EP1090226A1 - Doppelpumpen-aggregat - Google Patents
Doppelpumpen-aggregatInfo
- Publication number
- EP1090226A1 EP1090226A1 EP99931129A EP99931129A EP1090226A1 EP 1090226 A1 EP1090226 A1 EP 1090226A1 EP 99931129 A EP99931129 A EP 99931129A EP 99931129 A EP99931129 A EP 99931129A EP 1090226 A1 EP1090226 A1 EP 1090226A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- intermediate element
- connection
- pump unit
- main body
- plates
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2064—Housings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
Definitions
- the invention relates to a double pump unit for connecting two hydraulic pumps.
- the hydraulic pumps work either as so-called tandem pumps with the same delivery volume or as so-called contact pumps with different delivery volumes.
- a double pump unit according to the preamble of claim 1 is known from DE 195 36 997 Cl.
- two drive shafts of two hydraulic pumps arranged coaxially to one another are non-positively coupled to one another by means of a coupling.
- High-pressure lines and low-pressure lines are formed in a connecting piece surrounding the coupling piece in order to supply the cylinders of the hydraulic pumps with the high pressure and the low pressure cyclically via a respective control body.
- this publication shows the integration of a charge pump in the connecting piece in order to achieve increased pre-compression in the low-pressure line.
- the invention is therefore based on the object of providing a double pump unit which, based on a basic construction, can be easily adapted to different configurations.
- the invention is based on the finding that by subdividing the connecting piece m two connecting plates constructed in the same way for all configurations, and m an intermediate element arranged between the connecting plates, which can be exchanged and individually configured, for all configurations on — the same basic elements in each case can be used.
- the connection plates each have a cutout m in which the respective intermediate element can at least partially be used, so that the connection plates radially encompass the intermediate element at least partially and thus the intermediate element is fixed between the connection plates.
- there is a radial centering of the connection plates which is mediated by the intermediate element.
- the radial centering of the connection plates is essential for the exact coaxial alignment of the drive shafts of the hydraulic pumps.
- the intermediate element can be designed, for example, in a simple manner as a disk-shaped cylinder body.
- the cutouts in the connection plates are also cylindrical and correspond in diameter to the diameter of the intermediate element.
- connection plates can be screwed together in a radially outer area.
- the intermediate element can have at least one ring channel in order to enable different arrangements of the individual connections.
- a charge pump for example in the form of a gear pump, can be integrated in the intermediate piece.
- the intermediate element is divided into a main body and an insert body which is inserted in a recess in the main body and receives the charge pump.
- the main body forms a first axial projection and the insert body forms a second axial projection, each of which engages in a recess in the two connection plates.
- the cutouts of the connection plate and the main body are cylindrical in shape and each have the same diameter.
- a low-pressure connection and a connection from the charge pump to a first ring channel adjoining one of the connection plates are integrated in the main body.
- a connection from the charge pump to a second ring channel adjoining the other connection plate is integrated in the insert body.
- the ring channels ensure a flexible connection to the low pressure connections in the adjacent connection plates.
- FIG. 1 shows an axial section through an embodiment of a double pump unit according to the invention in a first configuration
- Fig. 2 shows an axial section through an embodiment of the double pump unit according to the invention in a second configuration.
- Fig. 1 shows an embodiment of the double pump unit 1 according to the invention in an axial longitudinal section. A first configuration of this double pump unit 1 is shown.
- the double pump unit consists of two hydraulic pumps 2 and 3, which are designed in the embodiment shown in swash plate construction.
- the hydraulic pumps 2 and 3 each have a drive shaft 4 and 5 which are aligned coaxially with one another.
- the drive shaft 4 of the hydraulic pump 2 on the left in FIG. 1 is extended with a drive pin 6 out of the housing 7 in order to enable the two hydraulic pumps 2 and 3 to be driven together.
- the drive shafts 4 and 5 are even closer via a first roller bearing 8 or 9 in the housing 7 or 10 of the respective hydraulic pump 2 or 3 and via a second roller bearing 11 or 12 in a first connection plate 13 or a second connection plate 14 to be described connector 15 bearings.
