AXIAL-PISTON MACHINE

Abstract: In the casing (1) of the proposed axial-piston machine is located a cylinder block (2) with cavities (10). The axes of the cavities (10) are parallel to the longitudinal axis (O₁-O₁) of the shalt (11) and pistons (12) are mounted inside said cavities with the possibility of reciprocating movement. Each of the pistons (12) is hingedly connected to one end (14a) of a rod (14). The other end (14b) of the rod (14) is hingedly connected to a sloped washer (15) which is mounted by means of a first support (22) on a sloped neck (23) of the shaft (11) mounted on supports in the casing (1) and which is hingedly connected by means of universal couplings (34 and 35) to the casing (1). The machine is further provided with a second spherically shaped support (49) of the sloped washer (15). The support (49) is connected to the casing (1) and its centre (O₃) coincides essentially with the geometrical centre of a coupling element (47) of the universal couplings (34 and 35). Through the centre (O₃) passes a bisector plane (p-p) constituting the symmetry plane of the universal couplings (34 and 35).

Description: FIELD OF ART The present invention relates to piston machines and, more specifically, to an axial-piston machine. BACKGROUND OF THE INVENTION Nowadays the automotive industry is one of the most rapidly developing branches of industry so that engineers are constantly turning to nontraditional layouts of engines, in particular to piston engines with axially-arranged cylinders. The advantages of axial arrangement of cylinders in I.C. piston engines manifested by their smaller weight and dimensions are widely known. As compared with traditional piston engines incorporating a crank gear for converting the reciprocating motion of pistons into rotary motion of the crankshaft the size and weight of automotive axial-piston engines are reduced 1.5 - 2 times and the aerodynamic resistance of the motor vehicle is reduced due a smaller space occupied by the engine under the engine hood. Modern requirements for reduction of the amount of cancerogenic substances exhausted by I.C. engines of transport facilities and for diminishing the consumption of nonreproducible supplies of fuel force machine builders to turn to the axial-piston engines with a variable cylinder volume. Under strenous conditions of city traffic the service consumption of fuel is reduced 30-40% with a proportionate reduction of the amount of cancerogenic substances in the engine exhaust. Thus, the axial-cylinder engine has marked a new era in the development of I.C. piston engines. However, up till now the attempts at devising a reliable design of the axial-piston engine have failed due to alternating fatigue stresses originated in the parts of the mechanism which converts the reciprocating motion of cylinder piston into rotary motion of the shaft. Attempts to ensure the reliable performance of the axial-piston engine brought to life an axial-piston machine (Application R/3420529 A₁). The frame of the known machine accommodates a cylinder block with cylindrical spaces whose axes are parallel with the longitudinal axis of the shaft. Reciprocating in said spaces are pistons, each articulated to one end of the rod whose other end is articulated to a swash plate. The articulated joint of the other end of the rod with the swash plate consists of a first cylindrical pin passing through the lugs of the yoke constituted by the other end of the rod and through an intermediate member, and a second cylindrical pin whose axis is perpendicular to the axis of the first pin, passing through the intermediate member and the lugs in the swash plate. The swash plate is installed, via a support, on the inclined crank of the shaft which latter is located on supports in the engine frame. The swash plate is connected by a universal joint with the frame. The support of the swash plate on the inclined crank of the shaft is spherical which provides for swinging of the plate while the reciprocating motion of pistons is converted into the rotary motion of the shaft. The universal joint yoke is located in the cylinder block with a provision for longitudinal motion, viz., along the longitudinal axis of the shaft. The movement of the yoke entails the movement of the spherical support over the inclined shaft journal and a reduction of the swash plate angle which brings about a reduction of the swept volume of engine cylinders. The use of one universal joint fails to ensure uniform precession of the swash plate due to changes in its angular velocity which take place twice per crank-shaft revolution in the plane perpendicular to the longitudinal axis of the swash plate. This produces a strong inertia moment of the mass of the swash plate and parts associated therewith, said moment resulting in rapid fatigue failure of the universal joint. The use of the universal joint as one of the swash plate supports impairs still further its reliability due to heavy alternating loads imposed by the swash plate on the joint. The provision of one spherical support of the swash plate results in this case in that the reaction forces originated on the swash plate and transmitted from it to the frame via the shaft and universal joint are destructive to the shaft due to strong bending moments applied to it and destructive to the universal joint due to alternating dynamic loads. The universal joint in the known design of the axial-piston engine is rather large because it performs the function of one of swash plate supports and this hinders the development of the spherical surface of the support resting on the inclined journal of the shaft. Said support takes the strongest forces arising in the engine while converting the reciprocating motion of the pistons into the rotary motion of the shaft and, in view of the limited dimensions of the spherical surface of the support, its serviceability is low due its limited durability. Next, the inclination angle of the longitudinal axis of the swash plate to the longitudinal axis of the crankshaft is 40°. This causes wide-amplitude angular oscillations or the swash plate relative to its axis which produces heavy inertia loads resulting in engine failure. It follows from the above that the known machine is one of the attempts to create an axial piston engine unrealized because of the above-cited