EP3737862B1 - Hydraulic machine, hydraulic assembly having the hydraulic machine, and hydraulic axle having the hydraulic machine - Google Patents

Hydraulic machine, hydraulic assembly having the hydraulic machine, and hydraulic axle having the hydraulic machine Download PDF

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Publication number
EP3737862B1
EP3737862B1 EP19700638.0A EP19700638A EP3737862B1 EP 3737862 B1 EP3737862 B1 EP 3737862B1 EP 19700638 A EP19700638 A EP 19700638A EP 3737862 B1 EP3737862 B1 EP 3737862B1
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EP
European Patent Office
Prior art keywords
hydraulic machine
hydraulic
rotation
axis
heat exchanger
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.)
Active
Application number
EP19700638.0A
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German (de)
French (fr)
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EP3737862A1 (en
Inventor
Andreas Guender
Jan Lukas Bierod
Johannes Schwacke
Saskia Ryznar
Oleg Stefanjuk
Marco Scholz
Emil Hanauer
Rene HUETTL
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3737862A1 publication Critical patent/EP3737862A1/en
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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
    • 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
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • 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
    • 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
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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
    • F04B1/2042—Valves

Definitions

  • the invention relates to a hydraulic machine according to the preamble of patent claim 1, a hydraulic unit with the hydraulic machine according to claim 11, and a hydraulic axle with the hydraulic machine according to claim 12.
  • the heart of a hydraulic circuit is a hydraulic machine, in particular a hydraulic pump. It is used to convert mechanical energy into hydraulic energy, in particular into hydrostatic energy, of a pressure medium conveyed by it. In the case of operation as a hydraulic motor, the conversion takes place in the opposite direction. During energy conversion, losses occur which, in the case of the hydraulic circuit, lead in particular to heating of the pressure medium. The loss occurring in the hydraulic machine or machines is responsible for the majority of the heating of the pressure medium, a much smaller part is caused by flow losses in lines. The heating of the pressure medium in the hydraulic pump is particularly great.
  • the thermal energy that occurs as a result of losses in the hydraulic pump is carried away by the pumped pressure medium into the hydraulic circuit until it is dissipated as heat to a coolant by means of an external heat exchanger.
  • the thermal energy is distributed over a large volume of oil, which means that a large amount of pressure medium has to be circulated in order to dissipate the heat.
  • Due to the large amount of pressure medium, however, a ⁇ T to the recooling coolant is comparatively small, so that the efficiency of the external heat exchanger is low and its heat exchange surface must be large, which keeps investment and operating costs high.
  • the cooling can be done, for example, by an external tube bundle or plate heat exchanger.
  • Coolant is water, for example.
  • both heat exchangers there is a risk of water entering the hydraulic oil, as the oil and cooling water sides are only separated by a seal in the case of the tube bundle heat exchanger and only by a thin layer of solder in the case of the plate heat exchanger. Both seals can fail due to operational wear and thus endanger the operational safety of the hydraulic machine and the components and processes it supplies through water ingress into the hydraulic oil.
  • the pamphlets DE 94 11163 U1 , JPH 08 22 64 12 and DE 27 03 686 each show a solution in which cooling takes place by flushing a housing interior of the hydraulic pump with pressure medium.
  • the pressure medium discharged from the hydraulic pump in this way is recooled with water in a separately arranged heat exchanger.
  • the amount of pressure medium to be circulated is large.
  • the quantity flushed out has to be continuously replenished, which entails expense in terms of device technology.
  • the pamphlet CN 106 224 228 shows a hydraulic pump whose housing is wrapped in a heat pipe. The heat is finally dissipated by re-cooling the heat pipe medium in a water bath.
  • a disadvantage of this solution is, for example, that the heat pipe is exposed to damage from impact due to its external exposure to the hydraulic pump.
  • the publication shows a related solution DE 10 2012 000 986 B3 , in which a cooling jacket for a hydraulic pump is proposed.
  • the disadvantage here is that such a cooling jacket design can take up a comparatively large amount of space.
  • the pamphlets DE 10 2011 054623 A1 and EP 3 168 470 A1 show hydraulic machines with a heat exchange device in a housing interior, the walls of which are disadvantageously complex and multi-part, consisting of components of the hydraulic machine such as sleeve, sealing sections, cylinder drum or drive shaft.
  • the invention is based on the object of creating a hydraulic machine with more efficient cooling, a hydraulic unit with the hydraulic machine and a hydraulic axis with the hydraulic machine.
  • the first task is solved by a hydraulic machine with the features of patent claim 1, the second by a hydraulic unit with the features of claim 11 and the last by a hydraulic axis with the features of claim 12.
  • a hydraulic machine has a housing interior and a group of hydrostatic working spaces mounted therein so that it can rotate about an axis of rotation. When the group rotates, these can be connected alternately to a high pressure and a low pressure of the hydraulic pump, in particular to a corresponding connection.
  • the pressure medium heats up.
  • the working spaces have a leakage volume flow into the interior of the housing.
  • a heat exchange device is accommodated in the interior of the housing for cooling. In particular, this comes into contact with the leakage volume or volume flow.
  • a wall of the heat exchange device is formed by a tube.