- the pistons 20 and 21 are supported by sliding shoes 22 and 23 on a swash plate serving pivoting cradle 24 or 25, which is pivotally mounted in the housing 7 or 10.
- An adjusting device 26 or 27 is used to adjust the pivoting cradle 24 or 25. By pivoting the pivoting cradle 24 or 25, the stroke of the pistons 20 or 21 and thus the delivery volume of the hydraulic pump 2 or 3 can be adjusted.
- a coupling piece 28 is used to connect the two drive shafts 4 and 5 of the hydraulic pumps 2 and 3, which is non-positively connected to the shafts 4 and 5, for example via a key-and-groove connection. Therefore, not only the drive shaft 4 of the first hydraulic pump 2 is driven via the drive pin 6, but also the drive shaft 5 of the second hydraulic pump 3 via the coupling piece 28.
- High pressure lines 29 and 30 and low pressure lines 31 and 32 are integrated in the connection plates 13 and 14.
- the cylinders 18 and 19 are connected cyclically to the respective high-pressure line 29 and 30 and the respective low-pressure line 31 and 32 via control bodies 33 and 43 adjoining the associated connecting plate 13 and 14, respectively, with each revolution of the cylinder drum 16 or 17.
- the line 31 or 32 can also carry high pressure and the line 29 or 30 low pressure.
- the first connection plate 13 has a cutout 34 and the second connection plate 14 has a cutout 35, into which an intermediate element 38 can be inserted.
- the intermediate element 38 is sealed by means of seals 36 and 37.
- the intermediate element 38 is designed as a disk-shaped cylinder body and is completely accommodated by the two cutouts 34 and 35 of the connecting plates 13 and 14, which are also cylindrical.
- the connection plates 13 and 14 enclose the intermediate element 38 radially, so that the intermediate element 38 is fixed between the connection plates 13 and 14.
- the connection plates 13 and 14 are in a region radially surrounding the intermediate element 38 39 or 40 are screwed together by preferably a plurality of screws 41 arranged around the circumference.
- the intermediate element 38 can be replaced after loosening the screws 41.
- the intermediate element 38 can be individually designed in accordance with the requirements of the special hydraulic pump unit 1. In the configuration shown in Fig. 1, the intermediate element 38 is particularly simple and therefore inexpensive to manufacture. This configuration of the intermediate element 38 allows a simple mechanical and hydraulic connection of the two hydraulic pumps 2 and 3, in particular in those cases in which no charge pump is required to increase the charge pressure.
- the connecting plates 13 and 14 are centered on each other by the intermediate piece 38, so that there is an exact coaxial alignment of the drive shafts 4 and 5.
- the intermediate element 38 is provided with an annular channel 42.
- the intermediate element 38 serves at the same time to supply the two hydraulic pumps 2 and 3 with the low pressure.
- the connection between the low-pressure connections 31 and 32 with the annular channel 42 supplying the low-pressure can be made at any point, so that a high flexibility in the arrangement of the connections is ensured.
- connection plates 13 and 14 of the two hydraulic pumps 2 and 3 are preferably identical and can also be mounted rotated through 180 ° on the housings 7 and 10 of the hydraulic pumps 2 and 3. There is thus the possibility that the high-pressure lines 29 and 30 and low-pressure lines 31 and 32 are interchanged by rotating the connecting plates 13 and 14. This installation flexibility is particularly important if the connection plates 13 and 14 are designed for different flow directions. It should be emphasized that this flexibility with the connectors known from the prior art, in which the Terminal plates 13 and 14 are integrally connected to each other, does not exist in principle.
- connection plates 13 and 14 in particular pressure relief valves for high-pressure protection, or control valves can also be integrated.
- FIG. 2 shows the exemplary embodiment already described with reference to FIG. 1 in an axial longitudinal section corresponding to a second configuration of the connecting piece 15.
- the connecting piece 15 consists of the connection plates 13 and 14 which have not been changed from the configuration shown in FIG. 1 and an intermediate element 38 which is configured differently from FIG. 1.