disadvantages. An attempt to eliminate the angular oscillations of the swash plate relative to its longitudinal axis was materialized in an axial-piston machine covered by the patent US, A, 2424660 which is considered as the closest prior art. The frame of this machine houses a cylinder block with spaces whose axes are parallel to the longitudinal axis of the shaft and which accommodate reciprocating pistons. Each piston is articulated with one end of the rod whose other end is articulated with the swash plate. The latter is installed via a support on the inclined journal of the shaft mounted on supports in the frame. The swash plate is connected by two universal joints with the frame. The swash plate support is an angular ball bearing whose inner race is connected rigidly with the inclined shaft journal while the outer race is secured on the swash plate. This shows that there is only one support which carries all loads imposed by the swash plate. Such a single-support fastening of the swash plate on the inclined shaft journal keeps the swash plate from moving along the inclined journal and from changing its angle of inclination. Thus, it proves impossible to develop a machine with a variable swept volume of its cylinders. In spite of the fact that the above-mentioned function of the machine is not attained, the connection of the swash plate with the frame via two universal joints improves considerably the performance of the machine since there are no angular oscillations of the swash plate along its longitudinal axis which, in turn, dispenses with the destructive inertia loads caused by such oscillations. Each universal joint consists of a ring with four pins which are arranged in one plane and have relatively perpendicular axes. Two coaxial pins of one universal joint are articulated with the swash plate while the other two pins of this joint are articulated with the intermediate member in the form of a ring. The latter is articulated with the coaxial pins of the other universal joint. The relatively-perpendicular pins are articulated with the lugs of a hollow part secured in the engine frame. Inasmuch as the known design has no fixed position of the bisector plane passing through the point of intersection of the longitudinal axes of the shaft and swash plate and dividing in two the angle formed by the planes each of which passes through the relatively-perpendicular axes of the universal joint pins, the service life of the unviersal joints is reduced considerably by virtue of additional unbalanced loads arising therein. DISCLOSURE OF THE INVENTION The main object of the invention is to provide an axial-piston machine wherein the design of the swash plate and the fixing of the position of the bisector plane of two universal joints relative to the centre of oscillations of the swash plate would improve its serviceability, extend operating life and broaden its operating capabilities. This object is achieved by providing an axial-piston machine whose frame accommodates a cylinder block with cylindrical spaces whose axes are parallel with the longitudinal axis of the shaft and which contain reciprocating pistons, each linked kinematically with a swash plate installed via a first support on the inclined journal of the shaft located on the frame supports and articulated with a first universal joint which is articulated to a connecting member which is articulated with a second universal joint the latter being articulated with the frame wherein according to the invention,there is a second support of the swash plate, interacting with said plate, connected with the frame and having a spherical shape with its centre serving in fact as the centre relative to which the angular motion of each universal joint occurs and passing through which is a bisector plane which is the plane of symmetry of universal joints and on which lies the centre of the connecting member of the universal joints. Such a design of the axial piston machine improves its reliability and serviceability due to the distribution of the load imposed on the swash plate between its supports the first of which transmits the active moment from the swash plate to the shaft while the second one transmits the reaction torque to the machine frame. Next, the alignment of the geometrical centre of the second support with the centre around which the two universal joints move angularly and through which passes the bisector plance of two universal joints reduces considerably the dynamic load originated in the ball joint of the swash plate with the second support. It should be noted that there is no relative axial movement of links in the universal joints which eliminates axial loads on the machine frame and promotes its reliability and performance. In the machines of a comparatively low power characterized by a comparatively light load imposed on the crankshaft it is good practice to locate the second support of the swash plate in the zone between two planes, each passing through two axes of the corresponding universal joint. In this case both universal joints encompass the second support. Such location of the second support makes it commensurable in size with the first support which carries the bulk of the load of the swash plate. Application of the reactive load of the swash plate to the second support makes said plate more reliable which in the long run ensures high reliability and performance of the machine as a whole. In the case of a machine with a variable swept volume of cylinders, it is necessary that the axis of the inclined shaft journal should form an acute angle with the longitudinal axis of the swash plate, the range of said angle varying from 10° to 32° on changes in the swept volume of the cylinders. Such a design ensures up to three changes of swept volume, these changes being quite smooth. Then, at such a degree of swept volume change each cylinder can work either at a constant compression ratio or obey a preset law of compression ratio changes. If the angle between the axis of the shaft inclined journal and the axis of the swash plate is smaller than 10° it becomes impossible to maintain a constant compression ratio and, moreover, to vary it within the limits in which it is greater at the minimum swept volume of the cylinders. If this angle is larger than 32° the bearing areas of the spherical