Hydraulic transmission

Abstract: A hydraulic transmission device comprises a rotatable casing (4) secured at one end by a first flange (3) to an input shaft (1) and at the other end to a second flange (5) which supports an output shaft (8). Drive is transmitted by fluid introduced into an area between the outwardly directed contoured teeth (50) extending around the periphery of a rotor (18), eccentrically mounted on said first flange (3) for rotation therewith, and the inwardly directed contoured teeth (51) extending around the periphery of an annular ring (17) secured to said output shaft (8), the diameter of the rotor (18) being smaller than the internal diameter of the annular ring (17) thereby allowing the respective teeth (50,51) of the rotor (18) and the ring (17) to mesh during rotation of the input shaft (1).

Description: The invention relates to a variable speed device that can be used for the transmission of power from an input shaft to an output shaft as defined by the features outlined in the preamble of claim 1 and known from US-A 2 101 899. The present invention provides a variable pump/motor having an internally lobed ring meshing with an externally toothed rotor, both rotatably mounted in an inner casing. A plate having a part circular recess and slot is in contact with the one end surface of the lobed ring and rotor and rotates with the rotor. Means are provided to alter the engagement of the slots relative to the rotor and lobed ring whilst the inner casing revolves. A priming pump is provided to prime the pump/motor and make up losses during running. Thus the invention comprises a hydraulic power transmission unit consisting of the features outlined in claim 1. Fig.1 is a longitudinal section on line B-B in Fig.2. Fig.2 is a section on line A-A in Fig. 1 showing the position of the plate Fig.3 is a section as Fig.2 showing the other limit of adjustment of the plate. Fig.4 is a longitudinal section of a second embodiment of the invention. An input shaft 1 has an extension that houses a square drive shaft (rotor drive shaft) 2 and a flanged member 3 that is in threaded engagement with an inner cylindrical casing 4 to close one end thereof. Inner casing 4 is in threaded engagement with a flanged member 5 that closes the other end of casing 4 and extends to house two bearings 6 and 7 that support the output shaft 8. The assembly is housed in an outer casing and fluid reservoir or housing 9. The assembly is not dependent on the outer casing 9 for support. The square drive shaft 2 extends through a clearance hole 10 in a valve plate (second plate) 11 into the rotor axial support 12 and crescent block (first plate) 13 which is rotatably mounted in the output shaft 8 extension 14 and supported against axial movement by a thrust race 44. The output shaft extension 14 is supported against axial movement by a thrust race 15. The valve plate 11 has one side in contact with a thrust race 45 and the other in running contact with an annular ring 17 having 15 radially inwardly directed contoured lobed teeth 51 and the eccentrically mounted rotor 18. Rotor 18 has 12 outwardly directed contoured lobed teeth 50 which are partially in mesh with the corresponding teeth 51 of ring 17 (Figs. 2 and 3). A part circular recess (arcuate recess) 19 is formed in the valve plate 11 and communicates with the meshed teeth of the lobed ring 17 and rotor 18. A further part circular slot (arcuate slot) 20 communicates between the fluid input port 21 and the lobed annular ring 17 and rotor 18 where they are out of mesh. The lobed annular ring 17 is held in position on the output shaft extension 14 by screws 22. A circumferential slot 23 is cut in the inner casing 4 and extends for a quarter of the circumference. A screw (peg means) 24 extends through the slot 23 into the valve plate 11. Screw 24 further extends through an oblique slot in a slide member 25 which is arranged to slide on the inner casing 4 between positions shown in chain dotted lines in Fig.1. A key 26 positions the slide member 25 on the inner casing 4. An adjustment rod 27 and a yoke 28 engage with two fixed rings 29 on the slide member 25 to provide external adjustment of the position thereof. A housing elememt 30 is fixed to the input shaft by a screw 31 and contains two elements 32 and 33 of a multi-start screw pump. Element 33 is held stationary by a screw 34 extending into the outer casing 9. A passageway 35 connects the screw pump with an inlet cavity 36 defined by the opposing faces of valve plate 11 and flanged member 3 within casing 4; ball 37 and part circular spring 38 act as a pressure relief valve. A plate 39 is secured to housing element 30 by screws 40 and contains a passageway 47 which connects the screw pump to a stationary recessed pump inlet plate 41. Pipe 42 provides a fluid feed for the screw pump and spring 43 urges plate 39 into contact with the inlet plate 41. Rotation of the input shaft 1 rotates the inner casing 4, slide member 25, flanged member 5, square drive shaft 2 and rotor axis 12. The output shaft 8 remains stationary when the valve plate 11 is in the position shown in Fig.2. Element 33 of the screw pump remains stationary whilst element 32 moves in and out of mesh with the rotation of the housing element 30. Fluid is thereby drawn up the pipe 42 and is forced through the inlet passageway 35, aperture 21 and cavity 36 into part circular slot 20 and thence into the recesses 46 of the rotor 18 and annular ring 17. Crescent element 16 of plate 13 which extends between annular ring 17 and rotor 18 to separate the respective recesses 46 causes the fluid to be transmitted to the point where the teeth are coming into mesh, further rotation then forces the fluid into the part circular recess 19 and as the teeth come out of mesh the recesses 46 accept the fluid and rotation of the output shaft 8 does not occur. Excess fluid pumped from the screw pump is allowed to escape through the relief valve 37, 38. Movement of the adjustment rod 27 causes rings 29 to move slide 25 along the inner casing 4 by causing screw 24 to move in the slot 23 of the inner casing 4 and rotate the valve plate 11 relative to the inner casing 4. As the valve plate 11 moves towards a position where the part circular slots 19 and 20 are in the position shown in Fig.3. the recesses 46 can no longer accept all of the fluid. In this position, therefore, there is an escape of fluid from between the teeth. The condition that all the fluid cannot be accepted means that the lobed annular ring 17 and output shaft 8 are forced to revolve at a low speed. Gradual adjustment of the valve plate 11 allows more fluid to be carried around, this forces increased rotation of the output shaft 8 relative to the input shaft 1. When the position shown as in Fig.3. has been reached no fluid other than leakage can be accepted thereby causing about a 1:1 rotation of the output shaft 8 with the input shaft 1. A needle roller bearing may be incorporated between the annular ring 17 and the inner casing 4 to ease rotation. The teeth ratio between ring 17 and rotor 18 allows contact therebetween over an arc approaching 120°. As noted the teeth are not straight flanked but are contoured, the precise contours being calculated to provide efficient operation. In Fig.4 there is illustrated a modified form of the device of Figs 1-3 in which like reference numerals refer to like parts. In the modified form a valve plate support sleeve 57 is provided within casing 4 having an end secured to valve plate 11 and the opposite end closed by an end cap 58 located between flanged member 5 and the thrust bearing 15. End cap 58 is secured to flanged member 5 and has a portion 60 extending into said housing, which portion houses bearing 6. Vents 59 are provided in flanged member 5 and end cap 58 to relieve internal hydraulic pressure that builds up as a result of leakage passed plate 11 when the device is in use. An overrun valve 55 urged into a closed position by spring 56 is provided between recess 19 in valve plate 11 and fluid inlet cavity 36. In the transmission devices described above the pressure ratio does not increase proportionally with the revs ratio but at only a little over half the ratio, thus at a 16:1 revs ratio the pressure ratio is only 8.2:1.

