The calculation of the differential transmission. Differential calculation. Differential guitar calculation formula
The outer circumferential module of conical gear wheels of differentials is recommended to choose by analogy of the design of the differentials of modern transport machines. For these purposes, the following formulas are used.
;
; (1)
;
where the empirical coefficient,
The number of satellite teeth,
Counting point
Satellite number
where the number of teeth of the semi-soul gear wheel.
The relation to conical differentials is, etc.
In all cases, the collection condition should be observed.
,
where an integer.
All seaming wheels differential spooled. Width of the gear crown
where is the external conical distance
The parameters of the source circuit are accepted according to GOST 13754-88. It is allowed to use the following parameters :. The displacement coefficients and are accepted equal to the module, but for the satellite is positive, and for the gear negative.
With the source circuit according to GOST, accept:
, then 
,
at, then 
.
In differentials, there is a blocking with a hydraulic friction clutch. If the friction clutch blocks the semi-axis of the differential, then the moment of friction coupling
where the calculated radius of the driving wheel,
KPD conical transmission.
By formula (1)
The number of flat-wheel teeth, and for the answer gears at 90º. Corresponds to the contour of the teeth rail.
The coefficient taking into account the impact of the bilateral application of the load,
The endurance limit of teeth with bending corresponding to the base number of voltage cycles,
The coefficient that takes into account the effect of the shape of the tooth and the concentration of bending
The coefficient that takes into account the dynamic load
The width coefficient of the gear crown.
To calculate the semi-axle gears and satellites, the highest moment on the grip of the leading wheels with the road surface is selected.
where the clutch coefficient
Ratio,
The efficiency of the side conical transmission.
Satellite
Satellite crosses are calculated from the circumferential force
where is the average radius of the circumferential force on the cross.
where the average radius of the surface of the contact of the satellite and spikes of the cross-axis relative to the axis of the semi-soles,
The diameter of the schip of the cross
The length of the cylindrical surface of the satellite under the spike of crosses.
Also calculate the sweat tension in contact of the spike crossliner with the differential housing
where the length of the cylindrical surface of the case of the differential under the spike of crosses.
The toothed wheels of the crossliner and a crusher of the differential are made of high-alloy steels used for the manufacture of transmission units, with cementation to a depth of 1.5 ... 1.9 mm and hardening to HRC e from 58 to 63 with a hardness of the core from 30 to 40. The differential housings are cast from Dake cast iron 35 ... 10 or steel.
Determine the number of satellite teeth according to the following formula
,
where the gear ratio from satellite to the semi-axis gear.
Usually taken in the calculations, based on the condition for the placement of the semi-axle gear of the spline end of the semi-axis diameter and the limitation of the size of the differential.
In the satellite differential from 2 to 4.
Pointers
Semi-axis serve to transmit torque from the mid-scene differential to the driving wheels of the machine and, in fact, are leading shafts. With the dependent suspension of wheels, the semi-axes are located inside the crankcase and, as a rule, are connected to the semi-axes of differential with the slots, and with the hubs of the leading wheels using slots or flanges that constitute one integer with the semi-axes. All types of semi-axes are calculated on fatigue resistance and static strength, taking on the calculation that the beams are not deformed. The following force actors are taken in the calculation:
- in the case of intensive overclocking or braking, the maximum torque and bending moments act on the axes;
- when driving machines, a bending moment is taken into account relative to the horizontal axis of the site;
- In the case of moving through the obstacle, a bending moment is taken into account relative to the horizontal axis to the field of a dangerous section of the semi-axis.
Consider the dynamism coefficient used for high-load vehicles ranging from 2 to 2.5, and for high-pass vehicles from 2.5 to 3.
When calculating the estimates of the static strength of the semi-axle, additional voltages are used:
s w: ASCII \u003d "Cambria Math" W: H-ANSI \u003d "Cambria Math" /\u003e
In this case, the equivalent voltage, which is compared with the allowable, is calculated by the following formulas
,
where the diameter of the semi-axis in a dangerous section.
For semi-axes and unloaded on ¾ semi-axes with intensive acceleration or braking
,
where the bending moments relative to the axes and.
When driving cars on the turn
When moving obstacles
In the existing structures, the diameter of the semi-axes in load vehicles accept 
mm.
Planetary broadcasts
The main relations of planetary mechanisms.
The planetary mechanism is called a mechanism consisting of gear wheels, in which the geometric axis of at least one wheel is movable. The geometric axis is called a satellite. Satellite can have one or more gear crowns, or consist of ingestion of several wheels.
