EA004837B1 - V.i. golubev`s rotary engine - Google Patents

Abstract

1. A rotary machine constructed in the form of a housing and a movable block, the block comprises at least two cylinders crossing by their axes and pistons therein, said cylinder block and the pistons are mounted so as to enable planoparallel, by equatorial circle, with equal angular velocities, synchronized and agreed motion in mutually opposite directions for both cylinder block and pistons using the cylinder block drive cranks and the piston drive cranks or links kinematically equivalent to said drive cranks, wherein the cylinder block and pistons are kinematically connected to at least one coupling link and the motion of both cylinder block and pistons are synchronized with synchronizing links kinematically connecting therein, characterized in that the synchronizing links and their kinematic connections are designed so as to form translation and rotary kinematic pairs. 2. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are designed as synchronizing cranks of the cylinder block and pistons connected by common rotary axes with corresponding drive cranks of the cylinder block and pistons in the form of cylinder guides mounted on the cylinder block and parallel to each cylinder axis, said guides interact with piston sliders mounted on each piston, an also in the form of at least one block of transverse guides, perpendicular to the cylinder axes and interacting with transverse sliders, the block of transverse guides is hinged connected to the synchronizing cranks of the cylinder block, and the transverse sliders are hinged connected to the piston synchronizing cranks. 3. The rotary machine according to claim 2, characterized in that the piston synchronizing cranks are directed opposite to the piston drive cranks, wherein to the synchronizing cranks of the cylinder block are directed in the same direction with the drive cranks of the cylinder block. 4. The rotary machine according to claim 3, characterized in that eccentricities of the synchronizing and drive cranks are equal, the synchronizing cranks of the cylinder block are combined with the drive cranks of the cylinder block, the block of transverse guides is combined with the cylinder block, the transverse guides are designed as additional cylinders, and the transverse sliders are designed as additional pistons provided with trunks. 5. The rotary machine according to claim 2, characterized in that the piston synchronizing cranks are directed in the same direction with the piston drive cranks, wherein to the synchronizing cranks of the cylinder block are directed opposite to the direction of the drive cranks of the cylinder block. 6. The rotary machine according to claim 5, characterized in that the machine is provided with two blocks of transverse guides designed as blocks of additional transverse cylinders, and transverse sliders as additional transverse pistons provided with trunks, the additional cylinder blocks are arranged symmetrical on both sides of the cylinder block. 7. The rotary machine according to claim 5, characterized in that the product of the block mass of the additional transverse cylinders to the eccentricity of the synchronizing cranks is equal to the block cylinder mass to the eccentricity of the drive cranks. 8. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are designed as synchronizing cranks of the cylinder block and pistons united by common rotary axes with corresponding drive cranks of the cylinder block and pistons, all synchronizing cranks are at a right angle to the drive cranks connected to them along stroke or counter stroke of the drive cranks rotation, as well as in the form of cylinder guides interacting with the piston sliders mounted on each piston, and also in the form of at least one block of longitudinal guides, parallel to the cylinder axes and interacting with longitudinal sliders, the block of the longitudinal guides is hinged connected to the synchronizing cranks of the cylinder block, and the longitudinal sliders are hinged connected to the piston synchronizing cranks. 9. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are designed as common cranks arranged along the rotation central axis, said cranks combine the functions of the piston synchronizing cranks and their drive cranks, and also in the form of cylinder guides interacting with the piston sliders hinged connected with the common cranks, wherein the cylinder block is formed from at least two pairs of co-axial, opposite cylinders, intersecting by their axes at a right angle on said hinged connections. 10. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are designed as the piston synchronizing cranks arranged parallel and directed in one direction and connected along the common rotation axes with corresponding piston drive cranks, and also in the form of the cylinder guides mounted on the cylinder block parallel to each cylinder axis and interacting with the piston sliders mounted on each piston sliders and also in the form of at least one synchronizing connecting rod hinged connected with the piston synchronizing cranks. 11. The rotary machine according to claim 1, characterized in that comprises two synchronizing connecting rods in the form of flat rings arranged symmetrically on both sides of the cylinder block. 12. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are designed as the synchronizing cranks of the cylinder block and pistons connected along the common rotation axes with corresponding drive cranks of the cylinder block and pistons, the synchronizing cranks of the cylinder block similar or counter directed relative to the drive cranks of the cylinder block, and piston synchronizing cranks are similar or counter directed relative to the piston drive cranks, and also in the form of cylinder guides mounted on the cylinder block parallel to the axis of each cylinder interacting with the piston sliders mounted on each piston, and also in the form of housing guides mounted on the housing parallel to the axis of each cylinder interacting with intermediate sliders, each of them is provided with transverse piston and transverse cylinder guides arranged perpendicular to the cylinder axis interacting, correspondingly, with the transverse piston slider and the transverse cylinder slider, the transverse piston sliders are hinged connected with the synchronizing piston cranks, and the transverse cylinder sliders are hinged connected with the synchronizing cranks of the cylinder block. 13. The rotary machine according to claim 2, or 8, or 9, or 10, or 12 characterized in that the cylinder guides are formed by the cylinder's walls, and the piston sliders are formed by the piston trunks. 14. The rotary machine according to claim 2, or 8, or 9, or 10, or 12 characterized in that the eccentricity of the synchronizing cranks exceeds the eccentricity of drive cranks. 15. The rotary machine according to claim 1, characterized in that the coupling link is designed as a central cog wheel with external toothing arranged rotatably in the housing interacting with an intermediate cog wheel with internal toothing arranged rotatably in the housing interacting with a gear ring with external toothing arranged movement free in the housing, the toothing has different gear ratio. 16. The rotary machine according to claim 1, 9, characterized in that the coupling ring is designed as an eccentric shaft arranged rotatably in the housing along the eccentric shaft central axis combining common cranks. 17. The rotary machine according to claim 1, characterized in that the coupling rink is designed as crank shaft arranged rotatably in the housing and hinged connected with the cylinder block.

Description

The invention relates to mechanical engineering, in particular to a fully balanced, multi-chamber rotary piston volumetric devices with plane-parallel rotational movement of the block (s) of cylinders and pistons moving in mutually opposite directions. The device can be used to work with incompressible and compressible working bodies, including those on hot gas (for example, as a basis for internal combustion engines, as well as devices of the “motor-reducer” type).

