RU2321767C1 - Screw hydraulic gerotor motor - Google Patents

Abstract

FIELD: oil and gas producing industry.

SUBSTANCE: invention relates to gerotor mechanisms of screw hydraulic motors in which rotor with bit is rotated by fluid medium delivered by pump which are used in drilling oil and gas wells. Proposed screw hydraulic gerotor motor has stator in form of tubular housing with fitted on elastomer, for instance, rubber lining with internal helical teeth, and rotor arranged inside stator with external helical teeth whose number is less by one than number of teeth of lining, pitches of helical teeth of lining and rotor are proportional to number of their teeth, and central longitudinal axes of rotor and lining are displaced relative to each other through value of eccentricity. Invention contains expressions and relations improving energy characteristics, mainly, developed power and torque, by providing maximum cross section area occupied by working medium at equal contour diameter, value of eccentricity of engagement in mechanism, number of teeth of lining and rotor owing to optimization of values of radii of circumferences whose envelopes inscribe end face profiles of teeth in lining and rotor, thus providing reduction of hydromechanical losses owing to uniform tension in all phases of contact of lining and rotor teeth, improved sealing over contact lines in zones of poles of engagement and reduction of contact loads in zone of maximum sliding speed.

EFFECT: improved energy characteristics.

3 cl, 7 dwg

Description

The invention relates to gerotor mechanisms of screw multi-start hydraulic motors, the rotation of the rotor with a bit in which is carried out by pumping a fluid, for drilling oil and gas wells.

A known gerotor mechanism with internal extracentroid engagement, in which the end profile of the teeth, for example, the stator is taken as the initial one, outlined by the equidistant of the shortened epicycloid or hypocycloid, and the conjugate profile of the rotor teeth is made as an envelope curve of the original profile (SU 93032 A, 03/21/1962).

A disadvantage of the known mechanism is that for the formation of the teeth of the rotor and stator (core of the mold) requires a different gear cutting tool, for example two worm cutters, and with the change in the number of teeth of the mechanism during its design and manufacture, the number of worm cutters required increases, which does not provide economic advantages.

A multi-way gerotor mechanism of a screw hydraulic machine is known, containing elements in the form of a stator and plates fixed therein with internal helical teeth made of elastomer, for example rubber, and a rotor with external helical teeth, the number of teeth in the stator lining being more than the number of rotor teeth per unit , the stator axis is offset relative to the axis of the rotor by an eccentricity equal to half the height of the teeth, and the end profile of the teeth of one of the elements is made as an envelope of the initial contour of the rail, the truncated cycloid equidistant with a displacement, while the end profile of the teeth of another element is made in the form of the envelope of the first element envelope when their centroids are rolled without slipping, and the equidistance value is half the magnitude of the diametrical interference in engagement (RU 2194880 C2, 12.20.2002).

A disadvantage of the known design is that it does not take into account some operating conditions, for example, temperature and loading conditions when drilling rocks of different hardness for "hot" wells with temperatures above 100 ° C, which require multi-start gerotor screw mechanisms with a gap in the engagement of the rotor-stator .

The use of downhole motors with an interference fit in the engagement of the gerotor screw mechanism reduces reliability and service life, which is explained by increased wear, a sharp decrease in energy characteristics, essentially developed power and torque, as well as jamming of the mechanism.

Another disadvantage of the known design is the inability to change the interference fit and correct the shape of the teeth of the rotor and stator without changing the outer diameters of the rotor and / or stator, which does not allow a reliable seal along the contact lines in the gerotor screw mechanism with a “zero” interference fit.

A known gerotor mechanism comprising a stator with internal helical teeth made of an elastic material, such as rubber, and a rotor with external helical teeth, the number of which is one less than the number of stator teeth, the rotor axis being offset relative to the stator axis by an eccentricity equal to half the radial the height of the teeth, the moves of the helical teeth of the rotor and stator are proportional to their number of teeth.