Classification of three-part planetary mechanisms
The link in which the satellite axes are installed - drove (H). The geometric axis whose geometric axis coincides with the main axis of the mechanism - the central (A, B, K). The main link of the planetary mechanism is called the link, perceiving the external moment in a loaded transmission, and is central.
a - solar gear,
h - drove
g - satellite,
b - Crown gear (epicyclic).
The planetary mechanism that rotates all 3 main links is called differential. Planetary mechanisms are indicated by compliance with the existing satellites, engagement and parameter values. Planetary mechanisms in which the main links are 2 central wheels and drove, denotes 2K-H. The planetary gearbox may consist of one planetary mechanism or several connected to each other. The classification of the three-part planetary mechanisms of type 2k-h is given in the classification of three-part planetary mechanisms. Large distribution in the planetary gearboxes, three-bedned planetary mechanisms of type A and D are significantly less commonly like B. kinematic and power characteristics of three-bred planetary mechanisms are determined by its kinematic parameter R WSP: RSIDR \u003d "00000000"\u003e
where and the angular velocity and the frequency of the link is respectively.
Expressions To determine the parameter, taking into account the sign are specified in the classification table of three-bred planetary mechanisms. The reduced equation of the parameter R WSP: RSIDR \u003d "00000000"\u003e
This equation is often referred to as the basic equation of the kinematics of the three-bedroom mechanism. In some cases, use the parameter k. . In this case, the main equation of kinematics takes the following
Purpose of work:
Determine the load on the satellite teeth, semi-scenes,
cross and load from satellites on the differential body.
Prototype:
As a prototype, take the differential of the KIA SPECTRA car.
Differential conical, two-caliper
Determination of the load on the satellite tooth and semi-axle gear
The load on the satellite and semi-axis gear is determined from the condition that the district force is distributed equally between all satellites, and each satellite transmits the force with two teeth. District force acting on one satellite
where R1 is the radius of the force application,
nC - the number of satellites, NC \u003d 2;
Mmax - the maximum moment
engine-developed
Mmax \u003d 130 NM;
iT - gear ratio of transmission,
iT \u003d ICP1 * IgP \u003d 
;
CD - dynamic coefficient,
2.5\u003e KD\u003e 1.5, in the calculation of the CD \u003d 2.
Figure 12 Core Differential Scheme
Schip crossed under satellite is experiencing a cutting voltage
Transforming formulas, we get:
where we accept τrs \u003d 120 MPa, and on the basis of this you can find D:
Satellite spikes under satellite is also experiencing stress of crumpled:
where we accept σcm \u003d 60 MPa, based on this we find L1;
The spike of crosses under satellite is experiencing a crimping voltage at the fastening site in the differential case under the action of the district force:
where the radius of the application of force m;
where we accept σcm \u003d 60 MPa, and on the basis of this we find L2;
During the calculation, the load on the satellite teeth, semi-axle gears, crossbar and loads from satellites on the satellite body was determined. Loads calculated with all assumptions satisfy the appropriate conditions.
Previously, in most enterprises, the instrument guitar was considered technologists (at least as much as I know). At the moment, technologists consider differentials at some enterprises, and on some this "care" passed to the teboreschikov, which is, to say when it is required to make a sabank! This is what I think that with the mass production of the gear there is a transition to production at small enterprises, where this task goes to the shoulders of the tear ... Personally, my opinion and I have already talked about it - to count the differential should be the technologies, although this skill does not prevent the skin . Of course it is not difficult, but why is an extra responsibility? I think you will agree with me. Basically no one just wants to take responsibility!
What do you need to know and have to calculate the differential on the green-cutting machine?
- Permanent machine differential guitar.
- The angle of inclination by dividing diameter.
- Module.
- There should be a book of selection of replaceable gears (a great and more acceptable option in electronic form. For example, Petrik M.I., Shishkov V.A. (1973). Tables for selecting gear wheels. "Or" Sandakov M.V. - Tables For selection of gears. Reference. "
- Calculator. I use the calculator on the smartphone.
The formula for calculating the differential guitar:
c (machine differential) × sinβ / mk
That is, the constant differential of the machine multiplying the sinus of the angular corner and divided into the module / value k is the number of cutters of the cutter. Typically, the cutters are separated, if not, we divide the module to multiply for example on 2 - if the mill is doubled.
Guitar differential to worm wheels when cutting with a tangential feed, is considered to be in another formula!