  • at least its course in the housing interior, cross section, wall thickness and/or material is designed at least as a function of the intended heat to be transferred and/or the intended temperature of the pressure medium.
  • the ⁇ T Due to the arrangement of the heat exchange device so close to the place where the pressure medium is heated, the ⁇ T is particularly high. A turbulent turbulence of a quantity of pressure medium present due to the leakage in the interior of the housing is also high due to the rotating work spaces. Just one of the two factors mentioned leads to an improved heat transfer, both together make the heat transfer particularly efficient. A small and simply constructed heat exchange surface in the interior of the housing is therefore sufficient. By including the heat exchange device in the A particularly efficient arrangement of the components required for cooling is realized in the interior of the housing.
  • the hydrostatic working spaces are preferably each delimited by a hydrostatic cylinder-piston unit of the hydraulic machine.
  • the hydraulic machine is preferably an axial piston machine and the cylinders are formed by cylinder bores formed in a rotatable cylinder drum. In which the pistons are arranged to be axially displaceable.
  • the axial piston machine is preferably designed in the form of a swash plate, with the pistons being slidably supported on a swash plate which is arranged fixed to the housing or is pivotably mounted.
  • a bent-axis design is possible, with the piston heads being non-rotatably connected to a drive shaft positioned relative to the axis of rotation.
  • the heat exchange device at least partially occupies an annular space which extends radially and axially between an inner wall of the housing and the group.
  • the annular space is particularly useful because it is present in any case and does not have to be expanded, or only slightly so, in order to arrange the heat exchange device.
  • the hydraulic machine is still small.
  • the annular space extends in the direction of the axis of rotation and is at least partially cylindrical around it.
  • it can have a conical or oval section, for example to promote turbulent turbulence of the leakage volume or leakage volume flow and thus make the heat transfer even more efficient.
  • the axis of rotation is encompassed by the heat exchange device in the form of a ring, in particular a circular ring, or polygonal, in particular four-, six- or eight-sided.
  • the shapes mentioned relate to a projection of a contour, in particular an outer and/or inner contour of the heat exchange device, into a plane whose normal is the axis of rotation.
  • a single-phase or two-phase fluid is arranged in the heat exchange device, in particular arranged to flow.
  • a simple design of the heat exchange device that can be produced inexpensively is given if, in a further development, it extends at least in sections in a helical or spiral shape around the axis of rotation. This results in a shape corresponding to specific temperature profile along the coil on the coolant side and/or on the housing interior side.
  • the heat exchange device extends at least in sections undulating around the axis of rotation and in the direction of the axis of rotation. Sections that predominantly extend parallel to or in the direction of the axis of rotation alternate with sections that predominantly extend circumferentially around the axis of rotation.
  • the heat exchange device extends in a direction radially to the axis of rotation with at least two windings or layers.
  • a first winding or layer extends radially inwards in a direction of the axis of rotation up to an apex of the first winding or layer, is guided radially outwards there by an amount of at least one pipe diameter of the heat exchange device and extends with a second wrap or layer back from the apex in the opposite direction.
  • the heat exchange device can extend partially or completely around the axis of rotation, so that an installation space of a component of the hydraulic machine that is occupied in the housing interior, in particular in the annular space, is bypassed by the heat exchange device.
  • the housing interior is delimited by a housing through which a drive shaft rotatable about the axis of rotation, with which the cylinder-piston units are non-rotatably connected, and an inlet and/or a return of the heat exchanger device pass through on the same side.
  • the housing interior is delimited by a housing which has high-pressure and low-pressure connections on the same side and has an inlet and/or a return of the heat exchange device passing through it.
  • the inlet and/or the return is preferably sealed against the housing on the outside.
  • the sealing point is thus easily accessible, controllable and serviceable.
  • a hydraulic unit has a hydraulic machine that is designed according to at least one aspect of the preceding description. At least one of the following is permanently connected to the hydraulic machine, in particular to its housing: a drive machine, in particular an electric machine, via which torque can be transmitted to the hydraulic machine, and a pressure medium tank, which can be connected to the low pressure and/or high pressure of the hydraulic machine.
  • the pressure medium tank can be designed as an open tank (open circuit) or pressure equalization tank (closed circuit).
  • Such a unit is provided, for example, for supplying pressure medium to a hydraulic cylinder.
  • a hydraulic axle has a hydraulic machine which, according to at least one aspect of the preceding description. At least one of the following is permanently connected to the hydraulic machine, in particular to its housing: a drive machine, in particular an electric machine, via which torque can be transmitted to the hydraulic machine, a hydraulic cylinder that can be supplied with pressure medium by the hydraulic machine, and a control block, in particular a valve control block, for controlling the pressure medium supply .
  • a tank or a pressure medium container that can be connected to the low pressure and/or high pressure of the hydraulic machine can be provided.
  • a first exemplary embodiment of a hydrostatic axial piston pump 1 has a housing 2 with an annular housing shell 4, which is closed at the front on the one hand by a drive-through cover 6 and on the other hand by a connection cover 8.