surface of the first support will be sharply reduced and the crankshaft will be subjected to considerable axial loads. For machines with a high torque transmitted by the crankshaft it is recommended that the second support should embrace both universal joints. The distance between cylinder axes in these machines is increased which has increased the swash plate diameter and, as a consequence, has made it possible to increase considerably the size of the second swash plate support. The increased size of the second support reduces the specific pressures in it by increasing its surfaces of interaction. Arrangement of two universal joints inside the second support reduces the diameter of the connecting member and the radium of universal joints so that the latter may be have a lighter weight. This reduces the dynamic load originated due to irregular movement of the connecting member thereby stepping up the reliability and serviceability of the machine. It is recommended that the second support be installed with a provision for moving along the shaft axis and that the first support of the swash plate should be provided with a spherical outer surface interacting with the congruent spherical surface of the swash plate and with the inner cylindrical surface which interacts with the cylindrical surface of the inclined shaft journal. Such a design of the machine ensures changes in the cylinder volume to suit the load characteristic of said machine. This is caused by the fact that the movement of the second support along the shaft axis causes the movement of the first support over the inclined shaft journal which will result in angular turning of the swash plate with relation to the geometrical centre of the second support due to interaction between the spherical surfaces of the second support and the swash plate. The spherical shape of the second support and the outer spherical surface of the first support ensures comparatively small forces required for moving the second support. Variations in the cylinder volume of the machine broaden its service capabilities. All the above considerations confirm the simplicity of the design of the mechanism for changing the swept volume of the machine cylinders and the possibility of developing axial-piston engines with the swept volume of cylinders varying in operation, having light weight and small size while ensuring efficient conversion of the energy produced by combustion of the air-fuel mixture into mechanical energy taken off the engine shaft. BRIEF DESCRIPTION OF THE DRAWINGS Other objects and advantages of the invention will be elucidated by the following examples of its realization with reference to the accompanying drawings in which: Fig. 1 is a schematic longitudinal section of the axial-piston engine according to the invention; Fig. 2 is a universal joint unit, enlarged; Fig. 3 is a longitudinal section of the axial-piston engine with a variable swept volume of cylinders according to the invention; Fig. 4 is a longitudinal section through the axial-piston engine with a variable swept volume of cylinders and a hydraulic drive for moving the swash plate according to the invention; Fig. 5 is another embodiment of the axial-piston engine according to the invention, longitudinal section; Fig. 6 illustrates the first and second supports of the swash plate and the universal joints turned through 90° in the plane perpendicular to the longitudinal axis of the shaft according to the invention, enlarged, longitudinal section; Fig. 7 illustrates an embodiment of the axial-piston engine with a variable swept volume of cylinders according to the invention, longitudinal section; Fig. 8 illustrates an embodiment of the axial piston engine with the cylinder pistons and swash plate in the position corresponding to the minimum swept volume of cylinders according to the invention, longitudinal section; Fig. 9 illustrates the first and second supports of the swash plate and the universal joints turned through 90° in the plane perpendicular to the longitudinal axis of the shaft in the position corresponding to the minimum swept volume of engine cylinders according to the invention, enlarged, longitudinal section; Fig. 10 is an embodiment of the axial piston engine with the cylinder pistons and swash plate in the position corresponding to the maximum swept volume of engine cylinders according to the invention, longitudinal section. BEST MODES OF CARRYING OUT THE INVENTION The axial piston machine realized in accordance with the present invention and embodied in a 5-cylinder I.C. engine comprises a frame 1 (Fig. 1) incorporating a cylinder block 2 and crankcase 3, interconnected by fastening elements (not shown). The oil pan 4 is attached to the cylinder block 2 and crankcase 3. The cover 5 is secured by bolts 6 to the cylinder block 2. Oil leaks are prevented by gasket 7 installed between the cylinder block 2 and crankcase 3, gasket 8 between the cylinder block 2 and the oil pan 4, and gasket 9 between the cylinder block 2 and the cover 5. The cylinder block has cylindrical spaces 10. The axes O₂-O₂ of said cylindrical spaces 10 are parallel with the longitudinal axis O₁-O₁ of the engine shaft 11. Accommodated in the cylindrical spaces 10 with a provision for reciprocating motion are pistons 12. Each piston 12 is connected by a kinematic linkage 13 with one end 14a of the rod 14 whose other end 14b is articulated with the swash plate 15. The kinematic linkage 13 is made up of a liner 16 with a spherical surface interacting with the spherical surface 14a of the rod 14. For holding the rod 14,the piston 12 is provided with a liner 17 whose axial motion relative to the piston 12 is limited by a threaded bushing 18 screwed into the piston 12. The articulated joint between the end 14b of the rod 14 and the swach plate 15 has the form of a ball head accommodated in a cylindrical socket 19 of the swash plate 15, the number of said sockets 19 being equal to the number of engine cylinders. Located in each socket 19 is a liner 20 with a spherical surface which interacts with the surface of the ball head of the rod 14, and a thereaded bushing 21 holding the rod 14. The swash plate 15 is mounted, via the first support 22, on the inclined journal 23 of the shaft 11. One end of the shaft 11 is connected to the hub 24 of the pulley 25 by a key 26. The hub 24 