Known volumetric device "Rotativnaya car Golubev VI" [1], the development of which is the proposed technical solution. The known device is made in the form of a housing (base) and a block of at least two cylinder axes intersecting at arbitrary angles with pistons placed in them. The cylinder block and pistons are installed with the possibility of plane-parallel (in which the axes of the cylinders do not change directions) on circles of equal radius, with equal angular speeds of coordinated and synchronized movement in directions opposite to each other for the cylinder block and pistons using drive cranks or kinematically equivalent links. (It is obvious that the drive link, functionally equivalent to a crank, may have a different constructive embodiment, for example, in the form of eccentric or crankshafts, a finger with a roller in a circular guide, earrings on two fingers, etc.). The connection to an external device for transmitting or receiving rotational energy is carried out using a connecting link (master or slave). The coordinated and synchronized movement of the block of cylinders and pistons is achieved by means of connecting synchronizing links. The movement of the pistons and the cylinder block is possible provided that the initial phases (positions) of the pistons in the cylinders and the corresponding drive cranks are matched with the angular position of the axes of the respective cylinders, while the oppositely directed rotational movements of the pistons and the cylinder block lead to a relative linear movement of the pistons in the cylinders. The condition for the said coordination is the continuous equality of the projections onto the axis of each cylinder of the conditional vectors of the drive pistons and cylinder blocks equal in magnitude to the eccentricity of the drive cranks and coinciding with them in direction. In the known device, the synchronizing links are made in the form of identical external gearing wheels mounted on the driving cranks of the pistons and the cylinder block. At the same time, in order to reduce the effect of gaps in the mesh, caused by uneven wear and thermal expansion, the connection of gear wheels between them is made through intermediate gear elastic rings made of antifriction material. The cylinders in the block may have a different cross section - round, oval, rectangular, part of the cylinder walls may be formed by the walls of the body (base). In particular, the known device has a cylinder block in the form of a flat ring, provided with tangentially placed through cavities, which together with the double-sided pistons and housing (base) walls installed, form working chambers relative to windows and channels for supplying and discharging the working fluid placed in the base walls . Since in the known device, the pistons and the cylinder block interact equally with the working fluid, and the synchronizing links combine them kinematically, the connecting link can, in principle, be connected to the cylinder block or any piston, however, for structural reasons, it is often preferable cylinder block that summarizes the power flows of several drive cranks. So, for example, in a known device, the connecting link is made in the form of a gear wheel mounted in the housing with the possibility of rotation with external gearing, over which the gear ring with internal gearing rigidly fixed on the cylinder block is driven. Obviously, it is possible to perform the crown with external engagement, and the gears - with the internal.

The known device is characterized by the movement of the centers of mass of the pistons and the cylinder block along circles of relatively small radius, which significantly reduces the centrifugal forces and allows you to completely balance the device. However, for normal operation of the device, high accuracy and constancy of the parameters of the reciprocal movement of the pistons and the cylinder block is required, which is largely determined by the type of kinematic pairs connecting the synchronizing links and driving cranks of the pistons and the cylinder block. In the known device, the synchronizing links are connected by gearing related to higher kinematic pairs. Such pairs are characterized by a high specific pressure in the contact patch and the need for gearing a guaranteed gap, which leads to an error in the mutual displacement of the pistons and the cylinder block. This disadvantage is aggravated by the general wear of gears and especially local wear and tear at the parts of the gears operating at the moments of high-pressure jumps in the corresponding working chambers. Reducing the accuracy of movement of the cylinder block and pistons leads to the emergence of a force interaction between them, the appearance of shock loads in the synchronizing and driving links, vibration and increased noise. This leads, in general, to an increase in mechanical losses and a decrease in the reliability of the device. It can also be noted that under conditions of high specific pressures in the contact patch, amplified by local application of shock loads, the application of cladding greases creating the effect of "friction without wear" in kinematic pairs with a specific pressure not exceeding about 250 MPa does not give the desired result. which is noticeably less than the usual specific pressures in the contact patch of gearing, the value of which, depending on the materials and technology of manufacturing gears, is 5001000 MPa. An additional disadvantage of the known device is the increased mechanical losses caused by the effect on the cranks of the drive of the cylinder block of forces increased by the ratio of times the reactive torque transmitted from the connecting link to the cylinder block. It can also be attributed to the additional disadvantages of certain layout constraints, due to the necessary circular arrangement of the drive cranks connected by a synchronizing toothed ring.

The present invention solves the problem of eliminating the main disadvantage of the prototype, the presence of high specific pressure and non-permanent (local) gaps in the gears of the synchronizing links. The main technical result of the proposed technical solution is to increase the accuracy of the mutual displacement of the cylinder block and pistons and, accordingly, reliability and durability by eliminating gearing in the links of synchronizing links, i.e. by reducing specific pressures and the influence of gaps in kinematic pairs connecting the synchronizing links with cranks drive the working bodies through the use of predominantly lower kinematic pairs or their equivalent kinematic connections s. (By definition [2], in the lower kinematic pair, the links contact over the surface or along lines and points through which the surface can be drawn, and the kinematic connection constructively replaces the kinematic pair, for example, the contact of the links through roller or needle bearings is equivalent to the lower rotational kinematic pair). Additional technical results are

- reduction of losses due to the reduction of the forces of the reactive moment acting on the drive cranks of the cylinder block;

- the expansion of the functional and layout capabilities (structural base) of the proposed device due to the variation of the execution of the synchronizing and connecting links, as well as their connections.

To do this, in a well-known rotary machine, made in the form of a housing and a block of at least two cylinders intersecting with their axes and placed in cylinders of pistons installed with the possibility of a plane-parallel, on circles of equal radius, with equal angular speeds, synchronized and coordinated movement in mutually opposite for the pistons and the cylinder block, the directions carried out by means of the driving cranks of the cylinder block and the driving cranks of the pistons, or kinematically equivalent mentioning null drive crank links, with a cylinder block and pistons, kinematically connected to at least one connecting link and synchronized movement of the cylinder block and pistons, performed by kinematically connecting synchronizing links, to achieve the main technical result in all embodiments of the device, synchronizing links and their kinematic compounds are made with the formation of translational and rotational kinematic pairs (or their equivalent kinematic Connections). The proposed general technical solution covers various specific variants of its implementation, which are determined by the variants of execution of synchronizing links and their connections, as well as the variants of execution of the connecting link and its connection. It is obvious that the translational kinematic pair is formed by the interaction of the guide and the slide, and the rotational kinematic pair - by the hinged connection of the links.

The first variant (1a) of synchronizing links and their kinematic connections can be represented as

- synchronizing cranks of the block of cylinders and pistons connected by common axes of rotation with corresponding driving cranks of the block of cylinders and pistons; mounted on a cylinder block parallel to the axis of each cylinder of cylinder guides, interacting with piston sliders installed on each piston;

- at least one block of transverse guides perpendicular to the axes of the cylinders and interacting with transverse sliders, the transverse guide block must be pivotally connected to the synchronizing cranks of the cylinder block, and transverse sliders must be pivotally connected to the synchronizing pistons of the cranks.

It is obvious that the shape of the block of transverse guides is determined by its compliance with the configuration of the cylinder block.

The walls of the cylinders can be used as parallel to the axes of the cylinders, and piston pistons can be used as piston sliders. If it is necessary to exclude the force interaction of the pistons with the walls of the cylinders, piston sliders and transverse guides can be made similarly to the known crosshead mechanism.

The synchronization link connection in the first embodiment is operable under the condition that the synchronizing cranks of the pistons are directed oppositely connected to them by the driving cranks of the pistons, and the synchronizing cranks of the cylinder block are directed to one side with the driving cranks of the cylinder block.

