GB2108584A - Oil-pump arrangements - Google Patents

Oil-pump arrangements Download PDF

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Publication number
GB2108584A
GB2108584A GB08228578A GB8228578A GB2108584A GB 2108584 A GB2108584 A GB 2108584A GB 08228578 A GB08228578 A GB 08228578A GB 8228578 A GB8228578 A GB 8228578A GB 2108584 A GB2108584 A GB 2108584A
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GB
United Kingdom
Prior art keywords
oil
pump
gearbox
pressure
mounting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
GB08228578A
Inventor
George Smart
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NEWAGE TRANSMISSIONS Ltd
Original Assignee
NEWAGE TRANSMISSIONS Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to GB8130159 priority Critical
Application filed by NEWAGE TRANSMISSIONS Ltd filed Critical NEWAGE TRANSMISSIONS Ltd
Publication of GB2108584A publication Critical patent/GB2108584A/en
Withdrawn legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H57/00General details of gearing
    • F16H57/04Features relating to lubrication or cooling or heating
    • F16H57/0434Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01MLUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00Pressure lubrication
    • F01M1/02Pressure lubrication using lubricating pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021Generation or control of line pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01MLUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00Pressure lubrication
    • F01M1/12Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10
    • F01M2001/123Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10 using two or more pumps

Abstract

Pumps A, B driven by a common shaft also have a common oil-inlet and deliver pressurized oil through respective outlets 78, 80, the pressure at the former being greater than that at the latter and regulated by a relief valve 87. The outlets are connected to a hydraulic system comprising e.g. clutches 31, 32 of a marine gearbox, and to a lubricating system in e.g. said gearbox. The lubricating oil circuit may include an oil cooler 83, an oil filter 84, and a relief valve 120. The pumps may be of the gear type. <IMAGE>

Description

SPECIFICATION Oil pump arrangements, particularly for gearboxes This invention relates to oil pump arrangements, particularly although not exclusively for gearboxes, and to gearboxes incorporating such oil pump arrangements.
The invention is particularly although not exclusively applicable for use in marine gearboxes installed between the power unit of a vessel and a driving propeller thereof to transmit the drive of the power unit to the propeller for propulsion purposes with appropriate speed reduction.
In a marine or other gearbox where ratio changes or reverse selection are effected by means of hydraulically operated clutches, it is necessary to provide a source of oil under pressure to operate such clutches, and an oil pump driven from a suitable rotary part of the gearbox is provided for this purpose. It is common practice to utilise the oil pump conventionally provided for circulating lubricating oil from a sump in the gearbox to the various moving parts of the gearbox requiring lubrication, for the additional duty of supplying the hydraulic pressure for clutch actuation, and it is often necessary to provide means for cooling the lubricating oil used in the gearbox.In such arrangements the oil pump is arranged to provide hydraulic pressure, which is maintained at a regulated level by a pressure relief valve for the hydraulic pressure actuation, and the bypass oil flow from the relief valve then passes to the lubrication and cooling functions. Such arrangements are not suitable however for highperformance gearboxes, where high powers are to be transmitted through comparatively small and lightly-constructed gearboxes and cooling of the gearbox components by means of oil, and extraction of heat from the oil, become more important and higher oil flow rates are required. In such a situation an increased flow rate of oil raised to and maintained at the fuil operating pressure for the hydraulic services has been provided, with consequent disadvantages.
it is an object of the present invention to provide an oil pump arrangement for a gearbox which alleviates these difficulties.
According to the present invention from one aspect, an oil pump arrangement, particularly but not exclusively for a gearbox, comprises an assembly of two oil pumps arranged to be driven from a single power source through a common driving shaft, and sharing a common oil inlet, each pump being provided with a separate delivery outlet for oil under pressure, the outlet of one pump being connected to a hydraulic pressure system having a pressure relief valve set to maintain a high pressure in that system, and the outlet of the second pump being connected to an oil lubrication system to provide a lubricating oil flow therein at a lower pressure than the said high pressure.
