RU2295062C1 - Hydraulic motor - Google Patents

Abstract

FIELD: hydraulic mechanical engineering.

SUBSTANCE: hydraulic motor comprises housing with bore and rotor with valve gates pivotally connected with the rotor for permitting deflection under the action of the centrifugal force, drain passage of low pressure, inlet passage of high pressure, device for deflecting valve gates rigidly connected with the housing. The discharge passage of low pressure is made in the deflecting device, and two adjacent valve gates form a closed high-pressure space. The valve gates have thickenings from the side of the rotor and are set in the axial cylindrical opening with slot made in the rotor. The outlet high-pressure passage is made in the deflecting device and arranged oppositely to the drain low-pressure passage. The closed space is in communication with the low-pressure drain passage through the by-pass made in the surface of the housing bore shaped into a longitudinal groove and arranged directly upstream of the deflecting device.

EFFECT: simplified structure and enhanced reliability and efficiency.

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Description

The invention relates to hydraulic engineering and can be used in the water drive of mining machines during hydraulic production.

Known volumetric hydraulic motor containing plates (gates) as displacers. The plates are flat, centrifugally moved in the radial grooves of the rotor, radially spring-loaded to guarantee exit from the grooves (Kovalevsky V.F. et al. Hydraulic drives of mining machines. Ed. 2nd, revised and additional - M., Nedra) , 1973, 504 s - p. 181, Fig. 72). The hydraulic motor is reliable when working on mineral oils. The use of such a hydraulic motor in water and especially in water with solid impurities is impossible due to the filling of the landing gaps in the groove-plate connection.

Known high-torque blade volumetric hydraulic motor (ibid., P. 183, Fig. 75) with extendable centrifugally and radially spring-loaded twin flat blades. Here, under the blades, to guarantee their extension from the rotor of radius R _p to the housing of radius R _{k, the} pressure of the working fluid is supplied, and their retraction into the rotor is due to their interaction with “copiers” of radial height h = R _to -R _p dividing the active part into several working chambers and rigidly connected to the body of the hydraulic motor. Here, unloading of the closed compressible space under the blades from pressure was used when they were retracted into the rotor (to reduce mechanical energy losses). This analogue also cannot be used for work on water for the same reasons as the first analogue.

Known volumetric hydraulic motor as.with. SU No. 11190075 (11/07/85, Bull. No. 41, auth. Medvedkov V.I. and Klemesheva T.M.) - prototype. 3 here blades swinging on hinges in the rotor (or in the body) are used (hereinafter - the gate); this allowed us to escape from the danger of filling the narrow slots available in the analogues, i.e. increase the reliability of the hydraulic motor. The swivel connection of the gate with the rotor is carried out using end spikes on the gate inserted into the corresponding holes of the side bushes rigidly connected to the rotor. This adversely affected the volumetric efficiency of the hydraulic motor, as the axial gap between the gate and the rotor is guaranteed to exist initially, and as it expands from wear, the leakage increases. To guarantee centrifugal deflection of the gates before contact with the housing bore with a radius of R _k and feeding into the working chamber at the right time liquid under pressure, a piston distributor is used - this can reduce the reliability of the hydraulic motor due to the filling of the gaps in the piston-rotor connection (see figure 4 of the prototype ) And finally, the deflection of the gates by “copiers” (hereinafter referred to as the deflectors) of the casing (see FIG. 3 of the prototype) is associated with an increase in mechanical energy losses due to the need to compress the fluid volume closed between adjacent gates. In the prototype, the fluid is discharged through the channels in the deflectors, and the supply is through the axial channel of the rotor and the radial piston distributor; this complicates the product.

Thus, the prototype has increased volumetric and mechanical losses when working on any liquid, as well as the complicated and insufficiently reliable design of the distributor for working on water - disadvantages.

The technical result of the invention is the elimination of these disadvantages, i.e. increasing the efficiency and reliability of the hydraulic motor, as well as simplifying its design.