is installed in a tworow angular rolling-contact bearing 27 accommodated in the cover 5 and intended to prevent axial displacement of the shaft 11. The hub 24 is secured on the latter with a bolt 28. The other end of the shaft 11 is installed in a rolling contact bearing 29 accommodated in the flange 3a of the crankcase 3. The outer race 29a of the bearing 29 is secured in the flange 3a by the cover 30 connected with the flange 3a by a screw joint 31. A cup 32 in the cover 30 prevents oil leaks from the crankcase 3. Sagging of the shaft 11 is reduced by the provision of an intermediate sliding-contact support 33. To prevent the swash plate 15 from turning relative to its axis, there is a kinematic linkage with the frame 1 in the form of universal joints 34 and 35. The universal joint 34 is formed by pins 36 made integral with the hub 37 rigidly cconnected with the swash plate 15 and by pins 38 (Fig. 2) located on the ring 39 mounted via needle bearings 40 on pins 36 (Fig. 1). The axes of pins 36 and 38 (Fig. 2) are relatively perpendicular in one plane. The universal joint 35 is formed by pins 41 made integral with the bushing 42 connected by splines with the frame 1. (Fig. 1) and by pins 43 (Fig. 2) made on the ring 44 which is installed on the pins 41 via needle bearings 45. The axes of pins 41 and 43 are relatively perpendicular in one plane. The pins 43 are connected by needle bearings 46 with the connecting member 47 in the form of a ring in which needle bearings 48 are mounted on pins 38. The axes of pins 36 and 41 lie in a single plane while the axes of pins 38 and 43 lie in a mutually perpendicular plane. The swash plate 15 (Fig. 1) has a second support 49 of a spherical shape. Said support 49 of the swash plate 15 is located between two planes: plane n-n passing through the axes of pins 36 and 38 (Fig. 2) i.e. through the axial plane of the joint 34, and plane m-m passing through the axes of pins 41 and 43, i.e. through the axial plane of the joint 35. Said support 49 (Fig. 1) has a ball head 50 and a cylindrical body 51 installed in the cylinder block 2 of the frame 1. The cylindrical body 51 of the support 49 at the side opposite to the ball head 50 is connected with the cylinder block 2 of the frame 1 by a screw joint 52 formed by the nut 53 screwed on the threaded end of the cylindrical body 51. To prevent changes in the position of the second support 49 relative to the cylinder block 2 of the frame 1, the tapered surface of the nut 53 is pressed against the corresponding surface on the cylinder block 2. The nut 53 is kept against working loose by a locknut 54. Located between the hub 37 and the ball head 50 is the first liner 55 and the second liner 56 each having a spherical surface interacting with the ball head 50. The centre O₃ of the ball head 50 of the support 49 coincides with the centre of the radius of curvature of the spherical surfaces of the first and second liners 55, 56, respectively, and is, essentially, aligned with the geometric centre of the connecting member 47. The bisector plane p-p which is the plane of symmetry of the universal joints 34 and 35 passes through the centre of the connecting member 47, i.e. through the centre O₃. The first support 22 is a bushing with a spherical external surface 22a and an internal cylindrical surface 22b encompassing the cylindrical surface 23a of the journal 23 of the shaft 11. The third liner 57 located between the hub 37 and the support 22 has an internal spherical surface interacting with the spherical surface 22a of the support 22 which interacts with the spherical surface of the second liner 56. The first, second and third liners 55, 56 and 57 are held against falling out of the hub 37 by a lockring 58. Location of supports 22 and 49 inside the hub 37 makes them commensurable. Inasmuch as the first support 22 takes the bulk of the load of the swash plate 15, i.e. the reaction and active loads while the second support 49 only a part of the reaction load, this steps up the reliability of the engine. The channels delivering lubricant to the above-specified articulated joints are not shown in Fig.1 in order not to encumber the drawing with excessive numbers that hamper the clear understanding of the disclosed technical solution. The cooling space 59 in the cylinder block 2 communicates with the space 60 in the head of the cylinder block 2 and with the space 61 of the cooling branch pipe 62 secured on the cylinder block 2 with fastening elements 63. The cylinder head incorporates spark plugs 64, one for each cylinder, and reciprocating inlet valve 65 and exhaust valve (not shown in the figure). Secured with bolts 66 on the shaft 11 in the zone of the flange 3a is a flywheel 67 with a ring gear 68 intended for meshing with the engine starting device (not shown in the drawing). The axial piston machine functions in the engine mode as follows. The toothed member of the starting device (not shown in Fig. 1) comes in mesh with the ring gear 68 of the flywheel 67 and rotates it. The flywheel 67 rotates the shaft 11. As the inclined journal 23 of the shaft 11 starts rotating, its motion is transmitted via the support 22 to the swash plate 15. Acting via the pins 36 and needle bearings 40, the hub 37 of the moving swash plate 15 causes angular motion of the ring 39 of the universal joint 34 around the axes of the pins 36. The movement of the ring 39 transmitted by the pins 38 (Fig. 2) and needle bearings 48 causes swinging of the ringshaped connecting member 47. The movement of the connecting member 47 acting via the pins 43 and needle bearings 46 causes angular motion of the ring 44 around the axes of the pins 41 (Fig. 1) due to a splined joint of the bushing 42 with the frame 1. Owing to the symmetry of the universal joints 34 and 35 the ring 39 turns around the axes of pins 36 through the angle equal to that of the ring 44 turning around the axes of the pins 41. Turning of the pins 36 and hub 37 caused by rotation of the inclined journal 23 of the shaft 11 puts in motion the swash plate 15. In the course of this motion the spherical surface of the liner 20 interacts with the spherical surface of the end 14b of the rod 14 and pulls said the latter to the right (in the drawing). The other end 14a of the rod 14 interacts by its spherical surface with the spherical surface of the liner 17. Said