Preferably a bypass connection is provided from the pressure relief valve to the oil lubrication system, through which bypass connection oil delivered by the first pump and bypassing the hydraulic pressure system via the relief valve passes into the oil lubrication system to augment the oil flow therein.
The oil lubrication system may include an oil cooler downstream of the bypass connection.
The arrangement may also include an oil sump from which the two pumps draw inlet oil to their common inlet, and an oil return path from the lubrication system and from the hydraulic pressure system to the sump whereby return oil from each of these systems is returned to the sump.
The invention from another aspect comprises a gearbox having at least one hydraulically-actuated clutch for effecting a change of operating mode, and having an oil lubrication system for lubricating and/or cooling working parts of the gearbox, the gearbox being provided with an oil pump arrangement as aforesaid, wherein the common inlet of the two pumps is connected to a sump of the gearbox to draw intake oil therefrom, the hydraulic pressure system supplied from the delivery outlet of the one pump is arranged for actuation of the clutch, and the oil lubrication system supplied at least in part from the delivery outlet of the second pump is arranged to lubricate and/or cool working parts of the gearbox at a lower pressure than that maintained in the highpressure system by the pressure relief valve.
Thus the invention makes it possible for only a sufficient quantity of oil to be raised to the high operating pressure for the hydraulic services, while a high flow rate of lubricating and cooling oil may be maintained by the second pump independently of the output of the first pump but possibly augmented by any bypass flow of oil from the hydraulic system.
The invention from yet another aspect comprises an oil pump assembly which comprises a housing incorporating mounting means for the assembly and including separate pump chambers each containing a gear pump comprising intermeshing driving and driven gear pinions, the driving pinions being both mounted on a common driving shaft and the driven pinions being both rotatably mounted on a common spindle.
In such a pump assembly, the housing may be a laminated structure including a hollow mounting member of annular cross-section having an integral mounting flange, a pair of annular pump chamber plates having a separating plate interposed between them, the mounting member being secured to the face of one pump chamber plate remote from the separating plate to close that side of that chamber, and an end cover secured to the face of the second pump chamber plate remote from the separating plate and from the mounting member to close that side of the chamber in the second pump chamber plate, and the driving shaft and the spindle for the driven pinion extend transversely through the separating plate.
A common oil inlet passage serving both pumps, and a delivery passage from one of the pumps, may be formed in the thickness of the wall of the mounting member, and a delivery passage for the second pump may be formed in the end cover.
The invention may be carried into practice in various ways, but one specific embodiment thereof will now be described by way of example only and with reference to the accompanying drawings, in which: Figure 1 is a developed sectional view of a marine gearbox, shown in contiguous planes of section represented by the lines A-B-C-D-E and D-F-G in Figure 2; Figure 2 is an end view of the gearbox of Figure 1 , as seen in the direction of the arrow X in Figure 1 but on a smaller scale; Figure 3 shows the twin oil pump duct of the gearbox of Figures 1 and 2, in section on the line M-N in Figure 2, and shown separated from the gearbox casing; and Figure 4 is a diagram showing the hydraulic circuits of the gearbox assembly of Figures 1 and 2.
In the illustrated embodiment the invention is applied to a marine gearbox providing selection between a single-speed forward drive and a reverse drive between its input and output. The gearbox 10 comprises a two-part casing 11 which splits along the plane 12 in Figure 2, which plane is inclined to the horizontal with the gearbox in its working position. The lower part 11 B of the casing 11 is formed with an oil sump 13.An input shaft 1 5 with a projecting splined input end 15A is journalled in tapered roller bearing races 1 6, 1 7 in the upper part of the casing 11, alongside a layshaft 1 8 journalled in tapered roller bearing races 1 9, 20, the bearing axes for the two shafts lying in the plane 12 so that the outer races of the respective bearings are retained in cooperating semi-circular recesses formed in opposite side walls of the upper and lower casing portions 11 A and 11 B. An output shaft 22 is journalled in roller bearing races 23, 24 and 25 retained in cylindrical bores formed in opposite side walls of the lower casing portion 11 B. The output shaft 22 carries a coupling flange 26 outside the casing portion 11 B.
