US3681919A - Hydrostatic-machine system - Google Patents

Hydrostatic-machine system Download PDF

Info

Publication number
US3681919A
US3681919A US84766A US3681919DA US3681919A US 3681919 A US3681919 A US 3681919A US 84766 A US84766 A US 84766A US 3681919D A US3681919D A US 3681919DA US 3681919 A US3681919 A US 3681919A
Authority
US
United States
Prior art keywords
hydrostatic
machines
flanges
assembly defined
recesses
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.)
Expired - Lifetime
Application number
US84766A
Other languages
English (en)
Inventor
Franz Forster
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Linde GmbH
Original Assignee
Linde GmbH
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
Application filed by Linde GmbH filed Critical Linde GmbH
Application granted granted Critical
Publication of US3681919A publication Critical patent/US3681919A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/033—Series gearboxes, e.g. gearboxes based on the same design being available in different sizes or gearboxes using a combination of several standardised units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0091—Casings, housings

Definitions

  • rrvnnosmnc-mcmm SYSTEM FIELD OF THE INVENTION BACKGROUND OF THE lNVENI'ION
  • a hydraulic pump may be driven by a prime mover or some other source of motive power and may have its output and input sides connected by a suitable conduit network to one or more hydraulic motors, with or without the intervention of control means in the form of valves.
  • the motor may have an output element which is connected with a load.
  • hydrostatic pump and hydrostatic motor are connected in a closed fluid circuit so that the rate of operation of the pump influences the operating parameters of the motor.
  • Such systems are used for the transmission of force with or without alteration in the transmission ratio and the motor and pump are commonly of the axial-piston type.
  • the pump may have an input shaft which rotates a cylinder barrel or otherwise successively displaces a number of pistons extending parallel to one another and generally contained in the cylinder barrel mentioned earlier. On one side of the assembly, fluid is forced by the pistons to the discharge port while fluid enters at the other side of the assembly and is drawn into the individual cylinders.
  • the outlet or discharge port is connected to the intake port of the hydrostatic motor which similarly may have a cylinder barrel with a plurality of pistons bearing against a control surface.
  • Axial-piston pumps and motors have been described at pages 395 if. of SER- VOMECHANISM PRACTICE, McGraw-l-lill Book Company, New York, i960 and are conventional in the art (see FLUID POWER, US. Government Printing Office, [960,pages 109- l l2and l99ff.).
  • a rotary hydrostatic pump has an input shaft which may be driven while the hydrostatic motor has an output shaft which may drive a load so that a transmission ratio in terms of speed and torque may develop between the input and the output shafts.
  • hydrostatic pump with a hydrostatic motor in a cornmon installation, such systems being described generically as hydrostatic transmissions.
  • hydrostatic machine is intended to designate either a hydrostatic pump or a hydrostatic motor.
  • a hydrostatic pump can be used as a motor and vice versa.
  • flange is used herein to designate a housing surface which is generally planar and can be connected flat against a corresponding surface by bolts or the like, extending transversely to the interface between the machines.
  • the term is not to be considered as necessarily implying a member which projects from another although such projecting members are not excluded in the first instance.
  • An assembly according to the present invention can include a large pump to which a large motor is joined flange-to-flange, a large pump connected to one or more small motors at corresponding flanges, a pump connectedtootherpumps ofthesamesizeorofsmaller size, or several motors interconnected and tied to a single pump.
  • the terns large” and small” as used herein, together with similar references to size" are intended to designate not only differences in the external dimereions and total volume of the hydrostaticmachines, but also differences in capacity in terms of fluid displacement per rotation. More particularly, I may join a pump with a motor of the same capacity in terms of the stroke volume per revolution, or a motor of larger stroke volume per revolution or another pump, into a single compact assembly. It will be apparent, therefore, that further enclosures for the hydrostatic pump or hydrostatic motor or the assembly are not required, that pedestals and like mounting structures for the hydrostatic machines can be avoided and that the complex connections of prior-art structure can be eliminated.
  • the prismatic housing has a number of faces which lie parallel to or perpendicular to the axis of rotation of the shaft of the machine and which are formed with respective connecting flanges, all of which may be identical.
