Field of the invention The invention relates to the liquid atomizing equipment and may be used in fire- suppression systems, sanitary engineering, in apparatuses for combustion of liquid fuels, as well as in the irrigation equipment, etc. Background of the invention It is known an atomizer of the prior art comprising a casing with liquid stream forming channels and a connection pipe for supplying of a liquid, wherein the axes of each pair of the channels are arranged such that fuel streams impinge and combine with one another to produce a single cone of an atomized jet with a minimal displacement from the atomizer central axis (US 5044562, published 03.09.1991, IPC F02M 51/06). Considerable difficulties experienced with the given apparatus are connected with substantial kinetic energy losses in the course of liquid atomization process, said losses resulting from formation of annular streams. It is also known an atomizer comprising a casing with liquid stream forming channels and a connection pipe for supplying of a liquid. Outlet apertures of the channels for supplying a liquid are provided in an axially symmetric V-shaped surface. The liquid atomization is provided in the apparatus of the prior art due to the collision of liquid streams with each other in a certain spatial region opposite outlet apertures of the liquid supplying channels (JP 11-076871, published 23.03.1999, IPC B05B 1/26). The atomizer of the above construction enables sprays of atomized droplets to be generated solely due to the collision of streams, with the consequent restricted possibilities in minimizing the energy consumption for the generation of an atomized liquid jet. The closest analog to the claimed invention is an atomizer comprising a casing with curved channels for the formation of liquid streams and a connection pipe for supplying of a liquid (US 5358179, published 25.10.1994, IPC B05 1/26). The intersecting axes of the outlet apertures of the channels intersect at some point beyond the atomizer casing. A finely atomized liquid jet is produced upon collision of liquid streams preliminarily created in the channels. Because of the curved channels available in the atomizer casing, the liquid stream takes on an additional angular velocity in front of the point of entry of the stream into cylindrical parts of the channels, whose axial lines intersect one another in the spatial region beyond the atomizer casing. An increase in the relative stream velocity due to the preliminary rotation of streams and, correspondingly, an increase in an angular velocity of the streams allow the effectiveness of atomization of the liquid stream into an atomized gas-droplet jet to be increased. However, regardless of the given advantages of the apparatus of the prior art, additional losses of kinetic energy occur in the process of creating vortex liquid streams owing to an increased hydraulic resistance of the liquid supplying channels. Disclosure of the invention It is an object of the present invention to provide a liquid atomizer permitting generation of finely-atomized liquid droplet jets of predetermined spatial configuration at reduced liquid flow velocities and pressure in the liquid supplying lines. The technical result to be achieved consists in the reduced consumption of energy used for the generation of finely atomized gas- droplet jets. The above technical result is provided through the employment of a liquid atomizer including a casing with liquid stream forming channels, and a connection pipe for supplying of a liquid. According to the present invention, the liquid stream forming channels are oriented in such a manner that their axial lines cross one another downstream from the outlet sections of the channels in a spatial region where a finely atomized liquid jet is generated. A minimal distance between the skew axial lines of the channels does not exceed an average hydraulic radius of the channel cross-section. In the general case, the hydraulic radius Rg for the channels of an arbitrary cross-section is determined from the ratio: Rg=ω/χ, where Rg - is an average hydraulic radius of the channels, mm; ω - is an effective cross-section of the liquid stream, mm2; χ - is a wetted perimeter of the channel, mm. With the cylindrical channels completely filled with the liquid, the hydraulic radius of the channels is determined from the formula: Rg=0.25D, where D is diameter of the cylindrical channels, mm. The average hydraulic radius Rh of few channels is determined from the formula: Rg=(RgI + Rg2 + ...