spherical surface interacts with the spherical surface of the threaded bushing 18 which transmits the force to the piston 12. The fuelair mixture enters through the open inlet valve 65 into the space 10 of the cylinder wherein the piston 12 moves to the right (in the drawings). As soon as the shaft 11 has turned through 180° the swash plate 15 starts moving towards the head of the cylinder block 2 of the frame 1 in the plane passing through the axes of the cylindrical space of the machine. During its movement the other spherical surface of the liner 20 interacts with the other spherical surface of the end 14b of the rod 14 and pushes the latter to the left (in the drawing). The spherical surface of the other end 14a of the rod 14 interacts with the spherical surface of the liner 16. Said liner 16 transmits the force to the piston 12. The intake valve 65 is closed. Under the force transmitted by the liner 16 to the piston 12 the latter moves in this cylinder to the left (in the drawing) and compresses the fuel-air mixture. In the TDC zone the fuel-air mixture is ignited by the spark plug 64. The volume of burning gases increases during combistion of mixture thus increasing the pressure of gases acting, in particular, on the surface of the piston 12 directed to the spark plug 64. The force built up by the pressure of hot gases moves the piston 12 to the right (in the drawing). The progressive motion of the piston 12 causes a compound motion of the swash plate 15 which converts it into the rotary motion of the shaft 11. The compound motion of the swash plate 15 is ensured by turning of the ring 44 relative to the axes of the pins 41, by swinging of the connecting member 47 and turning of the ring 39 relative to the axes of the pins 36. This compound motion of the swash plate 15 originates a reactive moment. The torque component of the reactive moment lying in the plane perpendicular to the axis of the shaft 11 is transmitted from the frame 1 via the splined joint of the frame 1 with the bushing 42, pins 41 of the bushing 42, ring 44, pins 43 of the ring 44, connecting member 47, pins 38 of the ring 39 and pins 36 to the swash plate 15. The other component of the reactive moment lying in the plane passing through the axis of the shaft 11 and being, essentially, a bending moment, is transmitted from the frame 1 to the swash plate 15 via the tapered surface of the nut 53 and the cylindrical surface of the sliding support 33, ball head 50, first 55 and second 56 liners and the hub 37. The spherical shape of the second support 49 of the slash plate 15 said support being connected with the frame 1, and the coincidence of its centre O₃ with the geometrical centre of the connecting member 47 through which passes the bisector plane p-p, i.e. the plane of symmetry of the universal joints 34 and 35 improve the reliability and serviceability of the machine since said coincidence of centres resolves the reactive moment into two components, i.e. the torque transmitted to the frame 1 through universal joints 34 and 35, and the bending moment transmitted through the ball support 49. Then the piston 12 moves to the left (in the drawing) and the exhaust gases are discharged through the open exhaust valve (not shown in the drawing). On completion of the exhaust stroke the working cycle is repeated over again. In a five-cylinder axial-piston engine according to the invention, with a summary cylinder volume of 2.7 l and a maximum torque of 220 Nm on the crankshaft, the load on the first support is approximately 4.0 t and about 4.0 t on the second support. Said axial-piston engine was run on the stand for 300 h without breakdowns. With a view to reducing the fuel consumption there is a version of the axial-piston engine according to the invention incorporating a technical solution which broadens its operational capabilities. In this version of the engine the change in its load curve is accompanied by changes in the swept volume of the cylinders. For this purpose the second support 49 is provided with a means 69 (Fig. 3) for moving it along the axis O₁-O₁ of the shaft 11a. The axis O₄-O₄ of the inclined journal 23a of the shaft 11a forms an acute angle, e.g. 12°, with the longitudinal axis O₅-O₅ of the swash plate 15 at the maximum volume of cylinders and 28° at the minimum volume of cylinders. The provision of this angle between the axes O₄-O₄ and O₅-O₅ ensures changes in the inclination angle of the longitudinal axis O₅-O₅ of the swash plate 15 to the longitudinal axis O₁-O₁ of the shaft 11a and maintains the compression ratio within the preset limits either constant or varying in accordance with the preset law, e.g. from ε = 10 at a minium cylinder volume and ε = 9 at a maximum cylinder volume. The cylindrical body 51a at the side opposite to the ball head 50a is connected by a spline joint with the threaded bushing 70. To prevent axial displacement of the threaded bushing 70 along the cylindrical body 51a, there is a nut 71 screwed on the threaded end of the cylindrical body 51a. In the zone of the head 50a the cylindrical body 51a has a key 72 fitting into the keyway of the cylindrical bushing 73. Said bushing 73 has splines 74 for connection with the bushing 42a and splines 75 which engage the splines 76 of the bushing 77. The cylindrical bushing 73 is installed in the cylinder block 2 of the frame 1 and is kept against shifting along the cylindrical body 51a by nuts 78. The bushing 77 installed in the cylinder block 2 of the frame 1 embraces the cylindrical body 51a, is connected by a splined joint with the frame 1 and has a circular shoulder 79 intended to limit the longitudinal displacement of the bushing 77 relative to the cylinder block 2 of the frame 1. The means 69 for moving the second support 49 is made up of a worm wheel 80 and worm 81 installed in the cylinder block 2 of the frame 1 and meshing with each other. The internal surface of the wheel 80 has a thread 82 engaging the thread of the bushing 70. As the load on the axial-piston engine changes, for example when the transport vehicle is slowed down, the rotation of the worm 81 puts in rotation the worm wheel 80. Turning of the worm wheel 80 moves the threaded bushing 70 to the left towards the head of the cylinder block 2. Movement of the threaded bushing 70 displaces the cylindrical body 51a of the second