  • Those flanges which are not employed for connection to another rotary hydrostatic machine may have an annular recess into which the cover plate fits so that the exterior of the assembly is flush.
  • a pump may, for example, be connected selectively with one motor or two motors, or two, three or more pumps may selectively be connected together in a single assembly.
  • three or more hydrostatic machines are connected together linearly.
  • the external configuration of the hydrostatic machine housing is a parallelopiped, preferably a rectangular parallelopiped with square sides, i.e., of generally cubic configuration.
  • five connecting flanges may be provided for the machines, the remaining surface serving to clear the shaft.
  • this surface is formed as a connecting flange according to the principles of the present invention, although it generally will be used to connect the pump to a driving source or a motor to the driven structure.
  • the flanges lie in planes parallel to the axis of rotation of the shaft or perpendicular thereto, each flange lying approximately at right angles to an adjoining flange of the machine. It is possible, however, to provide one or more flanges of a construction or configuration different from that of the connecting flange for accommodating,for instance, control or regulating devices designed to be mounted upon the housing. To this end, the flanges for the connection of control or regulating devices can be relatively small flanges while the main connecting flanges are geometrically similar but larger.
  • Geometrically identical flanges are preferably provided parallel to one another on opposite sides of the machine so that, for example, the larger flanges lie in a row to enable the machines to be interconnected in a row while the flanges to which the control members are affixed lie perpendicular to these main connecting flanges. It has also been found to be desirable, in some cases, to provide flanges which lie at an angle of, say, 45 to other flanges, thereby permitting other possibilities of connecting the several machines.
  • fluid ports may be provided for communication upon connection with another machine, thereby eliminating the need for ducts.
  • connections may be made between the port flanges by pipes, ducts or the like, terminating in flange covers by which such ducts are bolted to each machine.
  • a cubic configuration of the housing it is possible to provide a flange at the end of the machine opposite the driving side which is of a configuration identical to that of the lateral flanges, thereby enabling several machines to be connected in tandem.
  • the shaft of a hydrostatic pump may be inserted into a socket of another hydrostatic machine to which it is bolted so that rotation of the shah of this other machine also drives the shaft of the first-mentioned machine.
  • Still another feature of the present invention resides in the provision of mating centering means on the interconnectable flanges, e.g., in the form of an annular recess of each flange into which a ring may be fitted, for proper positioning of the interconnected machines. It is also conceivable to provide a mating centering arrangement whereby a circular ridge is permanently formed in one connecting flange and is receivable in a circular recess in the other.
  • the centering means should also be identical to the centering system provided for the regulating mechanism which may be attached elsewhere upon the housing.
  • I provide a plurality of bores traversable by bolts and extending through the housing while temrinating at the opposite flanges externally of the aforementioned circular recess.
  • These holes may be located at the vertices of a square i.e., along orthogonal diameters or diagonals of the connecting flange. Threaded bores may be provided along these diagonals within the circular recess to accommodate screws for attaching the cover plates for control mechanisms.
  • the screws traversing the cover plates may be countersunk therein to maintain a flush surface and the floor of the recess may lie in a plane parallel to the plane of the external surface of the flange to form the smaller connecting surface for the control mechanisms.
  • the flanges or one of them may be used for fastening the transmission upon a frame or other support, e.g., the housing of the driven machine or the machine to be driven.
  • FIG. 1 is a perspective view of a hydrostatic machine embodying the invention
  • FIG. 2 is an elevational view showing this machine connected with a machine of similar size to form a double-pump assembly according to the invention
  • FIG. 3 is a view similar to FIG. 2 showing an assembly in which the pumps are of different size
  • FIG. 4 is an elevational view of the principles of the present invention as applied to a hydrostatic transmission in which the pump and motor are of the same size;
