INTERNAL GEAR MACHINE

Abstract: An internal gear machine of the kind having variable displacement fluid chambers formed between an orbiting outer gear (33) and a rotating inner gear (31) has the orbiting outer gear (33) retained in its orbiting motion by a plurality of roller dowells closely fitting in a locating ring (19) disposed radially outside the outer gear (33) and extending therefrom to be received in arcuate recesses on the radial outside of the outer gear (33) as it orbits. The locating ring (19) is connected to an end piece (15) of the internal gear machine along a plane of torsional stress and this connection is reinforced by providing the end piece (15) with recesses (45) disposed coaxially with the roller dowells (41) and extending the roller dowells (41) closely within the recesses (45). The roller dowells (41) thus extend across the plane or torsional stress and provide reinforcement.

Description: The invention relates generally to internal gear machines. Such machines sometimes referred to as gerotor pumps or motors, usually have an orbiting outer gear disposed within a cover connected to a gear machine body. Many prior art hydraulic and pneumatic devices have utilized internal gear sets, often called gerotors or rotors, and have been used as pumps where shaft work is converted to hydraulic work and as motors where hydraulic work is converted to shaft work. Examples of gerotor pumps and motors are shown in Patent Specifications US-A-3572983; 4411607; 4545748 and 4586885. In an internal gear pump or motor, an inner gear or rotor having outwardly directed teeth co-operates with an external gear or rotor having inwardly directed teeth so that fluid chambers therebetween increase and decrease in volume as the inner and outer gears rotate in a housing. In one particular type of gerotor pump or motor, the inner gear rotates while the outer gear orbits in a cavity defined by a locating ring (a ring which locates the rotor set between the body parts) disposed radially outside of the outer gear. Extending radially along the inside of the locating ring are a plurality of cylindrical roller dowells which serve as guides to retain the outer gear in its orbital motion. These roller dowells are received in arcuate recesses on the radial outside of the outer gear. As the inner gear rotates, the corresponding motion of the outer gear is an orbiting motion because of the roller dowells being received in the arcuate recesses of the outer gear. The variable displacement chambers formed between the inner and outer gear as the outer gear orbits and the inner gear rotates function to transfer work between the fluid in the chambers and the rotating shaft connected to the inner gear. A significant problem with previously proposed constructions arises because the locating ring is connected to the pump or motor by a plurality of bolts which receive a very significant stress as the shaft starts and stops. For example, if the shaft is connected to a wheel driven by the hydraulic power of the motor, the wheel can be subjected to significant torsional stresses, all of which are received by the bolts which hold the locating ring in the motor. Generally, the point of failure of the motor is at the bolts so that the bolts are sheared off and the motor is broken between the locating ring and the motor body. Although it is possible to make the bolts larger and the locating ring thicker, there are also often size requirements with respect to the motor which make this difficult to accomplish. Therefore, it would be desirable to stengthen the connection between the locating ring and the body without increasing the size of the locating ring and the bolts. According to the invention there is provided an internal gear machine of the kind having variable displacement fluid chambers formed between a rotating inner gear and an orbiting outer gear, the orbiting outer gear being retained in an orbiting motion by a plurality of roller dowells received in arcuate recesses on the radial outside of the outer gear and closely fitting in a locating ring disposed radially outside the outer gear, the locating ring being connected to a gear machine end piece; characterised in that the gear machine end piece has cylindrical recesses extending coaxially with the roller dowells and sized closely to receive the roller dowells; and the roller dowells extend closely within the cylindrical recesses from the locating ring so as to reinforce the connection between the locating ring and the gear machine end piece against torsional stresses. Such an internal gear device has a reinforced connection between the locating ring and the end piece without the necessity of increasing the size of the device of the size of the bolts. The invention is diagrammatically illustrated by way of example in the accompanying drawings, in which: Figure 1 is a cross sectional view of an internal gear machine of previously proposed kind; Figure 2 is a similar view to Figure 1 but of an internal gear machine according to the invention; and Figure 3 is a cross sectional view of the internal gear machine shown in Figure 2 taken on line 3-3 in Figure 2. The present invention provides an improved internal gear motor or pump of the type shown in Patent Specification EP-A-0261757; Applicant's co-pending European Patent Application 88307211.8 and in Patent Specification US-A-4586885. The operation of the internal gears and other parts of the machine are well known in the art and are described in these documents. To the extent the general description of the operation of these parts is not described herein, the descriptions in these documents are hereby incorporated by reference. Referring now to Figure 1, an internal gear pump or motor 11 of previously proposed kind is shown in cross sectional view through the axis of the machine shaft. The machine 11 comprises a cylindrical housing 13 formed by a body 15, a cover 17 and a locating ring 19. The body 15 and the cover 17 are axial end portions of the housing 13 and the locating ring 19 defines the cavity therebetween in which a rotor set and valve plate rotate. These