The technical solution is achieved by the fact that

in a hydraulic motor containing a housing with a bore of radius R _k and a rotor of radius R _p <R _k with hinged and deflected centrifugally gates having a width B on an arc of radius R _k and a length L, a low and high pressure inlet drain channel, a deflector gates of radial height h = R _to -R _p , rigidly connected to the housing, while the low pressure drain channel is made in the deflector, and two adjacent gates, deflected to contact with the housing at a radius of the bore R _to form a closed cavity with high fluid pressure,

according to the invention, each gate on the rotor side is thickened in cross section in the form of a dumbbell and inserted into the axial cylindrical hole with a slot made in the rotor, and the slot corresponds to the opening of the rotor hole of the dumbbell part of the gate at an angle α> 180 °, forming a swivel-rotor hinge, and spring-loaded tangentially with the possibility of its forced rotation in the axial cylindrical hole until it contacts the housing bore, while the high-pressure inlet channel is made in the diverter and the drain is located opposite low pressure channel, and the closed cavity is hydraulically connected to the low pressure drain channel in the deflector using an additional channel, a bypass, which is made on the surface of the body bore in the form of a longitudinal groove with a width of V _p > V and a length L _p <L and placed directly in front of the deflector .

The invention is illustrated by drawings, where Fig. 1 shows a cross section of a hydraulic motor, Fig. 2 shows a node M in Fig. 1, Fig. 3 shows a view A in Fig. 2 at the moment of contact of the gate with the diverter, and Fig. 4 is shown enlarged swivel elements of the gate with the rotor.

The figures depict:

1 - diverter

2 - input channel of high pressure,

3 - case,

4 - rotor

5 - spring,

6 - gate,

7 - bypass (bypass channel),

8 - drain channel low pressure,

9 - recess under the spring,

10 - spring mount,

11 - dumbbell part of the gate,

12 - point of contact of the gate with the diverter.

Additionally marked:

In _p - the width of the groove (figure 2),

R _{to the} radius of the bore of the body (figure 3),

R _p - the radius of the rotor (figure 4),

In - the width of the gate at a radius R _to (figure 4),

L is the length of the gate (figure 3),

L _p - the length of the groove (figure 3),

h = R _to -R _p - the radial height of the diverter (figure 4),

α> 180 ° - the angle of coverage of the dumbbell part of the gate in its cross section by the bore of the rotor (figure 4),

a-b-c-d - the contour of a closed cavity (figure 1),

r is the radius of the dumbbell 11 and the bore in the rotor 4 under the gate 6.

The hydraulic motor has a housing 3 with a bore of radius R _to and a rotor 4 of radius R _p <R _to . Five gates 6 are pivotally mounted on the rotor (there may be a different amount). At the level of an arc of radius R _k, each gate has a width B, the length of the gate L in the axial direction is equal to the length of the rotor 4.

The hydraulic motor also includes two diverters 1, dividing the working part into two working chambers (there may be a different number). Each diverter has a low pressure drain channel 8; deflector radial height h = R _to -R _p . Deflectors are rigidly connected to the housing 3.

Between two adjacent gates 6, which are in contact with the bore of the housing of radius R _k , there is a closed cavity abcd with high liquid pressure.

Each gate 6 from the side of the rotor 4 is thickened in its cross section in the form of a dumbbell 11 of radius r; axial drilling of the same radius is made in the rotor (taking into account the technological gap). Each of these holes is opened towards the working chamber by a slot with the rotor body remaining on an arc of a circle of radius r corresponding to an angle α> 180 °. The gate is inserted into said rotor drilling.

Each gate 6 is supported tangentially by a spring 5, i.e. can be rotated in the hinge 11 to contact with the bore of the housing 3. Flat springs are mounted in the recesses 9 with screws 10 from falling out (the springs may be different).

The closed cavity abcd is hydraulically connected to the low pressure drain channel 8 in the diverter 1 using an additional channel 7 - bypass. The bypass is made on the surface of the housing bore of radius R _to in the form of a longitudinal groove with a width of B _n > B, has a length L _n <L and is placed immediately before the deflector 1.

The high pressure channel 2 is also made in the diverter 1 and is located opposite to the low pressure channel 8 (mirror).

The operation of the hydraulic motor.

The inlet and outlet of the fluid is carried out through the channels of the stationary body 3 and, accordingly, the high pressure channels 2 and low pressure channels 8 in the deflectors 1 connected rigidly to the body. The absence of a piston (prototype) or other mechanical distributor increases the reliability of the product and simplifies its design; the location of the channel 2 in the deflector 1 is mirror to the channel 8 allows the spring 5 to be made less rigid and, accordingly, to reduce mechanical losses when the gate is turned by the deflector. Water leaving channel 2 enters under the gate, helping the spring deflect the latter until it contacts the housing bore.