+ R8N)ZN, where Rgi, Rg2,...RgN - are hydraulic radius of the few channels 1...N, respectively, mm; N - is the number of the channels. In a preferred embodiment of the atomizer structure, the distance between the outlet sections of the channels and the region, where an atomized liquid jet is generated and at the boundary of which the distance between the skew axial lines of the channels is of minimal value, is selected to be below 80Rg. The channels of the atomizer may be made cylindrical. It is advisable that the length of the channels be not greater than 40Rg. An angle of intersection of front projections of the skew axial lines of the channels is selected within the range of from about 1° to about 179°, with optimal values of the given angle approximating 1° for producing long-distance flows and approximating 180° for producing gas-droplet jets having a wide spray cone. In the preferred embodiments of the liquid atomizer structure, the indicated angle is selected within the following ranges: from 50 to 70° and from 150 to 179°. The surface of the inlet section and/or outlet section of the channels may be made flattened. The planes or surface generating lines of the inlet and outlet sections of the channels provided in the casing may lie parallel to one another and may be arranged at an angle not greater than 90° with respect to an axis of symmetry of the casing. In the preferred embodiments of the invention, the given angle is selected within the range of from 50° to 70°. It is suitable that the axial lines of the channels extend perpendicular to the planes of the outlet sections of the channels. The surface of the inlet and/or outlet section of the atomizer channels may be made in the form of a body of rotation. Generating lines of the surfaces of the inlet and outlet sections of the channels may extend in parallel with one another. It is also advisable that the axial lines of the channels be perpendicular to the generating lines of the surface of the outlet sections of the channels. The channels may be equalized in their cross-section or a sectional area of at least one of the channels may exceed the sectional area of any other channel by no more than twice. An optimal number of the channels selected ranges from two to six. An axial channel may be encased in the atomizer casing. In order to accumulate the stream to be provided in a predetermined direction, the atomizer casing is equipped with a chamber formed as a body of rotation and located downstream from the outlet sections of the channels. In various embodiments of the liquid atomizer, this chamber may be conical or cylindrical in shape. In order to reduce hydraulic losses, the channels may be equipped with converging entry portions conical or conoid in shape. Brief description of the drawings The given invention is explained by examples of particular embodiments of the liquid atomizer with reference to drawings illustrating the following: Fig. 1 - is a general enlarged-scale view of the atomizer at the side of a region where an atomized liquid jet is generated; Fig. 2 - is a stepped cross-sectional view of the liquid atomizer taken in planes A-A; Fig. 3 - is a stepped cross-sectional view of the liquid atomizer taken in planes A-A of an embodiment provided with an additional cylindrical chamber; Fig. 4 - is a diagrammatic view illustrating formation of an atomized liquid jet in the spatial region where streams impinge upon one another (the view at the side of the region where an atomized liquid jet is generated); Fig. 5 - is a diagrammatic view of front projections of the axial lines of the channels with velocity vectors of impinging liquid streams (a stepped cross-sectional view taken in planes A-A); Fig. 6 - is a general view of the atomizer at the side of the region where an atomized liquid jet is produced in the version of embodiment with an angle of intersection of front projections of the axial lines of the channels equal to 179°; Fig. 7 -is a stepped cross-sectional view of the liquid atomizer illustrated in Fig. 6 in planes B-B. Preferred embodiment of the invention The liquid atomizer illustrated in Figs 1 and 2 comprises a casing 1 with two cylindrical liquid stream forming channels 2, and a connection pipe 3 for supplying of a liquid. The liquid stream forming channels 2 are oriented in such a manner that their skew axial lines 4 cross one another downstream from the outlet sections of the channels in a spatial region where an atomized liquid jet is produced (see Figs 4 and 5), with a minimal distance between the skew axial lines of the channels being not greater than an average hydraulic radius Rg of a cross- section of channels Ki and K2 (see Fig. 4). The length of cylindrical channels 2 is 8 Rg, which is in accordance with the terms of selection of optimal sizes of the channels 2 (the length of the channels does not exceed 40Rg). Generating lines 5 and 6 of the conical surfaces of the inlet and outlet sections of the channels 2 are arranged at an angle α with respect to an axis of symmetry 7 of the casing. In the considered example of embodiment of the invention, the value α is selected to be 50° (i.e., within the range of from 50° to 70° to comply with the claims of the invention). The generating lines 5 and 6 are extending parallel to each other and perpendicular to the axial lines 4 of the channels 2. The casing of the liquid atomizer in the given example of embodiment of the invention is provided with an axial channel 8. The axial lines 4 of the channels 2 of the liquid atomizer illustrated in Figs 2 and 3 are arranged at an acute angle β with respect to one another (see Fig. 5). In another example of embodiment of the liquid atomizer, the axial lines of the channels may be arranged at an obtuse angle (β=179°), as shown in Fig. 7. An embodiment of the liquid atomizer illustrated in Fig. 3 comprises a chamber 9 cylindrical in shape. The chamber 9 is located downstream from the outlet sections of the channels 2. The length of the chamber LK does not exceed a twenty-fold value of its diameter Dκ. The optimal value of Dκ/Lκ ratio in the embodiment under