The stator teeth profile in the end section is made as the envelope of the initial contour of the cycloidal rack, outlined by an equidistant with a radius R _{C1 of the} shortened cycloid, and the profile of the teeth of the rotor in the end section is made as the envelope of the other initial circuit of the cycloid rack with the equidistant radius of R _C2 , made more than R _C1 or the related relation R _C2 = R _C1 + (0.1 ... 0.5) E, where E is the radius of the generating circle equal to the eccentricity (RU 2166603 C1, 05/10/2001).

An embodiment of the known invention is the implementation of the gerotor mechanism in such a way that the profile of the stator teeth in the end section is made as the envelope of the initial contour of the cycloidal rack, outlined by an equidistant curve with a radius R _{C1 of a} shortened cycloid, and the profile of the teeth of the rotor in the end section is outlined by conjugate arcs of circles, and the protrusion of the rotor tooth is outlined by an arc of radius R _B greater than the radius of the stator equidistant R _C1 , or is associated with it by the ratio R _C2 = R _C1 + (0.1 ... 0.5) E, and the profile of the cavity of the rotor tooth is outlined by an arc of radius R _V , depending on the number of teeth of the rotor, its outer diameter and eccentricity (RU 2166603 C1, 05/10/2001).

A disadvantage of the known gerotor mechanism is that these gerotor mechanisms require selective assembly of working pairs due to the need to select the rotor and stator by radial interference.

In addition, during operation due to the occurrence of lateral interference, evenly distributed during convex-concave contact of the rotor tooth with the cavity of the stator tooth, increased wear of the lateral sides of the stator teeth made of elastic material occurs, while due to the presence of radial and lateral interference in the engagement friction forces in the zones of contact of the teeth, creating moments of resistance, preventing the rotation of the rotor around its axis and its planetary motion, which affects the energy characteristics of the mechanism.

Due to the fact that the initial contours of the tool rails of the rotor and stator are different, the possibility of manufacturing the rotor and core of the stator mold with one tool is excluded.

Closest to the claimed invention is a gerotor mechanism of a screw hydraulic machine containing a stator and a rotor eccentrically located in it, the teeth of which are in continuous contact and have a difference of their numbers equal to unity, the end profiles of the stator and rotor are formed by a common initial profile of the rail (mesh) with an offset , and the profile of this contour is outlined by the equidistant of the shortened cycloid, while the largest permissible positive and largest negative bias of the rail contour are given by the relation niy:

Δh _n ≤0.73aZ ₂ ^0.5 ,

| Δh _from | ≤1.04aZ ₁ ^0.41 ,

and the permissible value of the contour diameter is limited by:

D _{to min} ≤D _to ≤D _{to max} ,

Where

D _{to max} = D _f1 + 2Δh _n ,

D _{to min} = D _f1 -2Δh _from ,

where Δh _n , Δh _from is the largest allowable positive and greatest negative bias, respectively, of the rail contour,

D _{to max} , D _{to min} - the largest and smallest values of the contour diameter,

a is the eccentricity of the meshing mechanism,

Z _{1, 2} - the number of teeth of the stator and rotor, respectively,

D _f1 is the nominal diameter of the stator troughs in the absence of bias of the initial circuit, which is set by the formula:

D _f1 = 2 (rZ ₂ + a + r _c ),

where Z ₂ - the number of teeth of the rotor,

r is the radius of the rolling circle forming a normal cycloid of the original rail contour,

r _c is the distance from the shortened cycloid to the profile points of the initial rail contour (RU 2232317 C1, 07/10/2004).

A disadvantage of the known design is that with the selected contour diameter D _k , the eccentricity value "a", the numbers Z _{1, 2 of the} teeth of the stator and rotor, respectively, the passage area (the area occupied by the working fluid) of the multi-start gerotor mechanism cannot be changed and therefore, there is no way to improve energy characteristics, for example, the developed power and torque in the engine for rotating the rotor from the pump fluid supply or the developed pressure and flow rate in the pump for feeding ekuchey medium due to rotation of the rotor.