In this case, the second variant (1b) of the execution of synchronizing links and their connections (based on variant 1a) can be represented as

- synchronizing and driving cranks with equal eccentricity, synchronizing cranks of the cylinder block, combined with the driving cranks of the cylinder block;

- block transverse guides, combined with the cylinder block;

- transverse guides in the form of additional cylinders and, respectively, transverse slider in the form of additional piston.

In other words, in this case, synchronizing links conditionally “disappear” (i.e., drive cranks perform the function of synchronizing cranks) when the cylinder block is executed with initial and additional cylinders crosswise positioned (possibly with a different cross section) and additional pistons pivotally connected with corresponding equally executed synchronizing piston cranks and driving piston cranks coaxially combined into combined curved Types. The proposed particular solution involves the execution of a block of some set of cross-connected cylinders, the centers of intersection of the axes of which can be placed, in the general case, along a line of arbitrary shape, for example, along a circle.

The connection of the synchronizing links in the first embodiment is also efficient provided that the synchronizing cranks of the pistons are directed to one side with the driven cranks of the pistons, and the synchronizing cranks of the cylinder block are directed opposite to the driving cranks of the cylinder blocks.

In this case, the third option (1c) for the execution of synchronizing links and their connections (based on option 1a) can be represented as two blocks of transverse guides, made as a block of additional transverse cylinders, and transverse sliders - in the form of additional transverse thrones pistons the blocks of additional transverse cylinders must be placed symmetrically on both sides of the cylinder block, which allows balancing the cylinder block without using counterweights.

To balance the cylinder block due to the antiphase movement of blocks of additional transverse cylinders, it is necessary that the product of the mass of blocks of additional transverse cylinders by the eccentricity of the synchronizing cranks be equal to the product of the mass of the cylinder block by the eccentricity of the drive cranks of the cylinder blocks.

The fourth variant (1d) of execution of synchronizing links and their connections, can be represented as

- synchronizing cranks of the block of cylinders and pistons connected by common axes of rotation with corresponding driving cranks of the block of cylinders and pistons, all synchronizing cranks must be directed at right angles to the connected cranks of the connecting cranks along or against the direction of rotation of the driven cranks ( i.e. they must be ahead or lagging in phase by 90 °);

- cylinder rails mounted on the cylinder block parallel to the axis of each cylinder, interacting with piston sliders installed on each piston;

- at least one block of longitudinal guides parallel to the axes of the cylinders and interacting with longitudinal sliders, the block of longitudinal guides must be pivotally connected to the synchronizing cranks of the cylinder block, and the longitudinal sliders must be pivotally connected to the synchronizing cranks of the pistons.

The fifth embodiment of the synchronizing links and their connections on the kinematic basis of option 1b with additional cylinders and pistons can be represented as

- installed on one central (single) axis of rotation of common cranks, combining the functions of the synchronizing cranks of the pistons and the driving cranks of the pistons;

- cylinder guides interacting with piston sliders pivotally connected with common cranks;

- a cylinder block consisting of at least two pairs of coaxial, opposite cylinders intersecting with their axes under

Ί a right angle on the hinge joints of common cranks (i.e. the cylinder block is made in the form of an even star with radially spaced cylinders).

Here, the combination of synchronization and drive cranks implies that each crank performs both the drive function (for “its” pistons and cylinders) and the synchronization function (for perpendicular pistons and cylinders). At the same time, synchronizing links also conditionally “disappear”, since each pair of coaxial cylinders rigidly interconnected (for example, piston sliders in the form of rods) and driven (they are also synchronizing) piston cranks perform the function of synchronization with respect to perpendicular to it the same coaxial pair of cylinders with pistons also connected together.

(This option is preferable, for example, when implementing the device as an internal combustion engine. In this case, the rods can be unloaded from bending forces by transferring cylinder guides and piston sliders to the region of the mentioned central axis of rotation).

The sixth embodiment of the synchronization links and their connections, can be represented as

- installed in parallel and directed to one side synchronizing cranks of pistons connected by common axes of rotation with corresponding driving pistons of cranks;

- cylinder rails mounted on the cylinder block parallel to the axis of each cylinder, interacting with piston sliders installed on each piston;

- at least one synchronizing connecting rod pivotally connected to the synchronizing cranks of the pistons.

(In general, the piston's synchronization cranks can be directed in an arbitrary direction. However, to average the conditions of the synchronizing connecting rod operation, it is advisable to take the direction of the piston's synchronizing cranks that do not coincide with the direction of the piston's driving cranks, for example, an angle approximately equal to half the angle between the directions of the adjacent piston driving cranks. Here too, in order to simplify the construction, the cylinder guides can be formed by the walls of the cylinders, and piston sliders can be l made in the form of a piston piston).

The specific performance of the connecting rods depends on the configuration of the cylinder block. For example, for a disk-shaped cylinder block, the timing rods can be made in the form of flat rings placed symmetrically on both sides of the cylinder block. It is also possible to execute a synchronizing rod in the form of a flat ring cylinder block placed in the plane of symmetry, provided with radially protruding inward or outward pivots hinged to the synchronizing piston cranks.

The seventh embodiment of the synchronization links and their connections can be represented as

- synchronizing cranks of the block of cylinders and pistons connected by common axes of rotation with the corresponding drive cranks of the cylinder and pistons, the synchronizing cranks of the cylinder block must be the same or opposite direction relative to the drive cranks of the cylinder block, and the synchronizing cranks of the pistons must be opposite or equal to relative drive pistons;

- cylinder rails mounted on the cylinder block parallel to the axis of each cylinder, interacting with piston sliders installed on each piston;

- body guides mounted on the body parallel to the axis of each cylinder, interacting with intermediate sliders, each of which, in turn, is provided with transverse piston guide and transverse cylinder guide perpendicular to the axis of its own cylinder, interacting respectively with its own transverse piston the slider and transverse cylinder slider, while the transverse piston sliders are hingedly connected to the synchronizing cranks of the pistons, and the transverse cylinder pistons Alzuns are hingedly connected to synchronizing cranks of the cylinder block.

(It can be noted that the piston and cylinder guides can lie on one straight line and can be made as a single guide. To minimize gaps, each body guide can be made in the form of a plate mounted on the body and provided with a groove playing the role of the guide. Accordingly, the intermediate slider can be made in the form of a plate, provided, on the one hand, with a ridge placed in the said groove, and on the other hand, with a groove in which the piston pistons equipped with bearings are placed and ilindrovye slides).

To increase the accuracy of the synchronizing transmission, the eccentricity of the synchronizing cranks may exceed the eccentricity of the driving piston cranks, except for option 1b with the execution of guides in the form of additional cylinders placed in the original (i.e., single) unit, as well as in the fifth version with a central axis of rotation of the common cranks.

