DE2258135A1 - MULTIPLE ROTOR SCREW DRIVE - Google Patents

Description

Vsesojuznyj ordena Trudovogo Krasnogo Znameni Naufcno-issledovatel ¹ ski j institut burοvoj techniki

MULTIPLE ROTOR SCREW DRIVE

The invention relates to hydraulic and pneumatic machines, in particular multi-turn rotor screw drives.

The invention can be particularly successful for hydraulic Bottom hole drives are used for lowering boreholes and for hydraulic pumps, compressors and in all cases when the working conditions require the arrangement of the engine in a restricted space while maintaining the possibility of relatively high torques or to generate a high flow rate (for pumps).

A multi-turn rotor-screw drive is known, which is used as a bottom hole hydraulic screw motor which includes a housing in which a inner elastic covering having stator is housed. There is a screw thread on the surface of the lining the end-

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guided.

In the interior of the stator sits, eccentrically arranged, a rotor, on the outer surface of which a screw thread is also executed.

The rotor and stator represent a kinematic pair that is in constant contact, similar to a pair of gears with internal toothing, and form closed ones Cavities.

The rotor axis is around the eccentricity size "e" offset with respect to the stator axis. The number of teeth on the helical surfaces of the stator and rotor correspond to yours Corridors. In the known rotor-screw drive, the number of teeth Z ^ d «ls the stator is one greater than the number of teeth

Z _{2 of} the rotor. The ratio between the pitches T and t of the stator or rotor is directly proportional to the ratio between the number of teeth:

T Z-,

_7th
^Z 2

The ratio between the number of teeth on the helical surfaces on the stator and rotor is called the kinematic ratio i designated.

In the known design of the multi-turn rotor screw drives as the basis for the formation of the profiles its cross section is assumed to be cyclical teeth (Hypoz / kloide or Epiz / kloide).

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The cross-section of the stator profile is mutually exclusive alternating sections of cycloid curves and arcs The profile of the rotor cross-section represents the envelope of the stator profile when rolling the maximum Generating pitch circle

represents that proceeding from the condition of an uninterrupted Contact between the helical surfaces of the rotor and stator is chosen.

The stator circuit is assumed to be the output circuit. The profile of the stator cross-section is used as the starting profile, that of the rotor, however, assumed as an assigned profile. The stator profile is an equilibrium of the cycloid curve, which is removed from the latter by the size of the stator tooth radius "r". The cycloid itself is made by rolling without slippage on the stator output target circle of a

assumed
Another V circle is formed, the radius "h" of which is equal to the eccentricity in the case of a centroid-like toothing. The diameter D _{1 of} the stator output circle is assumed to be D ^ = 2e Z ^.

The assigned rotor profile is used as the envelope of the stator output profile when the rotor rolling circle is rolled formed on the stator pitch circle.

In the known design of the ear hole sole drive, the rotor engine generates a power during operation considerable torque, which creates specific pressures at the contact points of the rotor and stator

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cause rapid wear of the rotor and stator.

In addition, the known types of rotor works various assembly tools for the production of the Stator and rotor required, which complicates the technology of manufacturing the entire motor.

The invention is based on the object of developing such a multi-turn rotor-screw drive that a smooth toothing of the rotor during operation and stator ensures that the wear and tear of the two the latter is reduced.

This object is achieved on a multi-turn rotor screw drive that has a stator with screw thread on the inner surface and one in the stator contains eccentrically seated rotor with outer helical surface, the cross-sectional profile of the stator one behind the other represents lying circular arcs, each of which on both sides at sections of a cycloid curve connected by rolling without slippage on the stator

The radius of which is selected depending on the size of the mentioned eccentricity ^egg output target circuit of another ^pend ^ * is formed ^ei kreiaes. The cross-sectional profile of the rotor represents the envelope of the stator profile

when rolling within the stator output target circle

of the maximum rotor pitch circle resulting from the conditional one

ν uninterrupted contact between the helical surfaces of the rotor and stator is selected.

