Gear machine for use as a pump or motor

Abstract

 A gear machine (1) is described comprising a machine casing (2) closed by two covers (3 and 4) and within which two gear wheels (6) provided on respective shafts (7) supported by bushes (8) are in mutual engagement.
The main characteristic of the present invention is that a compensation area for the axial thrusts to which a bush (8) is subjected is defined between an elastic diaphragm (5) installed between the bush (8) and a cover (3), so that because of the clearance between the gear wheels (6) and bushes (8) rapid starting is possible even under load, whereas as pressure increases a corresponding flexure of the diaphragm (5) towards the bushes (8) occurs, so as to gradually compensate said clearance while at the same time partially balancing said axial thrusts.

Description

[0001] This invention relates to a gear machine for use as a pump or motor.

[0002] Current gear machines are known to comprise a machine casing closed at its axial ends by respective covers and internally housing two mutually engaging gear wheels. The gear wheels are provided on two rotatable shafts, namely the drive and driven shaft, which are supported by two bushes substantially of "8" shape. Gear machines of the compensation type and of the fixed clearance type are in use. In compensated machines, seal gaskets are installed between the bushes and covers to define a space which is hydraulically connected to that part of the machine through which high-pressure fluid flows. During operation, axial thrusts are created along the clearance walls defined between the gear wheel sides and the bushes and act on these latter, to be compensated by the axial thrusts created between the covers and the space defined by said gaskets. These latter are preloaded during machine assembly to compensate the gap between the gear wheels and bushes. A gear machine of the compensation type therefore allows the gap along the clearance walls to be taken up, allows the axial thrusts which arise along these latter to be balanced, and results in high volumetric efficiency for pumps and high mechanical efficiency for motors. However the machine has certain drawbacks due to the gasket preloading. In this respect, the preloading tends to urge the bushes towards the gear wheels so that on starting the machine there can be considerable friction between the bushes and gear wheels. For operation as a pump, the machine must be connected to a motor (normally electric) which has to overcome this initial separation friction and must therefore have a high starting torque. Consequently a powerful motor must be connected to the pump. It is apparent that the greater the motor power, the higher its cost. For operation as a motor, the machine must be connected to a pump able to feed fluid at high pressure both to overcome said friction and to overcome the initial load provided by the user device connected to the motor. Likewise, a powerful and therefore more costly pump has to be installed. In machines of the compensation type, the greatest inconvenience is therefore on starting, by virtue of the friction existing along the clearance walls.

[0003] In fixed clearance machines there is no compensation as no seal gaskets are provided along the spaces between the bushes and covers into which the high pressure fluid flows, so that in these machines there is no take-up of the play existing along the clearance walls. The machine components are machined to give only a small clearance along the clearance walls. In spite of this, because of the axial thrusts which arise on the bushes during operation, the fluid seeps along these clearance walls. If on the one hand this is an advantage on starting because it results in low friction, on the other hand it is also a serious drawback in that it considerably reduces machine efficiency. Moreover, because of the said machining, the machine itself is of higher cost and the device (pump or motor) upstream of the machine must be overdimensioned.

[0004] The object of the present invention is to provide a gear machine for use as a pump or motor which obviates the aforesaid drawbacks by operating as a fixed clearance machine on start-up, but as a compensation machine when under normal running for a predetermined fluid pressure.

[0005] This object is attained according to the present invention by a gear machine for use as a pump or motor of the type comprising a machine casing closed at each of its axial ends by a respective cover and internally housing two mutually engaging gear wheels provided on two rotatable shafts which are supported by two bushes and of which one extends to the outside of said machine casing, characterised in that between at least one of said covers and said machine casing there is installed a relatively elastic diaphragm in which there is provided a first hydraulic communication between a zone of said machine casing traversed by a high-pressure fluid and a first space delimited between said cover and said diaphragm by a first preloaded gasket assembly and having an area substantially equal to that defined area on said bushes on which axial thrusts are present during operation, and a second hydraulic communication between a zone of said machine casing traversed by low-pressure fluid and a second space delimited between said cover and said diaphragm by a second gasket assembly; the preload of said first gasket assembly being insufficient to cause flexure of said diaphragm at the start of operation and thus unable to influence the predetermined clearance existing between said bushes and gear wheels so that rapid starting is ensured even under load, whereas as fluid pressure increases, the fluid present in said first space causes corresponding flexure of said diaphragm towards said bushes so as to gradually compensate said clearance.