The input shaft 1 5 carries a toothed gear wheel 27 keyed to the shaft for rotation therewith and in permanent mesh with a similar gear wheel 28 keyed to the layshaft 18, the gear wheels 27 and 28 having equal numbers of teeth. Each of the gear wheels 27 and 28 is formed with an integral axially-projecting clutch housing 29 or 30 whose interior contains a multi-plate hydraulicallyactuated clutch 31 or 32. Each clutch comprises a set of annular outer clutch plates 33 keyed to the respective clutch housing 29 or 30 by means of notches in the outer periphery of the plates 33 slidably engaged with internal spline formations in the housing interior, and a cooperating set of annular inner clutch plates 34 similarly keyed to a sleeve 35 surrounding the respective shaft 1 5 or 1 8 by external splines on the sleeve.Each of the two sleeves 35 is an integral extension from one side of the hub of a gear pinion 36 or 37 journalled respectively on the shaft 1 5 or the shaft 1 8. The plates of the two cooperating sets 33 and 34 are respectively interposed between one another in alternating fashion, and one set of plates carries annular discs of friction material. The two sets of clutch plates 33 and 34 of each clutch can be axially compressed together against an end plate 38 bolted onto the respective housing 29 or 30, to engage the clutch, by means of a hydraulic piston 39 slidable in a cylinder 40 formed in the interior of the respective clutch housing, each piston 39 carrying an O-ring seal 41 in a circumferential recess in the piston.To actuate either clutch 31 or 32, hydraulic pressure fluid is admitted to the respective cylinder 40 behind the piston 39 via a feed passage (not shown), under the control of a selector valve 42 mounted on top of the gearbox casing 11.
The two gear pinions 36 and 37, which are freely rotatable on the respective shafts 1 5 and 18, have equal numbers of teeth, and are both in permanent mesh with a larger gear wheel 43 splined to the output shaft 22 at 44 for rotation therewith.
The selector valve 42 is of rotary spool type, operated by means of an operating arm 45 secured to its spindle, which can be turned into any selected one of three angular positions corresponding to forward drive, reverse drive and neutral. A ball catch (not shown) is provided for retaining the valve spool in any one of these three positions when selected, and a microswitch 46 cooperates with the spindle and is connected in electrical safety circuitry (not shown) which ensures that a prime mover (such as a marine engine) coupled to the input shaft cannot be started except when the neutral valve position has been selected.
It will be understood that when the selector valve 42 is in its neutral position both clutches 31 and 32 are disengaged, so that the drive of the input shaft 1 5 is transmitted by the intermeshing gearwheels 27 and 28 to the layshaft 18, but not to the output shaft 22 since both shafts 1 5 and 18 are free to rotate relatively to the pinions 36 and 37 journalled on them. However when forward drive is selected by means of the valve 42, the plate clutch 31 is actuated to couple the input shaft 15 to the pinion 36 and hence to the gearwheel 43 and output shaft 22, driving the output shaft with a speed reduction in the forward direction. When the valve 42 is moved via neutral to the reverse posiTion, the clutch 31 on the input shaft 1 5 is disengaged, freeing the forward drive, and the clutch 32 on the layshaft is actuated to couple the layshaft 1 8 (which is being driven by the input shaft via the gearwheels 27 and 28) to the pinion 37 and thence via the pinion 43 to the output shaft 22 to drive the latter in the reverse direction. The step-down transmission ratio between input and output depends on the relative numbers of teeth of the gearwheel 43 and each pinion 36, 37, but might be for example 1.5 :1, or 2:1,or 1.2 :1, as required.