  • a drive shaft 14 is rotatably mounted in the housing 2 via roller bearings 10 , 12 .
  • a cylinder drum 16 is connected in a rotationally fixed manner to the drive shaft 14 , in which a plurality of cylinder bores are introduced parallel to the axis of rotation 18 along a pitch circle arranged concentrically to the axis of rotation 18 .
  • a hydrostatic working piston 20 is guided in an axially displaceable manner in the respective cylinder bore and is slidably supported on the part of the housing cover 6 on a swash plate 22 fixedly arranged in the housing 2 .
  • a control disk 24 penetrated by through-holes (not shown) is arranged between the cylinder drum 16 and the connection cover 8.
  • the through-hole pressure kidneys
  • a housing interior 30 is formed in the housing 2 .
  • An annular space 34 is formed radially between the cylinder drum 16 and an inner wall 32 of the housing.
  • a helical heat exchange device 36 for dissipating thermal energy from the housing 2 extends around this axis and around the axis of rotation 18.
  • the heat exchange device 36 arranged in the annular space 34 heats the thermal Energy is transferred at precisely this point to a coolant flowing in the coil, for example water.
  • a ⁇ T is very high at this point and so is the heat transfer coefficient ⁇ . This means that a large amount of heat can be transferred over a small heat exchange surface.
  • the thermal energy dissipated by means of the cooling water can be used further, since its temperature level is particularly high above the ambient temperature.
  • a hot water supply can be supplied with heat on a secondary basis. This can be implemented, for example, by a 3-way circuit in which the cooling water circulates in the heat exchange device 36 until a sufficient ⁇ T is reached.
  • figure 2 shows a hydrostatic axial piston pump 101 according to a second embodiment.
  • the heat exchange device 136 of that according to figure 1 differs. Although it is also designed as a coil, the individual windings of the coil are in contact with one another in the axial direction.
  • figure 2 an inlet 38 and a return 40 of the heat exchange device 136 are shown. Both 38, 40 pass through the housing cover 6 and are sealed against the housing 2 on its outside (not shown). Cooling water flows through the inlet 38 into the coil of the heat exchange device 136 and, on its way through the coil to the return 40 , absorbs heat from the turbulent leakage oil in the housing interior 134 .
  • the turbulence generated by the cylinder drum 16 in the oil bath of the housing interior 30 proves to be advantageous for the heat transfer coefficient of the heat exchange device 136. Due to the narrower arrangement of the coils of the heat exchange device 136, a heat flow density is greater than in the first exemplary embodiment figure 1 , elevated.
  • the Figures 3 to 5 show the heat exchange device 136 according to FIG figure 2 in a perspective, a side and a plan view.
  • the comparatively short inlet 38 extends parallel to the axis of rotation 18 and is angled at a right angle relative to the axis of rotation 18 in the circumferential direction.
  • the coil then runs with adjacent turns in the direction of the axis of rotation 18 and circumferentially around it until the coil tube runs out tangentially at an apex of the heat exchange device 136 and is angled again at right angles, parallel to the axis of rotation 18 and is fed back as a return 40.
  • FIG figure 6 shows a third exemplary embodiment of a heat exchange device 236, which is based on the helical heat exchange device 36 according to FIG figure 1 builds up.
  • the heat exchange device 236 has two layers or windings in the radial direction instead of just one.
  • the individual windings are spaced apart from one another in the direction of the axis of rotation 18 .
  • the turbulent oil bath in the housing interior 30 can also reach the spaces between the windings.
  • internal windings extend circumferentially and in the direction of the axis 18 with a constant winding diameter up to a crest of the heat exchange device 36.
  • the diameter of the winding is expanded to a larger radius and the windings are returned circumferentially about the axis of rotation 18 in the reverse direction. This results in two windings or layers.
  • the external winding runs out as a return 40 on the side of the inlet 38, parallel to this.
  • figure 7 shows a third embodiment of a hydrostatic axial piston pump 201, which differs from the second embodiment according to figure 2 essentially by the modified heat exchange device 236 according to figure 6 differs.
  • FIG 8 A fourth exemplary embodiment of a hydrostatic axial piston pump 301 according to the invention is shown figure 8 .
  • the embodiment figure 7 it differs in the modified heat exchange device 336.
  • This is now undulating instead of helical.
  • a ring of circumferentially angled sections extending alternately parallel to the axis of rotation 18 is lined up in such a way that the tube of the heat exchange device 336 extends alternately in the circumferential direction around the axis of rotation 18 .
  • a temperature profile of the temperature difference ⁇ T that deviates from the previously shown exemplary embodiments can be implemented.
  • FIG 9 A very similarly constructed embodiment of a heat exchange device 436 is shown figure 9 .
  • the heat exchange device 436 differs in that comparatively few undulating sections are provided.
  • a final embodiment of a heat exchange device 536 shows figure 10 .
  • This extends helically in steps and also has a rectangular cross-section of the filaments. These run horizontally in sections, that is to say in a plane whose normal is the axis of rotation 18, and are connected to one another by sections which are respectively set against the planes.
  • a heat exchange device wound in a stepped and helical manner results in principle.
  • a hydraulic machine with a housing interior space in which an engine is arranged, via which mechanical energy can be converted into hydraulic energy and/or vice versa, subject to leakage.
  • a housing interior Space in which an engine is arranged via which mechanical energy can be converted into hydraulic energy and/or vice versa, subject to leakage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Description