[0006] The present invention will be more apparent from the description of a preferred embodiment thereof given hereinafter by way of non-­limiting example with reference to the accompanying drawings in which:

Figure 1 is an axial section through a gear machine constructed in accordance with the present invention; and

Figures 2, 3, 4 and 5 are sections on the lines II-II, III-III, IV-IV and V-V of Figure 1.

[0007] In Figure 1 the reference numeral 1 indicates overall a gear machine for use as a pump or motor. The machine 1 comprises a machine casing 2 closed at its axial ends by respective covers 3 and 4. A diaphragm 5 of relatively elastic material such as aluminium is mounted between the cover 3 and the corresponding axial end of the machine casing 2. As will be more apparent hereinafter, for determined pressures of the fluid flowing through the machine 1 the diaphragm 5 flexes towards the machine casing 2. Within this latter there act two mutually engaging gear wheels 6 provided on the central part of two rotatable shafts 7, one of which extends through the cover 4 to the outside of the machine casing 2. The shafts 7 are supported by two "8"-shaped bushes 8 which are also housed in the machine casing 2.

[0008] As shown in Figures 1 and 5, the machine casing 2 has an internal shape which reproduces the perimetral shape of the assembly formed from the two gear wheels 6. In the machine casing 2 in correspondence with the zone of engagement between the gear wheels 6 the casing 2 comprises on opposite sides two ports 11, namely an inlet port and outlet port. In correspondence with the ports 11 each bush 8 comprises cavities 12 which with the inner wall of the machine casing 2 define respective fluid channels. To support the shafts 7 each bush 8 comprises two parallel through holes 13, in each of which there is fitted a respective liner 14. Along the whole length of the holes 13 there is provided a recess 15, the purpose of which will be apparent hereinafter. One of the shafts 7 has substantially the same axial length as the machine casing 2, whereas the other extends through a hole 16 in the cover 4 to the outside of the machine 1 to be connected to an electric motor or a mechanical or electromechanical user device according to whether the machine 1 is used as a pump or motor. On each of the axial end faces of the machine casing 2 there is provided an annular seat 17 for a substantially elliptical retaining gasket 18. One gasket 18 makes contact with the inner face of the diaphragm 5 whereas the other makes contact with the inner face of the cover 4. The machine 1 is assembled by tightening down four screws 21, only one of which is shown in Figure 1. The screws 21 pass successively through a hole 22 provided in the cover 3, a hole 23 provided in the diaphragm 5 and a hole 24 provided in the machine casing 2, and are then screwed into a threaded bore 25 provided in the cover 4. When assembled, the head of the screws 21 abuts against a shoulder formed in the hole 22.

[0009] As shown in Figures 1 and 3, the diaphragm 5 comprises two through holes 31 which are coaxial with and face the bores 8 of the closer bush 8. As will be apparent hereinafter, a hydraulic seal is determined mechanically between the bush 8 and diaphragm 5 by the effect of the fluid pressure. In the diaphragm 5 there are also provided four small holes, two of which, indicated by 36a, are in line with the channels defined by the cavities 12, whereas the other two indicated by 36b are in line with the gap between the bush 8 and the inner wall of the machine casing 2. The first two holes 36a are symmetrical about a straight line orthogonal to that which joins the second two holes 36b and vice versa, as shown in Figure 3.