In order to reduce the reactive forces acting on the drive cranks of the cylinder block and expand the range of gear ratios, the connecting link can be made in the form of a central gear wheel mounted for rotation with external gearing and interacting with an intermediate gear wheel mounted for rotation the internal gearing interacting with the gear ring mounted on the case without the possibility of rotation with the external gearing, at the same time the gears engaging made with different gear ratios. In this case, the reactive moment is perceived by a gear ring mounted on the housing, and the presence of two gear links increases the number of possible gear ratio combinations. (It may be noted that the pitch diameter of the links may be the same, but the linking modules must be different).

In many cases, the execution of the device (for example, in the form of internal combustion engines) is not necessary in the reduction or multiplication of the speed of the drive cranks. In this case, when the cylinder block is made in the form of an even "star" (the fifth variant of connecting and executing synchronizing links), the connecting link can be made in the form of an eccentric shaft mounted in the housing with the possibility of rotation along the central axis, combining common cranks made in the form of eccentrics . This embodiment of the connecting link allows you to perform a cylinder block with cylinders in the same plane.

Similarly, the connecting link can be made in the form installed in the housing for rotation of the crankshaft, pivotally connected to the cylinder block. (At the same time, the mentioned crankshaft should correspond to the power flow transmitted, and its location relative to the cylinder block can be chosen quite arbitrarily, including on the outer side of the block. However, when positioning the cylinders around the circumference, for structural reasons, its central location is preferable).

The proposed options for connecting and executing synchronizing links solve, in principle, the task and justify their presentation in the form of generalized kinematic terms of distinctive essential features necessary and sufficient for obtaining a technical result.

FIG. 1a-d shows a kinematic diagram of a device with an annular block of tangential cylinders and a connecting link in the form of a gear wheel, showing the embodiments of a synchronizing transmission (conventionally separated by break lines):

a - with transverse sliders and block transverse guides, in-phase cylinder block;

b - with transverse guides and sliders in the form of additional cylinders and pistons;

in - with transverse sliders and block of transverse guides, antiphase cylinder block;

d - with longitudinal sliders and block of longitudinal guides.

FIG. 2 shows a kinematic diagram of the device with a connecting link in the form of a central eccentric shaft and a block of radial cylinders with combined synchronizing and driving piston cranks.

FIG. 3 a, b shows a kinematic diagram of the device with a connecting link in the form of a crankshaft and an annular block of tangential cylinders, showing options for connecting and executing synchronizing links (separated by break lines):

a - with a common connecting rod;

b - with body guides and intermediate sliders.

FIG. 4a, b is a drawing (sections in the plane of motion) of variants of the device, corresponding to 4a - fig. 1a; 4b - FIG. 1b.

FIG. 5a and b show transverse sections of variants of the device, corresponding to FIG. 4a, b.

The proposed device (for example, a pneumatic motor) contains (see Figs. 1a-5a, b) a housing 1 and a movable cylinder block 2 (intersecting with its axes) with pistons 3 placed in them. cylinders 2 and pistons 3 directions is carried out using the installed in the housing 1 of the drive cranks 4 of the cylinder 2 and the drive cranks 5 of the pistons 3 (or kinematically equivalent to the drive cranks of links). The necessary synchronization of the movement of the cylinder block 2 and the pistons 3 is achieved, in general, with the help of synchronizing links and their kinematic connections, which form only translational and rotational kinematic pairs, the concrete realization of which is represented by different variants of their implementation. These variants are shown in the form of kinematic diagrams (Figs. 1-3), and it is assumed that the cylinder block 2 on each kinematic diagram is common to all variants, and the variants are separated by break lines. Possible constructive implementations of the proposed device, corresponding to the kinetic magic circuits of FIG. 1a, b (in a layout similar to the prototype) is shown in FIG. 4a, b and 5a, b. In this case, the cylinder block 2 has the form of a disk with tangentially placed rectangular cylinders formed by the walls of the cylinder block 2 and the walls of the housing 1. Accordingly, the distribution mechanism (not shown) can be performed in the same way as in the prototype, namely, by appropriate placement of and diverting the working fluid channels in the walls of the housing 1 along the paths of movement of the working chambers 6. The connection of the proposed device with a power source (drive), or with a power consumer (load) is carried out With the help of connecting link 7 (slave or master), kinematically connected (most often) with the cylinder block 2 (Fig. 1, 3, 4, 5) or with the pistons 3 (Fig. 2).

In the first embodiment (Fig. 1a, 4a, 5a), the implementation of the synchronizing links and their kinematic connections is presented as

- synchronizing cranks 8 of the cylinder block 2 and synchronizing cranks 9 of the pistons 3 connected by common axes of rotation 10 and 11, respectively, with the driving cranks 4 of the cylinder 2 and the driving cranks 5 of the pistons 3, while the synchronizing cranks 9 of the pistons 3 are opposite to the driving cranks 5 the pistons 3, and the synchronizing cranks 8 of the cylinder 2 are directed to the same direction as the driving cranks 4 of the cylinder 2;

- mounted on the cylinder block 2 parallel to the axis of each cylinder of cylinder guides 12, interacting with 3 piston sliders 13 installed on each piston;

- two blocks of transverse guides 14, perpendicular to the axes of the cylinders and interacting with transverse sliders 15, while the blocks of transverse guides 14 are pivotally connected to the synchronizing cranks 8 of the cylinder 2, and the transverse sliders 15 are pivotally connected to the synchronizing cranks 9 of the pistons 3.

It is obvious that as the cylinder guides 12 and piston sliders 13 can be used (most often) - the walls of cylinders and piston pistons. In particular, in the constructive implementation of the device (Fig. 4a, 5a) with the connection of synchronizing links in the kinematic scheme of Fig. 1a, cylinder guides 12 and piston sliders 13 are combined with cylinders and pistons, and two transverse guide blocks 14 placed on both sides of the housing 1 of the block 1 are made in the form of lightweight discs equipped with radially placed through slots in which prismatic cross sliders 15 are placed. increase the accuracy of positioning of the pistons 3 eccentricity of the synchronizing cranks 8, 9 exceeds the eccentricity of the driving cranks 4, 5.

In the second variant (Fig. 1b, 4b, 5b), the implementation of synchronizing links and their kinematic connections is presented as

- a block of cylinders 2 with additional cylinders 16 (performing the functions of a block of transverse guides 14) and equipped with triples of additional pistons 17 (performing the functions of transverse sliders 15).

The proposed examples of constructive execution of the device and the connections of the synchronization links (Fig. 4a, b, 5a, b) also show the possible principle of the implementation of similar devices with another execution of the synchronization links and their connection, presented in the kinematic diagrams of Figs. 1c, g, 2, 3a, b.

In the third variant (Fig. 1c), the implementation of synchronizing links and their kinematic connections is presented as

- two blocks of additional transverse cylinders 18 (performing the functions of a block of transverse guides 14) and additional transverse pistons 19 (performing the functions of transverse sliders 15).