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S.

_ 5 -

'According to the invention, the relationship between the Eccentricity size of the engine and the radius of the circular arc of the stator cross-sectional profile in the range of 0.3 ·. · 0.85 was chosen.

By selecting this ratio, © becomes minimal Contact pressure achieved in the rotor-stator pair, which increases operational reliability and increases the service life of the Engine is extended.

On the inventive design of the multi-course

Rotor screw drive is the basis of the formation of its

ί Possibility of degj ne cross-sectional profile the """" ^ use of an extra-

centroid-like toothing assumed, in which the radius

assumed
of the ^v circle, which is used when creating the cycloid curve, is not equal to the eccentricity distance.

Extracentroidenary interlocking is created by the

Relationship between the eccentricity size and the radius of the

assumed
mentioned ν circle.

According to the invention in this case the ratio between the eccentricity size and the radius of the assumed Circle in the range of 0.9 ... 0.98.

This will increase the uniformity of the helical surfaces

ye of the rotor. and stator enlarged, making ^{v more} relative

Slippage and thus also wear can be reduced.

In addition, the screw surfaces can by the invention

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to the
the stator and rotor with the same tool ^y are executed, thereby manufacturing the course of the whole engine simplified.

The invention is explained below with reference to the description of exemplary embodiments and the accompanying drawings explained in more detail. It shows:

Fig. 1 multi-turn rotor screw drive; Type of application with a hydraulic bottom hole drive! General view and partial longitudinal section;

Fig. 2 section H-II of Fig. 1;

Fig. 3 Development of the stator cross-sectional profile;

4 shows a diagram of the dependence of the specific pressure value on the characteristic value Ce;

5 multi-turn rotor screw drive; Type of application for a hydraulic pump, overall view and longitudinal section;

Fig. 6 section VI-VI of Fig. 5;

7 multi-start Kotor screw drive; Type of application in a compressor, overall view and longitudinal section;

FIG. 8 section VIII-VIII of FIG. 7;

Fig. 9 Multi-turn rotor screw drive, * type of application in a reduction gear, overall view and longitudinal section;

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Big. 10 Section XX the Pig «9»

The hydraulic helical © BohrloehBOhlenaii- ■ drive (lig.l). contains © in housing 1, in the rigid one © elastic Covering 2 attached let, .aaf its inner surface a ten-start screw thread is produced »The housing 1 with the lining 2 represents the stator 3 of the

Rotor drive mechanism. Inside the stator 3 sits with an eccentricity "e" of the Rote® 4, on whose external surface a nine-pitch screw thread is executed . Thus the kinematic ratio of the rotor drive mechanism is i = 9s10.

In the example given here, there is a. Rotor engine used with extracentroid-like cycloid delineation * In Fig. 2 is the cross-sectional profile of the rotor engine shown in which the cross-sectional profile of the stator 3 one after the other alternating sections of a cycloidal curve which the teeth of the stator 3 outlines, and the arcs with a radius "r" that defines the tooth gaps in the cross section of the Outline stator represents. A cycloidal curve that is called a The basis of the profile construction of the stator 3 is used by rolling without slippage at the starting target circle of the

assumed
tors 3 of another ^ circle, whose

Diameter depending on the eccentricity size "e" ' is chosen. Usually, the target output circle of the stator depends on the intended operating conditions of the engine dependent and is determined by the

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permissible diameter size determined.

The cross-sectional profile of the rotor 4 is a with reference to FIG the profile of the bar 3 associated with the outline and is called Envelope of the starting profile of the stator 3 when rolling the pitch circle of the rotor 4 on the pitch circle of the stator 3 formed.