The disadvantages of the known design are explained by the fact that the shape of the initial engagement contour (rail) is standardized and is set essentially in accordance with OST 39-164-84, while the contour diameter D _k can only be changed by replacing the number of teeth Z _{1 of the} stator or eccentricity "a" gear engagement, which imposes restrictions on the design of the mechanism and the optimization of the characteristics of the engine or pump.

The technical problem to which the invention is directed is to improve the energy characteristics of a gerotor screw hydraulic motor, essentially developed power and torque, by ensuring the maximum cross-sectional area occupied by the working fluid, with the same contour diameter D _k , the magnitude of the gear eccentricity, the number of teeth of the lining and the rotor by optimizing the values of the radii of the circles, the envelopes of which outline the end profiles of the teeth in the lining and the rotor, as a result of which there is a reduction in hydromechanical losses due to uniform interference in all phases of contact between the teeth of the plate and the rotor, improved compaction along the contact lines in the area of the poles of engagement, and reduced contact loads in the zone of maximum sliding speeds.

The essence of the technical solution lies in the fact that in a gerotor screw hydraulic motor containing a stator, which is a tubular body with an elastomer cover fixed to it, for example, rubber, with internal helical teeth, and a rotor located inside the stator with external helical teeth, the number of which one less than the number of teeth of the lining, the moves of the helical teeth of the lining and the rotor are proportional to their number of teeth, and the central longitudinal axis of the rotor and the lining are offset by an eccentric value According to the invention, the end profile of the teeth in the elastomer lining is outlined as an envelope of the radius r _s when the coordinate system X _os , Y _os , which belongs to a circle of radius r _s , and the center of a circle of radius r _s is located on a circle with radius R _oc , drawn from the center of the coordinate system X _OS , Y _OS , and the center of the coordinate system X _OS , Y _{OS is} offset from the central longitudinal axis of the plate by the amount of eccentricity a _w between the central longitudinal axis of the rotor and the plate and is defined by the expression:

R _oc = r _if -r _s -a _w ,

where r _if is the radius of the cavities of the teeth of the lining, the angle of rotation φ _c of the coordinate system X _os , Y _os relative to the fixed coordinate system X _k , Y _k , the center of which is located on the central longitudinal axis of the lining, and the angle of rotation ψ _from the coordinate system X _c , Y _c , the center of which is located on the central longitudinal axis of the plate, relative to the fixed coordinate system X _to , _{To to} are connected by the ratio:

ψ _c = φ _c Z _p / Z _c ,

where Z _p and Z _c - the number of teeth of the rotor and, accordingly, the lining, and the coordinates X _s , Y _{from the} nominal profile of the lining are defined by the expressions:

X _c = (X _oc cosφ _c -Y _oc sinφ _c + a _w ) cosψ _c + (X _oc sinφ _c -Y _oc cosφ _c ) sinψ _c ,

Y _c = - (X _os cosφ _s -Y _os sinφ _s + a _w ) sinψ _c + (X _os sinφ _s + Y _os cosφ _c ) cosψ _c ,

in this case, the end profile of the teeth of the rotor is made in the form of an envelope of teeth of the plate made of elastomer or in the form of an envelope of the initial contour of a cycloidal rack, outlined by the equidistant of a shortened cycloid, or in the form of an envelope of the initial contour of a rack formed by pairing circular arcs.

In addition, the radius r _s , the envelope of which forms the end profile of the teeth in the lining, and the eccentricity a _w between the central longitudinal axes of the rotor and the lining are related by the relation: r _s = (0.618 ... 2.618) a _w , and the hardness of the lining with internal helical teeth made of rubber is 70 ± 3 units. Shore A.

This embodiment of a gerotor screw hydraulic motor provides the maximum cross-sectional area occupied by the working fluid with the same contour diameter D _k , the magnitude of the eccentricity of the engagement a _w mechanism, the number of teeth Z _c (lining) and Z _p (rotor) by optimizing the radii r _s , r _m circles whose envelopes outline face profiles of the teeth in the second plate and the rotor, respectively, thereby enabling reduction hydromechanical losses due to uniform tightness in all phases of the teeth contact and a rotor electrode, improve the seal along the contact lines in the engagement pole area and reducing contact stresses in the maximum sliding speeds zone.