In its general length and layout as just described, the gearbox 10 is of known form with which the invention is not concerned. It is however with the hydraulic means for actuating the clutches 31 and 32 and for cooling the gearbox and lubricating its shafts that the invention is directly concerned.
Thus, a twin oil pump unit 50 is mounted on one side wall of the casing 11, in a position in which it is driven by the layshaft 1 8. The pump unit 50 comprises a pump housing 51 with an integral mounting flange 52 with bolt holes, by which the pump unit can be bolted onto the casing 11 by means of bolts 53. The inner facing 54 of the flange 53 has a counterbore 55 which locates around the outer roller race of the bearing 20 for the layshaft 18 to position the pump unit correctly on the housing 11, and carries a sealing ring 56 is an annular groove 57 in the facing. Attached to the pump housing 51 are two plate-like pump chamber casings 60A and 60B having a spacer plate 62 interposed between them, and an end cover 63 is mounted on the outer face of the pump chamber casing 62 which is further from the mounting flange 52.The assembly of casings 60A, 60B, spacer plate 62 and end cover 63 are held together and to the pump housing 51 by means of bolts 66. Each of the two pump chamber casings 60A and 60B forms a pump chamber for a gear pump A or B formed by a driving gear pinion 67A or 67B, and a driven gear pinion 68A or 68B intermeshing with the respective driving pinion, all as shown in Figure 1. The two driving pinions 67A and 67B are carried by a common driving shaft 69,journalled in the housing 51 and end cover 53, and the two driven pinions 68A and 68B are journalled on a common dead shaft 70.The inner end of the driving shaft 69 (which is coaxial with the counterbore 55 and layshaft 18) has a diametral coupling tongue formation 72 (Figure 1) which engages in a cooperating diametral coupling groove 73 formed in the outer end face of the layshaft 18 whereby the driving shaft, and hence the two gear pumps A and B, are driven from the layshaft of the gearbox, which it will be recalled is driven from the input shaft.
The pump housing 51 is formed in its thickness with an inlet passage 75 (Figure 3) whose mouth is connected by an intake pipe 76 (Figure 2) with the interior of the sump 1 3 of the gearbox, and whose inner end opens into the pump chamber within the casing 60A, and communicates via a hole 77 in the spacer plate 62 with the pump chamber within the casing 60B, so that the two pumps A and B draw in oil from the sump via the common inlet passage 75. The pump housing 51 is also formed in its thickness with an outlet passage 78 leading from the pump chamber in casing 60A to the hydraulic selector valve 42 of the gearbox, via passageways in the wall of the housing portion 11 A, not shown in Figures 1 and 2.The end cover is formed with an outlet passage 80 leading from the pump chamber in casing 60B to a pipe line 81 running externally of the gearbox housing 11 which delivers low-pressure cooling and lubricating oil to the gearbox via an external oil cooler 83 (shown diagrammatically in Figures 3 and 4) and a filter unit 84 mounted on the gearbox housing 11 adjacent to the selector valve block 86 of the gearbox.
The hydraulic circuits of the gearbox and pump assembly 10, 50 are shown diagrammatically in Figure 4. The pump A delivers oil at a high delivery pressure, regulated by means of a pressure relief valve 87, to the selector valve 42 which delivers the pressure oil to whichever of the clutches 31 and 32 is to be actuated. The delivery outlets of the selector valve are to feed channels formed in the bedplate of the valve block 86, that associated with the clutch 31 being shown at 88 in Figure 1.
Each of the clutches is associated with a twochannel oil delivery ring 89 journalled on the hub 106 of the respective gear wheel 27 or 28 and provided with sealing rings 90. The ring 89 on the shaft 15 has one inlet nipple 91 which connects the oil feed channel 88 to a radial passage 92 in the ring 89 opening into a circumferential groove 93 on the hub 106 of the gearwheel 27. From the groove 93 a radial passage 94 in the hub connects with an axial passage 95 leading into the clutch cylinder 40 behind the piston 39, whereby highpressure oil from the valve 42 can be made available for clutch actuation.