[0010] As shown in Figures 1 and 2, on the side facing the diaphragm 5, the cover 3 comprises two cylindrical recesses 41 coaxial with the holes 31 and communicating by way of two holes 42 which extend from the recesses 41 and intersect in the central part of the cover 3. A threaded bore 43 extends from the recess 41 coaxial to the shorter shaft 7, and into which, on operation as a motor, there is screwed one end of a discharge pipe for drainage reasons which will be apparent hereinafter. On operation as a pump, the bore 43 is engaged by a sealing plug. The space in which the recesses 41 are provided is delimited by an annular seat 44 housing a retaining gasket 45. The seat 44 and hence the gasket 45 are of "8" shape which substantially copies the perimetral shape of the bush 8. In correspondence with the cavities 12 provided in the bush 8 and reproduced in the gasket 45, in that face of the cover 3 facing the diaphragm 5 there are provided two opposing annular seats 46 for respective retaining gaskets 47. The assembly formed by the gaskets 45 and 47 is contained in an elliptical seat 48 engaged by a corresponding retaining gasket 51 which reproduces substantially the shape of the gasket 18. It should be noted that the seats 46 use part of the extension of the seat 44 and part of the extension of the seat 48. Respective antiextrusion gaskets 52 constructed preferably of a rigid material such as teflon are laid to the inside of the respective retaining gaskets 45 and 47 along the seats 44 and 46. Five spaces 53, 54, 55, 56 and 57 are therefore defined on that face of the cover 3 which faces the diaphragm 5. The space 53 is delimited by the gasket 45, the spaces 54 and 55 oppose each other about the central part of the cover 3 and are delimited by the gaskets 47, and the spaces 56 and 57 oppose each other about the central part of the cover 3 and are delimited by a portion of the gasket 44 and a portion of the gasket 51. As will be apparent hereinafter, the space 53 for hydraulic communication with the holes 31 is in a zone through which low-pressure fluid passes, as is evident from the fact that for motor operation the space 53 is connected to discharge through the bore 43. By way of the holes 36a, the spaces 54 and 55 are in hydraulic communication with the cavity 12 in the low pressure zone and with the cavity 12 in the high pressure zone, according to the direction of rotation of the shafts 7. In operation as a pump, the hole 36a communicating with the cavity 12 in the low pressure zone is shown by a dashed line (Figure 3) and indicated by 61. It has a diameter greater than the other holes 36a and 36b. In operation as a pump, to facilitate drainage of the fluid which seeps along the holes 13 in the bushes 8 and its recycling to the suction side, within the space 55 or 54 there is provided an oblique bore 62 (shown by dashed lines in Figures 1 and 2) which connects the hole 61 to the intersection of the holes 42. Finally, it should be noted that for essential drainage purposes, an axial through bore 64 shown by dashed lines in Figure 1 is provided in the shorter shaft 7. If the machine is operated as a motor and is series-connected so that the fluid is not fed to discharge but to a further user device, the spaces 54 and 55 are simultaneously in a high-pressure zone. The spaces 56 and 57 are connected by the holes 36b to a high-­pressure zone defined within the machine casing 2.

[0011] As shown in Figures 1 and 4, on that face of the cover 4 facing the machine casing 2 there is a recess 65 coaxial with the shorter shaft 7. The recess 65 is in hydraulic communication with a seal assembly 67 by way of an oblique bore 66. When in operation, the effect of the fluid pressure between the cover 4 and the corresponding bush 8 mechanically determines a hydraulic seal. For operation as a motor, a pressurised fluid enters the machine casing 2 through one port 11 to rotate the gear wheels 6 and convert hydraulic energy into mechanical energy. The fluid is then discharged at a lower pressure through the other port 11. Any fluid which seeps along the holes 13 in the bushes 8 and specifically between the liners 14 and the wall of the holes 13 is drained to the outside through the bore 43. In this respect, the fluid which seeps along that bush 8 closer to the cover 3 flows out towards the recesses 41, which mutually communicate (hole 42) and of which one is provided along the bore 43. The fluid which seeps along the other bush 8 flows out towards the recess 65 and also along the bore 16, and from this latter through the bore 66 to the recess 65. From this latter the fluid flows towards the bore 43 passing through the bore 64, the hole 31 and the recess 41 in succession. Both for motor and for pump operation the holes 36b communicate with the maximum pressure zone, which is that relative to those teeth of the gear wheel 6 distant from the engaging teeth. At the commencement of operation there is a gap between the clearance walls defined by the faces of the teeth of the gear wheels 6 and the corresponding faces of the bushes 8 because temporarily unbalanced axial thrusts act on said faces of the bushes 8. The bushes 8 therefore move towards the respective covers 3 and 4 to result in absence of friction between the gear wheels 6 and bushes 8. Consequently the gear wheels 6 immediately begin to rotate even if the pressure of the fluid fed into the casing 2 is low. At this stage the volumetric efficiency is low because a certain quantity of fluid seeps along said clearance walls without performing any work on the gear wheels 6. The seal assembly contained between the cover 3 and diaphragm 5 comprises gaskets which because they are of greater thickness than the seat which houses them become preloaded on assembly. The thrust exerted by these gaskets is absorbed by the diaphragm and is insufficient to flex the diaphragm 5. Thus on starting, the gasket preloading does not affect the clearance between the bush 8 and gear wheels 6 and therefore does not influence the mechanical efficiency, which remains high. In the meantime a quantity of the fluid fed into the casing 2 occupies the spaces 56 and 57 and one of the spaces 54 or 55 defined between the cover 3 and diaphragm 5. The total contact area between the cover 3 and diaphragm 5 in which high-pressure fluid is present is large and substantially equal to that area of the bush 8 over which said axial thrusts are developed. The motor operation is of the fixed clearance type on starting, but with increasing pressure the diaphragm 5 flexes to an extent dependent on the pressure and on the size of the compensation area between the cover 3 and diaphragm 5. As the diaphragm 5 flexes it takes up the gap along the clearance walls. This gap is not totally taken up because part of the compensation pressure is used in overcoming the reaction produced by the flexure of the diaphragm 5. Summarising, a machine is provided in which the compensation system, necessary for obtaining high volumetric efficiency, does not penalise mechanical efficiency, to thus ensure highest overall efficiency. In particular, at vary low speed the high mechanical efficiency obtained by virtue of the low friction force along the clearance walls is vital in enabling the machine to start if there is a high resistant torque on the shaft 7.