Die Erfindung betrifft eine Hydromaschine gemäß dem Oberbegriff des Patentanspruchs 1, ein hydraulisches Aggregat mit der Hydromaschine gemäß Anspruch 11, sowie eine hydraulische Achse mit der Hydromaschine gemäß Anspruch 12.The invention relates to a hydraulic machine according to the preamble of patent claim 1, a hydraulic unit with the hydraulic machine according to claim 11, and a hydraulic axle with the hydraulic machine according to claim 12.

Herzstück eines hydraulischen Kreislaufs ist eine Hydromaschine, insbesondere eine Hydropumpe. Über sie wird mechanische in hydraulische, insbesondere in hydrostatische Energie eines von ihr geförderten Druckmittels gewandelt. Im Falle eines Betriebes als Hydromotor erfolgt die Wandlung in umgekehrter Richtung. Bei Energiewandlung treten Verluste auf, die im Falle des hydraulischen Kreislaufs insbesondere zur Erwärmung des Druckmittels führen. Dabei ist der in der oder den Hydromaschinen auftretende Verlust für den Großteil der Erwärmung des Druckmittels verantwortlich, ein weitaus kleinerer Teil ist von Strömungsverlusten in Leitungen verursacht. Besonders groß ist die Erwärmung des Druckmittels in der Hydropumpe.The heart of a hydraulic circuit is a hydraulic machine, in particular a hydraulic pump. It is used to convert mechanical energy into hydraulic energy, in particular into hydrostatic energy, of a pressure medium conveyed by it. In the case of operation as a hydraulic motor, the conversion takes place in the opposite direction. During energy conversion, losses occur which, in the case of the hydraulic circuit, lead in particular to heating of the pressure medium. The loss occurring in the hydraulic machine or machines is responsible for the majority of the heating of the pressure medium, a much smaller part is caused by flow losses in lines. The heating of the pressure medium in the hydraulic pump is particularly great.

