US3614274A - Hydraulic rotary piston machine - Google Patents

Hydraulic rotary piston machine Download PDF

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Publication number
US3614274A
US3614274A US3614274DA US3614274A US 3614274 A US3614274 A US 3614274A US 3614274D A US3614274D A US 3614274DA US 3614274 A US3614274 A US 3614274A
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Prior art keywords
ring
rollers
rotary piston
piston machine
channel
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Expired - Lifetime
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Carl V Ohrberg
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Danfoss AS
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Danfoss AS
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Priority to DE19691931143 priority Critical patent/DE1931143A1/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/104Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement having an articulated driving shaft

Abstract

The invention relates to a rotary piston machine of the type having an externally toothed star member and a surrounding internally toothed ring member. The star and ring members have cooperably engaging teeth and are eccentrically offset relative to each other. The ring member teeth are in the form of rotatable rollers which are journaled in casing portions on opposite sides of the ring member. The ring member has slots in radially aligned and surrounding relation to the rollers and plates in the slots are biased into sealing engagement with the rollers by spring means and/or hydraulic means.

Description

United States Patent inventor Carl V. Olu'berg Havnbjerg, Denmark Appl. No. 46,280 Filed June 15, 1970 Patented Get. 19, 1971 Assignee Danfoss A/S Nordborg, Denmark Priority June 19, 1969 Germany P 19 31 143.4
HYDRAULIC ROTARY PISTON MACHINE Primary Examiner-Carlton R. Croyle Assistant Examiner-John J. Vrablik Attorney-Wayne B. Easton ABSTRACT: The invention relates to a. rotary piston machine of the type having an externally toothed star member and a surrounding internally toothed ring member. The star and ring members have cooperably engaging teeth and are eccentrically offset relative to each other. The ring member teeth are in the form of rotatable rollers which are journaled in casing portions on opposite sides of the ring member. The ring member has slots in radially aligned and surrounding relation to the rollers and plates in the slots are biased into sealing engagement with the rollers by spring means and/or hydraulic means.
PATENTEUHCI 1s |97| sum 1 0F 2 31514 2 74 HYDRAULIC ROTARY PISTON MACHINE The invention relates to a hydraulic rotary piston machine, in which an externally toothed wheel cooperates with an internally toothed ring, the teeth of which are constituted by rollers which are arranged in recesses in an outer ring and are mounted in side portions connected to this outer ring.
In rotary piston machines of this kind, which may operate as pumps or motors, the axes of the toothed wheel and the toothed ring are offset from each other; it is also possible for the center point of one toothed element to revolve about the center point of the other toothed element. During this movement the teeth of the toothed wheel are in close contact with and slide over those of the outer ring, and between the teeth and the side portions there are formed displacement chambers which increase and decrease in size cyclically.
By forming the teeth of the toothed ring as rollers, manufacture can be simplified. Furthermore, these rollers should rotate during the sliding contact with the teeth of the toothed wheel, so that wear is reduced. In this connection however difficulties are encountered in practice.
In a first known arrangement, short rollers, the length of which corresponds to the width of the outer ring, are mounted in the recesses themselves. Here a compromise must be made. On the one hand, the rollers must fit the recesses so well that no path is created along which the fluid under pressure can leak; on the other hand however there must be a sufficient clearance to allow the rollers to be properly lubricated. This system is particularly sensitive to dirt which can force its way between the rollers and the recesses. Furthermore, the loosely fitted rollers are not only loaded on one side by the toothed ring but also by the hydraulic fluid, so that increased mechanical friction between the rollers and certain points in the recesses results.
The last-mentioned disadvantage is avoided in a construction in which cylindrical rollers of greater length are used and these are mounted in both side portions. The other disadvantages are however still present. Furthermore, in practice it is virtually impossible for three parts, namely the two side plates and the outer ring containing the recesses, to be so produced, aligned and kept in alignment during the period of operation, in such a manner that no jamming of the rollers occurs.
The object of the invention is to provide a hydraulic rotarypiston machine of the initially described kind in which the rollers can rotate freely with little friction and in which, at worst, insignificant losses of oil due to leakage occur.
According to the invention this object is achieved by arranging the rollers in the recesses so that there is clearance between them and by causing a sealing slide pin, guided in the outer ring, to be pressed against the periphery of each roller.
In this construction it is only necessary for the spaced-apart bearings for each roller to be aligned with each other in the two side portions. This problem can be readily solved. Since there should be clearance between the roller and the recess, there is very considerable latitude for the alignment of this recess with the bearings. Furthermore, the clearance allows the compressed fluid to penetrate behind the rollers and thus to relieve them of load. The sealing slide pins prevent losses due to leakage, despite this clearance. Dirt causes no trouble at all in the gap and, if it passes over the top of the roller and below the sealing slide pin, it merely leads to the pin being lifted from the roller for a brief period. Thus, perfect low-friction operation is ensured.
Each sealing slide pin can be spring loaded. Instead of or in addition to this, each sealing slide pin can also be loaded by the pressure of the hydraulic medium. The latter has the advantage that in the case of higher working pressures, which tend to causelosses by leakage, a higher sealing pressure is also applied by the slide pins.
In particular, the lower ends of all the grooves in which the sealing slide pins are guided can be connected to a common passage system which is connected to the pressure side of the machine. In the case of a reversible rotary-piston machine it is advisable to connect the common passage system of passages to the two unions by way of a nonretum valve in each case. Then automatically caters for the passage system always containing hydraulic medium at higher pressure.