  • FIG. 5 is an elevational view showing a similar transmission but with hydrostatic pump and motor of different sizes
  • FIG. 6 is an elevational view of a transmission wherein the input and output shafts of the interconnected hydrostatic machines lie in a Z-configuration;
  • FIG. 7 is an elevational view showing a hydrostatic transmission with two output shafts lying at right angles to the input shafts;
  • FIG. 8 is an elevational view of a similar transmission wherein, however, the hydrostatic pump and motors are of the same capacity
  • FIG. 9 is an elevational view of a right-angle transmission according to the present invention.
  • FIG. 10 is an elevational view of a Z-type transmission according to another embodiment of the invention.
  • FIG. 11 is an end view of the transmission showing how some of the connecting flanges may lie in an angle of 45 with respect to other flanges;
  • FIG. 12 is a diagrammatic elevational view, partly in section, of a hydrostatic pump according to the invention.
  • FIG. 13 is a detail view showing the connection of two hydrostatic machines at the connecting flanges.
  • FIGS. 14 16 are detail views illustrating another aspect of the invention.
  • FIG. 1 I have shown a hydrostatic machine having a cubic housing I with surfaces 8 S, and S constituting connecting faces and formed with connecting flanges 2 of circular configuration.
  • the unused flanges 2 are closed by circular cover plate 3.
  • a circular ring may be inserted into the recess fonned by the connecting flange 2 or the latter may be provided with a ridge protruding beyond the face of the connected surface.
  • the surfaces 8,, S and 8,, respectively opposite the surfaces S through 8; may, except for surface 5., be identical to the parallel faces.
  • the faces are of identical dimensions, i.e., each is a square with length and height equal to those of the other surfaces.
  • openings or bores 20 which lie along orthogonal diameters of the circular recess 2 and along diagonals of the respective surfaces.
  • the bores 20 are throughgoing, i.e., extend between and terminate at the opposite surfaces S and S S and S and S and S and S Hence, tie bolts 8 can be inserted through aligned bores 20 or an assembly of such machines to hold them together as illustrated in FIG. 1.
  • the flange 2 is formed with a surface bounded by an inner circular wall 2b, the surface 2a lying in a plane close to and parallel to the surface S S in which it is formed.
  • Several or all of the lateral flanges S S S and S may be provided with bores 16, forming a port for the flow of hydraulic fluid to the machine (intake port) or for the flow of fluid out of the machine (discharge port).
  • the plate 3 may be formed with countersinks 23 into which the bolts 22 are recessed so that the exterior of the assembly remains flat even when the cover plates are in place.
  • the cover plates may block the ports 16 as required.
  • FIG. 2 I have shown an assembly of two hydrostatic pumps 5 and 6, both of which may be identical to that illustrated in FIG. 1.
  • the shaft 4 of hydrostatic machine 5 extends through the housing and is formed with an internally splined socket 7 communicating with an opening in the rear flange 5a which is exposed when the corresponding cover plate is removed.
  • the splined shaft 4a of the hydrostatic machine 6 is matingly received in the socket 7 so that both pumps are operated together.
  • the hydrostatic machines 5 and 6, therefore, form a double-pump assembly and can also be constituted as a high-pressure distributor for the hydraulic medium.
  • Tie bolts 8 are threaded through the aligned bores 20 (FIG.
  • the machine 6 of course, has the same overall dimensions as the machine 5 and the resulting aggregate has a length twice that of each machine and a width and height equal to that of the individual machines.
  • the lateral face 6b of the pump 6 has its flange closed by a plate 30 affixed to screws 22 which may be countersunk therein as previously noted.
  • the plate 3a is formed with a conduit 12 which thereby registers with the port 16 to provide fluid communication to and from the pump.
  • the port 16 of the flange 2 of face 5b of machine 5 is shown to be exposed.
  • FIG. 3 Another double-pump aggregate has been illustrated in FIG. 3 wherein, however, the large-capacity pump 5 is affixed to a small-capacity pump 9 by tie bolts 10 which are threaded into the bores 21 on the rear flange 5a of the large pump 5.
  • the shaft of pump 9 is received in the socket 7 of pump 5 as previously described.
  • the flanges 9a of the pump 9 are shown to be square but of a geometrically similar configuration to the flanges 5a and 5b of the pump 5.
  • the throughgoing bores 20a of these flanges are shown to be located at the vertices of a square of the same dimensions as the square at the comers of which lie the bores 20 of the large pump 5.
  • flanges 9a, 5a and 5b are geometrically similar, complementary and can be joined in a building-block construction.