Bei konventionellen Lösungen wird die in der Hydropumpe verlustbedingt anfallende thermische Energie vom geförderten Druckmittel in den hydraulischen Kreislauf hinein verschleppt bis sie mittels einem externen Wärmetauscher als Wärme an ein Kühlmittel abgeführt wird. Hierbei wird die thermische Energie auf ein großes Ölvolumen verteilt, wodurch eine große Menge an Druckmittel umzuwälzen ist, um die Wärme abzuführen. Aufgrund der großen Druckmittelmenge ist aber auch ein ΔT zum rückkühlenden Kühlmittel vergleichsweise klein, sodass der Wirkungsgrad am externen Wärmetauscher klein ist und dessen Wärmeaustauschfläche groß sein muss, was Investitions- und Betriebskosten hoch hält.In conventional solutions, the thermal energy that occurs as a result of losses in the hydraulic pump is carried away by the pumped pressure medium into the hydraulic circuit until it is dissipated as heat to a coolant by means of an external heat exchanger. Here, the thermal energy is distributed over a large volume of oil, which means that a large amount of pressure medium has to be circulated in order to dissipate the heat. Due to the large amount of pressure medium, however, a ΔT to the recooling coolant is comparatively small, so that the efficiency of the external heat exchanger is low and its heat exchange surface must be large, which keeps investment and operating costs high.

Die Kühlung kann beispielsweise durch einen externen Rohrbündel- oder Plattenwärmetauscher erfolgen. Kühlmittel ist beispielsweise Wasser. Bei beiden Wärmetauschern besteht das Risiko eines Wassereintritts in das Hydrauliköl, da die Öl- und Kühlwasserseite im Falle des Rohrbündelwärmetauschers nur über eine Dichtung und im Falle des Plattenwärmetauschers nur über eine dünne Lötschicht getrennt sind. Beide Dichtungen können durch betriebsbedingten Verschleiß versagen und so die Betriebssicherheit der Hydromaschine und der von ihr versorgten Komponenten und Prozesse durch Wassereintritt in das Hydrauliköl gefährden.The cooling can be done, for example, by an external tube bundle or plate heat exchanger. Coolant is water, for example. With both heat exchangers there is a risk of water entering the hydraulic oil, as the oil and cooling water sides are only separated by a seal in the case of the tube bundle heat exchanger and only by a thin layer of solder in the case of the plate heat exchanger. Both seals can fail due to operational wear and thus endanger the operational safety of the hydraulic machine and the components and processes it supplies through water ingress into the hydraulic oil.

Die Druckschriften DE 94 11163 U1 , JPH 08 22 64 12 und DE 27 03 686 zeigen jeweils eine Lösung, bei der eine Kühlung mittels einer Spülung eines Gehäuseinnenraums der Hydropumpe mit Druckmittel erfolgt. Das auf diese Weise aus der Hydropumpe ausgetragene Druckmittel wird in einem gesondert angeordneten Wärmetauscher mit Wasser rückgekühlt wird. Auch hier ist die umzuwälzende Druckmittelmenge groß. Zudem muss die ausgespülte Menge permanent nachgespeist werden, was vorrichtungstechnischen Aufwand mit sich bringt.The pamphlets DE 94 11163 U1 , JPH 08 22 64 12 and DE 27 03 686 each show a solution in which cooling takes place by flushing a housing interior of the hydraulic pump with pressure medium. The pressure medium discharged from the hydraulic pump in this way is recooled with water in a separately arranged heat exchanger. Here, too, the amount of pressure medium to be circulated is large. In addition, the quantity flushed out has to be continuously replenished, which entails expense in terms of device technology.