The execution of a gerotor screw hydraulic motor in such a way that the radius r _s whose envelope forms the end profile of the teeth in the plate and the eccentricity a _w between the central longitudinal axes of the rotor and the plate are related by the relation: r _s = (0.618 ... 2.618) a _w , additionally reduces the likelihood of resonant transverse vibrations of the engine in the borehole under axial loads that change when the engine acts on the bottom due to the synchronization of multi-start multi-step screw (lock) chambers between the teeth of the mouth pa and plates.

Below is the best version of a gerotor screw hydraulic motor for drilling horizontal oil wells.

Figure 1 shows a longitudinal section of a gerotor screw hydraulic motor.

Figure 2 shows a cross-section aa in figure 1 of the stator and rotor of the rotor screw hydraulic motor, the ratio of the number of teeth of the rotor-lining is 5/6.

Figure 3 shows a diagram of the formation of the end profile of the teeth in the lining of the elastomer.

Figure 4 shows the formation of the end profile of the teeth in the lining of the elastomer, which is outlined as an envelope curve of the set of radii r _s when turning the coordinate systems shown in figure 3, with the following values:

r _s = 7.6125 mm, a _w = 3.5 mm, r _if = 31.675 mm with a nominal diameter of the valleys of the lining D _k = 63.35 mm.

Figure 5 shows an example of a gerotor screw hydraulic motor with the same contour diameter D _to :

lining r _if = 31.675 mm from the circumference r _s = 7.6125 mm;

the end profile of the teeth of the rotor, r _a = 28.175 mm, is made in the form of an envelope of the teeth of the lining of the elastomer;

S = 592 mm ² - the cross-sectional area occupied by the working fluid; there are no errors in engagement (interference and clearances).

Figure 6 shows an example of a gerotor screw hydraulic motor with the same contour diameter D _to :

lining r _if = 31.675 mm from the circumference r _s = 7.6125 mm;

the rotor r _a = 28.175 mm is made in the form of an envelope of the initial contour of the cycloidal rack (gearing), outlined by the equidistant of a shortened cycloid;

S = 588 mm ² - the cross-sectional area occupied by the working fluid;

the numbers 0.0539, as well as 0.045 and 0.0042 indicate the interference in mm in engagement.

Figure 7 shows an example of a gerotor screw hydraulic motor with the same contour diameter D _to :

lining r _if = 31.675 mm from the circumference r _s = 7.6125 mm;

the end profile of the teeth of the rotor r _a = 28.175 mm is made in the form of an envelope of the initial contour of the rack (mesh), formed by pairing arcs of circles;

S = 582 mm ² is the cross-sectional area occupied by the working fluid;

the numbers 0.1599, as well as 0.032 and 0.0031 indicate the interference in mm in engagement.

When performing the lining and the rotor, shown as in Fig.6, but calculated according to OST 39-164-84:

D _k = 2r _if , r _if = 31.675 mm;

Δh _1n = 0 (displacement of the initial contour of the rail for the formation of the profile of the teeth of the lining);

Δh _2n = 0.6125 mm (offset of the initial contour of the rail for the formation of the profile of the teeth of the rotor);

S = 572 mm ² - the cross-sectional area occupied by the working fluid, with the same interference in the engagement, with the nominal diameters of the valleys D _k = 63.35 mm and the diameter of the rotor D _a = 56.35 mm.

The rotor screw hydraulic motor contains a stator, which is a tubular housing 1 made of steel 40X GOST 4543-71, with a lining 2 made of elastomer fixed therein, essentially made of rubber IRP-1226-5 TU 2512.003.45055793-98, with internal screw teeth 3, and a rotor 4 located inside the stator, made of steel 30X13 GOST 5949-75, with external helical teeth 5, the number of which is one less than the number of teeth 3 of the lining 2, the moves of the helical teeth 3 of the lining 2 and the helical teeth 5 of the rotor 4 are proportional to their the number of teeth (not shown), and the central the main longitudinal axis 6 of the rotor 4 and the central longitudinal axis 7 of the plate 2 are offset from each other by the amount of eccentricity 8, shown in figures 1, 2.