  • An inner flange 2d in the form of a recess may be provided as described for the larger hydrostatic machine and may be covered by an appropriate plate affixed by bolts 220 as shown in FIG. 3.
  • the pump 5 is shown to be affixed to a hydrostatic motor of similar dimensions as represented at 11 by tie bolts 8, the motor shaft being aligned with the shaft 4 of the pump.
  • the combination of pump and hydrostatic rnotor constitutes an in-line" hydrostatic transmission.
  • the hydraulic connections are provided by conduits 12 on opposite lateral sides of the transmission, terminating in cover plates 13 which are seated in the flange recesses 2 of the hydrostatic pump and motor and are secured by screws 22.
  • a similar in-line transmission is provided in FIG. 5 wherein a smallcapacity hydrostatic motor is connected to the hydrostatic pump 5 by bolts 10 threaded into bores 21 in the rear face 50 of this pump.
  • the output shaft 15 of the transmission is aligned with the input shafi 4 of the pump.
  • hydraulic communication is provided by means of ducts 12a.
  • One end of each duct 12a is fixed in a cover plate 13 received in the flange recess 2 and held in place by screws 22 while the other end of the duct is fixed at its elbow to a geometrically similar cover plate 13a received in a flange recess 2d of the smaller motor 14 and held in place by screws 224 as described with reference to FIG. 3.
  • FIG. 6 illustrates another compact transmission according to the invention wherein the hydrostatic pump 5 is connected at one of its lateral flanges 5c with the lateral flange 11b of a hydrostatic motor I l of identical dimensions.
  • the transmission is of the Z-drive type wherein the input shaft 4 to the pump and the output shaft 110 of the motor are parallel to one another but are offset by a center-to-center distance equal to the width W of one of the hydrostatic machines.
  • the overall width S of the assembly is 2W while the length" of the compact housing structure is represented at L and is, of course, equal to W.
  • the tie bolts 8, in this embodiment, traverse the bores 20 which run transversely to the shafts.
  • a duct 12 aflixed to plates 13 serves to make hydraulic connection between the two hydrostatic machines.
  • FIGS. 7 and 8 illustrate embodiments of hydrostatic transmissions in the form of a drive axle of a motor vehicle.
  • the large-capacity pump is driven at its shafi 4 by the internal combustion engine of the vehicle and, in turn, has its hydraulic output connected by a plate 13b and a line 12d to a duct l2e running symmetrically to opposite sides of the pump and communicating via plates 13a with a pair of hydrostatic motors 14, the output shafts 15 of which reach to opposite sides of the vehicle and are connected to the vehicle wheels.
  • Bolts 10 secure the small-capacity hydrostatic motors to the lateral flanges of the pump at the bores 21 thereof.
  • the hydraulic fluid return, on the opposite side of the transmission, not illustrated, can be similar to that shown at 12d and 12s.
  • the stroke volume per revolution of the motors 14 may collectively be equal to that of the pump.
  • the arrangement of FIG. 8, however, provides a pair of hydrostatic motors 11, each of which has a stroke volume per revolution equal to that of the pump.
  • the tie bolts 8a are here used to hold the assembly together and have a length at least equal to 3W
  • I have shown an L-drive or right-angle transmission wherein the hydrostatic motor 14 is affixed to one lateral side of the pump 5 by the bolts mentioned previously.
  • the system of FIG. 9 is constructed with the same elements as that of FIG. 5, but whereas the input and output shafts of the latter are coaxial, the coplanar shafls 4 and lie at right angles to one another. In all of the embodiments previously described, unused flange recesses 2 are closed by plates 3.
  • FIG. 10 I have shown a Z-drive of the type described in connection with FIG. 6 but wherein the flanges 30 and 31 of the hydrostatic pump 32 and the hydrostatic motor 33, opposite the respective shafts 34 and 35, are provided with control devices 23 and 36 for varying the displacement of the respective hydrostatic machines.
  • the bolts 22 secure these control devices within the recesses 2 of the respective flanges and are threaded into the bores 21 thereof.
  • FIG. 11 A modification of the invention is illustrated in FIG. 11 wherein the hydrostatic pump 40 has flanges 41 and 42 inclined at angles 3 of 45 to the flanges 43 and 44 and carrying hydrostatic motors 11 as previously described.
  • the conduits 45 and 46 are attached via plates of the type shown at 13 to the remaining lateral flanges of the pump 40 and to the intake and discharge ports ofthe motor 11.
  • the hydrostatic rrmchine illustrated in FIG. 12 is seen to have a housing 51 of prismatic configuration provided at its lateral faces with connecting flanges as described.