The rollers can be held in the side portions in bearings, either plain bearings or roller hearings, in order to reduce friction still further. The invention will now be described in more detail by reference to an embodiment illustrated in the drawing, in which:
FIG. 1 is a longitudinal section through a rotary piston machine constructed in accordance with the invention, and
FIG. 2 shows a section on line A-A of FIG. 1.
The casing of the rotary piston machine illustrated consists of a bearing portion 1, an intermediate part 2, a side portion 3, an outer ring 4, a second side portion 5, a slide plate 6, a casing ring 7 and a cover plate 8. The parts 1-5 are interconnected by screw bolts 9, and the parts 4-8 by screwbolts 10.- A main shaft 11 is mounted in bearings 12 and 13 in the bearing portion 1. A universal-joint shaft 14 which, through an outer toothed portion at both ends engages in a corresponding inner toothed portion, connects the main shaft 17 to an internally toothed ring 15. This toothed ring meshes with rollers 16, which are rotatably mounted in bearings 17 and 18 in the side portions 3 and 5 and are fitted in recesses 19 in the outer ring 4, there being clearance between the nollers and the recesses. Between the teeth of the toothed ring 15, the roller 16, the rest of the outer ring 4 and the two side portions 3 and 5 there are thus formed displacement chambers 20, which increase and diminish in size cyclically with each revolution of the toothed wheel 15.
Sealing slide pins 21 are guided in grooves 22 in the outer ring 4 and are pressed against the peripheral surfaces of the rolls 16 by a leaf spring 23 or the pressure obtaining in the chamber 24. This results in a perfect seal between adjacent displacement chambers 20, despite the clearance between each roller 16 and recess 19.
The sealing slide pins 21 are intended only to effect a seal and therefore do not need to reciprocate as in slide valve pumps or pusher-type engines. The accuracy of the machining of the grooves and surfaces of the slide pins does not therefore need to be as great. Furthermore, the rate of revolution of the rollers is very low; no particularly heavy demands are therefore made on the material cf the slide pins and a casehardened steel is adequate.
The spaces 24 below the pusher pins 21 are interconnected through an annular groove 25 in the side potion 5. This annular groove communicates, by way of axial passages 26, with an annular groove 27 which in turn communicates through two similar paths with the unions 28 and 29 in the cover plate 8. Only one of these paths is shown. it consists of an axial bore 30 in the slide plate 6, a nonretum valve 31 in the casing ring 7 and a connecting passage 32 in the cover plate 8. The nonretum valve ensures that the spaces 24 in each case communicate with the side under higher pressure, even when the machine is of the kind that can operate in reverse.
An astial passage 33 in the side portion 5 leads into the displacement chambers 20 between each two rollers 16, and this passage is continued as an axial passage 34 in the slide part 6. Since nine rollers 16 are present in this embodiment, there are also nine such passages 33, 34. Cooperating with the mouths of the passages 34 is a rotary slide valve 35, which is driven at the same speed as the toothed ring 15 by a universal-joint shaft 36, both ends of which likewise engage through an outer toothed portion with corresponding inner toothed portions. The rotary slide valve 35 is mounted on the journal 37 which is held in the cover plate 8. The rotary slide valve contains eight openings 36 which communicate with; the unions 28 through an annular groove 36, and between each pair of these openings the rotary slide valve contains eight further openings 40 which communicate with the union 29 through an annular groove 41. In this way the rotary slide valve 35 and the slide plate 6 constitute a commutator valve: which ensures that the displacement chambers 20 are connected in the correct sequence with the high-pressure and low-pressure sides of the machine respectively.
To relieve the rotary slide valve of pressure, the openings 38 are interconnected on that side opposite the annular sleeve 39 by an annular groove 42, and the openings 40 are interconnected on that side opposite the annular groove 41 by an an nular groove 43. Moreover, a recessed area 44, similar to the mouth, is provided in the cover plate 8 opposite each of the passages 34, and from each opening 38, 40 there runs a-cutoff passage 45 which extends to the end face of the cover plate 8, so that the same pressure obtains in the recesses 44 as at the mouths of the passages 34.
All spaces into which leaking oil can penetrate, and particularly the central spaces 46, the space 47 for the bearing and the space 48 outside the rotary slide valve are interconnected through passages 49, 50 and 51. Fitted in the cover plate 8 are two nonreturn valves (not illustrated) through each of which the leaking oil is passed to the low-pressure union.
The embodiment described relates to a specific type of rotary piston machine. The principle of forming the teeth as rollers, here described, can however also be used in any other geared or rotary piston machines.
I claim:
I. A rotary piston machine comprising an externally toothed wheel member and a surrounding internally toothed ring member, said members having cooperably engaging teeth and being eccentrically offset relative to each other, a casing.
including casing portions on opposite sides of said ring member, said ring member having teeth formed as cylindrically shaped rollers, said rollers being joumaled in said casing portions, said ring member defining slots in radially aligned and surrounding relation to said rollers, plates in said slots, and biasing means biasing said plates into sealing engagement with said rollers.
2. A rotary piston machine according to claim 1 wherein said ring member has circumferentially arranged recesses, said rollers being disposed in said recesses.
3. A rotary piston machine according to claim 1 wherein said biasing means are springs.
4. A rotary piston machine according to claim 1 wherein said biasing means includes channel means having fluid communication with the outer ends of said slots, and means for supplying pressurized fluid to said channel means.
5. A rotary piston machine according to claim 4 wherein said casing includes inlet and outlet ports, said channel means having fluid communication with said inlet port.
6. A rotary piston machine according to claim 5 wherein said channel means has fluid communication with said outlet port, and one way valve means disposed between said ports and said channel means.