Moreover, the blocks of additional transverse cylinders 18 can be structurally similar to the cylinder block 2 and are symmetrically placed relative to it (not shown), and the eccentricity of the synchronizing cranks can be greater than the eccentricity of the drive cranks. To balance the product of the mass of blocks of additional transverse cylinders 18 by the eccentricity of the synchronizing cranks 8 of the cylinder 2 must be equal to the product of the mass of the cylinder 2 by the eccentricity of the driving cranks, thus achieving compensation of the centrifugal forces acting on the cylinder 2.

In the fourth version (Fig. 1d), the implementation of synchronizing links and their kinematic connections is presented as

- synchronizing cranks 8 of the cylinder block 2 and synchronizing cranks 9 of the pistons 3 connected along the common rotation axes 10 and 11, respectively, with the driving cranks 4 of the cylinder 2 and the driving cranks 5 of the pistons 3, all the synchronizing cranks are directed at right angles to the connected crankshafts them drive the cranks along or against the course of their rotation;

- mounted on the cylinder block 2 parallel to the axis of each cylinder of cylinder guides 12, interacting with 3 piston sliders 13 installed on each piston;

- at least one block of longitudinal guides 20 parallel to the axes of the cylinders and interacting with the longitudinal synchronizing sliders 21, while the block of the longitudinal guides 20 are hinged to the synchronizing cranks 8 of the cylinder 2 and the longitudinal synchronizing sliders 21 are hinged to the synchronizing cranks of 9 pistons 3

It is obvious that structurally the device and the block of the longitudinal guides 20 can be made similar to the original device and its block of transverse guides 14 shown in FIG. 4a, 5a (a separate drawing of this design variant is not shown).

In the fifth version (Fig. 2), the implementation of synchronizing links and their kinematic connections is presented as

- installed on the Central axis of rotation of the 22 common cranks 23, United in eccentric shaft 24;

- cylinder block 2, consisting of at least eight cylinders (two "crosses");

- installed parallel axes of each pair of opposed cylinders of cylinder guides 12 (in the form of bushings of piston rods), interacting with piston sliders 13 (in the form of piston rods) respectively installed parallel to the axes of the pistons 3, it is also possible to use the walls of the cylinders as cylinder guides 12, and piston pistons as piston sliders 13.

In fact, the fifth is the development of the particular solution shown in FIG. 1b and 4b, 5b, “enlarged” to an independent full-sized cylinder block 2. Accordingly, the constructive implementation of this device variant (not shown) can be built on the basis of the design shown in FIG. 4b and 5b.

In the sixth variant (Fig. 3 a), the implementation of synchronizing links and their kinematic connections is presented as

- installed in parallel and directed in one direction to the synchronizing cranks 9 of the pistons 3, connected along the common axes of rotation 11 with the corresponding driving cranks 5 of the pistons 3;

- installed on the cylinder block 2 parallel to the axis of each cylinder of cylinder guides 12, interacting with piston sliders installed on each piston 13;

- at least one synchronizing rod 25 (in the particular case of an annular form) pivotally connected to the synchronizing cranks 9 of the pistons 3;

It is obvious that cylinder walls 12 can be used as cylinder guides 12, and piston rods as piston sliders 13. The constructive implementation of this device variant (not shown) may be similar to that shown in FIG. 4a, 5a with the replacement of blocks of transverse guides 14 with synchronized connecting rods 25 made in the form of flat rings.

In the seventh variant (fig. 3b) the realization of synchronizing links and their kinematic connections is presented in the form

- synchronizing cranks 8 of the cylinder block 2 and synchronizing cranks 9 of the pistons 3 connected along common axes of rotation 10, 11 with the corresponding driving cranks 4 of the cylinder 2 and the driving cranks 5 of the pistons 3, while the synchronizing cranks of the cylinder block 2 are equally directed relative to the driving cranks 4 blocks of cylinders 2, and the synchronizing cranks 9 of the pistons 3 are oppositely directed relative to the drive cranks 5 of the pistons 3, and the eccentricity of the synchronizing cranks exceeds the eccentricity drawing of drive cranks;

- installed on the cylinder block 2 parallel to the axis of each cylinder of cylinder guides 12, interacting with piston sliders installed on each piston 13;

- mounted on the housing 1 parallel to the axis of each cylinder case guides 26, interacting with intermediate sliders 27, each of which is provided with transverse cylinder guide 28 and transverse piston guide 29, which are perpendicular to the axis of "their" cylinder 30, and interacting respectively with cross cylinder slider 30 and transverse piston slider 31, while the transverse cylinder slider 30 is pivotally connected to the synchronizing cranks 8 of the cylinder block 2, and the transverse piston slider s 30 pivotally connected with synchronizing cranks 9 of pistons 3;

It is obvious that the cylinder guides 12 can be formed by the walls of the cylinders, and piston sliders 13 by triples of pistons. The constructive implementation of this device variant (not shown) may be similar to that shown in FIG. 4a, 5a with the arrangement of the body guides 26 and intermediate sliders 27 on the body 1 symmetrically on both sides of the cylinder block 2. In this case, the body guide 26 can be made in the form of a box cover fixed to the body 1 provided with a groove (guide) at the bottom under it, the intermediate slider 27 can be made in the form of a plate, equipped with a ridge (slider) on one side, and a slot (guide) on the other side, in which transverse cylindrical slider 30 and transverse piston are placed evye slides 31.

The external system (load or engine) can be connected to the proposed device through the connecting link 7 (master or slave) in different ways, depending on the design implementation of the device and its purpose. Accordingly, the connecting link 8 may have variants of constructive and functional implementation.

In the first embodiment (Fig. 1a-d, 4a, b, 5a, b) connecting the external system (gear) connecting link 7 is made in the form installed in the housing 1 with the possibility of rotation of the central gear 32 with external gearing, equipped with a gear coupling 33 ( Fig. 5a) and interacting with mounted on the cylinder block 2 for rotation by an intermediate gear wheel 34 in the form of a ring with internal gearing, simultaneously interacting with gear ring 35 mounted on the housing 1 without rotation by means of an external gear warming Differences in gear ratios of gears are determined by the required reduction value.

In the second embodiment (Fig. 2), the connection of the external system (gearless) connecting link 7 is made in the form of an eccentric shaft 24 mounted in the housing 1 for rotation along the central axis 22 (i.e., the eccentric shaft 24 simultaneously performs the functions of a connecting link 7 and common cranks.

In the third variant (fig. 3 a, b) of connecting the external system (gearless) connecting link 7 is made as installed in the housing 1 with the possibility of rotating the crankshaft 36 pivotally connected to the cylinder block 2 (i.e. the crankshaft 36 simultaneously performs functions of the connecting link 7, as well as the "main" drive crank shaft of the cylinder block).

The proposed device, for example, in the mode of the pneumatic motor, works as follows.