The essential features of a gerotor screw hydraulic motor is that the end profile of the teeth 3 in the cover 2 of the elastomer is outlined as an envelope curve of radii r _s when turning the coordinate system X _OS , Y _OS , which contains a circle of radius r _s , and the center of the circle of radius r _s is on a circle with a radius R _oc drawn from the center of the coordinate system X _OS , Y _OS , and the center of the coordinate system X _OS , Y _{OS is} offset from the central longitudinal axis 7 of plate 2 by an eccentricity of 8, and _w between the central longitudinal axes 6 of the rotor 4 and 7 of the plate 2 and is defined by the expression:

R _oc = r _if -r _s -a _w ,

where r _if is the radius of the dents 3 of the plate 2, the rotation angle φ _c of the coordinate system X _OS , Y _OS relative to the fixed coordinate system X _k , Y _k , the center of which is located on the central longitudinal axis 7 of the plate 2, and the rotation angle ψ _c of the coordinate system X _with , _With , the center of which is located on the Central longitudinal axis 7 of the plate 2, relative to the fixed coordinate system X _to , _{To to} are connected by the ratio:

ψ _c = φ _with Z _p / Z _c ,

where Z _p and Z _c are the numbers of teeth of the rotor 4 and, respectively, of the plate 2, and the coordinates X _c , Y _{from the} nominal profile of the plate are determined by the expressions:

X _c = (X _os cosφ _s -Y _os sinφ _c + a _w ) cosψ _c + (X _os sinφ _c -U _os cosφ _c ) sinψ _s ,

_With Y = - (X _axes cosφ _{c- axes} sinφ _c + a _w) sinψ _c + _(oc x sinφ _c + Y _axes cosφ _c) cosψ _c, 2, 3, 4.

In this case, the end profile of the teeth 5 of the rotor 4 is made in the form of an envelope of teeth 3 of the plate 2 made of elastomer or in the form of an envelope of the initial contour of a cycloidal rail, outlined by an equidistant of a shortened cycloid, or in the form of an envelope of the initial contour of a rail formed by the conjugation of circular arcs, shown in figure 5 , 6, 7, respectively.

The essential features of a gerotor screw hydraulic motor is also that the radius r _s , the envelope of which forms the end profile of the teeth 3 in the lining 2, and the eccentricity 8, and _w between the central longitudinal axis 6 of the rotor 4 and the central longitudinal axis 7 of the lining 2 are related by the ratio: r _s = (0.618 ... 2.618) and _w , while the hardness of the lining 2 with internal helical teeth made of rubber is 75 ± 3 units. Shore A, shown in figure 2.

Figure 3 shows an example of profiling point "C" of the lining 2 of the tubular body 1 from the generatrix of a circle of radius r _s .

When designing ask:

r _if is the nominal radius of the circumference of the vertices of the part with external teeth (the circumference of the depressions for the part with internal teeth);

a _w is the center-to-center distance in a pair;

Z _c is the number of teeth of the stator lining;

δ - interference in the rotor pair - stator lining.

Based on the required energy characteristics, assign the radius of the circumference r _s = (0.618 ... 2.618) a _w and find the profile of the lining 2 of the stator by the formulas:

R _oc = r _if -r _s -a _w ,

X _oc = R _oc + r _s cosα _c ,

Y _oc = r _s sinα _c ,

ψ _c = φ _c Z _p / Z _c ,

X _c = (X _os cosφ _c - _os sinφ _c + a _w ) cosψ _c + (x _os sinφ _c + y _os cosφ _c ) sinψ _c ,

_With Y = - (X _axes cosφ _{c- axes} sinφ _c + a _w) sinψ _c + _(oc x sinφ _c + Y _axes cosφ _c) cosψ _c,

Where

R _oc - the radius of the center of the generatrix of the circumference of the plate 2 of the stator r _s ,

R _op is the radius of the center of the generatrix of the circumference of the rotor r _m ,

X _with and Y _with - coordinates of the nominal profile of the plate 2 of the stator,

φ _s and ψ _s are the current rotation angles of the plate and its generating circle r _s ,

_with α - angle between the axis X _axes and the normal to the profile of the stator electrode at the time of profiling,

r _s is the radius of the circumference of the lining 2 of the stator.