Claims (6)

1. A rotary piston machine comprising an externally toothed wheel member and a surrounding internally toothed ring member, said members having cooperably engaging teeth and being eccentrically offset relative to each other, a casing including casing portions on opposite sides of said ring member, said ring member having teeth formed as cylindrically shaped rollers, said rollers being journaled in said casing portions, said ring member defining slots in radially aligned and surrounding relation to said rollers, plates in said slots, and biasing means biasing said plates into sealing engagement with said rollers.
2. A rotary piston machine according to claim 1 wherein said ring member has circumferentially arranged recesses, said rollers being disposed in said recesses.
3. A rotary piston machine according to claim 1 wherein said biasing means are springs.
4. A rotary piston machine according to claim 1 wherein said biasing means includes channeL means having fluid communication with the outer ends of said slots, and means for supplying pressurized fluid to said channel means.
5. A rotary piston machine according to claim 4 wherein said casing includes inlet and outlet ports, said channel means having fluid communication with said inlet port.
6. A rotary piston machine according to claim 5 wherein said channel means has fluid communication with said outlet port, and one way valve means disposed between said ports and said channel means.
US3614274D 1969-06-19 1970-06-15 Hydraulic rotary piston machine Expired - Lifetime US3614274A (en)

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DE19691931143 DE1931143A1 (en) 1969-06-19 1969-06-19 Hydraulic rotary piston machine