three portions 15, 17, 19 of the housing are held together by a plurality of bolts 21. Extending through the axial centre of the housing 13 is a shaft 23. The shaft 23 is retained for rotation in the housing 13 by bearings 25 and 27. In the case of a motor, the shaft 23 is driven by hydraulic work in variable displacement chambers 29 between an inner gear 31 and an outer gear 33 (the rotor set). Rolls 30 extend as teeth of the gear 31 in the meshing of the rotor set. Hydraulic fluid is conveyed to and from the variable displacement chambers 29 through an inlet 35 and an outlet 37 disposed in the cover 17. A valve plate 39 regulates the flow of fluid into and out of the variable displacement chambers 29 as it rotates with a plurality of openings therein. The internal gear machine shown in Figure 1 is of a kind wherein the outer gear 33 orbits while the inner gear 31 rotates. This motion is dictated by roller dowells 41 which are closely received in cylindrical cavities spaced about the radial inside of the locating ring 19. The roller dowells 41 serve as guides or teeth to cause the outer gear 33 to orbit rather than rotate in a cavity 43 between the outer gear 33 and the locating ring 19. In the previously proposed machine 13 shown in Figure 1, the roller dowells 41 extend between the valve plate 39 and the body 15 on the opposite side of the valve plate 39. In contrast in a machine 13 of the invention as shown in Figures 2 and 3, the roller dowells 41 extend into cylindrical recesses 45 in the internal gear machine body 15. The recesses 45 are sized closely to receive the roller dowells 41. The roller dowells 41 extend from the valve plate 39 sufficiently into the body 15 to reinforce the connection between the locating ring 19 and the body 15. In the machine of Figure 1 this junction is supported solely by the bolts 21. Because the roller dowells 41 are closely received in the locating ring 19 and in the cavities 45 of the body 15, the roller dowells 41 reinforce the connection between the locating ring 19 and the body 15 against torsional stresses. In operation, as the internal gears 31, 33 rotate the shaft 23 with respect to the body 15, the torsional stress of this work is received along the plane or junction between the locating ring 19 and the body 15. This is the same plane as that along which Figure 3 is taken. Also, as stresses are exerted on the shaft 23, for example by a wheel, these stresses are again received at the same location. In the machine of Figure 1, all of these torsional stresses are concentrated on the bolts 21. Although tightening these bolts increases the friction forces between the locating ring 19 and the body 15, this still does not provide sufficient reinforcement to prevent the shearing of the bolts 21. This problem of bolt failure at this position is increased by repeated working of the bolts as these stresses cycle on the bolts 21. In the machine of the invention, reinforcement is provided for the connection between the locating ring 19 and the body 15 by means of the extended roller dowells 41. This improvement can be achieved without significant additional expenditure simply by boring the cylindrical cavities 45 and providing longer roller dowells 41. In fact, longer roller dowells 41 can be replaced by stacking a short roller dowell as shown in Figure 1 and a shorter roller dowell which is received adjacent the valve plate 39 so that the longer dowell extends across the plane between the locating ring 19 and the body 15. In this way standard shorter roller dowells can be stacked so as to avoid production of a new longer roller dowell. In some hydraulic pumps or motors, the valve plate is disposed on the opposite side of the rotor set from the arrangement depicted in Figures 1 through 3. In this case the roller dowells 41 cannot be extended into the body 15 but can be extended into the cover 17. Although this does not provide a reinforcement at the junction between the body 15 and the locating ring 19 (the plane of maximum torsional stress in the motor because the body 15 receives greater torsional stress than the cover 17), it does provide a significant improvement over a motor which has only the bolts 21 for connection. By means of reinforcing the cover/locating ring connection, the motor is stiffened which reduces the working stresses at the body/locating ring junction. This reduces the tendency of the bolts 21 to fail at the body/locating ring junction even though the reinforcement of the roller dowells is concentrated at the cover/locating ring junction. Thus, the roller dowells may extend into close fitting cavities in either end portion of the motor. Of course, it is better to reinforce the motor at the end portion receiving the greater torsional stress.

Claims: 1. An internal gear machine of the kind having variable displacement fluid chambers formed between a rotating inner gear (31) and an orbiting outer gear (33), the orbiting outer gear being retained in an orbiting motion by a plurality of roller dowells (41) received in arcuate recesses on the radial outside of the outer gear (33) and closely fitting in a locating ring (19) disposed radially outside the outer gear (33), the locating ring (19) being connected to a gear machine end piece(15, 17); characterised in that the gear machine end piece (15, 17) has cylindrical recesses (45) extending coaxially with the roller dowells (41) and sized closely to receive the roller dowells (41); and the roller dowells (41) extend closely within the cylindrical recesses (45) from the locating ring (19) so as to reinforce the connection between the locating ring (19) and the gear machine end piece (15 or 17) against torsional stresses. 2. An internal gear machine according to claim 1, wherein the gear machine has two end pieces (15, 17), one (15) of which receives greater torsional stresses than the other (17), said one (15) being the end piece having the cylindrical recesses (45) receiving the roller dowells (41).

Inventors: DLUGOKECKI, ANDREW N.
Applicants: PARKER HANNIFIN CORPORATION
Application year: 1988
Main classification: F01C1
IPC codes: F16H1, F04C2