid containers such as pipes and pressure vessels - interference-fitted bearing bushes, sleeves and the like.
Cylinders can act as beams or shafts eg. ( load building blocks which have already been examined ) but in the present context cylinders are loaded primarily by internal and external ( gauge ) pressures pi and po due to adjacent fluids or to contacting cylindrical surfaces.
The following notes examine cylinder safety and derive appropriate design equations. Since the analysis presupposes an elastic material, superposition may be applied if other loading mechanisms such as bending or torsion occur. The treatment ignores end effects and the axial variation of pressures and stresses - so all cross- sections are loaded and stressed identically, and cylinder length is of no consequence. Secondary stresses arising from incompatibility between cylinder and end closure are examined in the context of pressure vessels.

Cylinders are classed as being either :

The tangential stress is uniform across the wall; so, from equilibrium of the free body : σt = ( pi Di - po Do ) / 2 t
Since Di / t > > 1, this equation with ( i), yields :
( 1) σt = Δp Di / 2 t where Δp = pi - po
σa = Δp Di / 4 t (CLOSED) or σa = 0 (OPEN)
The radial stress is zero, the tangential stress is always the principal of greatest magnitude, and the axial stress is either zero in the case of open thin cylinders or half the tangential stress in closed thin cylinders. The Mohr's circles thus appear as shown. Derivation of the design equations corresponding to the various failure theories is left as an exercise for the reader :-

Shafts rotating only at constant speed n (rev/s) are considered here, and as shafts are usually statically determinate they may be examined by the techniques of elementary statics. Also, since - power = force ( N) ∗ linear velocity ( m/s) in translational applications and - power = torque ( Nm) ∗ angular velocity ( = 2π n rad/s) in rotational applications, . . . . then it follows that torque is a major load component in power transmitting rotating shafts.
Torque may be transferred to or from the end of one shaft by a second coaxial shaft - this is a pure torque, a twist about the shaft axis. The transfer is accomplished by a shaft coupling (illustrated in the Squirrel Cage Motors chapter) which consists of two often identical half-couplings which are each mounted on one of the shafts before being connected together non-permanently.
The mounting of a half-coupling on a shaft must prevent relative rotation when torque is applied - this is achieved by a positively interlocking element exemplified by a key (or a derivative of this such as a spline) or by friction. Shown here is the free body of a shaft keyed to a coupling half - the torque on the shaft is equilibrated by an equal and opposite torque on the half-coupling. Free bodies of the individual elements clarify how the key's faces give rise to an equilibrating couple on both the shaft and the half-coupling (refer to the tutorial problems for more details).
The typical friction-based mounting below comprises a split tapered bush which is forced by screws into a mating taper machined in the bore of the half-coupling. The bush contracts onto the shaft causing high pressures and corresponding high surface friction which equilibrates the torque - provided tightening is sufficient.
Torque may be transferred also at any point along a shaft by a gear, belt pulley, or chain sprocket for example, mounted on the shaft as described above. These common elements apply forces offset from the shaft axis, and therefore useful torque T must be accompanied by a corresponding radial load with consequential bending - this is why the generalised shaft design model ( 11) incorporates both torque and bending moment load components.
A spur gear and a belt pulley are sketched, each subjected to loading tangential to its effective or pitch cylinder of diameter D. The load on the spur gear arises from inter-tooth contact with its mating gear and comprises two components - the useful tangential component Ft and the unwanted but unavoidable radial component Fr (commonly 0.36 Ft ). Gear forms other than spur ( see the Spur Gears chapter) give rise also to a load component parallel to the shaft axis - but for all gears, shifting the offset force as above, T = Ft D/2.
A belt, being flexible, cannot withstand compression - the pulley is therefore subjected to two strand tensions Fmax and Fmin both of which must exceed zero. The net torque T = ( Fmax - Fmin ) D/2 is clockwise here. The tension ratio Fmax/Fmin must lie between a lower limit of unity (corresponding to no torque transfer) and an upper limit dictated by incipient belt slip around the pulley. (This may be demonstrated by equally pulling the ends of a bit of rope wrapped around a post, then progressively increasing the pull on one end.) A chain sprocket is similar though the minimum tension may drop to zero due to the positive drive not relying on friction.
The mounting of a half-coupling and the like on a shaft is, locally, intrinsically indeterminate. This is exemplified by the pulley boss illustrated which extends from A to C along the stepped shaft. The actual distributions of bending and torque in the shaft are shown. To the left of A and to the right of C there are no immediate transverse loads, so the bending moment is linear. But within AC the boss contributes to the shaft's stiffness and also distributes the pulley load gradually into the shaft, so the bending moment variation is non-linear. Similarly the torque is some constant value (zero here) in the shaft to the left of A and another constant value T to the right of C - within AC the torque increases in a complex indeterminate fashion.
No attempt is made to resolve this bending/torsional indeterminacy - the actual distributions are instead replaced by approximate distributions based on external loads concentrated at the mid-point B. This leads to a bending moment diagram characterised by straight segments and a torque diagram which increases stepwise at B. The approximation is justified in view of unknown stiffness details and stress concentration due to shoulders (used for positive longitudinal location) and mountings (square keys, shrink fits etc.) In this example a cross-section between B and C is critical since the diameter is the smaller DA (neglecting the blending radii which reduce stress concentration at the shoulder), the torque is the fully developed T, and the bending moment is to all intents and purposes the peak MB.
Shafts are supported in two bearings (sliding or rolling) which allow the shafts to turn freely - there is no appreciable torque exerted by the bearings. A sliding bearing needs a lubricant film in the clearance space between shaft and bearing bush; in the fully hydrodynamic bearing illustrated the oil is dragged into the wedge-shaped gap causing a pressure build-up (similar to that in hydroplaning) which supports the shaft without metal-to-metal contact and little friction.
A rolling bearing (of which the ball bearing illustrated is but one example) comprises two hardened races between which a number of identical hardened elements roll. Not shown are various necessary details such as means for preventing axial movement of races, for dust sealing and for lubricant retention.
There are many different embodiments of these two bearing classes. A bearing supports a shaft over a finite axial length and so is intrinsically indeterminate no matter what its form - however it is approximated like the boss ABC above by a concentrated reaction at its mid-point.
The transverse forces on a shaft are seldom coplanar, so it is usually necessary to resolve forces into two convenient orthogonal longitudinal planes and to separately consider bending in each. For example the horizontal shaft ABCD, figure (a), is simply supported in bearings at A, D and carries gears or pulleys at B, C.