[0012] It is apparent that by using the machine 1 it is not necessary to overdimension the pump upstream of the motor as this when under full running conditions has substantially the same mechanical efficiency as a compensation motor. Obviously, a diaphragm similar to the diaphragm 5 can also be installed between the cover 4 and the machine casing 2. Again in this case, partial take-up of the gap at said bush 8 will occur when the fluid flexes the diaphragm 5.

[0013] For pump operation, one port 11 is connected to a fluid tank and the other port 11 is connected to a user device. On connecting the shaft 7 extending outside the machine 1 to the shaft of a for example electric motor, the mechanical energy of the motor shaft is converted into hydraulic energy in that the gear wheels 6 draw liquid from the tank and deliver it to the user device. It should be noted that as the liquid is delivered to the user device the pressure increases at the outlet port and in all those spaces communicating with it either by virtue of seepage along the bushes 8 and casing 2 as described heretofore or through the channel provided at the outlet port 11. It should also be noted that in contrast to motor operation, in which drainage is to the outside so as not to compromise the seal assembly 67, in pump operation the drainage fluid can be conveniently recycled by feeding this drainage fluid to said channel defined at the inlet port 11. For pump operation the bore 43 is therefore closed, and to improve drainage the bore 62 is provided and the hole 36 communicating with the inlet port 11 is enlarged (as indicated by 61).

[0014] When operating as a pump, there is again a gap along the clearance walls on starting, and this substantially reduces the friction which the electric motor must overcome for initial separation. As the pressure gradually increases, the diaphragm 5 flexes to partially take up the gap and partially compensate axial thrusts, to obtain a volumetric efficiency substantially higher than the initial value. Thus on starting, the pump behaves as a fixed clearance pump with all its associated advantages, whereas as pressure increases it behaves as a compensated pump with all the advantages deriving therefrom. It must be emphasized that the use of the machine 1 obviates the need to use a powerful motor to overcome initial separation friction as is required for balanced pumps of the prior art. At high pressure, the pump volumetric efficiency is greater than that of fixed clearance pumps of the prior art. For pump operation, a second diaphragm 5 can also be installed as described with reference to operation as a motor. It should be noted that although the machine 1 comprises one extra component, it is of reduced manufacturing cost as no precision finishing machining is required to define the clearance along the clearance walls and the preload to apply to the gaskets on tightening-down during assembly. In addition the use of the machine 1 as described results in a saving in the members installed upstream or downstream thereof.

[0015] Finally, it is apparent that modifications can be made to the described and illustrated machine 1, but without leaving the scope of protection of the present invention.

[0016] In particular, a respective diaphragm 5 of convenient material and thickness in relation to the flexing pressure can be connected to each cover 3 and 4. In addition, it is apparent that the machine 1 is reversible, ie can operate with the gear wheels 6 rotating in one or other direction at choice.