Everything is simple, the main thing is not to be mistaken and not get confused in numbers!
Calculate the differential angle of 10 degrees, 33 minutes, 23 seconds. Permanent 15, Module 8. Milling cutter overhead.
We find the sine angle of 10 33 23. To do this, we translate this angle into a decimal. How to do it? 23/3600 + 33/60 + 10 \u003d 0.0063888888888880 + 0.55 + 10 \u003d 10,556388888889 Determine sinus 10,5563888888889, it is equal to 0.183203128805159.
Next, open the table of the selection of replacement gears (I use Petrik M.I., Shishkov V.A) and are looking for a number (gear ratio) 0.343505866509673. In this case, it is necessary to find the most closely as possible. Most of all suits 0.3435045. Differential guitar: 43 61 83 92 - the first value up the fractions, the second bottom.
Configure the differential guitar. 43 leading, 92 led. We put 43, connect it from 83, 83 on one shaft from 61, 61 connect from 92. That's:
Differential is a mechanism that distributes the torque summitable to it between the output shafts and ensures their rotation with unequal angular velocities.
Classification and Differential Requirements are considered in detail.
On modern cars, symmetric conical differentials obtained the greatest propagation (Figure 1.1). Such differentials, called often simple, are used both on passenger and trucks, and both as integrity and as an inter-axis.
Figure 1.1 - Calculated Symmetric Conical Differential Scheme
Satellites and semi-axes are performed with straight. The number of satellite and gear teeth can be both even and odd, but according to the assembly conditions, the condition should obey:
where is the number of teeth of the semi-axle gear; - number of satellites; K is an integer.
The spike of crosses under satellite is experiencing stress of crumpled and cut.
The stress of crumples S, Pa, calculated by the formula
, (1.2)
where is the moment on the case of the differential, n × m; - radius application of the axial force acting on the satellite axis, m; - the diameter of the satellite axis (schip diameter of the crosslinor), m; L - the length of the axis on which the satellite rotates, m.
Moment on the housing, n × m, the intercheses of the car with wheel formula 4 2 is determined by the formula
, (1.3)
where is the maximum torque of the engine, n × m; - gear ratio of the first gearbox; - gear ratio of the main transmission.
The radius of the application of the axial force, M, acting on the satellite axis, is determined by the formula
, (1.4)
where is the outer circumferential module, m.
The diameter of the schip of crosses, m, calculated by the formula
, (1.5)
where - permissible pressure between spikes and satellites, PA.
Permissible pressure between spikes and satellites of differentials:
· Light cars - \u003d 80 MPa;
· Freight cars - \u003d 100 MPa.
The length of the L, M axis, on which the satellite rotates, can be approximately determined by the formula
, (1.6)
where b is the width of the gear of the satellite, m; - Half of the angle of the initial cone of satellite, hail.
Half the angle of the initial cone of satellite, hail, calculated by the formula
, (1.7)
where is the number of satellite teeth.
Permissible stresses of crumpled - [s] \u003d 50 ¸ 60 MPa.
Cutting voltage, pa, satellite axis is determined by the formula
. (1.8)
Permissible cutting stresses - \u003d 100 ¸ 120 MPa.
The radial forces in the symmetric differential are balanced, the axial is perceived by the case of the differential.
The ends of the satellites are calculated on crumpled under the action of axial power. Axial force, n, determined by the formula
, (1.9)
where is the radius of the occupational power application in engagement, m.
The engagement angle is a \u003d 20 °.
The radius of the application of the district force in the gearing during calculations can be taken with an equal radius of the application of the axial force acting on the satellite axis.
The stress of crumpled, pa, the satellite end is calculated by the formula
, (1.10)
where is the diameter of the end surface of the satellite, which perceives the axial load, m.
The diameter of the end surface of the satellite, m, perceiving the axial load, is determined by the formula
. (1.11)
Permissible stresses of crusions - \u003d 10 ¸ 20 MPa.
The ends of the semi-axial gears are calculated on grounding under the action of the axial force acting on the semi-axle gear.
Axial power, n, acting on a semi-axle gear, are determined by the formula
. (1.12)
Matching the end of the head of the semi-axis gear, path, calculated by the formula
, (1.13)
where, the largest and smallest radii of the protorting surface of the gear, which perceives the axial load, respectively, m.
The largest radius of the gear surface can be taken equal to the radius of the axial force application, acting on the satellite axis.
The smallest radius of the gear surface can be approximately determined by the formula
, (1.14)
where is the radius of the semi-axis, m.