Specific pressures arise at the contact points between rotor 4 and stator 3. The value of the specific Pressure quantity is given analytically in a general form by the following equation:

K = f (M, i Ce, L, E, M ), here is

M - the torque generated by the engine;

i ^Z 2
- - the kinematic ratio of the rotor-engine;

ej dimensionless geometric characteristic value of the rotor drive mechanism;

L - length of the rotor and stator;
^E i / A - physical-mechanical constants for the material of the elastic stator lining.

If M, L _t E and / Vf remain the same, the equation mentioned takes the following form:

k = f (i, G ₆ ).

In Fig. 4 is the dependence between the relative specific return value K and the characteristic value C for rotor -Thrusters with different kinematic ratios

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shown. From the S ¹ Ig. 4 it can be seen that the rotor thrusters have a value range of G _Q which corresponds to the smallest specific pressure values. During an investigation analysis it was found that the value range C. s 0.3 ···· 0 ₈ 85, in which the specific pressure values do not exceed the minimum value © by more than 15 ... 20%, is more optimal for all engines applies «In the example given here, a rotor drive line is shown,

is.
whose characteristic value C ₀ = Q, 55 £ ~ l) aaid © h, the specific pressure values could be reduced by ^ / 17% in comparison with the well-known hydraulic screw-like drilling loooiigoiilünaJitJriQfoen *

The extra centroid toothing assumed in this example is represented by the eccentricity number C 3 e. ge ¹¹

indicates. Here h - radius d ©! ^ ® ^ ¹ ™ ⁶¹¹ ® ^{11 of the} circle, which is used to create the cycloid curve® b@nu.tzt.

To reduce the mutual slip of the stator 3 and rotor 4 and to increase the uniformity of their helical surfaces, it is recommended to set the ebb centroid number in the range of G _Q = 0.9 »... 0.98 depending on the operating conditions and the materials of the stator 3 and the hotor 4.

In the example given, the extra centroid number is assumed to be C _{0 =} ei _ 0.95.

The hot or 4 of the rotor engine is through a two-joint connection 5 connected to the output shaft 6, on

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-lo the end of which the (not specified in the drawing) working tool of the bottom hole drive is attached. The output shaft 6 is mounted in the spindle 7 in radial bearings 8. The thrust bearings 9 arranged in the spindle 7 serve to absorb the axial load during operation of the bottom hole drive. The end of the shaft 6 is guided to the outside through a stuffing box IO. The housing 1 of the bottom hole drive is connected to the hydraulic pump (not shown in the drawing) by a transition piece 11 and a pipe distributor.

The operation of the drive at the bottom of the borehole is as follows.

A hydraulic pump presses the liquid into cavity A of the drive, in which the same pressure value is established. The cavity A is referred to as a high pressure cavity. The helical teeth of the rotor 4 and stator 3 touch and thereby form final chambers on the flight length ¹¹ T ' ^{1 of} the helical surface of the stator 3. Several chambers are connected to the high pressure cavity A and several chambers to the low pressure cavity β . This is why there is an unbalanced force and consequently a torque in every cross section of the engine. Under the action of these forces there is a radial deformation of the elastic covering 2 on the stator 3 and a displacement of the rotor 4 in a direction transverse to its axis.

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movement, in which v ^u Zahiieides stator 5 shifts.

The Kotor 4 drives via the two-joint connection 5 the output line 6 and consequently also that at its end fixed working tools of the bottom hole drive

When the rotor 4 is running, the radial forces determine the Value of the contact pressure quantity in the eotor-stator pair. aside from that the contact pressure is also dependent on the pressure gradient in the chambers of the drive connected to the high pressure cavity A and Bodice pressure cavity B communicates.

Due to the multiple turns of the stator 5 and rotor 4 the number of chambers and lines of contact increases, and the pressure gradient between the turns is reduced.

Therefore the proposed engine has a higher one Efficiency and can withstand a considerably greater load than an engine of the same size, but not one of the features mentioned above.

In Fig. 5 is a hydraulic pump in which a Rotor engine used is shown. The pump contains the housing 12 with a suction or pressure nozzle.