The other clutch 32 can similarly be supplied with high-pressure actuating oil from the valve 42 via the associated oil delivery ring 89 on the layshaft 18.
The oil from the pump A bypassed by the highpressure relief valve 87 (which is incorporated in the position 87A of the selector valve block) is delivered by an external pipe 96 (Figures 3 and 4) extruding from an outlet socket on the valve block 86 to a branch connector 98 (Figure 3) in the lubrication pipeline 81, so that bypass oil from the high-pressure circuit joins the delivery flow from the pump B upstream of the cooler 83, thus increasing the total flow available for lubrication of the gearbox.
The delivery of lubricating oil from pump B, augmented by any bypass oil from the highpressure circuit, passes through the oil cooler 83 and filter 84 to the lubrication circuit in the gearbox casing 11. The intake connection for cooled inlet oil into the filter unit 84 is by external piping, not shown in Figures 1 and 2, and the filter outlet is connected by further external piping, also not shown, to delivery channels in the bedplate of the valve block 86 leading to each of the oil delivery rings 89 on the shafts 1 5 and 18, that for the ring on the shaft 1 5 being shown at 101 next to the channel 88. A nipple 102 of the ring 89 supplies low-pressure oil from the channel 101 to a radial passage 103 in the ring 89, and thence to a circumferential groove 104 around the hub 106 of the gear 27 to lubricate the bearing of the ring 89. A radial passage 105 in the hub 106 leads from the groove 104 to a circumferential groove 107 formed around the input shaft 1 5. Oil thus supplied to the groove 107 is delivered through an inclined passageway 108 formed in the inlet shaft 1 5 to an annular space 109 defined between the shaft 1 5 and the surrounding sleeve 35, to lubricate the bearing of the gear pinion 36. The oil passes from the space 109 outwardly through apertures 110 in the sleeve 35 to the clutch plates 33 and 34, which thus operate immersed in cooling oil which escapes from the outer circumference of the clutch to drain down to the sump 13.
As shown in Figure 4, the low-pressure lubricating circuit extending from the filter 84 is also provided with a pressure relief valve 120 which regulates the oil pressure in the lubricating circuit to a level lower than that in the highpressure circuit. Bypass oil from the low-pressure relief valve 120 (which can be seen in Figure 2 below the bedplate of the valve block 86) drains down back to the sump 13.
Any leakage oil from the high-pressure clutch actuation system of pump A which passes the piston 39 will join the flow of lower-pressure lubrication oil in which the clutch plates are immersed, and will drain down with the latter to the sump for recirculation. After the actuation of either of the clutches, when the selector valve 42 is moved either to the neutral setting or to the setting for actuation of the other clutch, the highpressure circuit branch leading from the valve to the previously-actuated clutch will be connected to a return passage (not shown) venting into the interior of the gearbox housing 11 so that the pressure behind the piston 39 of that clutch will be relieved and surplus oil will be returned to the sump for recirculation.
Thus it can be seen that the illustrated embodiment provides a twin oil pump unit having a single housing for attachment to a gearbox, one pump of the unit being arranged to supply highpressure oil to a hydraulic circuit for operation of hydraulic services of the gearbox, while the other pump is arranged for the operation of the lubricating and cooling circuit of the gearbox at a lower pressure but higher flow rate, being augmented by bypass oil from the high-pressure circuit. Thus the requirements of the two circuits are met in an optimum manner in a compact and simple fashion.
If the illustrated gearbox is provided with an additional mechanical power outlet for an angle drive, this may be lubricated from the lowpressure lubrication circuit by means of a branch connection shown at 125 in Figure 4, draining back to the sump.
Figure 5 is a diagram showing the external piping arrangements for the oil cooler 83 and filter 84; Figure 6 is a sectional elevation of the valve block 86 showing details of the selector valve 42; Figure 7 is an underneath plan view of the valve block 86 showing the channels for pressurised oil to the clutches 31 and 32; and Figures 8 and 9 are respectively a plan and an end elevation of the valve block 86.