Claims

1. A gear machine for use as a pump or motor of the type comprising a machine casing (2) closed at each of its axial ends by a respective cover (3 and 4) and internally housing two mutually engaging gear wheels (6) provided on two rotatable shafts (7) which are supported by two bushes (8) and of which one extends to the outside of said machine casing (2), characterised in that between at least one of said covers (3 and 4) and said machine casing (2) there is installed a relatively elastic diaphragm (5) in which there is provided a first hydraulic communication (36a and 36b) between a zone of said machine casing (2) traversed by a high-pressure fluid and a first space (56, 57, 54 or 55) delimited between said cover (3 or 4) and said diaphragm (5) by a first preloaded gasket assembly (45, 47 and 51) and having an area substantially equal to that defined area on said bushes (8) on which axial thrusts are present during operation, and a second hydraulic communication (31 or 36a) between a zone of said machine casing (2) traversed by low-pressure fluid and a second space (53, 55 or 54) delimited between said cover (3 or 4) and said diaphragm (5) by a second gasket assembly (45 and 47); the preload of said first gasket assembly (45, 47 and 51) being insufficient to cause flexure of said diaphragm (5) at the start of operation and thus unable to influence the predetermined clearance existing between said bushes (8) and gear wheels (6) so that rapid starting is ensured even under load, whereas as fluid pressure increases, the fluid present in said first space (56, 57 and 54 or 55) causes corresponding flexure of said diaphragm (5) towards said bushes (8) so as to gradually compensate said clearance.

2. A gear machine as claimed in claim 1, characterised in that the hydraulic communication between said high pressure zone and a first part (56 or 57) of said first space is effected by two first through holes (36b) provided in said diaphragm (5) in line with the gap existing between said bush (8) and the inner wall of said machine casing (2);

3. A gear machine as claimed in claim 2, characterised in that said diaphragm (5) is provided with two second through holes (36a) one of which is arranged to hydraulically connect a second part (54 or 55) of said first space to said high-pressure zone, and the other to hydraulically connect a first part (55 or 54) of said second space to said high-pressure zone.

4. A gear machine as claimed in claim 3, characterised in that said first holes (36b) are in a position symmetrical about a straight line orthogonal to that joining said second holes (36b) and vice versa.

5. A gear machine as claimed in claim 4, characterised in that in the central part of said diaphragm (5) there are provided two third through holes (31) coaxial with fourth holes (13) provided in said bush (8) to support said shafts (7); said third holes (31) hydraulically connecting said low-pressure zone to a second part (53) of said second space by way of said fourth holes (13).

6. A gear machine as claimed in claim 5, characterised in that a respective notch (15) is provided longitudinally along said fourth holes (13) to allow passage of that fluid which during operation seeps between said gear wheels (6) and said bushes (8) towards said second part (53) of said second space.

7. A gear machine as claimed in claim 5 and/or 6, characterised in that said bush (8) comprises on opposite sides of its outer surface two cavities (12) which with the inner wall of said machine casing (2) define respective channels, one arranged to hydraulically connect said high-pressure zone to said second part (54 or 55) of said first space by way of one of said second holes (36a), and the other arranged to hydraulically connect said low-pressure zone to said first part (55 or 54) of said second space by way of the other of said holes (36a).

8. A gear machine as claimed in claim 7, characterised in that said second part (53) of said second space is delimited by a first gasket (45) having a perimetral shape similar to that of said bush (8); within said second part (53) of said second space there being provided two first cylindrical recesses (41) coaxial with said third (31) and fourth (13) holes and connected together by two fifth holes (42) which extend from these recesses and intersect within said cover (3).

9. A gear machine as claimed in claim 8, characterised in that said first part (55 or 54) of said second space is delimited by a second gasket (47) having a perimetral shape substantially similar to but more extensive than said cavity (12) with which it is in hydraulic communication by way of one of said second holes (36a).

10. A gear machine as claimed in claim 9, characterised in that said second part (54 or 55) of said first space is delimited by a third gasket (47) having a perimetral shape substantially similar to but more extensive than said cavity (12) with which it is in hydraulic communication by way of the other of said holes (36a).

11. A gear machine as claimed in claim 10, characterised in that said first part (56 and 57) of said first space is delimited externally by a fourth gasket (51) and internally by said first (45), second (47) and third (47) gaskets.

12. A gear machine as claimed in claim 11, characterised in that for operation as a motor, a discharge port (43) is provided in correspondence with one of said recesses (41) to allow drainage to the outside.

13. A gear machine as claimed in claim 12, characterised in that for pump operation, said diaphragm (5) is provided with a sixth through hole (61) communicating with a seventh through hole (62) provided in said cover (3) and opening into the intersection of said fifth holes (42).

14. A gear machine as claimed in any one of the preceding claims, characterised in that said diaphragm (5) is of aluminium construction.

Drawing