The minimum diameters of the semi-seizhes are shown in Table 1.2.
Table 1.2 - minimum semi-axes diameters
Continuation of table. 1.2.
The permissible stresses of the crumpled - \u003d 40 ¸ 70 MPa.
When turning, the number of satellite speeds on the axis does not exceed \u003d 20 ¸ 30 rpm. Therefore, the calculation of wear is not required. The number of revolutions increases sharply when bounces, however, this case is not characteristic of normal operating conditions.
The load on the satellite teeth and semi-axial gears is determined from the condition that the district force is distributed equally between all satellites and each satellite transfers the force with two teeth.
Settlement point on satellite and on the semi-axle gear, calculated by the formula
. (1.15)
Calculation of the teeth of the gear wheels on bending voltages is produced by formulas for conical main gears. Permissible tensions of teeth bending - \u003d 500 ¸ 800 MPa.
When choosing the basic parameters of gear wheels of symmetric conical differentials, tables 1.1 can be used.
Table 1.1 - geometric parameters of symmetric conical differentials
| Car | Number of teeth | External District Module, mm | Cone Distance, mm | Corner profile | Width of the crown, mm | Number of satellite | |
| Satellites | Gears | ||||||
| ZAZ-968. | 3,50 | 39,13 | 20 ° 30 ¢ | 11,0 | |||
| Moskvich-2140. | 4,13 | 35,53 | 22 ° 30 ¢ | 12,6 | |||
| VAZ-2101. | 4,0 | 37,77 | 22 ° 30 ¢ | 12,0 | |||
| GAZ-24. | 5,0 | 47,20 | 23 ° 30 ¢ | ––– | |||
| UAZ-469. | 4,75 | 44,90 | 22 ° 30 ¢ | 35,0 | |||
| GAZ-53A. | 5,75 | 62,62 | 22 ° 30 ¢ | 21,0 | |||
| ZIL-130. | 6,35 | 78,09 | 22 ° 30 ¢ | 27,0 | |||
| Ural-375 N | 6,35 | 78,09 | 20 ° | 27,0 | |||
| KAMAZ-5320. | 6,35 | 78,09 | 22 ° 30 ¢ | 27,0 | |||
| MAZ-5335 | 5,50 | 62,77 | 20 ° | 22,5 | |||
| KRAZ-257B1 | 8,0 | 98,39 | 20 ° | 30,2 | |||
| BelAZ-540A. | 8,0 | 98,39 | 20 ° | 30,2 | |||
| BelAZ-548A. | 9,0 | 110,68 | 20 ° | 37,0 |
1. Bocharov N. F. Designing and calculation of machines of high passability: Textbook for athmirs / N. F. Bocharov, I. S. Zitovich, A. A. Mongyan. - M.: Mechanical Engineering, 1983. - 299 p.
2. Bukharin N. A. Cars. Design, load modes, workflows, strength of car units: studies. Manual for universities / N. A. Bukharin, V. S. Prozorov, M. M. Schukin. - M.: Mechanical Engineering, 1973. - 504 p.
3. Lukin P. P. Designing and calculation of the car: a textbook for students of the athm following P. P. Lukin, G. A. Gasparyantz, V. F. Rodionov. - M.: Mechanical Engineering, 1984. - 376 p.
4. Opepchugov V.V. Car: Design Analysis, Elements of Calculation: Textbook for students of universities / V. V. ospchugov, A. K. Frumkin. - M.: Mechanical Engineering, 1989. - 304 p.
5. Designing vehicle transmissions: reference book / A. I. Grishkevich [and others]. - M.: Mechanical Engineering, 1984. - 272 p.
| |
Compilers
Alexey Vladimirovich Buynkin
Vladimir Georgievich Romashko
Let the differential transmission, which are known for the number of teeth of all the wheels (Fig. 9):
Fig. 9. Differential transmission. Example of calculation.
z. 1 =80; z. 2 =20; z. 2" =30; z. 3 =30; n. 1 \u003d 300 rpm; n H.\u003d 200 rpm.
It is required to determine the numbers of revolutions of all transmission.
According to the Willice formula: 
Sign "-" before the meaning n. 3 corresponds to the case when the direction of rotation of the link 4 is opposite to the direction of rotation of the links 1 and H..
n. 2 \u003d N. 2 'because z. 2 I. z. 2 'tightly fastened on one shaft.
If in differential transmission the leading links to bind with each other additional gear transmission, then it turns out closed differential transmission.
