RU2309237C1 - Gerotor mechanism for hydraulic screw-rotor machine - Google Patents

Abstract

FIELD: drilling equipment, particularly gerotor mechanisms to be used in drives or pumps.

SUBSTANCE: gerotor mechanism comprises stator made as tubular body 1 and as covering member 2 with inner helical teeth 3, rotor 4 with outer helical teeth 5. Central longitudinal axes 6, 7 of rotor 4 and covering member 2 are shifted one from another by eccentricity 8 value a_w. Covering member 2 teeth end profile defines enveloping curve having r_s radii and formed by rotation of coordinate system X_oc, Y_oc including circle of r_s radius. Rotor teeth end profile defines enveloping curve having r_m radii and formed by rotation of coordinate system X_op, Y_or including circle of r_m radius. Center of circle having r_m radius is located on circle with R_op radius starting from coordinate system X_op, Y_or origin point offset from central longitudinal rotor axis by calculated eccentricity value aw. Radius r_s, radius r_m and eccentricity aw are related with each other.

EFFECT: improved power characteristics, power and torque developed in engine or pressure and flow rate in pump.

2 cl, 9 dwg

Description

The invention relates to gerotor mechanisms of screw hydraulic machines located in wells, and can be used in engines for rotating rotors from a pumped fluid supply or in pumps for supplying a fluid due to the rotation of rotors intended, for example, for drilling oil and gas wells, oil production and pumping liquids.

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 conjugated profile of the rotor teeth is made as an envelope curve of the original profile [1].

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 mills, and with the change in the number of teeth of the mechanism during its design and manufacture, the number of worm mills required increases, which does not provide economic benefits.

A known gerotor mechanism comprising a stator with internal helical teeth made of 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 cycloidal rack with the equidistant radius of R _C2 , made more than R _C1 or the related relation R _С2 = R _С1 + (0,1 ... 0,5) E, where Е is the radius of the generating circle equal to the eccentricity [2].

An embodiment of the known invention is the implementation of the gerotor mechanism in such a way that the stator tooth profile in the end section is made as the envelope of the initial contour of the cycloidal rack, outlined by an equidistant curve with a shortened cycloid radius R _C1 , and the profile of the rotor teeth in the end section is outlined by conjugate arcs of circles, and the protrusion of the rotor tooth defined by an arc of radius R _B greater than the radius of the stator equidistant R _C1 or 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 defined by an arc of radius R _V depending on the number of teeth of the rotor, its outer diameter and eccentricity [2].

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, distributed evenly 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 appears, 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 rail profile (meshing) with an offset , and the profile of this contour is outlined by the equidistant of the shortened cycloid, while the largest allowable positive and greatest negative bias of the rail contour are specified with the relation niy:

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

Where

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:

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 _with - the distance from the shortened cycloid to the profile points of the original rail contour [3].

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 multiple-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 the gerotor mechanism of a screw hydraulic machine, essentially the developed power and torque in the engine or the developed pressure and flow in the pump by ensuring 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 of the mechanism, the number of teeth of the lining and the rotor due to the optimization of the radii of the circles, the bend The components of which outline the end profiles of the teeth in the lining and the rotor, as a result of which the hydromechanical losses are reduced due to the uniform interference in all phases of the contact between the teeth of the lining and the rotor, the seal is improved along the contact lines in the area of the engagement poles and the contact loads are reduced in the zone of maximum sliding speeds.

The essence of the technical solution lies in the fact that in the gerotor mechanism of a screw hydraulic machine 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 with external helical teeth located inside the stator, which are 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 amount of e stsentrisiteta according to the invention the end face profile of teeth in coated elastomer is outlined as an envelope curve radii r _s when turning system X _axes coordinates and Y _axes, which belongs to a circle of radius r _s, and the center of radius r _s is located circumferentially on the circumference with R _oc radius 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:

where r _if is the radius of the cavities of the teeth of the lining, 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 of the plate, and the angle of rotation ψ _from the coordinate system X _s , 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:

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:

the end profile of the teeth of the rotor is outlined as an envelope curve of radii r _m when the coordinate system X _op , U _op , which belongs to a circle of radius r _m , and the center of a circle of radius r _m is located on a circle with a radius R _op drawn from the center of the coordinate system X _Oh , U _Oh , and the center of the coordinate system is X _Oh , Y _{Oh is} offset from the central longitudinal axis of the rotor by the amount of eccentricity a _w and is defined by the expression:

R _op = r _if -r _m -2a _w ,

and the rotation angle φ _p system X _op coordinate, Y _op relatively fixed system X coordinate _Cr, Y _Cr, the center of which is located on the central longitudinal axis of the rotor, and rotation angle ψ _p coordinate system X _p, Y _p, whose center is located on the central longitudinal the rotor axis relative to the fixed coordinate system X _kr , Y _kr , are related by the relation:

ψ _p = φ _p (Z _p -1) / Z _p ,

where Z _p - the number of teeth of the rotor, and the coordinates X _p , U _{p the} nominal profile of the rotor are determined by the expressions:

X _p = (X _op cosφ _p -Y _op sinφ _p + a _w ) cosψ _p + (X _op sinφ _p -Y _op cosφ _p ) sinψ _p ,

Y _p = - (X _op cosφ _p -Y _op sinφ _p + a _w ) sinψ _p + (X _op sinφ _p + Y _op cosφ _p ) cosψ _p .