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CA (1) CA923761A (en)
CH (1) CH499718A (en)
CS (1) CS149702B2 (en)
DE (1) DE1931143A1 (en)
DK (1) DK134078C (en)
ES (1) ES380351A1 (en)
FR (1) FR2052479A5 (en)
GB (1) GB1301528A (en)
HU (1) HU165799B (en)
PL (1) PL71765B1 (en)
SE (1) SE359892B (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3692439A (en) * 1971-02-03 1972-09-19 George V Woodling Fluid pressure responsive mechanism in a fluid pressure device
US3915603A (en) * 1973-05-03 1975-10-28 Eaton Corp Radial balancing means with sealing vanes for a hydraulic device
US3917437A (en) * 1974-03-18 1975-11-04 Edwin A Link Seal for a rotary piston device
WO2001046560A1 (en) * 1999-12-20 2001-06-28 Sauer-Danfoss Holding A/S Hydraulic machine
US20060140811A1 (en) * 2003-07-14 2006-06-29 Josef Bachmann Gear pump having optimal axial play
US20080145259A1 (en) * 2006-12-18 2008-06-19 Hitachi, Ltd. Oil Pump and Method of Assembling the Oil Pump

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2221183C2 (en) * 1972-04-29 1982-12-30 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen, De
WO1982000172A1 (en) * 1980-07-08 1982-01-21 Erasov F Planetary hydromotor
DE19961400C2 (en) * 1999-12-20 2001-11-08 Sauer Danfoss Nordborg As Nord Hydraulic machine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1471761A (en) * 1922-02-04 1923-10-23 Herman A Weidenbach Rotary pump
US1997184A (en) * 1935-04-09 Rotary engine
US3289602A (en) * 1965-09-03 1966-12-06 Trw Inc Fluid pressure device
US3452680A (en) * 1967-08-11 1969-07-01 Trw Inc Hydraulic motor-pump assembly
US3460481A (en) * 1967-09-27 1969-08-12 Trw Inc Rotor-stator gear set in a hydraulic motor-pump device
US3516765A (en) * 1966-01-26 1970-06-23 Bendix Corp Fluid actuated actuator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1997184A (en) * 1935-04-09 Rotary engine
US1471761A (en) * 1922-02-04 1923-10-23 Herman A Weidenbach Rotary pump
US3289602A (en) * 1965-09-03 1966-12-06 Trw Inc Fluid pressure device
US3516765A (en) * 1966-01-26 1970-06-23 Bendix Corp Fluid actuated actuator
US3452680A (en) * 1967-08-11 1969-07-01 Trw Inc Hydraulic motor-pump assembly
US3460481A (en) * 1967-09-27 1969-08-12 Trw Inc Rotor-stator gear set in a hydraulic motor-pump device

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3692439A (en) * 1971-02-03 1972-09-19 George V Woodling Fluid pressure responsive mechanism in a fluid pressure device
US3915603A (en) * 1973-05-03 1975-10-28 Eaton Corp Radial balancing means with sealing vanes for a hydraulic device
US3917437A (en) * 1974-03-18 1975-11-04 Edwin A Link Seal for a rotary piston device
WO2001046560A1 (en) * 1999-12-20 2001-06-28 Sauer-Danfoss Holding A/S Hydraulic machine
US6619937B2 (en) 1999-12-20 2003-09-16 Sauer-Danfoss Holding A/S Hydraulic machine
US20060140811A1 (en) * 2003-07-14 2006-06-29 Josef Bachmann Gear pump having optimal axial play
US7713041B2 (en) * 2003-07-14 2010-05-11 Gkn Sinter Metals Holding Gmbh Gear pump having optimal axial play
US20100239449A1 (en) * 2003-07-14 2010-09-23 Gkn Sinter Metals Holding Gmbh Gear Pump Having Optimal Axial Play
US7887309B2 (en) 2003-07-14 2011-02-15 Gkn Sinter Metals Holding Gmbh Gear pump having optimal axial play
US20080145259A1 (en) * 2006-12-18 2008-06-19 Hitachi, Ltd. Oil Pump and Method of Assembling the Oil Pump
US7959422B2 (en) * 2006-12-18 2011-06-14 Hitachi, Ltd. Oil pump and method of assembling the oil pump

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PL71765B1 (en) 1974-06-29
FR2052479A5 (en) 1971-04-09
CA923761A1 (en)
CH499718A (en) 1970-11-30
ES380351A1 (en) 1973-04-16
GB1301528A (en) 1972-12-29
DK134078B (en) 1976-09-06
CS149702B2 (en) 1973-07-25
CA923761A (en) 1973-04-03
SE359892B (en) 1973-09-10
DK134078C (en) 1977-02-07
DE1931143A1 (en) 1971-02-04
HU165799B (en) 1974-11-28

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