  • the shaft 52 drives a cylinder barrel 53 whose pistons 54 ride against a control plate 55 which is inclined to the axis of the shaft 52 at an angle variable by a control device 23 or 36 not illustrated.
  • the discharge and intake ports 56 and 57 of the barrel communicate via a control plate 58 and suitable pipes with the ports 16 previously described.
  • FIG. 13 I have shown an embodiment of the flange coupling of two hydrostatic machines represented generally at 60 and 61. It can be seen that the juxtaposed faces 62 and 63 of the flanges lie in planes P and Pg which are parallel to and close to the planes P and P of the circular recesses 64 and 65 formed in the faces 62 and 63. To center the machines with respect to one another, I prefer to use a ring 66 having a cylindrical outer surface 67 which snugly fits against the inner wall 68 of the recess 65 and is received within the recess 64. The axial height H of this ring is equal at least to twice the depth d of the recesses. The bolts 8 pass through both machines as previously described.
  • I may provide the small-capacity unit with a ridge which is received in the recess of the large-capacity unit in place of the ring 67.
  • the plate 70 is here shown to lie flush with the surface 63 when the flange of the machine 61 is to be closed and is held in place by the screws 71 which are wholly received in countersinks 72 of the plate.
  • FIGS. 15 and 16 I have shown an arrangement wherein the principles of the present invention are applied to the interconnection of machines of different sizes, using a coaxial flange connection.
  • the large machine 101 is provided at its connecting flanges with coaxial circular recesses 102 and 202 of large and small diameter, respectively. Any number of such recesses can be provided in steps, depending upon the standard sizes chosen.
  • the small machine 103 has a recess I04 corresponding to the step 202 and may also be stepped if smaller units are to be accommodated.
  • a connecting ring is received in the smaller step 202 and in the step 104 of the two machines and both may be bolted together, e.g., as shown in FIG. 14 or via bolts.
  • each flat face or flange has a recess and the recesses of equal diameter are connected by a ring which projects axially and coaxially from one flange into the other, the faces being substantially flush with one another as already described.
  • the coaxial connection is formed by an adapter ring 303 of stepped profile.
  • the large diameter step is snugly received in the large-diameter recess 302 of the larger machine while the smaller step projects axially from the flange face of the larger machine and is received in the smaller diameter coaxial recess 304 of the smaller machine.
  • each of the flanges may be formed with stepped recesses and the rings may be cylindrical, i.e., unstepped.
  • a hydrostatic assembly comprising at least two piston-stroke hydrostatic machines, each having a respective shaft rotatable independently of the slmft of the other machine, each of said hydrostatic machines being formed with a respective closed housing having generally planar sides and being closed at all sides to enable independent operation of each machine, the shaft of each of said machines projecting only through one side of the respective housing, means in other sides of each housing forming a fluid inlet and a fluid outlet for the respective machines, said sides of said housings defining geometrically similar confronting flanges, means for detachably securing said machines together with said housin in abutting relationship at said flanges, said flanges being constructed and arranged to enable hydrostatic machines of the same dimensions and configurations and hydrostatic machines of different dimensions and geometrically similar configurations to be affixed to either of the machines in the formation of the assembly, and removable conduit means attached to corresponding sides of said machines for interconnecting the inlets and outlets thereof.
  • each of said housings is prismatic, at least one of said machines being provided within the respective housing with means receiving the projecting shaft of the other machine for coupling of said shafts for joint rotation.
  • each of said machines has a plurality of geometrically identical flanges for interconnection of other machines thereto.
  • conduit means includes at least one plate received in one of said recesses and formed with a duct communicating with the port of the corresponding recess.
  • hydrostatic assembly defined in claim 8, further comprising means on at least one of said machines for securing a control device externally to the housing thereof.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Control Of Fluid Gearings (AREA)
  • Motor Power Transmission Devices (AREA)
US84766A 1969-10-30 1970-10-28 Hydrostatic-machine system Expired - Lifetime US3681919A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691954682 DE1954682A1 (de) 1969-10-30 1969-10-30 Hydrostatische Maschine