Thus as shown in Figures 6 and 7, highpressure oil delivered from pump B via the delivery passage 78 passes, through a passage (not shown) in the wall of the gearbox housing portion 11 A, to an inlet 125 in the valve block 86 communicating with a spring-loaded pressure relief valve 126 which regulates the oil pressure to a predetermined value, bypass oil from the valve 126 passing to a bypass port 127 in the valve block 86. The bypass port is connected by the external pipe 96 to the junction 98 in the pipe 81, and as shown in Figure 5, the low-pressure oil flow in pipe 81 from pump B, augmented by any bypass flow through pipe 96, passes through an external pipe 1 28 to the inlet 1 29 of the oil cooler.
Cooled oil leaving the oil cooler via its outlet 1 30 is delivered by an external pipe 131 to the oil filter 84, and the filtered oil passes through an external pipe 132 to a low-pressure inlet port 1 35 on the valve block 86, seen in Figure 8. The port 135 connects, via a passage 1 36 in the valve block, with the oil delivery channel 101 formed in the underside of the base plate of the valve block 86, opposite ends of the channel 101 communicating with the nipples 102 of the feeder rings 89 of the respective clutches 31 and 32, to supply lowpressure oil continuously to the clutches for cooling and lubrication as described with reference to Figures 1 and 2.
Referring again to Figure 6, the high-pressure oil delivered from pump A to the port 135, and pressure-regulated by the bypass valve 1 26, enters an axial inlet passage 140 in the spool 141 of the selector valve 42. A radial port 142 in the spool communicates with the passage 140 to deliver the pressure oil to one or other of two passages 144 and 145 in the valve housing portion 146 of the valve block 86, the far ends of the passages 144 and 145 being visible in Figure 7 and connecting respectively with the high-pressure oil delivery channels 88 in the base plate of the block 86 leading to the nipples 91 of the feeder rings 89 of the respective clutches 31 and 32. Thus, depending upon the angular position to which the valve spool 42 is turned by its operating arm 45, high-pressure oil from pump A is delivered to the cylinder 40 of the respective clutch 31 or 32 behind its piston 39 to actuate the clutch, selecting forward or reverse drive as described above. The operating arm 45 has a ball catch 1 50 which holds it in the selected one of its three positions, and the safety ball catch 151 associated with the microswitch 46 previously referred to, is shown in Figure 6.

Claims (14)

1. An oil pump arrangement, particularly but not exclusively for a gearbox, comprising an assembly of two oil pumps arranged to be driven from a single power source through a common driving shaft, and sharing a common oil inlet, each pump being provided with a separate delivery outlet for oil under pressure, the outlet of one pump being connected to a hydraulic pressure system having a pressure relief valve set to maintain a high pressure in that system, and the outlet of the second pump being connected to an oil lubrication system to provide a lubricating oil flow therein at a lower pressure than the said high pressure.
2. An oil pump arrangement as claimed in Claim 1, having a bypass connection from the pressure relief valve to the oil lubrication system, through which bypass connection oil delivered by the first pump and bypassing the hydraulic pressure system via the relief valve passes into the oil lubrication system to augment the oil flow therein.
3. An oil pump arrangement as claimed in Claim 2, in which the oil lubrication system includes an oil cooler downstream of the bypass connection.
4. An oil pump arrangement as claimed in any one of Claims 1 to 3, including an oil sump from which the two pumps draw inlet oil to their common inlet, and having an oil return flow path from the lubrication system and from the hydraulic pressure system to the sump whereby return oil from each of these systems is returned to the sump for recirculation.
5. An oil pump arrangement as claimed in any one of Claims 1 to 4, in which the pump assembly comprises a housing incorporating mounting means for the pump assembly and including separate pump chambers each containing a gear pump comprising intermeshing driving and driven pinions, the driving pinions being both mounted on the common driving shaft and the driven pinions being both rotatably mounted on a common spindle.