We shall use a tightened nut and bolt, in which the detailed stress variation is extremely complicated, to illustrate some of the simplifying assumptions which are usually made in routine analysis and design.
The leftmost sketch below shows an assembly comprising a nut and bolt which fasten two components together. The nut and bolt pair can be regarded as a sub-assembly or component in its own right. Before any identification of the stresses can be attempted, all external effects on this sub-assembly must be known. A free body of the nut and bolt demonstrates that the external load on them is the force P due to contact over annular areas with the two fastened components.

The flow analogy is useful when visualising how stress is transmitted through a loaded component. In the analogy, lines of force (or force paths ) in the component are likened to streamlines in a fluid channel whose shape is similar to that of the component - fluid enters and leaves the channel at locations which correspond to the areas where the external loads are applied to the component.

A free body of portion of the bolt which includes the bolt head shows that the external load P is equilibrated by stress σ in the shank. If the free body boundary cuts the shank in the middle then the stress is uniform across the shank cross-section of area A - that is σ = P/A.
But if the boundary lies close to the head or to the thread and nut, then stress concentration occurs and the maximum stress is greater than P/A.
If it is required to calculate the elastic extension, δ, of a bolt whose length L is relativey large, then a first approximation neglects stress concentration to obtain δ = Lε = L(σ/E) = LP/AE = P/k where the stiffness , k, of the bolt is defined as k = AE/L.
If the accent is on bolt safety rather than on deflection, then the core area Ac should be used for stress calculations - this minimum area in the force transmission path is formed by a transverse plane cutting the bolt thread between the plain shank and the nut's contact face.
The rightmost sketch above employs similar reasoning to illustrate details of the complex transfer of force across the thread into the bolt, together with the high stress concentration in way of the thread root, which may lead to localised yielding.

The external effects on each member of an assembly - the loads and deformations - must be resolved before stresses and strains internal to the member can be examined. If the assembly is statically indeterminate then resolution is carried out by a three-pronged attack :-

( 2) εx = [ σx - ν ( σy + σz ) ] / E + αt ; γxy = τxy / G etc.
which includes a thermal expansion term due to the temperature rise t.
If a component is loaded uniaxially and uniformly then, like the bolt above, equations (2) degenerate to :-
( 2a) δ = P / k + L α t
where δ is the extension of the component whose length is L and cross-sectional area is A, and on which the tensile load is P; the axial stiffness of the component is k = AE/L.
If the load is compressive or if the deformation is a shortening then the signs of the various terms of ( 2a) will have to be changed by inspection or by the positive tensile convention.
If a component is bent then its stiffness (load/deflection) follows from beam theory

بسم الله الرحمن الرحيم


متوفر لدى الحمد لله أخر إصدار من أقوى برامج صيانة السيارات الألمانى ELSA WIN 3.7 لصيانة وتشخيص أعطال (SKODA-VW-SEAT-AUDI) البرنامج متميز جدا فى تشخيض الاعطال وإعطاء بيانات كاملة عن كل جزء بالسيارة حتى مكان تركيب المسمار لكل جزء داخل السيارة وخريطة كاملة للأعطال وطريقة إصلاحها بشكل ممتاز وهيوفر على القائم بعملية الصيانة جهد كبير جدا


وصف البرنامج من الشركة المصنعة

ELSA Win 3.7 Electronic Service Information System for Windows Versions Elsa 3.7 works under anyone WINDOWS NT (SP6a), WINDOWS 2000 SP2 or WindowsXP. The program is completely established on a hard disk (full installation Audi + VW with all accessible languages borrows more than 10 Gb). The program Elsa 3.7 contains the detailed de......ion of technology of repair, electric schemes, bodyworks, the catalogue of spare parts for guarantee replacement. On "old" models of the information it is not enough. The full information in the program Elsa 3.5 is submitted in German, in English and others If during installation of disks Audi and VW the some people CD will not be requested - be not frightened, on missed CDs there is an information on others (Danish, Polish and others languages..... If you will mark all languages - that the program will request ALL CDs. The full information on repair basically on new automobiles 1986-2009, electric schemes 1992-2009. In new versions of programs add the information not only on new, but also on old machines. For normal work of the program it is required to establish disk UTILS CD, INSTALL CD and last UPDATE Audi and VW.

صورة البرنامج




للمزيد من المعلومات عن كيفية الحصول عن البرنامج يرجى زيارة هذا الرابط


أضغط هنا

بسم الله الرحمن الرحيم

محتاج جهاز تشخيص اعطال مع العلم ان اكثر شغلى فى السيارات اليابانيه والكوريه وبعض الاوربيه مع العلم انى توصلت لنتيجه ارجو تاكيدها وهو carman scan vg + وشكرا