Publications (1)

Publication Number Publication Date
US3681919A true US3681919A (en) 1972-08-08

Family

ID=5749713

Family Applications (1)

Application Number Title Priority Date Filing Date
US84766A Expired - Lifetime US3681919A (en) 1969-10-30 1970-10-28 Hydrostatic-machine system

Country Status (4)

Country Link
US (1) US3681919A (es)
JP (1) JPS553544B1 (es)
DE (1) DE1954682A1 (es)
GB (1) GB1290248A (es)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4142452A (en) * 1976-05-10 1979-03-06 Linde Aktiengesellschaft Axial-piston machine with inclinable control surface
US4537562A (en) * 1982-01-05 1985-08-27 Malte Lindmark Pump
US4601643A (en) * 1982-01-29 1986-07-22 Aerzener Maschinenfabrik Gmbh Rotary compressor machines
US4671063A (en) * 1985-05-29 1987-06-09 Midwestern Reliable Equipment, Inc. Hydraulic intensifier
US4778349A (en) * 1985-11-15 1988-10-18 Browning Henry A Multiple machine drive shaft and coupling adapter assembly
US5974797A (en) * 1996-10-08 1999-11-02 Tokimec Inc. Hydraulic actuator package
EP1092091A1 (en) * 1998-05-29 2001-04-18 Dresser Equipment Group, Inc. Pumping system and method for multiple liquids
US20040175277A1 (en) * 2002-06-28 2004-09-09 Cox C. Paul Hydrostatic pump assembly having symmetrical endcap
US20120285150A1 (en) * 2010-11-30 2012-11-15 Mitsubishi Heavy Industries, Ltd. Power generating apparatus of renewable energy type
US20140271233A1 (en) * 2013-03-15 2014-09-18 Agilent Technologies, Inc. Modular pump platform
WO2020192964A1 (de) * 2019-03-26 2020-10-01 Sew-Eurodrive Gmbh & Co. Kg Getriebe und verfahren zum herstellen unterschiedlicher getriebe, insbesondere einer getriebebaureihe
US20230220912A1 (en) * 2020-06-19 2023-07-13 Flender Gmbh Scalable transmission housing, and housing series

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3265002D1 (en) * 1982-03-13 1985-09-05 Vickers Systems Gmbh Sliding vane pump, particularly for power steering
DE102011104015B4 (de) 2011-06-11 2021-12-30 Atlanta Antriebssysteme E. Seidenspinner Gmbh & Co. Kg Getriebe mit einer Ritzel-Lager-Einheit und Zahnstangenantrieb