- the intermediate element 38 consists a main body 50, an insert body 52 inserted into a cutout 51 of the main body 50 and a charge pump 54 inserted into a cutout 53 of the insert body 52.
- the charge pump 54 is designed as a gear pump in a crescent moon design. However, it can also be thought of training with paddle wheels or in the manner of a turbine.
- an axial projection 55 is provided, which in the exemplary embodiment is designed with a cylindrical outer contour and engages in the recess 35 of the connecting plate 14, which is likewise cylindrical in the exemplary embodiment.
- the insert body 52 protrudes axially from the main body 50.
- the section of the insert body 52 protruding from the main body 50 forms a second axial projection 53 which engages in the recess 34 of the connecting plate 13.
- the cutout 34 of the connecting plate 14 is also cylindrical, the cutouts 34, 51 and 35 preferably having the same diameter.
- the connection plates 13 and 14 therefore radially partially encompass the intermediate element 38 and the intermediate element 38 is fixed between the connection plates 13 and 14.
- the different configurations of the double pump unit 1 do not require any adjustments to the connection plates 13 and 14 and the individual construction is limited to a special configuration of the intermediate element 38.
- An already installed double pump unit 1 can therefore be easily converted after loosening the screw connection 41.
- the cost of manufacturing and storing the components is extremely low, since most components can be used uniformly for all configurations.
- a low-pressure connection 56 is integrated on the main body 50 and is connected to the charge pump 54. Furthermore, a connection 57 from the charge pump 54 to a first ring channel 57 adjoining the connecting plate 14 is provided in the main body 50. A connection 58 is provided in the insert body 52 from the charge pump 54 to a second annular channel 59 adjoining the connection plate 13.
- the ring channels 57 and 59 have the advantage that the connection to the respective low-pressure line 31 or 32 can be made at a suitable point.
- connection plates 13 and 14 and the main body 50 of the intermediate element 38 are screwed to one another by means of screws 41 in an area radially surrounding the insert body 52.
- the intermediate piece 38 takes over both the function of the centering and the function of the integration of the charge pump 54.
- a complex piping to connect the two hydraulic pumps 2 and 3 to the charge pump 54 is not necessary.
- the charge pump 54 can also be rotated through 180 ° be installed if the drive shafts 4 and 5 are driven in the opposite direction of rotation.
- the invention is not limited to the exemplary embodiment shown.
- other charge pumps can also be used or additional functions can be integrated on the intermediate element 38.
- control valves, pressure relief valves and other hydraulic components can also be arranged in the intermediate element 38.
- the configuration according to the invention allows a connection of two hydraulic pumps 2 and 3 that is optimized in terms of cost and overall length.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19828180 | 1998-06-24 | ||
DE19828180A DE19828180C2 (de) | 1998-06-24 | 1998-06-24 | Doppelpumpen-Aggregat |
PCT/EP1999/004303 WO1999067532A1 (de) | 1998-06-24 | 1999-06-22 | Doppelpumpen-aggregat |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1090226A1 true EP1090226A1 (de) | 2001-04-11 |
EP1090226B1 EP1090226B1 (de) | 2003-03-05 |
Family
ID=7871895
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99931129A Expired - Lifetime EP1090226B1 (de) | 1998-06-24 | 1999-06-22 | Doppelpumpen-aggregat |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1090226B1 (de) |