consideration is 1.7. The skew axial lines 4 of the channels 2 are crossing one another with a minimal distance between them not greater than the average hydraulic radius Rg of the channels 2. The channels 2 are made cylindrical in shape and equalized in their cross-sections. With two similar channels 2 having diameter D=2 mm, the hydraulic radius Rg is 0.25D=O.5 mm. The distance between the outlet sections of the channels and the region, where an atomized liquid spray is generated and at the boundary of which the distance between the skew axial lines of the channels is minimal, is 40Rg (see Fig. 5), i.e., it does not exceed 80Rg in accordance with the claims of the invention. A boundary 10 of the spatial region where an atomized liquid spray is generated is depicted in Fig. 5 and is characterized by a minimal distance between the skew axial lines 4 of the channels 2. Fig. 5 shows a point of intersection of front projections of the skew axial lines 4 of the channels 2, said point defining a minimal distance between the skew axial lines 4 extending in parallel planes. The angle β of intersection of front projections of the skew axial lines 4 of the channels 2 shown in Fig. 5 is 50°, i.e., in the range of optimal values β of from 50° to 70° according to the claims of the invention (Fig. 5). One more embodiment of the liquid atomizer structure is represented in Fig.6. In the atomizer of the given embodiment, axial lines 1 1 of channels 12 are arranged at an angle to an axis of symmetry 13 of the casing, with said angle approximating 90°. The distance between the axial lines 1 1 of the channels 12 does not exceed Rg, as it is in the first embodiment of the structure. The channels 12 are provided in a cylindrical sleeve 14, which is axially inserted into a casing 15 of the liquid atomizer (Fig. 7). The front projections of the skew axial lines 11 of the channels 12 intersect one another at an angle of 179° (within the range of the optimal values of 150-179°). In the given embodiment of the liquid atomizer, the surface of the outlet sections of the channels 12 is made conical and the surface of the inlet sections of the channels 12 is made cylindrical. A generating line 16 of the conical surface of the outlet sections of the channels 12, correspondingly, does not extend parallel to a generating line 17 of the cylindrical surface of the inlet sections of the channels 12. The liquid stream forming channels 12 are equipped with conical entry portions 18 facilitating the reduction of hydraulic losses. The casing 15 in the atomizer of the second embodiment, as well as that of the first embodiment, comprises a connection pipe 19 for connection to a liquid supply line. Atomized liquid jets are generated with the help of the liquid atomizer of the present invention in the following manner. The working liquid is delivered from the liquid supply line, to which the liquid atomizer is joined through the connection pipe 3, to the channels 2 and 8 for forming liquid streams. Since the skew axial lines 4 of the channels 2 cross in the spatial region, where an atomized liquid jet is generated, with a minimal distance between the axial lines not exceeding the average hydraulic radius of the channels 2, only peripheral parts of the liquid streams impinge upon one another. As shown in Fig. 4, upon formation of liquid streams Si and S2 discharged from channels Ki and K2, there occurs a collision and impingement of the peripheral parts of the liquid streams Si and S2 flowing at the velocities of Vl and V2, in the region, where an atomized liquid jet is generated. It should be pointed out that Fig. 4 shows the vectors of the velocities Vi and V2 of the streams Si and S2, respectively, with normal components Vn i and Vn2 extending perpendicular to a drawing plane and tangential components Vτi and V12 lying in the plane of drawing. In the region of impingement of the streams Sj and S2, a vortex formation zone is developed owing to the action of tangential velocity components Vτi and Vτ2 (exemplified in Fig. 4 by round arrows), where the liquid streams are intensively broken-up and, as a consequence, a finely atomized gas-droplet jet spray is generated. In the vortex formation zone, the liquid stream is caught by the impinging streams and rotated at an angular velocity ω and at a linear velocity Vτ. The vortex formation zone expands as the liquid streams Si and S2 are brought closer to each other and entrains the liquid streams in the process of displacement away from the outlet sections of the channels 2. The axial displacement of the vortex formation zone is effected at the velocity Vn, which is a resultant speed of liquid droplets in the region of impingement of the liquid streams (see Figs 4 and 5). The angular velocity ω of rotation of the liquid stream in the vortex formation region, which is located in the center of impingement of the liquid streams, may be estimated. The velocities of the streams in the stream impingement region are from unities to tens meters per second. The axial displacement of the axial lines of the liquid streams is on the order of 1 mm and less. It is presupposed that the displacement of the axial lines of the liquid streams Si and S2 with respect to the axial lines of the channels Ki and K2 at distances not in the excess of 80Rg from the outlet