support 49, i.e. the second support 49 proper. The spherical surface of the moving second support 49 interacts with the spherical surface of the liner 55 which, in turn, interacts with the hub 37 of the swash plate 15. The latter moves and so does its first support along the inclined journal 23a of the shaft 11a towards its axis O₁-O₁ which reduces the angle between the axis O₅-O₅ of the swash plate 15 and the axis O₁-O₁ of the shaft 11a. The movement of the swash plate 15 causes the pistons 12 to move toward the head of the cylinder block 2 of the frame 1 so that the distance from the face surface of each piston 12 to the head of the cylinder block 2 of the frame 1, the stroke of pistons 12, and the swept volume of the cylinders of the axial-piston engine are reduced. A shorter stroke of the pistons 12 reduces the mechanical losses and the losses for suction of fuelair mixture and for exhausting the burnt gases from the cylinder which enhances the engine efficiency. A certain increase in the compression ratio caused by the reduction of the distance from the end face of each piston 12 to the head of the cylinder block 2 improves combustion of the fuel-air mixture which raises the engine efficiency. As the transport vehicle powered by the disclosed axial piston engine gains speed, the worm 81 rotating in the opposite direction puts in rotation the worm wheel 80. Rotation of said wheel 80 moves the bushing 70 away from the head of the cylinder block 2 unit the end of the bushing 70 comes to bear against the end face of the bushing 77. In the course of movement of the bushing 70 the cylindrical body 51a of the support 49 moves to the right (in the drawing) and its ball head 50a interacts with the spherical surface of the liner 56. The second spherical surface of the liner 56 interacts with the spherical surface 22a of the support 22 which, interacting by its cylindrical surface 22b with the cylindrical surface of the inclined journal 23 of the shaft 11a, transmits the force to the hub 37 via the liner 57 and lockring 58. This force moves the swash plate 15 away from the cylinder block 2 which increases the angle between the axis O₅-O₅ of the swash plate 15 and the axis O₁-O₁ of the shaft 11a. The movement of the swash plate 15 is accompanied by the movement of the pistons 12 away from the head of the cylinder block 2, thereby increasing the distance from the end face of each piston 12 to the head of the cylinder block 2 of the frame 1, the stroke of the pistons 12 and the swept volume of the cylindrs of the axia-piston engine. While the swash plate 15 is moving, it turns relative to the centre of the spherical surface O₆ of the first support 22 which is accompanied by the turning of the swash plate 15 relative to the geometrical centre O₃ of the second support 49. Thanks of the spherical shape of the second support 49 and the external spherical surface 22a of she first support 22, the forces required for moving the second support 49 are small. The introduction of the worm pair 80, 81 in the capacity of one of the element of the means 69 for moving the second support 49 ensures the self-braking effect which allows the swash plate 15 to be fixed in any one of its intermediate positions. In another embodiment of the I.C. engine, the changes in its load curve accompanied by the changed in the cylinder volume are ensured by a means 83 (Fig. 4) for moving the second support 49 along the axis of the shaft 11a. Said means 83 has the form of a piston 84 installed in the cylinder block 2 of the frame 1, secured by a nut 85 on the end of the cylindrical body 51b facing the head of the cylinder block 2 and provided with sealing rings 86. The cylindrical bushing 73 is made in a similar way while the bushing 77a has sealing rings 87 and a circular space 88 communicating through the line 89 with the source of a liquid delivered under pressure (not shown in the drawing). As the load on the axial-piston engine changes, for instance when the transport vehicle is slowed down, the liquid is delivered under pressure through the line 89 into the space 88. The force developed the liquid pressure moves the piston 84 and the second support 49 connected therewith towards the head of the cylinder block 2. Changes in the position of the swash plate 15 and the corresponding changes in the volume of cylinders proceed similarly to those described above. As the transport vehicle is accelerated, the space 88 is put in communication with the discharge line. The force developed by the pressure of hot gases acting on the end face of each piston 12 moves the corresponding piston 12 which acts on the swash plate 15 via the above-described kinematic linkage. The position of its second support 49 is changed similarly to the process described above and causes the piston 84 to move away from the head of the cylinder block 2. Irrespective of the design of the mechanism for moving the second support 49 the operating capabilities of the axial-piston machine are broadened. With relation to the axial-piston machine of 2.7 l volume the consumption of fuel under city traffic conditions is reduced by 30-35%. The use of liquid under pressure for moving the second support 49 allows the cylinder volume to be adjusted without participation of the driver. The axial-piston machine realized in accordance with the invention and embodied in a 7-cylinder I.C. engine comprises a frame 1c (Fig. 5) incorporating a cylinder block 2c and a crankcase 3c held together by fastening elements (not shown in the drawing). An oil pan 4c is secured to the cylinder block 2c and crankcase 3c. Secured to the cylinder block 2c with bolts 6c is the cylinder head 5c. To prevent oil leaks there are gaskets: gasket 7c between the cylinder block 2c and crankcase 3c, gasket 8c between the cylinder block 2c and the oil pan 4c, and gasket 9c between the cylinder block 2 and the head 5c. The cylinder block 2c has cylindrical spaces 10c whose axes O₈-O₈ are parallel to the longitudinal axis O₇-O₇ of the engine shaft 11c. Piston 12c reciprocate in the cylindrical spaces 10c provided with cylinder sleeves 90. Each piston 12c is connected by articularted linkage 13c with one end of the rod 14c whose other end is articulated to the swash plate 15. The articulated linkage 13c is formed by a liner 16c with a spherical surface interacting with the spherical