An interference fit is obtained by increasing the values of r _if and r _m in the formulas for determining the profile of the rotor 4 by a value of δ.

Gerotor screw hydraulic motor operates as follows. Drilling fluid - a clay fluid with abrasive particles, having a density of up to 1500 kg / m ³ , with a content of up to 1% sand, up to 5% of petroleum products, is fed into the upper part of the gerotor screw engine through a drill pipe string (not shown).

Under the influence of the differential pressure of the drilling fluid, the rotor 4 performs a planetary motion inside the stator, rolling around with helical teeth 5 along the helical teeth 3 of the plate of elastomer 2, mounted in a tubular body 1, shown in Fig.1, 2.

In this case, the central longitudinal axis 6 of the rotor 4 rotates around the central longitudinal axis 7 of the elastomer plate 2 fixed in the tubular body 1 along a circle of radius a _w , and the rotor 4 itself rotates around its central longitudinal axis 6 in the opposite direction to the planetary motion shown in figure 2.

The kinematic movement of the rotor 4 relative to the lining 2 of the tubular body 1 is determined by rolling without sliding the teeth 5 of the rotor 4 along the helical teeth 3 of the lining 2 of the tubular body 1, shown in Figs. 2, 5, 6, 7, and the end profile of the teeth 5 of the rotor 4 is made at the same contour diameter D _to , as shown:

- figure 5, the lining r _if = 31.675 mm from the circumference r _s = 7.6125 mm, and the end profile of the teeth of the rotor, r _a = 28.175 mm, is made in the form of an envelope of the teeth of the lining of elastomer,

- or in Fig.6, the lining r _if = 31.675 mm from the circumference r _s = 7.6125 mm, and the end profile of the teeth of the 5 rotor r _a = 28.175 mm is made in the form of an envelope of the initial contour of the cycloidal rack (gearing), outlined by the equidistant of the shortened cycloid ,

- or in Fig. 7, the lining r _if = 31.675 mm from the circumference r _s = 7.6125 mm, and the end profile of the teeth 5 of the rotor r _a = 28.175 mm is made in the form of an envelope of the initial contour of the rail (meshing) formed by the conjugation of circular arcs.

In this case, the end profile of the teeth 3 is outlined as an envelope of radius r _s when the coordinate system X _{os is} rotated, Y _os , which contains a circle of radius r _s , and the center of a circle of radius r _s is located on a circle with radius R _oc drawn from the center of the coordinate system X _OS , Y _OS , and the center of the coordinate system X _OS , Y _{OS is} offset from the central longitudinal axis 7 of the lining 2 by the amount of eccentricity 8, a _w between the central longitudinal axes 6 of the rotor 4 and, accordingly, 7 of the lining 2 and is defined by the expression:

R _oc = r _if -r _s -a _w ,

where r _if is the radius of the gaps of the teeth of the shell 2, the angle of rotation φ _from the coordinate system X _OS , Y _OS relative to the stationary coordinate system X _k , Y _k , the center of which is located on the central longitudinal axis 7 of the shell 2, and the rotation angle ψ _c of the coordinate system X _with , _With , the center of which is located on the Central longitudinal axis 7 of the plate 2, relative to the fixed coordinate system X _to , _{To to} are connected by the ratio:

ψ _c = φ _c Z _p / Z _c ,

where Z _p and Z _c are the number of teeth 5 of the rotor 4 and, accordingly, 3 of the plate 2, and the coordinates X _c , Y _{from the} nominal profile of the plate are defined by the expressions:

X _c = (X _os cosφ _c - _os sinφ _c + a _w ) cosψ _c + (x _os sinφ _c + y _os cosφ _c ) sinψ _c ,

_With Y = - (X _axes cosφ _{c- axes} sinφ _c + a _w) sinψ _c + _(oc x sinφ _c + Y _axes cosφ _c) cosψ _c.