An elastic covering 15 with a screw surface is provided in the interior of the housing 12. The housing 12 with lining

15 forms a stator, inside of which a rotor 14 is eccentric sits, which has a cardan shaft 15 and intermediate shaft

16 is connected to a drive (not shown in the drawing). In the example given here, this is

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Rotor drive mechanism with a kinematic ratio ia - g ~ = s 2: 2 and a characteristic value of C ₈ = 0.5.

The rotor 14 is driven, whereby in the area of the Suction nozzle generates a negative pressure and the liquid is sucked into the cavity of the housing 12. While running of the rotor 14 with respect to the stator there is a pressure redistribution and an increase in funding.

The multiple turns of the rotor engine are guaranteed a relatively high liquid flow through the pump and

small dimensions. In the example given here the specific contact pressures in the rotor drive are reduced by ^ 24% compared to the known design.

In Fig. 7 is the application of the rotor engine shown for the construction of a compressor.

The compressor includes a housing 17 with the duct for coolant a ζuführung, one arranged in the casing 17 stator 18 and a rotor 19. The rotor is carried out via an output shaft 20 and propeller shaft 21. To accommodate axial and radial forces are bearings 22, A seal 23 is used to seal the augkajom $ r of the compressor. The operation of the device proceeds in a manner similar to that of the known rotary compressors.

In the construction of the compressor described here, a rotor drive mechanism with a kinematic ratio of 5 * 6 and a characteristic value C _Q m 0.5 is used. As a result, the specific contact pressure in the rotor-stator pair is reduced by XB>% compared to the known design

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of the rotor engine guaranteed.

In J ¹ Ig, 9 an example of the use of a multi-speed rotor drive mechanism as a reduction gear is shown. A rotor drive mechanism, which contains the stator 25 and rotor 26, is arranged in the housing 24 of the reduction gear. In contrast to the hydraulic and pneumatic devices, in which the length © "L" should not be less than the gear "T" of the stator screw surface, the length of the drive in the example shown here depends on the contact pressure and the rigidity of the Reduction gear determined starting. Inside the recess of the rotor 26 bearing 27 "in which a!» Anchor 28 is mounted, arranged »The latter workpiece is constructed as a crankshaft" in the shaft axis of 'the axis represents wave itself to the amount of eccentricity ⁿ e " The rotor 26 is connected by the cardan shaft 30 to the output shaft 29 of the reduction gear

drive connected.

The support bearings 31 are used to accommodate axial and radial forces.

The torque transmitted by the device is reduced by 'L ^ times, since the multi-speed rotor drive is a planetary gear with a gear ratio of Z ₂

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and the torque it ^e £ be IELT.

The rotor engine according to the invention ensures minimum specific pressure values on the transmission parts of the reduction gear.

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Claims (2)

PATENT CLAIMS: 1.) Multi-turn rotor-screw drive ^ one thing Stator with screw thread® on the inner surface and contains a rotor seated eccentrically in the stator with an outer helical surface, the cross-sectional profile of the Stator successively adjoining circular arcs, which alternate with sections of a cycloid curve, represents the by rolling without slippage on the stator output target circle assumed
of another ν circle is formed, the radius of which dius is assumed as a function of the size of the eccentricity mentioned, and the cross-sectional profile of the rotor an envelope of the stator profile during rolling within the stator output circle of the maximum rotor rolling circle represents that from the condition of uninterrupted contact between the helical surfaces of the rotor and stator is chosen, characterized in that the ratio of the eccentricity value "e" of the engine to the radius of the circular arc of the cross-sectional profile of the stator O) is selected in the range 0.2 ... 0.85. 2. Multi-turn Ttotor screw engine according to claim 1, characterized in that the ratio of the eccentricity value "θ" of the engine assumed
to the radius "h" of the ν circle in the range 0.9 · ... 0.98 is chosen. 309824/0337 Blank page