Die Druckschrift CN 106 224 228 zeigt eine Hydraulikpumpe deren Gehäuse von einem Wärmerohr umwickelt ist. Die endgültige Abfuhr der Wärme erfolgt durch Rückkühlung des Mediums des Wärmerohres über ein Wasserbad. Nachteilig an dieser Lösung ist beispielsweise, dass das Wärmerohr durch seine außenseitige Exposition an der Hydropumpe der Beschädigung durch Stoß ausgesetzt ist.The pamphlet CN 106 224 228 shows a hydraulic pump whose housing is wrapped in a heat pipe. The heat is finally dissipated by re-cooling the heat pipe medium in a water bath. A disadvantage of this solution is, for example, that the heat pipe is exposed to damage from impact due to its external exposure to the hydraulic pump.

Eine verwandte Lösung zeigt die Druckschrift DE 10 2012 000 986 B3 , in der ein Kühlmantel für eine Hydropumpe vorgeschlagen wird. Nachteilig hierbei ist, dass eine derartige Kühlmantelkonstruktion vergleichsweise viel Bauraum beanspruchen kann.The publication shows a related solution DE 10 2012 000 986 B3 , in which a cooling jacket for a hydraulic pump is proposed. The disadvantage here is that such a cooling jacket design can take up a comparatively large amount of space.

Die Druckschriften DE 10 2011 054623 A1 und EP 3 168470 A1 zeigen Hydromaschinen mit einer Wärmetauscheinrichtung in einem Gehäuseinnenraum, deren Wandungen nachteilig komplex und mehrteilig, bestehend aus Komponenten der Hydromaschine wie Hülse, Dichtabschnitte, Zylindertrommel oder Triebwelle, ausgeführt sind.The pamphlets DE 10 2011 054623 A1 and EP 3 168 470 A1 show hydraulic machines with a heat exchange device in a housing interior, the walls of which are disadvantageously complex and multi-part, consisting of components of the hydraulic machine such as sleeve, sealing sections, cylinder drum or drive shaft.

Dem gegenüber liegt der Erfindung die Aufgabe zur Grunde, eine Hydromaschine mit effizienterer Kühlung, ein hydraulisches Aggregat mit der Hydromaschine und eine hydraulische Achse mit der Hydromaschine zu schaffen.In contrast, the invention is based on the object of creating a hydraulic machine with more efficient cooling, a hydraulic unit with the hydraulic machine and a hydraulic axis with the hydraulic machine.

Die erste Aufgabe wird gelöst durch eine Hydromaschine mit den Merkmalen des Patentanspruchs 1, die zweite durch ein hydraulisches Aggregat mit den Merkmalen des Anspruchs 11 und die letzte durch eine hydraulische Achse mit den Merkmalen des Anspruchs 12.The first task is solved by a hydraulic machine with the features of patent claim 1, the second by a hydraulic unit with the features of claim 11 and the last by a hydraulic axis with the features of claim 12.

Vorteilhafte Weiterbildungen der Erfindungen sind in den jeweils abhängigen Ansprüchen beschrieben.Advantageous developments of the invention are described in the respective dependent claims.

Eine Hydromaschine hat einen Gehäuseinnenraum und eine darin um eine Drehachse rotierbar gelagerte Gruppe hydrostatischer Arbeitsräume. Diese sind bei Rotation der Gruppe alternierend mit einem Hochdruck und einem Niederdruck der Hydropumpe, insbesondere einem entsprechenden Anschluss, verbindbar. Im Betrieb der Hydromaschine erwärmt sich das Druckmittel. Die Arbeitsräume weisen dabei einen Leckagevolumenstrom in den Gehäuseinnenraum hinein auf. Zur Kühlung ist im Gehäuseinnenraum eine Wärmetauscheinrichtung aufgenommen. Insbesondere kommt diese in Kontakt mit dem Leckagevolumen oder -volumenstrom. Erfindungsgemäß ist eine Wandung der Wärmetauscheinrichtung von einem Rohr gebildet. Insbesondere ist zumindest dessen Verlauf im Gehäuseinnenraum, Querschnitt, Wandungsdicke und / oder Material zumindest in Abhängigkeit der bestimmungsgemäß zu übertragenden Wärme und / oder der bestimmungsgemäßen Temperatur des Druckmittels ausgelegt.A hydraulic machine has a housing interior and a group of hydrostatic working spaces mounted therein so that it can rotate about an axis of rotation. When the group rotates, these can be connected alternately to a high pressure and a low pressure of the hydraulic pump, in particular to a corresponding connection. During operation of the hydraulic machine, the pressure medium heats up. The working spaces have a leakage volume flow into the interior of the housing. A heat exchange device is accommodated in the interior of the housing for cooling. In particular, this comes into contact with the leakage volume or volume flow. According to the invention, a wall of the heat exchange device is formed by a tube. In particular, at least its course in the housing interior, cross section, wall thickness and/or material is designed at least as a function of the intended heat to be transferred and/or the intended temperature of the pressure medium.