In this case, the radius r _s , the envelope of which forms the end profile of the teeth 3 in the lining 2, and the eccentricity 8, a _w between the central longitudinal axis 6 of the rotor 4 and the central longitudinal axis 7 of the lining 2 are related by the relation: r _s = (0.618 ... 2.618) and _w .

A gerotor screw hydraulic motor for rotating the rotor from the pump fluid supply improves energy characteristics, essentially developed power and torque, by ensuring the maximum cross-sectional area occupied by the working fluid, with the same contour diameter D _to , the magnitude of the eccentricity of the gear engagement, the number of teeth of the lining and rotor by optimizing the values of the radii of circles, the envelopes of which outline the end profiles of the teeth in the lining and the rotor, as a result of which A reduction in hydromechanical losses due to uniform interference in all phases of contact between the teeth of the lining and the rotor, improvement of compaction along the contact lines in the area of the poles of engagement and reduction of contact loads in the zone of maximum sliding speeds is noted.

Claims (3)

1. A rotor screw hydraulic motor containing a stator, which is a tubular body with a sheath of elastomer, for example rubber, fixed to it, with internal helical teeth, and a rotor with external helical teeth located inside the stator, the number of which is one less than the number of teeth of the sheath, the moves of the helical teeth of the plate and the rotor are proportional to their number of teeth, and the central longitudinal axis of the rotor and the plate are offset by an eccentricity, characterized in that the end profile of the tooth into the plates of elastomer is made as an envelope curve of radii r _s when turning the coordinate system X _OS , Y _OS , which belongs to a circle of radius r _s , and the center of a circle of radius r _s is located on a circle with a radius R _oc drawn from the center of the coordinate system X _OS , Y _os , and the center of the coordinate system X _os , Y _{os is} offset from the central longitudinal axis of the plate by the amount of eccentricity a _w between the central longitudinal axes of the rotor and plate and is defined by the expression R _oc = r _if -r _s -a _w , where r _if is the radius of the depressions of the teeth of the lining, the rotation angle φ _c of the coordinate system X _OS , V _OS relative to the fixed coordinate system X _k , Y _k , the center of which is located on the central longitudinal axis of the plate, and the rotation angle ψ _c of the coordinate system X _c , Y _c , the center of which is located on the central longitudinal axis the plates relative to the fixed coordinate system X _k , Y _k are related by the relation ψ _c = φ _with Z _p / Z _c , where Z _p and Z _c - the number of teeth of the rotor and, respectively, the lining, and the coordinates X _s , Y _{from the} nominal profile of the lining are determined by the expressions X _c = (X _oc cosφ _c -Y _oc sinφ _c + a _w ) cosψ _c + (X _oc sinφ _c -Y _oc cosφ _c ) sinψ _c , Y _c = - (X _os cosφ _s -Y _os sinφ _s + a _w ) sinψ _c + (X _os sinφ _s + Y _os cosφ _c ) cosψ _c , in this case, the end profile of the teeth of the rotor is made in the form of an envelope of teeth of the plate made of elastomer or in the form of an envelope of the initial contour of a cycloidal rail, outlined by an equidistant shortened cycloid or in the form of an envelope of the initial contour of a rail formed by conjugation of circular arcs. 2. The rotor screw hydraulic motor according to claim 1, characterized in that the radius r _s , the envelope of which forms the end profile of the teeth of the plate, and the eccentricity a _w between the central longitudinal axes of the rotor and the plate are connected by the ratio r _s = (0.618 - 2.618) and _w . 3. The rotor screw hydraulic motor according to claim 1, characterized in that the hardness of the lining with internal helical teeth made of rubber is 70 ± 3 units. Shore A.

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