The working fluid (compressed air) using any known distribution mechanism (not shown, since the implementation of the distribution mechanism does not directly affect the execution of synchronizing links and their kinematic connections), is fed into the corresponding working chambers 6. For example, the distribution mechanism can be implemented like the one presented in the prototype, where the working chambers 6 move along circular paths relative to the inlet and outlet channels of the working body located in the walls of the housing 1 (not shown). Expanding, the working body moves the cylinder block 2 and the pistons 3 in opposite directions, which causes rotation in opposite directions of the connected drive cranks 4 of the cylinder 2 and the drive cranks 5 of the pistons 3. Mutual, strictly coordinated movement of the cylinder block 2 and pistons 3 is provided the proposed options for performing synchronizing links and their kinematic compounds in the form of rotational and translational kinematic pairs. Strictly speaking, when performing the cylinder block 2 with intersecting axes of the cylinders and with the correct initial position of the pistons 3 in the cylinders, as well as with ideal interaction (the gaps in kinematic pairs are infinitely small and there is no friction) of the cylinder guides 12 and piston sliders 13 (or cylinder walls and the piston pistons 3) the function of the synchronizing link can be performed by the cylinder block 2 itself, which uniquely defines the spatial position of the pistons 3, their movement in the cylinders. Kinematic analysis shows that the uncertainty of the position of the piston 3 in each cylinder (or piston slider 13 and cylinder guide 12) occurs at the time of coincidence of the directions of the drive crank 5 of the piston 3 and the drive cranks 4 of the cylinder 2, which corresponds to the average position of the piston in the cylinder. Indeed, at this moment the tangents to the circles of the trajectories of motion of the piston 3 and the cylinder are parallel to each other, as well as parallel to the walls of the cylinder or its cylinder guide 12, which leads to the disappearance of the kinematic interaction between them, i.e. to the emergence of kinematic uncertainty. Obviously, with the mentioned ideal case, the length of the kinematic uncertainty zone tends to an infinitely small value. A finite size gap that actually exists in a forward kinematic pair dramatically increases the length of the kinematic uncertainty zone and the piston slider 13 (thrust piston 3) under the action of pressure forces of the working fluid does not interact with the cylinder block 2 (the gap is related to the interaction forces in the translational pair) and as a result “ slips "zone of kinematic uncertainty, which leads, taking into account the influence of friction forces, to jamming of the cylinder block 2. It should be noted that with extreme positions n rshnevogo slider 13 (trunk piston 3) when the drive cranks 4 cylinder 2 and the piston 5 driven cranks 3 are directed in opposite directions, kinematic uncertainty minimum (clearance is perpendicular to the translational forces of interaction pair) and the influence of the gap becomes negligible. When turning the drive cranks relative to the considered position at an angle of approximately ± 45 °, the kinematic uncertainty remains quite small. At the same time, it is also necessary to note the almost insignificant influence of the gap in the rotational kinematic pair: “drive crank 5 of piston 3 - piston slide 13 (throned piston 3)” under the assumption that this gap is commensurate with the gap in the translational kinematic pair mentioned.

The proposed technical solution is based on the considered kinematic features of the interaction of translational pairs and consists in providing a rigid relationship (synchronization) between the position of the cylinder block 2 and each piston 3 in the region of its average position (approximately ± 45 ° in the angle of rotation of the drive cranks relative to their coincident in the direction of ). This is achieved by a rigid kinematic connection, in the general case, moving synchronizing links, forming, as already noted, translational and rotational kinematic pairs. At the same time, links that are currently in the area of large kinematic uncertainty are connected with links that are currently in the area of small kinematic uncertainty. In the process of moving, these links alternately “hold” each other in the required position, thus carrying out their synchronized and coordinated movement. In particular, (Fig. 1a, 4a, 5a) under the action of the pressure of the working fluid on the ends of the cylinders, the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Together with the drive cranks 4, the synchronizing cranks 8 of the cylinder block 2 coinciding in direction (but having greater eccentricity) rotate around the common axis of rotation 10. Accordingly, along with them, the block of the transverse guides 14 around the hinge mounted on the synchronizing cranks 8 interacting with transverse sliders 15 pivotally mounted on synchronizing cranks 9 pistons 3. On the other hand, synchronizing cranks 9 pistons 3 rotations are rotated in the opposite direction (clockwise) around the common axis 11, since they are connected to the oppositely directed drive cranks 5 of the pistons 3, which also rotate under the action of the pressure forces of the working fluid on the pistons 3. It can be seen that with this arrangement the synchronizing links and kinematic connection, each piston slider 15 or piston piston 3, which is in the area of maximum kinematic uncertainty, is kinematically rigidly connected through a synchronizing crank 11 with its own transverse floor Zune 15, which is at this time in the region of minimal kinematic uncertainty and vice versa, each transverse slider 15, which is in the region of maximum kinematic uncertainty, is in the same way associated with "its" piston slider 13 or tronkovom piston 3, which is in this region in the region of minimum kinematic uncertainty and interacting with the cylinder block 3 through the cylinder guide 12 or the wall of the cylinder, (FIG. 1b, 4b, 5b) under the action of pressure forces of the working fluid on the ends of the cylinders of the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Together with the drive cranks 4, the opposite in direction and having (unlike in Fig. 1a) equal eccentricity synchronizing cranks 8 of the cylinder block 2 around a common axis of rotation rotate

10. In this case, the role of the block of transverse guides is played by the actual block of cylinders 2 with additional cylinders 16 placed in it (i.e. transverse guides), and additional piston-shaped pistons 17 play the role of piston sliders. It can be seen that the principle of operation of synchronizing links does not differ from their work in the kinematic scheme shown in FIG. 1a;

(Fig. 1c) under the action of the pressure forces of the working fluid on the cylinder ends of the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Together with the drive cranks 4, the synchronizing cranks 8 of the cylinder block 2, which are opposite in direction and having a greater eccentricity, rotate around the common axis of rotation 10. They are, respectively, two blocks of additional transverse cylinders 18 (along perform the role of a block of transverse guides 14), interacting with additional transverse pistons 19 (play the role of transverse sliders 15), a hinge o installed on synchronizing cranks 9 pistons 3, also having a greater eccentricity. On the other hand, the synchronizing cranks 9 of the pistons 3 rotate in the opposite direction (clockwise) around a common axis 11, since they are connected to the equally directed driving cranks 5 of the pistons 3, which rotate under the action of the pressure forces of the working fluid on the pistons 3. that the principle of operation of synchronizing links is not significantly different from their work in the kinematic scheme shown in FIG. 1a, but blocks of additional transverse cylinders 18 may balance the cylinder block 2;

(Fig. 1d) under the action of pressure forces of the working fluid on the ends of the cylinders, the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Together with them, the synchronizing cranks 8 of the cylinder block 2, which are perpendicular in direction and having a greater eccentricity, rotate around them around a common axis of rotation 10. Accordingly, along with them the block of parallel longitudinal guides 20 mm that interacts with longitudinal synchronizing sliders 21 pivotally mounted on the pistons 9 of the pistons 3. On the other hand, the synchronizing crank s 9 pistons 3 rotate in the opposite direction (clockwise) around a common axis 11, because they are connected with perpendicularly directed drive cranks 5 pistons 3, which also rotate under the action of the working fluid pressure forces on the pistons 3. It can be seen that the axes of the cylinders and the longitudinal guides, as well as, respectively, the perpendicularity of the synchronizing and driving cranks, the principle of operation of the synchronizing links is not significantly different from their work in the kinematic scheme presented oh in fig. 1a;

