SYNCHRONIZATION MECHANISM

Abstract: The device is a radial reciprocating engine with a built in synchronizing mechanism, which is designed thus that the two rotating main parts of the machine, the centre shaft (1) and the outer rim (2), by means of two cam rollers (24 and 23) are articulatedly connected to a synchronizing hub (3) journalled in parallel to these parts and by means of this device the parts are impressed a synchronous rotation at the same time as it is obtained a transfer and balancing of the forces and moments generated by the pressure medium.

Description: SYNCHRONIZATION MECHANISM The device is a radial reciprocating engine provided with a built in synchronizing mechanism, which is intended to be driven as pump or motor and which may be designed with a fixed or an infinitely adjustable displacement. By actuation of the synchronizing mechanism both the rotating main por¬ tions of the engine; the centre shaft 1 and the outer rim 2, are urged to rotate at a synchonous speed and the mechanism simultaneously causes; at one hand a transfer of the forces generated by the pressure medium and on the other hand a balancing by means of the force moment, which from the out¬ side is supplied or led away through the shaft journal of the machine. In connection hereto is also obtained a re- lieving of the cross head forces on the pistons 11 and cylinders 10, fitted between the centre shaft 1 and the outer rim 2. The synchronizing mechanism consists of a synchronizing hub 3, supported thus that its centre of rotation coincides with the line c-c and being designed with a guide rail-provided control arm, which in combination with two cam rollers 24 and 23, affixed to the centre shaft 1 and to the outer rim 2 resp., causes a restricted rotation of these portions. The centre shaft 1, with the rotational centre a-a, is supported in fixed bearings in the machine frame. At distance e, on both sides of the line a-a are found the rotational centra b-b and c-c for the outer rim and for the synchronizing hub 3 resp. At the machine type having an adjustable displacement a parallel displacement of these rotational centra is effected towards the line a-a " with the result that the flow volume at first is reduced to 0 and thereupon, at continued adjustment, increases to the original value, but with a reversal of the flow direction. The following drawings are attached hereto: Drawing I shows a machine designed for constant displacement Fig 1 - longitudinal section Fig 2 - cross section d-d Fig 3 - section f-f of the synchronization hub Drawing II shows a machine with adjustable displacement Fig 4 - longitudinal section Fig 5 - two cross sections g-g and h-h Fig 6 - external view of the adjustment apparatus Drawing III shows three schematical sketches Fig 7 - simplification of section d-d according to Fig 2 Fig 8 - load and moment distribution at an arbitrary and 9 angular rotation ° at forward and rearward position resp. Drawing I. In the machine with constant displacement -is shown that the frame consists of a shell 4 with two bearing bracings 5 and 6 bolted thereto and having built in bearings 7 and 8 for the centre shaft 1, one end of which is shaped into a shaft journal for force transmission and with the opposite end thereof shaped to receive the feed slide 9. Ex- ternally the centre shaft in section d-d has a number of spherical borings 13 for fitting of the cylinders 10. From each boring there is a radially directed hole 14 for commu¬ nication with the feed slide 9. The centre shaft is designed for receiving a cam roller 24 bolted thereto at a distance r x from the rotational centre (a-a). The outer rim 2 is supported by two bearings 15 and 16, which with the bearing attachment 17 are mounted thus that the rotational centre b-b will become parallel to (a-a) at distance e from this. Furthermore the outer rim has inter- nally a number of spherical borings 21 for fitting of pis¬ tons 11 and there is furthermore a cam roller 23 bolted thereto at the distance R 1 from the rotational centre (b-b) . The synchronizing hub 3 has a supporting bearing 18 built into the bearing attachment 19, which is mounted thus that the line c-c will become the centre of rotation. This line is parallel to and positioned at distance e from the rota- tional centre (a-a) of the centre shaft but at the opposite side as compared to the line (b-b). Drawing II. At the machine with adjustable displacement, some details are exchanged and redesigned and the adjustment means are furthermore added. The shell 4 has bores for guide bushings 26, 27, 28 and 29 and guide screws 36 and 38 for guiding the new bearing attachments 20 and 22. The bushing 27 is a guidance for an adjustment screw 30, which is arranged in threads in the bearing attachment 20, and which has a gear wheel 32 clamped thereto, and which receives its motion from a gear wheel 35 fitted to the adjustment hand wheel 37. The bearing attachment 22 for the synchronizing hub receives its motion in the same manner via the gear wheel 33 from the hand wheel 37, but with the intermediary of a left hand adjustment screw 31, for giving this attach¬ ment an opposed movement at adjustment. Drawing III. Fig. 7 is a schematic sketch of the cross section d-d shown in Fig 2. The machine is operated as motor with the "right-hand half" as pressure side and the rotating main parts, the centre shaft 1 and the outer rim 2, have been urged to complete the same rotational angle α° from the initial position. The restricted guiding is effected in that the cam rollers 23 and 24 are urged by the guide rails of the synchronizing hub to take up such positions that their rotational centra together with the rotational centra of the main parts form two congruent triangles, all equally situa¬ ted sides of which being parallel. Due to the pressure of the pressure medium excerted upon the cylinders 10 and the pistons 11 fitted between the centre shaft 1 and the outer rim 2, a piston force P k is generated, which with the perpen¬ dicular distance to the rotational centre b gives rise to a moment P k *X x , which via the cam roller 23 and further via the synchronizing arm and via the cam roller 24 is transformed to an output torque at the centre shaft. The reaction force P k acting in opposite direction upon the cylinder 10 causes with the momentum arm X 2 , a counter clockwise torque P k X 2 , acting directly upon the rotational centre. The final result is an output moment from the machine M = P k X x - 2 X 2 , where the relation between the momentum arms is ^ * 2 = R Q • --- ' Q .

Claims: AMENDED CIAI S [received by the International Bureau on 8 January 1991 (08.01.91); original claim 1 replaced by amended claim 1 (1 page)] A radial reciprocating engine, the frame of which is desig¬ ned as a tubular shell (4) with a bearing bracing (5, 6) bolted to each end thereof for receiving the two rotating main portions of the engine, the centre shaft (1) and the outer rim ( ), which e-re. both provided with spherical attachments for the pressure medium actuated pistons (11) and cylinders (10), c h a r a c t e r i z e d t h e r e i n that on the opposite side of the rotational centre of the centre shaft (1) in relation to that of the outer rim, but with the same adjustable eccentricity there is mounted a synchronizing hub (3) provided with a guide rail, forming together with two cam rollers (24, 23) fitted to the centre shaft (1) and to the outer rim (2) resp. , a synchronizing mechanism, which besides restricted guiding of the rotation of the two main portions (1,2), transfer and balance the forces and moments generated by the pressure medium, thus that the different pairs of piston and cylinder will be subjected to axially directed forces only and are entirely relieved from moment transferring cross head forces. STATEMENT UNDER ARTICLE19 Claim 1 has been limited to take full account of the references listed in the International Search Report. These references were all cited in the granting procedure of the basic Swedish applica¬ tion, and the claim now filed corresponds to the amended claim earlier filed in the Swedish application and which resulted in issue of a Swedish patent 8900841-1. None of the references shows or indicates a solution of the type defined in the amended claim.

Inventors: KYRLIN UNO, KYRLIN, UNO
Applicants: KYRLIN UNO, KYRLIN, UNO
Application year: 1990
Main classification: F04B1
IPC codes: F03C1, F04B1