DE (2) | DE19828180C2 (de) |
WO (1) | WO1999067532A1 (de) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10021485B4 (de) | 2000-05-03 | 2006-03-23 | Brueninghaus Hydromatik Gmbh | Hydrostatische Maschine |
DE20018570U1 (de) * | 2000-10-30 | 2002-03-21 | Liebherr Machines Bulle S A | Hydrostatische Doppelaxialkolbenpumpe |
US6705840B1 (en) | 2002-06-19 | 2004-03-16 | Hydro-Gear Limited Partnership | Inline tandem pump |
US6953327B1 (en) | 2003-03-11 | 2005-10-11 | Hydro-Gear Limited Partnership | Dual pump |
US6973783B1 (en) | 2004-02-27 | 2005-12-13 | Hydro-Gear Limited Partnership | Zero turn drive apparatus |
US7137250B1 (en) | 2004-03-08 | 2006-11-21 | Hydro-Gear Limited Partnership | Zero turn drive apparatus with power take off |
US7377105B1 (en) | 2004-11-12 | 2008-05-27 | Hydro-Gear Limited Partnership | Dual pump assembly |
US7162870B1 (en) | 2004-11-12 | 2007-01-16 | Hydro-Gear Limited Partnership | Pump assembly |
US7347047B1 (en) | 2004-11-12 | 2008-03-25 | Hydro-Gear Limited Partnership | Pump assembly |
EP1748189B1 (de) | 2005-07-27 | 2012-09-26 | Poclain Hydraulics | Tandem-Axialkolbenpumpe |
US7726126B1 (en) | 2005-12-21 | 2010-06-01 | Hydro-Gear Limited Partnership | Dual pump apparatus with power take off |
DE202006005682U1 (de) | 2006-04-05 | 2006-06-14 | Lincoln Gmbh & Co. Kg | Schmiermittel- oder Hydraulikpumpe |
US9010105B1 (en) | 2007-08-01 | 2015-04-21 | Hydro-Gear Limited Partnership | Transmission and engine configuration |
RU194266U1 (ru) * | 2019-09-27 | 2019-12-04 | федеральное государственное бюджетное образовательное учреждение высшего образования "Иркутский национальный исследовательский технический университет" (ФГБОУ ВО "ИРНИТУ") | Аксиально-поршневая гидромашина |
JP7285768B2 (ja) * | 2019-12-16 | 2023-06-02 | 株式会社クボタ | ハウジング構造 |
US20230358220A1 (en) * | 2022-05-04 | 2023-11-09 | Caterpillar Inc. | Pump having a flange for mounting an auxiliary pump |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1937347A1 (de) * | 1969-07-23 | 1971-02-04 | Bosch Gmbh Robert | Hydroaggregat |
DE2332584A1 (de) * | 1973-06-27 | 1975-01-09 | Johannes Neukirch | Axialkolbenpumpe oder -motor |
DE2652231C2 (de) * | 1976-11-16 | 1983-10-13 | Linde Ag, 6200 Wiesbaden | Axialkolbenmaschine |
DE3324583A1 (de) * | 1982-07-07 | 1984-01-12 | Linde Ag, 6200 Wiesbaden | Zweimaschinen-aggregat mit anschluss fuer einen weiteren verbraucher mechanischer energie |
JPS5920576A (ja) * | 1982-07-26 | 1984-02-02 | Ebara Corp | 可変容量形アキシヤルピストン機械の容量制御機構 |
DE3238362A1 (de) * | 1982-10-15 | 1984-04-19 | Linde Ag, 6200 Wiesbaden | Axialkolbenmaschine |
DE3716374C2 (de) * | 1987-05-15 | 1995-02-23 | Linde Ag | Aggregat aus einer Primärenergiequelle und mehreren, an diese angeflanschten Axialkolbenpumpen |
DE4225380B4 (de) * | 1992-07-31 | 2004-07-15 | Linde Ag | Hydrostatisches Aggregat mit einer Hauptpumpe und einer Nebenpumpe |
DE19536997C1 (de) * | 1995-10-04 | 1997-02-20 | Brueninghaus Hydromatik Gmbh | Doppelpumpe mit Ladepumpe |
-
1998
- 1998-06-24 DE DE19828180A patent/DE19828180C2/de not_active Expired - Fee Related
-
1999
- 1999-06-22 WO PCT/EP1999/004303 patent/WO1999067532A1/de active IP Right Grant
- 1999-06-22 DE DE59904464T patent/DE59904464D1/de not_active Expired - Lifetime
- 1999-06-22 EP EP99931129A patent/EP1090226B1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9967532A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE19828180C2 (de) | 2000-04-20 |
EP1090226B1 (de) | 2003-03-05 |
WO1999067532A1 (de) | 1999-12-29 |
DE19828180A1 (de) | 2000-01-13 |
DE59904464D1 (de) | 2003-04-10 |
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