6. An oil pump arrangement as claimed in Claim 5, in which the housing is a laminated structure comprising a hollow mounting member of annular cross-section with an integral mounting flange, a pair of annular pump chamber plates having a separating plate interposed between them, the mounting member being secured to the face of one pump chamber plate remote from the separating plate and closing that side of that chamber, and an end cover secured to the face of the other pump chamber plate remote from the separating plate and from the mounting member and closing that side of the said other chamber, and the driving shaft and the spindle for the driven pinions extending transversely through the separating plate.
7. An oil pump arrangement as claimed in Claim 6, in which the common oil inlet of the delivery outlets respectively comprise passages formed in the thickness of the wall of the mounting member, and in which the other delivery outlet comprises a passage formed in the end cover.
8. A gearbox having at least one hydraulicallyactuated clutch for effecting a change of operating mode of the gearbox, and having an oil lubrication system for lubricating and/or cooling working parts of the gearbox, the gearbox being provided with an oil pump arrangement as claimed in any one of Claims 1 to 7, wherein the common inlet of the two pumps is connected to a sump of the gearbox to draw intake oil therefrom, the hydraulic pressure system supplied from the delivery outlet of the one pump is arranged for actuation of the clutch, and the oil lubrication system supplied at least in part from the delivery outlet of the second pump is arranged to lubricate and/or cool working parts of the gearbox at a lower pressure than that maintained in the high-pressure system by the pressure relief valve.
9. A gearbox as claimed in Claim 8 having an input shaft, a layshaft and an output shaft, the layshaft being permanently coupled by gearing to the input shaft for rotation therewith but in the opposite direction thereto, and the output shaft being selectively coupled by hydraulicallyactuated clutch means either to the input shaft or to the layshaft, the said clutch means being actuated by the high-pressure system under the control of hydraulic valve means, and the driving shaft of the pump assembly being coupled to the layshaft for rotation thereby.
10. An oil pump assembly which comprises a housing incorporating mounting means for the assembly and including separate pump chambers each containing a gear pump comprising intermeshing driving and driven gear pinions, the driving pinions being both mounted on a common driving shaft and the driven pinions being both rotatably mounted on a common spindle.
11. An oil pump assembly as claimed in Claim 10, in which the housing comprises a laminated structure including a hollow mounting member of annular cross-section having an integral mounting flange, a pair of annular pump chamber plates having a separating plate interposed between them, the mounting member being secured to the face of one pump chamber plate remote from the separating plate to close that side of that chamber, and an end cover secured to the face of the second pump chamber plate remote from the separating plate and from the mounting member to close that side of the chamber in the second pump chamber plate, and in which the driving shaft and the spindle for the driven pinions extend transversely through the separating plate.
12. An oil pump assembly as claimed in Claim 11, in which a common oil inlet passage serving both pumps, and a delivery passage from one of the pumps, are formed in the thickness of the wall of the mounting member, and in which a delivery passage for the other pump is formed in the end cover.
13. A gearbox assembly substantialiy as specifically described herein with reference to the accompanying drawings.
14. A twin oil pump assembly for a gearbox, substantially as specifically described herein with reference to Figures 1 to 3 of the accompanying drawings.
GB08228578A 1981-10-06 1982-10-06 Oil-pump arrangements Withdrawn GB2108584A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB8130159 1981-10-06

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Publication number Priority date Publication date Assignee Title
GB2286017A (en) * 1994-01-21 1995-08-02 Concentric Pumps Ltd Improvements relating to pumps
EP1593881A1 (en) * 2004-04-22 2005-11-09 BorgWarner Inc. Cooling fluid feeding arrangement for a dual clutch transmission and method of feeding cooling fluid for such a transmission

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DE3237032A1 (en) 1983-04-28

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