Claims: A hydraulic power transmission device comprising;- a fixed housing having opposed end faces (9) through which extend axially aligned input and output shafts (1 and 8); a rotatable cylindrical casing (4) positioned in said housing and closed at each end by first and second flanged members (5 and 3) rotatable therewith, said output shaft (8) being journalled in said first flanged member (5) and said input shaft (1) being secured to or integral with said second flanged member (3); an annular ring 17 located within said casing (4) and secured to said output shaft (8) and having a, plurality of inwardly directed contoured teeth (51); a rotor (18) contained within said annular ring (17) presenting planar surfaces therewith opposed to said first and second flanged members (5 and 3), said rotor (18) being carried on a driven shaft (2) parallel to said input shaft (1) and secured to said second flanged member (3), said rotor (18) having a smaller diameter than the inner diameter of said annular ring (17) and including a plurality of outwardly directed contoured teeth (50) dimensioned to mesh with the teeth (51) of said annular ring (17), said rotor (18) having fewer teeth than said annular ring (17) whereby rotation of said input shaft (1) causes the rotor (18) to rotate within said annular ring (17); a first plate (13) including a crescent shaped element (16) extending parallel to said driven shaft (2) between the non-meshing teeth of said annular ring (17) and said rotor (18); a second plate (11) to define with other components of the device a fluid inlet cavity (36) therebetween, means being provided to change the position of said second plate (11) between first and second positions with respect to said casing (4), characterised in that: said first plate (13) is secured to said driven shaft (2) and is in mating relationship with the planar surface of the annular ring (17) and the rotor (18) opposed to said first flanged member (5), said second plate (11) is contained within said casing (4) having one surface in mating contact with the other planar surface of said annular ring (17) and said rotor (18) and an opposite surface spaced from said second flanged member (3) to define said fluid inlet cavity (36) therebetween, said means acting to rotate said second plate (11) between said first and second positions, said second plate (11) being secured to said casing (4) for rotation therewith, said second plate (11) further containing an arcuate recess (19) in said face contacting said other planar surface, said recess (19) being positioned to overlie the teeth (50, 51) of said annular ring (17) and said rotor (18), said second plate (11) further containing an arcuate slot (20) diametrically opposed to said recess (19) and positioned to overlie said teeth (50, 51) to provide communication between said fluid inlet cavity (36) and the spaces (46) between said meshing teeth (50, 51), said second plate (11) further including a central clearance passageway (10) through which said rotor drive shaft (2) extends; said device further including a hydraulic pump means (32, 33) actuated by said input shaft (1), passageway means being provided to transfer fluid from said pump means (32, 33) into said fluid inlet cavity (36). A transmission device according to claim 1 wherein the means to rotate said second plate (11) comprises a circumferential slot (23) in said rotatable casing (4) through which a peg means (24) extends into and is secured to said second plate (11); said peg means (24) projecting outwardly of said casing (4) to co-operate with said means to move said peg means (24) in said slot (23) to rotate said second plate (11) between said first and second positions. A transmission device according to claim 2 wherein said means comprises a slide member (25) extending lengthwise of said casing (4) and rotatable therewith, said slide member (25) including an oblique slot into which said peg means (24) projects, said slide member (25) being moveable axially with respect to said casing (4). A device according to anyone of claims 1-3 wherein there is provided a plate support sleeve (57) secured at one end to said second plate (11), closed at the opposite end by a flange member (58), and carried by said output shaft (8), said sleeve (57) being located within said rotatable casing (4) for rotation therewith. A transmission device according to any one of claims 1-4 wherein the annular ring (17) has 15 teeth and the rotor (18) has 12 teeth. A transmission device according to any one of claims 1-5 wherein the pump means (32, 33) is a multi-start screw pump.

Inventors: BLYTHING WILLIAM CHARLES, BLYTHING, WILLIAM CHARLES
Applicants: BLYTHING WILLIAM CHARLES, BLYTHING, WILLIAM CHARLES
Application year: 1988
Main classification: F16H39
IPC codes: F16D31