surface of the rod 14c. For holding the rod 14c in the piston 12c, there is a liner 17c whose axial movement relative to the piston 12c is limited by a threaded bushing 18c connected with the piston 12c by a screw joint. Besides, the articulated linkage 13c incorporates an articulated joint of the other end of the rod 14c with the swash plate 15c in the form of a support with spherical surfaces, said support being lcoated in a cylindrical socket 19c made in the swash plate 15c, the total number of such sockets 19 being seven. Each socket 19c accommodates a ball -type thrust bearing 91. The spherical surface of the ball-type thrust bearing 91 is mated with the corresponding spherical surface of the support of the other end of the rod 14c. Each socket 19c accommodates a liner 20c with a spherical surface interacting with the spherical surface of the support of the other end of the rod 14c, and a threaded bushing 21c holding the rod 14c in the swash plate 15c. The swash plate 15c is installed via the first support 92 on the inclined journal 23c of the shaft 11c. One end of the shaft 11c is connected with the hub 24c of the pulley 25c by the key 26c. The hub 24c is installed in the two-row angular rolling-contact bearing 27c located in the head 5c and preventing the axial displacement of the shaft 11c. To prevent axial displacement, the hub 24c is secured on said shaft 11c by a bolt (not shown in the drawing). The other end of the shaft 11c is installed in the rolling-contact bearing 29c located in the flange of the crankcase 3c. The outer race of the bearing 29c is secured in the flange of the crankcase 3c by a cover 30c connected by a screw joint 31c with the flange of the crankcase 3c. The cup 32c in the cover 30c prevents oil leaks from the crankcase 3c. Probable sagging of the shaft 11c is averted by an intermediate sliding support 33c. Turning of the swash plate 15c about its axis is prevented by its kinematic linkage with the frame 1c, said linkage being constituted by universal joints 34c and 35c (Fig. 6). The universal joint 34c consists of pins 36c secured in the hub 37c of the swash plate 15c and of pins 38c made on the ring 39c which is installed with the aid of needle bearings 40c on pins 36c. The axes of the pins 36c and 38c are relatively perpendicular in a single plane. The universal joint 35c is formed by the pins 41c made integral with the bushing 42c, and by the pins 43c located on the ring 44c which is installed with the aid of needle bearings on the pins 41c. The axes of the pins 41c and 43c are relatively perpendicular in a single plane. The pins 43c are connected by needle bearings 46c with the connecting member 47c in the form of a ring accommodating needle bearings 48c located on the pins 38c. The axes of pins 36c and 41c lie in the same plane while the axes of the pins 38c and 43c lie in the relatively perpendicular plane. The swash palte 15 has a second spherical support 93 of a spherical shape. Said support 93 has a hollow ball head 94 and a cylindrical body 95 accommodated in the holder 96 connected with the cylinder block 2c of the frame 1c. The cylindrical body 95 of the support 93 at the side opposite to the hoillow ball head 94 is connected with the holder 96 by a bushing 97 (Fig. 5) with flange 98 and by a threaded bushing 99 connected by a screw joint with the threaded end of the cylindrical body 95. To ward off the axial displacement of the bushing 97 and holder 96, the bushing 97 is secured on the holder 96 with the aid of fastening elements (not shown in the figure). In order to prevent changes in the position of the second support 93 relative to the cylinder block 2c of the frame 1c, the tapered surface of the threaded bushing 99 is pressed against the corresponding surface on the bushing 97. The cylindrical body 95 is connected by a spline joint with the holder 96 and installed on the bushing 100 which embraces the support 33c of the shaft 11c and is arranged concentrically with the body 95. The relative axial displacement of the bushing 100 and cylindrical body 95 is prevented by a pin 101. Installed between the hub 37c and the hollow ball head 94 are liners 102 with a spherical surface 102a interacting with the outer spherical surface 94 a of the hollow ball head 94. The centre O₉ of the outer spherical surface of the hollow ball head 94 of the second support 93 coincides with the centre of the radius of curvature of the spehrical surface of liners 102 and virtually coincides with the geomatrical centre O₁₀ of the connecting member 47c. The bisector surface p-p passing through the centre of the connecting member 47c, i.e. through the centre O₁₀ is the plane of symmetry of the universal joints 34c and 35c. The first support 92 is, essentially, a bushing with an outer spherical surface 92a and an inner cylindrical surface 92b which embraces the cylindrical surface of the journal 23c of the shaft 11c. Located between the journal 23c of the shaft 11c and the inner cylindrical surface 92b is a bushing 103. The support 92 is provided with a key 104 and a lockring 105. The liners 106 and 107 located between the hub 37c and the support 92 have spherical surfaces interacting with the spherical surface 92a of the support 92. The liners 106 and 107 are held against falling out of the hub 37c by a lockring 108. The seven-cylinder axial-piston I.C. engine functions similarly to the above-described process. This engine develops a high torque which imposes a heavy load on its second support 93. The bending moment caused by this load and taken by the external spherical surface 94a of the head 94 of the second support 93 is transmitted to the cylinder block 2c of the frame 1 via the holder 96. The force of the swash plate 15c is transmitted to the inclined journal 23c of the shaft 11 via the bushing 103. Due to a comparatively large meridional size of the hollow ball head 94, the universal joints 34c and 35c are accommodated in its space which diminishes the diametrical dimension of the connecting member 47c and their radial dimensions and, consequently, their mass. A reduction of the dynamic load caused by the uneven motion of the connecting member 47c has enhanced the reliability and serviceability of the axial-piston I.C. engine. For changing the load curve of the seven-cylinder I.C. engine, there is a means 109 (Fig. 7) for