In addition, the radius r _s , the envelope of which forms the end profile of the teeth in the lining, the radius r _m , the envelope of which forms the end profile of the teeth of the rotor, and the eccentricity a _w between the central longitudinal axes of the rotor and the lining are related by the relations:

r _s = (0.618 ... 2.618) a _w , r _m = (0.166 ... 2.618) a _w .

This embodiment of the gerotor mechanism of a screw hydraulic machine 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 of} circles, the envelopes of which outline the end profiles of the teeth in the lining and the rotor, respectively, as a result of which the hydromechanical losses are reduced due to uniform interference in all contact phases slaughter of the plate and rotor, improvement of compaction along the contact lines in the zone of the poles of engagement and reduction of contact loads in the zone of maximum sliding speeds.

In addition, the execution of the gerotor mechanism of a screw hydraulic machine in such a way that the radius r _s whose envelope forms the end profile of the teeth in the lining, the radius r _m whose envelope forms the end profile of the teeth of the rotor and the eccentricity a _w between the central longitudinal axes of the rotor and the lining are connected by the relations:

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 chambers between the teeth of the rotor and the lining.

Below is the best version of the gyratory mechanism of a helical hydraulic motor for drilling directional and horizontal oil wells.

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

In Fig.2 shows a section aa in Fig.1 across the stator and rotor of the 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.

Figure 4 shows a diagram of the formation of the end profile of the teeth of the rotor.

Figure 5 shows the formation of the end profile of the teeth in the lining, 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; and _w = 3.5; r _if = 31.675.

Figure 6 shows the lining and rotor calculated according to OST 39-164-84: D _to = 2r _if ; r _if = 31.675; 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 (offset of the initial contour of the rail for the formation of the profile of the teeth of the rotor); S = 587 mm ² - the cross-sectional area occupied by the working fluid; numbers 0.054; 0.046 and 0.004 denote an interference fit in a pair in mm at nominal diameters of the troughs D _k = 63.35 mm and the diameter of the rotor D _a = 56.35 mm.

Figure 7 shows an example of the execution of the gerotor mechanism of a screw hydraulic motor with the same contour diameter D _k : lining r _if = 31.675 from the circle r _s = 7.6125; a rotor r _a = 28.175 from a circle r _m = 7.38; S = 593 mm ² is the cross-sectional area occupied by the working fluid; the numbers 0.012; 0.012 and 0.004 denote the gap in mm in pairs.

On Fig shows an example of the execution of the gerotor mechanism of a screw hydraulic motor with the same contour diameter D _to : lining r _if = 31.675 from the circle r _s = 0,618 a _w = 2,163; the rotor r _a = 28.175 from the circle r _m = 0.166 and _w = 0.581; S = 576 mm ² is the cross-sectional area occupied by the working fluid; numbers 0.021; 0.002 and 0.009 denote the gap in mm in pairs.

Figure 9 shows an example of the execution of the gerotor mechanism of a screw hydraulic motor with the same contour diameter D _k : lining r _if = 31.675 from the circle r _s = 2,618 a _w = 9,168; a rotor r _a = 28.175 from a circle r _m = 2.6 a _w = 9.1; S = 599 mm ² - the cross-sectional area occupied by the working fluid; numbers 0.004; 0.006 and 0.001 denote the gap in mm in pairs.

The gerotor mechanism of a hydraulic screw motor contains a stator, which is a tubular body 1 with a sheath 2 made of elastomer, for example, rubber, with internal helical teeth 3 fixed in it, and a rotor 4 with external helical teeth 5 located inside the stator, the number of which is one less than the number 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 number of teeth (not shown), and the central longitudinal axis 6 of the rotor 4 and the central longitudinal axis 7 of the lining 2 are shifted between themselves by the magnitude of the eccentricity 8, shown in figures 1, 2.

An essential feature of the gerotor mechanism of a screw hydraulic motor is that the end profile of the teeth 3 in the cover 2 of the elastomer is outlined as an envelope of the radius r _s when the coordinate system X _os , Y _os , which has a circle of radius r _s , and the center of the circle of radius r _s located on the circle with radius R _oc, drawn from the center of the system of coordinates X _a, Y _a, and the coordinate system center _axes X, Y _axes is offset from the central longitudinal axis 7 of the electrode 2 by the amount of eccentricity of 8, and _w between the central rodolnymi rotor axes April 6 and 7 of the electrode 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 _from 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 _c -Y _os sinφ _c + a _w ) cosψ _c + (X _os sinφ _s -U _os cosφ _c ) sinψ _c ,

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

shown in figure 3, 5.