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4142452A (en) * 1976-05-10 1979-03-06 Linde Aktiengesellschaft Axial-piston machine with inclinable control surface
US4537562A (en) * 1982-01-05 1985-08-27 Malte Lindmark Pump
US4601643A (en) * 1982-01-29 1986-07-22 Aerzener Maschinenfabrik Gmbh Rotary compressor machines
US4671063A (en) * 1985-05-29 1987-06-09 Midwestern Reliable Equipment, Inc. Hydraulic intensifier
US4778349A (en) * 1985-11-15 1988-10-18 Browning Henry A Multiple machine drive shaft and coupling adapter assembly
US5974797A (en) * 1996-10-08 1999-11-02 Tokimec Inc. Hydraulic actuator package
EP1092091A1 (en) * 1998-05-29 2001-04-18 Dresser Equipment Group, Inc. Pumping system and method for multiple liquids
EP1092091A4 (en) * 1998-05-29 2002-06-05 Dresser Equipment Group Inc PUMPING SYSTEM AND CORRESPONDING METHOD FOR PUMPING MULTIPLE LIQUIDS
US20040175277A1 (en) * 2002-06-28 2004-09-09 Cox C. Paul Hydrostatic pump assembly having symmetrical endcap
US20120285150A1 (en) * 2010-11-30 2012-11-15 Mitsubishi Heavy Industries, Ltd. Power generating apparatus of renewable energy type
US20140271233A1 (en) * 2013-03-15 2014-09-18 Agilent Technologies, Inc. Modular pump platform
US10473096B2 (en) * 2013-03-15 2019-11-12 Agilent Technologies, Inc. Modular pump platform
WO2020192964A1 (de) * 2019-03-26 2020-10-01 Sew-Eurodrive Gmbh & Co. Kg Getriebe und verfahren zum herstellen unterschiedlicher getriebe, insbesondere einer getriebebaureihe
US11746879B2 (en) 2019-03-26 2023-09-05 Sew-Eurodrive Gmbh & Co. Kg Transmission and method for producing different transmissions, in particular a range of transmissions
US20230220912A1 (en) * 2020-06-19 2023-07-13 Flender Gmbh Scalable transmission housing, and housing series

Also Published As

Publication number Publication date
DE1954682A1 (de) 1971-05-06
GB1290248A (es) 1972-09-20
JPS553544B1 (es) 1980-01-25

Similar Documents

Publication Publication Date Title
US3681919A (en) Hydrostatic-machine system
US5540563A (en) Unitary housing for double hydraulic unit
US3680312A (en) Hydrostatic machine
US3486335A (en) Common valve plate hydrostatic transmission
US4442865A (en) Mechanism for changing over fluid passages
US3332323A (en) Rotary actuator
US8104277B1 (en) Pump assembly
US7918088B1 (en) Dual pump assembly
US3165892A (en) Small car transmission
KR970703504A (ko) 연속적 변환이 가능한 유체정역학적 트랜스미션(continuously variable hydrostatic transmission)
US5378130A (en) Tandem type gear pump having an integral inner middle partition wall
US4092905A (en) Axial piston pump
US3158164A (en) Multiple block fluid distribution panel for mounting fluid control devices and method of directing fluid flow through the blocks
US5396768A (en) Gearless hydro-mechanical transmission
US3658452A (en) Gear pump or motor
US4195480A (en) Manifolded multiple hydraulic pump structure
US3830593A (en) Hydraulic pumps with double axial pistons
US4129192A (en) Hydrostatic transmissions
US3584985A (en) Hydrostatic control equipment particularly for steering systems
US5307731A (en) Housing system for hydraulic units
US2254274A (en) Metering device
US4747266A (en) Hydromotor
US3949824A (en) Drive arrangements for mechanical handling vehicles
US1502310A (en) Pump or motor
US3211107A (en) Hydraulic pump or motor