Differential closed gear
Closed differential transmission It has one leading link (mobility) and moving central wheels.
As an example, consider the differential transmission, (Fig. 10, but) in which two leading link 1 and H.. If these links close the wheel 1 ` , 5` , 5, 4, then a closed differential transmission will be (Fig. 10, b.).
Fig. 10 Preparation of differential closed transmission
Usually, a system of two algebraic equations is drawn up for kinematic research. One of them is the equation for determining the transfer ratio from the leading link to the slave of the differential part with the help of the Willis formula. The second equation is the closure equation to determine the transfer ratio of the ordinary part of the transmission.
As a result of solving the resulting system, the angular velocities of all links are determined, and, accordingly, the gear ratio of the mechanism.
For the case in fig. 10, b. We accept for the leading link 1. The system of equations is written in the form:
Numerator and denominator of the left side of equation (6) Delim on W 1:
,
using (7), we get
To determine the angular velocities of the satellites, we use the methodology from the previous example:
Planetary broadcasts
Planetary mechanism, which has one of the central wheels fixed, is called planetary transmission. Mixed central wheel called reference. For example, if in differential transmission (Fig. 10), the central wheel 3 is rigidly connected with the rack, the planetary transmission with one degree of mobility will be obtained (Fig. 11).
Consequently, setting the movement of the central wheel 1, get the value of the angular velocity drove H.. If W is given H.You can define W 1.
Planetary transmissions are used to obtain significant gear ratios, elevated efficiency values \u200b\u200bwith dimensions less than the dimensions of ordinary gear.
Fig. 11. Planetary transmission.
To withdraw the formula of the transfer ratio in the planetary transmission (Fig. 11), the formula of the Willis is applied:
,
since w 3 \u003d 0.
Consequently, with a leading wheel 1. 
With a leading leash H..
- gear ratio of processed movement with a fixed leash and a library 3: 
.
In general, for planetary gear:
where - gear ratio from rolling wheel 1 to a fixed central wheel n. When stopped leash H..
Determined by relations (8) for ordinary transmissions.
Mixed broadcasts
Transmissions consisting of ordinary and planetary mechanisms are called mixed or combined. The procedure for calculating such gear is the following:
1. The entire transmission is divided into separate simple types of known gear on the principle: the output link of the previous one is the input for the subsequent stage.
2. The transfer relations of the selected mechanisms are calculated.
3. The overall gear ratio of the entire mixed compound is equal to the product of individual gear ratios from clause 2.
4. Determining the angular velocities of central wheels and satellites is based on the methods set out in the previous sections.
As illustration, consider a number of examples.
Example 1. Determine the gear ratio of the gearbox (Fig. 12).
Fig. 12. Reducer scheme.
Decision.
a) dismember the mixed connection on the ordinary transmission with multiple engagement (1,2,2`, 3) and on the planetary gear (3`, 4,4`, 5, H.);
b) 
;
e) to find the angular velocity of satellites:
Example 2. Determine the gear ratio of the gearbox (Fig. 13).
Fig. 13. Reducer scheme.
Decision.
a) highlight elementary gears: (1,2); (2`, 3,3`, 4, H. 1); (H. 2 , 4`,5, 5`,6);
b) 
;
d) 
;
e) 
;
e) 
;
g) To, for example, find the angular speed of satellites 3 - 3` We use the formula:
where you can determine from paragraph d).
Example 3. Determine the gear ratio, W 4, W 5 gearbox (Fig. 14).
Fig. 14. Reducer scheme.
Decision.
a) we allocate the following steps: ordinary transmission 1,2,2`, 3; Planetary transmission 3`, 4,6, H.; Planetary broadcast H., 5,7,4`, 8; ordinary transmission 8`, 9;
in) 
(the "-" sign is selected in accordance with the rule of arrows);
d) 
;
e) 
;
g) 
;
h) with a leading track 1 of paragraphs B) and d) we find:
; Further, ,
.
Example 4. Determine on the initial data the number of teeth of the 9th and 10th wheel of the mechanism (Fig. 15).
Fig. 15. Reducer scheme
Given:z. 1 =20; z. 2 =60; z. 3 =20; z. 4 =15; z. 5 =60; z. 6 =65; z. 7 =78; z. 8 =24; n. 1 \u003d 3200 rpm; n. 10 \u003d 200 rpm.
Decision.
but) 
;
;
in) 
;
e) 
,
;
e) 
;
g) from the condition of the content of the entire mechanism:
h) 
.