(Fig. 2) under the action of pressure forces of the working fluid on the ends of the cylinders of the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Accordingly, together with the cylinder block 2, parallel to each other around the central axis of rotation 22, the cylinder guides 12 or cylinder walls interacting with the piston sliders 13 or with the piston pistons 3 are circumferentially displaced. with their own drive cranks 5 into the eccentric shaft 24, rotate in the opposite direction (clockwise) around the central axis of rotation 22 under the action of the working fluid pressure forces on the pistons 3 It can be seen that, considering the fact that the considered variant is actually a joint on one eccentric shaft 24 of two fragments (two “crosses”) of the kinematic scheme shown in FIG. 1b, the principle of operation of synchronizing links is not significantly different from their work in the mentioned kinematic scheme;

(Fig. 3 a) under the action of the pressure forces of the working fluid on the cylinder ends of the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Accordingly, together with the cylinder block 2, they make a plane-parallel rotational movement and cylinder guides 12 interacting with piston sliders 13, or cylinder walls interacting with pronkovy pistons. On the other hand, connected to the drive cranks 5 of the pistons 3 and having a greater eccentricity, as well as directed in one direction (in general, not coinciding with the direction of the drive cranks 5), the synchronizing cranks 9 of the pistons 3 rotate around a common axis of rotation 11 in the opposite direction (clockwise) under the action of the pressure force of the working fluid on the pistons 3. The synchronizing rod 25, which rigidly combines parallel synchronizing cranks 9 and driving cranks 5 through hinges, makes flat parallel rotational (clockwise) movement and kinematically connects piston sliders 13 or piston pistons, including, most importantly, placed in cylinder guides 12 (or cylinders) intersecting at an angle equal to or close to 90 °, You can see that Considering that the cylinder block 2 always contains at least a pair of such cylinders, the principle of operation of the synchronizing links does not differ significantly from their work in the kinematic diagram shown in FIG. 1a;

(Fig. 3b) under the action of the pressure forces of the working fluid on the cylinder ends of the cylinder block 2 begins to move, rotating the drive cranks 4 of the cylinder 2 (for example, counterclockwise). Together with the drive cranks 4 rotate and connected to them equally (or oppositely) directional synchronizing cranks 8 of the cylinder 2 around a common axis of rotation 10. Accordingly, together with the cylinder block 2 make a plane-parallel rotational movement and cylinder guides 12, interacting with piston sliders 13, or cylinder walls interacting with tronkovye pistons. On the other hand, connected to the drive cranks 5 of the pistons 3 and oppositely directed synchronizing cranks 9 of the pistons 3, rotate around a common axis of rotation 11 in the opposite direction (clockwise) under the action of the pressure forces of the working fluid on the pistons 3. In the process of rotation related to one the cylinder synchronizing cranks 8 of the cylinder 2 and the synchronizing cranks 9 of the pistons 2 retain the necessary mutual position, interacting through the corresponding transverse cylinder sliders 30 and transverse piston sliders 31 with a transverse cylinder guide 28 and with a transverse piston guide 29 placed in intermediate sliders 27. In turn, intermediate sliders 27 cannot be twisted, since they themselves move in body guides 26 and simultaneously interact through cross-cylinder sliders 30 s 8-cylinder synchronizing cranks

2. It can be seen that the position of the piston slider 13 in the cylinder guide 12, or the piston piston 3 in the cylinder relative to the transverse piston slide 31 in the transverse piston guide 29 provides for the minimization of the kinematic uncertainty, therefore, the principle of operation of the synchronizing links is not significantly different from their work in The kinematic scheme shown in FIG. 1a

The transfer of motion from the connecting link 7 to the cylinder block 2 and the pistons 3 or vice versa, depending on the purpose of the device, can occur in different ways.

In the first variant (Fig. 1a-d, 4a, b, 5a, b), the pistons 3 transfer their half of the power flow through the piston sliders 13 or the piston pistons 3 by the cylinder guide 12, or through the walls of the cylinders to the cylinder block 2. The cylinder block 2 performs a plane-parallel rotational motion on the drive cranks 4 and the intermediate gear wheel 34 installed therein with the possibility of rotation simultaneously with one of its gear teeth (of larger diameter) fixed to the crown 35 fixed on the body 1, and the second toothed gear 35 captivity (smaller diameter) - for the connection for link 7 in the form of the sun gear 32 to which the external system can be attached by means of a toothed coupling 33. The increased number of transmission times in the reaction torque is transmitted to the body 1 through a ring gear 35 mounted thereon.

In the second embodiment (Fig. 2), the cylinder block 2 performs plane-parallel rotational motion on the drive cranks 4 and transmits its half of the power flow through the cylinder guides 12 (cylinder walls) to the piston sliders 13 or to the piston pistons 3. Each pair of opposite pistons 3 rotates its own , made in the form of an eccentric, common crank 23. Since all eccentrics are combined into an eccentric shaft 24, it acts as a connecting link 7. With identical execution of the pistons, the centrifugal forces acting on the eccentric and the eccentric shaft 24 are mutually compensated. At the same time, the pressure forces of the working fluid on the eccentrics only create a pair of equal forces (only torque), since in any working chamber 6 the pressure of the working fluid on the piston 3 is equal to the force acting on the end of "its" cylinder, and this force is transmitted through the cylinder block 2 and a cylinder guide 12 (cylinder walls), a perpendicular cylinder at a given moment, its piston slider 15 (a piston piston 3), an eccentric directed opposite to the eccentric in question. The reactive moment is transmitted to the housing 1 through piston sliders 13 (piston pistons 3), cylinder guides 12 (cylinder walls), and a cylinder block 2 mounted in the housing 1 driving cranks 4.

In the third variant (Fig. 3 a, b), the pistons 3 transfer their half of the power flow to the cylinder block 2 through piston slides 13 (piston pistons 3), cylinder guides 12 (cylinder walls). The cylinder block 2 summarizes the power flows and performs plane-parallel rotational motion on the drive cranks 4, at the same time rotating the connecting link 7, made in the form of a crankshaft 36.

The proposed implementation of a rotary volumetric device with synchronization of the relative position of the cylinder block and pistons using only rotational and translational kinematic pairs allows reducing vibrations, increasing the reliability and durability of the device, allows using modern cladding lubricants (additives), significantly improving the work and manufacturing technology of kinematic systems with redundant connections, which include the proposed device. It is particularly preferable to use the proposed device as an element base for creating a system such as a planetary “gear motor” with a large reduction value used, for example, in vehicle drives, in screw drives of helicopters, propellers, and drill columns. The preference of various embodiments of the device depends on the application. For example, FIG. 1a-d, 4a, b, 5a, b are pneumohydraulic devices with a reducer, the most “dense” arrangement can be achieved in the variant of fig. 1b, 4b, 5b;

FIG. 2 - devices based on hot gas, for example, internal combustion engines, while the possibility of connecting the cylinder block to the connecting link through a gearbox similar to that shown (Fig. 4a, 5a) is not excluded;

FIG. 3 a, b - pneumohydraulic devices, while the possibility of connecting the cylinder block to the connecting link through a gearbox similar to that shown (Fig. 4a, 5a) is not excluded, and in the variant with a synchronizing rod (Fig. 3a) a reducer link, but with the direction of plane-parallel rotation opposite to the block of cylinders.