The rotor 4 with gates 6 rotates (according to the drawing - clockwise) due to the torque from the pressure of the fluid on the gates at a radius of R = 0.5 (R _to + R _p ). Some gates (“workers”) are deflected by springs 5 and fluid pressure until they contact the bore of housing 3 of radius R _k , and some are under these deflectors. In this case, the “working” gate is in force contact on one side with the body on an arc of length B, approximately equal to the width of the gate at a radius R _k , and on the other hand, with the rotor along the generatrix of the dumbbell portion 11 of the gate, i.e. along the longitudinal line. The loss of the gate from the bore of a rotor of radius r is prevented by an angle α> 180 ° of the dumbbell part of the gate being covered by the rotor. It does not require spikes on the ends of the gates, bushings rigidly connected to the rotor, and holes in these bushings for mounting the gates, as in the prototype. Those. The claimed design of the hydraulic motor in this part is simplified in comparison with the prototype.

Mentioned the surface of the gate with a width of B and the contact area of the dumbbell part of the gate with the rotor during operation of the hydraulic motor are rubbed and leaks through these connections do not increase in contrast to the prototype (in terms of connecting the gate to the rotor), i.e. volumetric efficiency of the hydraulic motor is increased.

According to the drawing, the torque in this hydraulic motor is created simultaneously by two gates. In each working chamber (there are two of them in the drawing), a pair of adjacent gates is formed, bounding the abcd cavity with the liquid under pressure. When the gate leading in front touches the point 12 of contact with the deflector 1, the latter must turn this gate counterclockwise (according to the drawing), i.e. compress the volume of fluid in the circuit a-bcd. Compression, of course, does not occur, but the moment of the engine is spent on forcing a part of the liquid through the gaps, for example, at the ends of the gates, i.e. mechanical losses increase. To eliminate this harmful effect in the inventive hydraulic motor in front of the diverter 1, a longitudinal (along the axis of the engine) groove 7 with a width of B _n > V is made. Now, when the next gate approaches the point 12, the high-pressure cavity in the a-bcd circuit communicates through the groove (bypass) 7 with the low pressure drain channel 8 and the gate is almost freely deflected in the hinge 11, being sunk by the diverter 1 into the rotor 4. This measure is prevented reduction in mechanical efficiency of the hydraulic motor, which was not provided for in the prototype.

Being within the width B _{n of the} groove 7, the gate 6 can deviate under the action of the springs 5 up to the "bottom" of the groove, i.e. fall into the groove, which will increase mechanical losses when the gate is withdrawn from the groove. To this negative effect does not occur, in the inventive hydraulic motor, the axial length of the groove L _{n is} made less than the length of the gate (rotor) - the gate does not fall into the groove.

Thus, with the improvements made, the known hydraulic motor is simplified, its reliability has increased and volumetric and mechanical energy losses have decreased.

Claims (1)

A hydraulic motor comprising a housing with a bore of radius R _k and a rotor of radius R _p <R _k with hinged and centrifugally deflectable gates having a width B on an arc of radius R _k and length L, a low and high pressure inlet drain channel, a gate deflector radial height h = R _k -R _p rigidly connected to the housing, while the low pressure drain channel is made in the deflector, and two adjacent gates deflected before contact with the housing at the radius of the bore R _k form a closed cavity with high fluid pressure, distinguishing the fact that each gate on the rotor side is thickened in the cross section in the form of a dumbbell and inserted into the axial cylindrical hole with a slot made in the rotor, and the slot corresponds to the coverage of the dumbbell part of the gate with the rotor hole covering an angle α> 180 °, forming a swivel joint - the rotor, and is spring loaded tangentially with the possibility of its forced rotation in the axial cylindrical hole until it contacts the housing bore, while the high-pressure inlet channel is made in the deflector and is located opposite the drain channel at low pressure, while the closed cavity fluidly communicated with a drain passage of low pressure in the diverter via an additional channel - the bypass, which is formed on the surface of the bore of the body in the form of a longitudinal groove width B _n> B and a length L _n <L and disposed just prior to the diverter.

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