Procedure for performing work
1. Make the kinematic diagram of the test gear. If the scheme is known, then go to clause 2.
2. Determine the degree of mobility and type of mechanism.
3. Depending on the condition of the task, to form the values \u200b\u200bof the source data: the number of teeth wheels, the module, angular velocities of the leading links, etc.
4. Create an algorithm for calculating a transfer ratio of the compound.
5. Conduct calculations.
6. If necessary, then determine the values \u200b\u200bof the angular velocities of all mechanism links, setting the numerical value of the angular velocity of the master.
7. For a field mechanism, check the correctness of the received gear ratio by a marking of the relative direction of rotation of the leading and slave links and measure the numbers of revolutions.
8. Make conclusions based on the results of work.
5. Options for calculated tasks
| № VA-RI-ANTA | Kinematic scheme | Conditions |
 | Given: z. 0 =20, z. 1 =30, z. 2 =100, z. 3 =100, z. 4 =30, z. 5 =90, z. 6 =20, z. 7 =30, z. 8 \u003d 10, W 0 \u003d 55 s -1. To find: i. 0-8, W 1, W 8. | |
 | Given: z. 0 =20, z. 1 =56, z. 2 =22, z. 3 =18, z. 4 =68, z. 5 =24, z. 6 =24, z. 7 =40, z. 8 =44, z. 9 =64, z. 10 =22, z. 11 =28, z. 12 =40, z. 13 =20, z. 14 =18, z. 15 =102, n. 0 \u003d 900 rpm. To find: i. 0-15 , n. 15 , n. 5 , n. 9 . | |
 | Given: z. 0 =20, z. 1 =40, z. 2 =35, z. 3 =70, z. 4 =15, z. 5 =30, n. 5 \u003d 115 rpm. To find: n. 1 , n. 4 . | |
 | Given: z. 0 =20, z. 1 =60, z. 2 =20, z. 3 =15, z. 4 =60, z. 5 =65, z. 6 =78, z. 7 =24, m. 8-9 =6, n. 0 \u003d 3200 rpm, n. 9 \u003d 200 rpm. Find: Armor distance between 8 and 9 wheels. | |
 | Given: z. 0 =24, z. 1 =24, z. 2 =28, z. 3 =80, z. 4 =28, z. 4 =26, z. 5 =30, z. 6 =12, z. 7 =28, n. 8 \u003d 250 rpm. To find: n. 0 . | |
 | Given: z. 0 =20, z. 1 =22, z. 2 =80, z. 3 =80, z. 4 =18, z. 5 =30, z. 6 =30, z. 7 =18, n. 0 \u003d 650 rpm. To find: i. 0-7 , n. 4 . | |
 | Given: z. 0 =80, z. 1 =30, z. 2 =40, z. 3 =28, z. 4 =24, z. 5 =42, z. 6 =40, z. 7 =80, z. 8 =28, z. 9 \u003d 40, w 0 \u003d 10 s -1. To find: i. 0-9, W 3, W 5. | |
 | Given: z. 0 =20, z. 1 =60, z. 2 =20, z. 3 =15, z. 4 =60, Z. 5 =65, z. 6 =78, z. 7 =24, n. 0 \u003d 3200 rpm, n. 9 \u003d 200 rpm. To find: z. 8 I. z. 9 . | |
 | Given: z. 0 =20, z. 1 =17, z. 2 =57, z. 3 =80, z. 4 =25, z. 5 =20, z. 6 =85, z. 7 =90, z. 8 =14, z. 9 =61, n. 0 \u003d 900 rpm. To find: i. 0-9 , n. 1 , n. 5 . | |
 | Given: z. 0 =20, z. 1 =40, z. 2 =30, z. 3 =34, z. 4 =30, z. 5 =34, z. 6 =28, z. 7 =40, z. 8 =20, z. 9 =70, n. 0 \u003d 300 rpm. To find: i. 0-9 , n. 1 . |
Literature
1. The theory of mechanisms and mechanics of machines: Tutorial for universities / K.V. Frolov [et al.]; MSTU them. N. E. Bauman; Ed. K.V. Frolova. - 5th ed., Sure.- M.: Publishing House MSTU. N. E. Bauman, 2004.- 662 p.
2. I. I. Artobolevsky. Theory of mechanisms and machines. M., 1988.
3. I. I. Artobolevsky, B. V. Edelstein. Collection of tasks on the theory of mechanisms and machines. M., 1973.