Durch die Anordnung der Wärmetauscheinrichtung derart nah am Ort der Erwärmung des Druckmittels, ist das ΔT besonders hoch. Auch ist eine turbulente Verwirbelung einer durch die Leckage im Gehäuseinnenraum vorhandenen Druckmittelmenge aufgrund der rotierenden Arbeitsräume hoch. Bereits einer der beiden genannten Faktoren führt zu einem verbesserten Wärmeübergang, beide zusammen machen den Wärmeübergang besonders effizient. Es reicht daher eine kleine und einfach aufgebaute Wärmeaustauschfläche im Gehäuseinnenraum aus. Durch die Aufnahme der Wärmetauscheinrichtung im Gehäuseinnenraum ist eine besonders effiziente Anordnung der zur Kühlung benötigten Komponente realisiert.Due to the arrangement of the heat exchange device so close to the place where the pressure medium is heated, the ΔT is particularly high. A turbulent turbulence of a quantity of pressure medium present due to the leakage in the interior of the housing is also high due to the rotating work spaces. Just one of the two factors mentioned leads to an improved heat transfer, both together make the heat transfer particularly efficient. A small and simply constructed heat exchange surface in the interior of the housing is therefore sufficient. By including the heat exchange device in the A particularly efficient arrangement of the components required for cooling is realized in the interior of the housing.

Vorzugsweise sind die hydrostatischen Arbeitsräume jeweils von einer hydrostatischen Zylinder-Kolbeneinheit der Hydromaschine begrenzt.The hydrostatic working spaces are preferably each delimited by a hydrostatic cylinder-piston unit of the hydraulic machine.

Vorzugsweise ist die Hydromaschine eine Axialkolbenmaschine und die Zylinder sind von in einer rotierbaren Zylindertrommel ausgebildeten Zylinderbohrungen gebildet. In denen sind die Kolben axial verschieblich angeordnet.The hydraulic machine is preferably an axial piston machine and the cylinders are formed by cylinder bores formed in a rotatable cylinder drum. In which the pistons are arranged to be axially displaceable.

Vorzugsweise ist die Axialkolbenmaschine in Schrägscheibenbauweise ausgebildet, wobei die Kolben an einer gehäusefest angeordneten oder verschwenkbar gelagerten Schrägscheibe gleitend abgestützt sind. Alternativ ist eine Schrägachsenbauweise möglich, wobei die Kolbenköpfe drehfest mit einer zur Drehachse angestellten Triebwelle verbunden sind.The axial piston machine is preferably designed in the form of a swash plate, with the pistons being slidably supported on a swash plate which is arranged fixed to the housing or is pivotably mounted. Alternatively, a bent-axis design is possible, with the piston heads being non-rotatably connected to a drive shaft positioned relative to the axis of rotation.

In einer Weiterbildung nimmt die Wärmetauscheinrichtung zumindest abschnittsweise einen Ringraum ein, der sich radial und axial zwischen einer Gehäuseinnenwandung und der Gruppe erstreckt. Der Ringraum bietet sich besonders an, da er ohnehin vorhanden ist und zur Anordnung der Wärmetauscheinrichtung nicht oder nur geringfügig erweitert werden muss. So baut die Hydromaschine trotz der im Gehäuseinnenraum angeordneten Wärmetauscheinrichtung dennoch klein.In a further development, the heat exchange device at least partially occupies an annular space which extends radially and axially between an inner wall of the housing and the group. The annular space is particularly useful because it is present in any case and does not have to be expanded, or only slightly so, in order to arrange the heat exchange device. Despite the heat exchange device arranged in the interior of the housing, the hydraulic machine is still small.