sections of the channels is insignificant. Based on the given parameters, the rotational velocity of the vortex in the region of generation of an atomized jet will make from unities to hundreds thousands revolutions per second. Owing to the effect of a centrifugal force, the resulting high-velocity vortex breaks up the impinging liquid streams. The result is that the thin liquid films are converted into small droplets. The distance between the outlet sections of the channels and the region, where an atomized liquid jet is generated and at the boundary of which the distance between the intersecting skew axial lines of the channels Ki and K2 is minimal, does not preferably exceed eighty-fold values of the average hydraulic radius of the channels. This is due to the fact that at greater distances from the outlet sections of the channels, the streams Sj and S2 are substantially expanded and their flow paths are offset with the accompanying kinetic energy losses. The impact forces of the interacting streams combined with the centrifugal force of the vortex created provide the generation of a uniform droplet jet of finely atomized liquid in the region of generation of an atomized liquid jet. In addition, the action of the centrifugal force allows smaller droplets to be produced at lower pressure differences. The collision of the streams allows a spatially uniform droplet jet to be produced. Thus, at the equal initial kinetic energy of the liquid streams, the energy efficiency of the liquid stream atomization process is substantially increased and the spatial uniformity of the finely atomized liquid droplet jet is improved with the use of the given invention. The above effect is exhibited in full measure when the minimal distance between the axial lines 4 of the channels 2 (Ki and K2) and, respectively, between the axial lines of streams Si and S2 (see Fig. 4) does not exceed the average hydraulic radius Rg of the channels 2. The following dependence should be taken into consideration: the greater the distance between the axial lines of the channels, the smaller is the angular velocity ω of rotation of the vortex and, as a consequence, to a lesser extent is exhibited the effect of atomization of liquid streams by the action of the centrifugal force. It should be also born in mind that an increase in the number of the channels 2 results in a more uniform atomized liquid jet spray owing to the complete impingement of the streams in the zone of action of the vortex centrifugal force. However, there exist actual limitations as to the number of the channels at which the effect of liquid atomization by the action of the centrifugal force is exhibited in fuller measure: in the preferred embodiment of the liquid atomizer the number of the channels should not exceed six. The use of liquid atomizers with various angles β of intersection of the front projections of the skew axial lines 4 of the channels 2 ranging from 1° to 179° (see Figs 5 and 7) allows liquid atomization sprays with various cone angles and various intensities of surface spraying to be achieved. In case of an embodiment where one of the channels 2 has a cross-sectional area exceeding that of other channel 2, there may be generated a finely atomized droplet jet with an atomized liquid spray offset with respect to the axis of symmetry 7 of the casing 1. However, the cross-sectional area of one channel should not exceed that of the other channel by more than twice. The given limitation is due to the reduced effectiveness of stream splitting in case of substantial difference in the cross-sectional areas of the channels 2, since this substantial difference in the cross- sectional areas of the channel results in a substantially reduced effectiveness of atomization process by the action of centrifugal force. The liquid flow kinetic energy losses owing to a friction force impose limits on the length of the channels 2 by twenty-fold values of their diameters. An increased length of the channels implies a reduced pressure difference in the channel 2 defining the value of kinetic energy and, consequently, a reduced flow velocity from the channel 2. The distance between the outlet sections of the channels and the boundary 10 of the spatial region where an atomized liquid jet is generated (see Fig. 5) is selected on condition that the kinetic energy losses of the streams associated with the effect of a medium resistance force are minimal. Because more complete stream splitting is provided when the streams approach the impingement zone with a maximal kinetic energy (velocity), the said distance should not exceed 80Rg. The maximal uniformity of a droplet jet is provided on condition that the outlet apertures of the channels 2 are equally spaced from the axis of symmetry 7 of the casing 1. In such a case, the flows impinge upon one another in a single focal plane extending perpendicular to the axis of symmetry 7 of the casing 1. Displacement of the outlet apertures of the channels 2 with respect to the equally spaced position allows atomized droplet jets of various spatial configuration to be generated. In order to accumulate the atomized stream in a predetermined spatial region and to increase the liquid stream atomizing effectiveness, the atomizer is equipped with a chamber 9 located downstream from the outlet