An essential feature of the gerotor mechanism of a screw hydraulic motor is that the end profile of the teeth 5 of the rotor 4 is outlined as an envelope curve of radii r _m when the coordinate system X _op , U _op , which has a circle of radius r _m and the center of a circle of radius r _m is located on a circle with a radius R _op drawn from the center of the coordinate system X _op , U _op , and the center of the coordinate system X _op , U _{op is} offset from the central longitudinal axis 6 of rotor 4 by an eccentricity of 8, and _{w is} defined by the expression:

R _op = r _if -r _m -2a _w ,

and the angle of rotation φ _p system X _op coordinate, Y _op relatively fixed system X coordinate _Cr, Y _Cr, the center of which is located on the central longitudinal axis 6 of the rotor 4, and the rotation angle ψ _p X _p coordinate system, Y _p, whose center is located on the the central longitudinal axis 6 of the rotor 4 relative to the fixed coordinate system X _cr , Y _cr , are related by the ratio:

ψ _p = φ _p (Z _p -1) / Z _p ,

where Z _p - the number of teeth of the rotor, and the coordinates X _p , U _{p the} nominal profile of the rotor are determined by the expressions:

shown in figure 4.

An essential feature of the gerotor mechanism of a hydraulic screw motor is that the radius r _s , the envelope of which forms the end profile of the teeth 3 in the lining 2, the radius r _m , the envelope of which forms the end profile of the teeth 5 of the rotor 4, and also an eccentricity 8, a _w between the central the longitudinal axis 6 of the rotor 4 and the Central longitudinal axis 7 of the plate 2 are connected by the relations:

Figure 3 and 4 shows the profiling scheme of the point "C" of the lining 2 of the tubular body 1 from the generatrix of a circle of radius r _s and, accordingly, the point "P" of the rotor 4 from the generatrix of a circle of radius r _m .

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 is the interference fit in the rotor-lining of the stator.

Based on the required energy characteristics, the radii of the forming circles r _s = (0.618 ... 2.618) a _w , r _m = (0.166 ... 2.618) a _{w are} assigned, and the profile of the stator lining 2 is found by the formulas:

rotor profile:

R _op = r _if -r _m -2a _w ,

x _op = R _op + r _m cosα _p ,

y _op = r _m sinα _p ,

ψ _p = φ _p (z _p -1) / z _p ,

x _p = (x _op sin cosφ _p- oh _op sinφ _p + a _w ) cosψ _p + (x _op sinφ _{p- op op} cosφ _p ) sinψ _p ,

y _p = - (x y cosφ _{p op op sinφ p + a w) sinψ} p + (x _OR y sinφ _p + _op cosφ _p) cosψ _p,

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 _s and y _s are the coordinates of the nominal profile of the lining 2 of the stator,

x _p and y _p - coordinates of the nominal profile of the rotor 4,

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

φ _p and ψ _p are the current rotation angles of the rotor 4 and its generating circle r _m ,

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

α _p is the angle between the axis X _OP and the normal to the profile of the rotor 4 at the time of profiling,

r _s is the radius of the generatrix of the circumference of the lining 2 of the stator,

r _m is the radius of the generatrix of the circumference of the rotor 4.

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 mechanism of a screw hydraulic machine operates as follows. When using the gerotor mechanism in a hydraulic screw motor, drilling fluid is supplied to the upper part of the gerotor mechanism through a drill pipe string (not shown in FIG.).

Under the influence of the differential pressure of the drilling fluid, the rotor 4 makes a planetary movement inside the stator, rolling around with helical teeth 4 along the helical teeth 3 of the plate of elastomer 2, mounted in a tubular body 1, is shown in figures 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 the teeth 5 of the rotor 4 without sliding, the end profile of which is outlined as an envelope of the radius r _m curve when the coordinate system is rotated X _op , U _op , which has a circle of radius r _m and the center of a circle of radius r _m is located on a circle with a radius R _op drawn from the center of the coordinate system X _op , U _op , and the center of the coordinate system X _op , U _{op is} offset from the central longitudinal axis 6 of rotor 4 by an eccentricity of 8, and _w living:

R _op = r _if -r _m -2a _w ,

and the angle of rotation φ _p system X _op coordinate, Y _op relatively fixed system X coordinate _Cr, Y _Cr, the center of which is located on the central longitudinal axis 6 of the rotor 4, and the rotation angle ψ _p X _p coordinate system, Y _p, whose center is located on the the central longitudinal axis 6 of the rotor 4 relative to the fixed coordinate system X _cr , Y _cr , are related by the ratio:

ψ _p = φ _p (Z _p -1) / Z _p ,

where Z _p - the number of teeth of the rotor 4, and the coordinates X _p , U _{p the} nominal profile of the rotor 4 are determined by the expressions:

X _r = (X _{op op} cosφ sinφ _p -I _p + a _w) cosψ _p + (X _{op op} sinφ cosφ _p -I _p) sinψ _p,

Y _p = - (x _op cosφ _p - y _op sinφp + а _w ) sinψ _p + (x _op sinφ _p + y _op cosφ _p ) cosψ _p ,

along helical teeth 3 of the lining 2 of the tubular body 1, the end profile of the teeth 3 of which is outlined as an envelope of the 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 plates 2 and define expression:

where r _if is the radius of the gaps of the teeth of the shell 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 shell 2, and the rotation angle ψ _from 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:

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:

The radius r _s , the envelope of which forms the end profile of the teeth 3 in the lining 2, the radius r _m , the envelope of which forms the end profile of the teeth 5 of the rotor 4, as well as the eccentricity 8, and _w between the central longitudinal axis 6 of the rotor 4 and the central longitudinal axis 7 plates 2 are connected by the relations:

When using the gerotor mechanism in screw pumps, the rotor 4 is rotated and, rolling around the teeth 3 of the lining 2 of the tubular body 1, converts the mechanical energy of rotation into hydraulic energy of the fluid flow.

The kinematics of movement of the rotor 4 of the screw pump and the benefits obtained by using the claimed gerotor mechanism are similar to those described above for a screw hydraulic motor.

The gerotor mechanism of a screw hydraulic machine when used in engines for rotating rotors from a pump fluid supply or in pumps for supplying a fluid by rotating the rotors improves the energy characteristics, essentially the developed power and torque in the engine or the developed pressure and flow rate in the pump by ensuring the maximum cross-sectional area occupied by the working fluid with the same contour diameter D _k , the magnitude of the eccentricity of the gearing mechanism, the number of teeth of the plates and of 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 the hydromechanical losses are reduced due to the uniform interference in all phases of the contact of the teeth of the lining and the rotor, and the seal is improved along the contact lines in the area of the engagement poles and reducing contact loads in the zone of maximum sliding speeds.

Information sources:

1.SU 93032 A, F16H 01/32, F16H 55/08, 03/21/1962.

2. RU 2166603 C1, E21B 4/02, 05/10/2001.

3. RU 2232317 C1, F16H 1/32, F16H 55/08, 07/10/2004 - prototype.

Claims (2)

1. The rotor mechanism of a screw hydraulic machine, comprising 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 rotor are proportional to their number of teeth, and the central longitudinal axis of the rotor and plate are offset by an amount of eccentricity, characterized in that the end profile of teeth in an elastomer lining 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 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 plates relative to a fixed coordinate system X _k , Y _k are related by the relation: Ψ _c = φ _c Z _p / Z _s , 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 defined by the expressions:

the end profile of the teeth of the rotor is outlined as an envelope curve of radii r _m when the coordinate system X _op , U _op , which belongs to a circle of radius r _m , and the center of a circle of radius r _m is located on a circle with a radius R _op drawn from the center of the coordinate system X _Oh , U _Oh , and the center of the coordinate system is X _Oh , Y _{Oh is} offset from the central longitudinal axis of the rotor by the amount of eccentricity a _w and is defined by the expression: R _op = r _if -r _m -2a _w , and the rotation angle φ _p system X _op coordinate, Y _op relatively fixed system X coordinate _Cr, Y _Cr, the center of which is located on the central longitudinal axis of the rotor, and rotation angle ψ _p coordinate system X _p, Y _p, whose center is located on the central longitudinal the rotor axis relative to the fixed coordinate system X _kr , Y _kr , are related by the relation: ψ _p = φ _p (Z _p -1) / Z _p , where Z _p is the number of teeth of the rotor, and the coordinates X _p , U _{p of the} nominal profile of the rotor are determined by the expressions: X _p = (X _op cosφ _p -Y _op sinφ _p + a _w ) cosψ _p + (X _op sinφ _p -Y _op cosφ _p ) sinψ _p , Y _p = - (X _op cosφ _p -Y _op sinφ _p + a _w ) sinψ _p + (X _op sinφ _p + Y _op cosφ _p ) cosψ _p , 2. The gerotor mechanism of a screw hydraulic machine according to claim 1, characterized in that the radius r _s , the envelope of which forms the end profile of the teeth in the lining, the radius r _m , the envelope of which forms the end profile of the teeth of the rotor, as well as the eccentricity a _w between the central longitudinal axes the rotor and the plates are related by the relations: r _s = (0.618 ... 2.618) and _w , r _m = (0.166 ... 2.618) and _w .

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