Sources of information [1] Auth. St. USSR № 1290004 Rotational Machine VI Golubeva. Publ. 02/15/87. Bul No. 6

[2] Kraynev A.F. Dictionary-reference mechanisms. 2nd ed., M., Mechanical Engineering, 1987 (p. 145).

Claims (17)

CLAIM 1. A rotative machine, made in the form of a housing and a movable block of at least two cylinders intersecting with their axes with pistons placed in them, while the cylinder block and pistons are installed with the possibility of a plane-parallel, on circles of equal radius, with equal angular speeds, synchronized and coordinated movement in mutually opposite directions for the block of cylinders and pistons by means of driving cranks of the block of cylinders and driving cranks of pistons or kinematically equivalent mentioning at the same time, the block of cylinders and pistons are kinematically connected to at least one connecting link, and the synchronization of the movement of the block of cylinders and pistons is performed by means of kinematically connecting synchronizing links, characterized in that the synchronizing links and their kinematic connections are made with the formation of translational and rotational kinematic pairs. 2. A rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are made in the form of synchronizing cranks of the block of cylinders and pistons connected by common axes of rotation with the corresponding driving cranks of the block of cylinders and pistons, and installed on the block of cylinders parallel to the axis of each cylinder of cylinder guides, interacting with piston sliders installed on each piston, and also in the form of at least one block of transverse guides, perpendicular cylinder's axis and cooperating with the transverse slides, the transverse guide block is pivotally connected to the synchronizing cranks the engine block and the transverse slides are pivotally connected to the synchronizing cranks pistons. 3. A rotary machine according to claim 2, characterized in that the synchronizing cranks of the pistons are directed opposite to the driving cranks of the pistons, and the synchronizing cranks of the cylinder block are directed to the same direction as the driving cranks of the cylinder block. 4. The rotary machine according to claim 3, characterized in that the eccentricities of the synchronizing and driving cranks are equal, the synchronizing cranks of the cylinder block are combined with the driving cranks of the cylinder block, and the transverse guide block is integrated with the cylinder block, while the transverse guides are made in the form of additional cylinders, and the transverse crawlers are made in the form of additional pistons fitted with thrones. 5. A rotary machine according to claim 2, characterized in that the synchronizing cranks of the pistons are directed in one direction with the driving cranks of the pistons, and the synchronizing cranks of the cylinder block are directed opposite to the driving cranks of the cylinder block. 6. The rotary machine according to claim 5, characterized in that it is provided with two blocks of transverse guides made in the form of blocks of additional transverse cylinders, and transverse sliders - in the form of additional transverse pistons equipped with threes, the blocks of additional cylinders are placed symmetrically on both sides of the block cylinders. 7. The rotary machine according to claim 6, characterized in that the product of the mass of blocks of additional transverse cylinders by the eccentricity of the synchronizing cranks is equal to the product of the mass of the cylinder block by the eccentricity of the driving cranks. 8. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are made in the form of synchronizing cranks of the block of cylinders and pistons connected by common axes of rotation with the corresponding driving cranks of the block of cylinders and pistons, all synchronizing cranks are directed under right angles to the cranks connected to them along or against the rotation of the cranks, as well as in the form of cylinders mounted on the cylinder block parallel to the axis of each cylinder cylinder guides, interacting with piston sliders installed on each piston, and also in the form of at least one block of longitudinal guides parallel to the axes of cylinders and interacting with longitudinal sliders, while the block of longitudinal guides is pivotally connected to the synchronizing cranks of the cylinder block, and the longitudinal sliders are hinged connected to the synchronizing piston cranks. 9. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are made in the form of common cranks installed along the central axis of rotation, combining the functions of the synchronizing cranks of the pistons and their drive cranks, and also in the form of cylinder guides interacting with piston ones sliders pivotally connected to common cranks, wherein the cylinder block is formed from at least two pairs of coaxial, opposite cylinders intersecting with their axes at right angles to the mentioned Utyh swivel. 10. A rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are made in the form of piston pistons connected in parallel and directed to one side and connected in common axes of rotation with corresponding piston driving cranks, as well as cylinder block parallel to the axis of each cylinder of cylinder guides, interacting with piston sliders installed on each piston, and also in the form of at least one synchronizing connecting rod, pivotally connected to the synchronizing piston cranks. 11. The rotative machine of claim 10, characterized in that it contains two synchronizing connecting rod, made in the form of flat rings, placed symmetrically on both sides of the cylinder block. 12. The rotary machine according to claim 1, characterized in that the synchronizing links and their kinematic connections are made in the form of synchronizing cranks of the block of cylinders and pistons connected along common axes of rotation with corresponding driving cranks of the block of cylinders and pistons, while the synchronizing cranks of the block of cylinders are the same or oppositely directed relative to the drive cranks of the cylinder block, and the synchronizing cranks of the pistons oppositely or equally directed relative to the drive crankshaft pistons, as well as cylinder rails mounted on the cylinder block parallel to the axis of each cylinder, interacting with piston sliders installed on each piston, as well as body rails mounted parallel to the axis of each cylinder, interacting with intermediate sliders, each equipped with placed transverse piston and transverse cylinder guides perpendicular to the axis of the cylinder, interacting, respectively, with the transverse piston slide and transverse cylinder slider, with the transverse piston sliders pivotally connected to the synchronizing piston cranks, and transverse cylinder sliders pivotally connected to the synchronizing cranks of the cylinder block. 13. Rotational machine according to claims 2 or 8, or 9, or 10, or 12, characterized in that the cylinder guides are formed by the walls of the cylinders, and the piston sliders are formed by the pistons. 14. Rotational machine according to claim 2, or 8, or 9, or 10, or 12, characterized in that the eccentricity of the synchronizing cranks exceeds the eccentricity of the driving cranks. 15. The rotary machine according to claim 1, characterized in that the connecting link is made as a central gear wheel installed in the housing with the possibility of rotation with external gearing, interacting with the intermediate gear wheel with internal gearing that is mounted on the cylinder block and interacting with the installed in the housing without the possibility of rotation with an external gearing, with the gear teeth with different gear ratios. 16. Rotational machine according to claims 1, 9, characterized in that the connecting link is made in the form of an eccentric shaft mounted in the housing with the possibility of rotation along the central axis, combining common cranks. 17. The rotative machine according to claim 1, characterized in that the connecting link is made in the form of a crankshaft mounted in a housing rotatably and hingedly connected to a cylinder block.