section of the channels 2 (Fig. 3). In the example of an embodiment of the atomizer illustrated in Fig. 3, the chamber 9 is made cylindrical in shape. Upon flowing of liquid from the channels 2, low pressure is created at their outlet sections due to the stream ejection effect. In the course of flowing of liquid streams through the channels 2, a countercurrent gas flow is formed in the chamber 9 owing to the inflow of gas from the ambient medium, said gas flow encouraging the liquid atomization process. An increase in the length LK to the value exceeding 20Dκ (where DK is diameter of the cylindrical chamber 9) results in a reduction of the given effect under the action of the friction force. The optimal size of the chamber 9 in the given example of embodiment of the atomizer complies with the ratio of Dκ/Lκ=1.7. An additional reduction in the hydraulic losses of liquid is due to the fact that the generating lines 5 and 6 of the conical surfaces of the inlet and outlet sections of the channels 2 are running parallel and perpendicular to the axial lines 4 of the channels 2. The cone angle of the atomized liquid jet may be changed through the use of an atomizer casing having different inclination angles of the conical surface generating line 6 with respect to the axis of symmetry 7 of the atomizer. The cone angle of the atomized liquid jet is also changed by the action upon the region of generation of the atomized liquid jet, where the liquid streams impinge upon one another, of an axial liquid stream that is generated in the axial channel 8 of the casing 1 (see Figs 1 to 3). A finely atomized droplet jet may be also generated with the use of a liquid atomizer illustrated in Figs 6 and 7. The working liquid is supplied into the cavity of a casing 15 of the liquid atomizer through a connection pipe 19 for connecting the atomizer to the liquid supplying line. The liquid is then delivered into the channels 12 through entry portions 18 conical in shape. The employment of conical entry portions 18 in the example of embodiment of the atomizer structure under consideration allows hydraulic losses at the channel entry to be decreased to thereby increase the liquid stream flowing velocity. The front projections of the intersecting skew axial lines 11 of the channels 12 intersect at an angle of 179°. Since the axial lines 1 1 of the channels 12 in the considered embodiment of the atomizer are offset by a distance smaller than Rg, only the peripheral parts of the liquid streams impinge upon one another in the region of generation of an atomized liquid jet. The result is that vortex formation occurs in the region of impingement of liquid streams (the region of generation of an atomized liquid jet), said vortex formation being similar to that represented in the description of the embodiment of the atomizer illustrated in Figs 1 to 3. The created vortex having an angular rotation velocity ω provokes breaking-up of liquid streams by the action of the centrifugal force to thereby convert said liquid streams into droplets. The conical shape of surfaces of the outlet sections of the channels 12 in the given embodiment of the atomizer structure provides the impingement of the liquid streams upon 5 one another in the immediate vicinity of the outlet sections of the channels 12. In this region the kinetic energy (velocity) of the streams closely approaches the maximal value to encourage more complete breaking-up of the streams in the region of generation of an atomized jet. Furthermore, the conical surface of the outlet sections of the channels defines in the cylindrical sleeve 14 a cavity where the streams impinge upon one another and the vortex formation 0 region is created. The interaction between the atomized liquid streams and the conical surface of the sleeve 14 facilitates the accumulation of a finely atomized droplet jet in a certain spatial region and formation of a spray of an atomized liquid jet of desired configuration. Utilization of the liquid atomizer implemented in accordance with the present invention 5 provides generation of a spray of finely atomized liquid with uniform intensity and degree of atomization of droplets throughout the flow section, with the energy consumption for the generation of an atomized liquid jet being significantly reduced. It has been established on the basis of investigations made with the use of a working pressure ranging between 0.2 MPa and 0.5 MPa that finely atomized droplet jets of various configuration may be generated and the o desired spraying intensities on vast and restricted areas may be provided by means of the given liquid atomizer. Industrial application of the invention The invention may be used in fire-suppression systems and as part of processing equipment utilized for a variety of purposes. Along with fire-suppression systems, the liquid 5 atomizer may be alternatively used for fuel combustion in heat power engineering, in transport as well as for moistening of environment and spraying of disinfecting substances and insecticides.

Preferable as it is, the represented example of embodiment of the invention does not yet 0 cover any of other possible versions of the embodiment within the scope of claims of the invention, which may be implemented with the help of means and methods known for those skilled in the art.