moving the second support 93. This means 109 is similar to that described above. The difference lies in that the external surface of the flange 98a of the bushing 97c has a thread 110 meshing with the threaded portion 82c of the worm wheel 80c meshing meshing with the worm 81c. The seven-cylinder axial-piston engine operates in those modes similarly to the modes described above. Rotating, the worm 81c transmits rotation to the worm wheel 80c which shifts the bushing 97c. This shifting of the bushing 97c moves the threaded bushing 99 and the cylindrical body 95. The movement of the cylindrical body 95 sets in motion the hollow ball head 94 of the second support 93. Its external spherical surface 92a interacting with the spherical surface of the corresponding liner 102 sets in motion the swash plate 15c. The movement of the swash plate 15c sets in motion the bushing 103 of the first support 92 along the axis of the inclined journal 23c of the shaft 11c and the spherical surface of the liner 107 interacts with the spherical surface 92a of the second support 93. Changes in the postion of the longitudinal axis of the swash plate 15c and of the axes of universal joints 34c and 35c relative to the longitudinal axis of the shaft 11c and the resultant changes in the position of the longitudinal axis of the swash plate 15c relative to the axis of the inclined journal 23c of the shaft 11c proceed similarly to those described above. In another embodiment of the I.C. engine there is a means 111 (Fig. 8) for moving the second support 93. Said means 111 is realized similarly to that described above. The difference lies in that the flange 98b of the bushing 97c functions in the capacity of a piston. The surface of the piston facing the holder 96 and its end face define the space 112 connected by a hydraulic line 113 with a source of liquid under pressure (not shown in the drawings). As the liquid is delivered from the pressure source through the hydraulic line 113 into the space 112, the piston in the form of a flange 98b and the threaded bushing 99 start moving thus setting in motion the cylindrical body 95. The pistons 12c will occupy a position corresponding to say, a compression ratio ε = 10 at a minimum value of the swept volume of the cylinders 114. The subsequent processes are similar to those described above. The disclosed design of the second support 49 (Fig. 9) makes it possible to counterpose two ducts 115, the longitudinal section of each of said ducts lying in the plane turned through 90° relative to the plane of the drawing of the engine illustrated in Fig. 8. Said ducts 115 are intended to deliver lubricant to the friction surfaces of the second support 49. As the liquid is discharged from the space 112 (Fig. 10), the force developed by the pressure of gases and applied to the faces of the pistons 12c puts in motion the first 22 and second 49 supports as described above. As a result, the supports 22 and 49 will come to a position corresponding to the maximum swept volume of the cylinders 114. From now on the engine functions as has been laid down above. The five-cylinder axial-piston engine realized according to the present invention, with a total cylinder volume of 2.7 l, developing a maximum torque of 220 Nm on the crankshaft with 1.0 - ton on each of the first and second supports has been run for 300 h on a stand without breakdowns. It gave a 30-35% fuel saving under the city traffic conditions.

Claims: An axial-piston machine whose frame (1,1c) accommodates a cylinder block (2,2c) with cylindrical spaces (10,10c) whose axes are parallel to the longitudinal axis (O₁-O₁) of a shaft (11,11a,11c) and which accommodate reciprocating pistons (12,12c), each linked kinematically with a swash plate (15,15c) mounted via a first support (22,92) on the inclined journal (23,23c) of the shaft (11,11a,11c) mounted on supports (27,29,27c,29c) in the frame (1,1c) and articulated with a first universal joint (34,34c) which is articulated to a connecting member (47,47c) which is articulated with a second universal joint (35,35c) the latter being articulated with the frame (1,1c) characterized in that the machine incorporates a second support (49,93) of the swash plate (15,15c), said support having a spherical shape, interacting with the swash plate (15,15c) and connected with the frame (1,1c), the centre (O₃) of the second support (49,93) serving, essentially, as the centre around which angular motion of each universal joint (34,35; 34c,35c) takes place and through which passes the bisector plane (p-p) serving as a plane of symmetry of universal joints (34,35; 34c,35c) and on which lies the centre of the connecting member (47,47c) of the universal joints (34,35; 34c,35c). An axial piston machine as claimed in claim 1 characterized in that the second support (49) of the swash plate (15) is located in the zone between two planes, each passing through two relatively-perpendicular axes (n-n and m-m) of the universal joint (34, 35). An axial piston machine as claimed in claim 1 characterized in that the second support (49) of the swash plate (15) embraces two universal joints (34, 35). An axial piston machine as claimed in claims 1,2 or 1,3 characterized in that the second support (49) of the swash plate (15,15c) is capable of moving along the axis (O₁-O₁) of the shaft (11,11a,11c) and that the first support (22,92) has an external spherical surface (22a,92a) interacting with a congruent spherical surface of the swash plate (15,15c) and an internal cylindrical surface (22b,92b) interacting with a cylindrical surface of the inclined journal (23,23c) of the shaft (11a,11c). An axial piston machine as claimed in claim 4 characterized in that the axis (O₄-O₄) of the inclined journal (23,23c) of the shaft (11a,11c) forms an acute angle with the longitudinal axis (O₅-O₅) of the swash plate (15,15c), said angle varying from about 10° to about 32° with changes in the swept volume of the cylindrical space (10,10c).

Inventors: ISTOMIN SERGEI SERGEEVICH, KUTENEV VADIM FEDOROVICH, ROMANCHEV JURY ALEXANDROVICH, ISTOMIN, SERGEI SERGEEVICH, KUTENEV, VADIM FEDOROVICH, ROMANCHEV, JURY ALEXANDROVICH
Applicants: TSNI AVTOMOBILNY I AVTOMOTORNY, TSENTRALNY NAUCHNO-ISSLEDOVATELSKY AVTOMOBILNY I AVTOMOTORNY INSTITUT
Application year: 1990
Main classification: F02B75
IPC codes: F02B75, F01B3, F16H23