In einer Weiterbildung erstreckt sich der Ringraum in Richtung der Drehachse und um diese zumindest abschnittsweise zylindrisch. Dabei kann er alternativ oder ergänzend einen konischen oder ovalen Abschnitt aufweisen, um beispielsweise eine turbulente Verwirbelung des Leckagevolumens oder Leckagevolumenstromes zu begünstigen und so den Wärmeübergang noch effizienter zu gestalten.In a further development, the annular space extends in the direction of the axis of rotation and is at least partially cylindrical around it. Alternatively or additionally, it can have a conical or oval section, for example to promote turbulent turbulence of the leakage volume or leakage volume flow and thus make the heat transfer even more efficient.

In einer Weiterbildung ist die Drehachse von der Wärmetauscheinrichtung ringförmig, insbesondere kreisringförmig, oder vieleckig, insbesondere vier- oder sechs- oder achteckig, umgriffen. Die genannten Formen beziehen sich auf eine Projektion einer Kontur, insbesondere einer Außen- und / oder Innenkontur der Wärmetauscheinrichtung, in eine Ebene, deren Normale die Drehachse ist.In a development, the axis of rotation is encompassed by the heat exchange device in the form of a ring, in particular a circular ring, or polygonal, in particular four-, six- or eight-sided. The shapes mentioned relate to a projection of a contour, in particular an outer and/or inner contour of the heat exchange device, into a plane whose normal is the axis of rotation.

Vorzugsweise ist in der Wärmetauscheinrichtung ein Fluid einphasig oder zweiphasig angeordnet, insbesondere strömend angeordnet.Preferably, a single-phase or two-phase fluid is arranged in the heat exchange device, in particular arranged to flow.

Eine einfache und kostengünstig zu fertigende Bauform der Wärmetauscheinrichtung ist gegeben, wenn diese sich in einer Weiterbildung zumindest abschnittsweise helix- oder wendelförmig um die Drehachse erstreckt. Dabei stellt sich ein der Bauform entsprechendes, spezifisches Temperaturprofil entlang der Wendel auf der Seite des Kühlmittels und / oder auf der Seite des Gehäuseinnenraums ein.A simple design of the heat exchange device that can be produced inexpensively is given if, in a further development, it extends at least in sections in a helical or spiral shape around the axis of rotation. This results in a shape corresponding to specific temperature profile along the coil on the coolant side and/or on the housing interior side.

Um ein anderes spezifisches Temperaturprofil entlang der Wendel auf der Seite des Kühlmittels und / oder auf der Seite des Gehäuseinnenraums einzustellen, erstreckt sich in einer alternativen Weiterbildung die Wärmetauscheinrichtung zumindest abschnittsweise ondulierend um die Drehachse und in Richtung der Drehachse. Dabei wechseln sich Abschnitte, die sich überwiegend parallel zur oder in Richtung der Drehachse erstrecken, mit Abschnitten, die sich überwiegend umfänglich um die Drehachse erstrecken, ab.In order to set a different specific temperature profile along the coil on the side of the coolant and/or on the side of the housing interior, in an alternative development the heat exchange device extends at least in sections undulating around the axis of rotation and in the direction of the axis of rotation. Sections that predominantly extend parallel to or in the direction of the axis of rotation alternate with sections that predominantly extend circumferentially around the axis of rotation.

Um insbesondere eine größere Wärmetauschfläche bereitzustellen, erstreckt sich in einer Weiterbildung die Wärmetauscheinrichtung in Richtung radial zur Drehachse mit wenigstens zwei Wicklungen oder Lagen.In order in particular to provide a larger heat exchange surface, in a further development the heat exchange device extends in a direction radially to the axis of rotation with at least two windings or layers.

In einer einfach zu fertigenden Weiterbildung erstreckt sich eine erste Wicklung oder Lage radial innen in einer Richtung der Drehachse bis hin zu einem Scheitel der ersten Wicklung oder Lage, ist dort um einen Betrag mindestens eines Rohrdurchmessers der Wärmetauscheinrichtung nach radial außen geführt und erstreckt sich mit einer zweiten Wicklung oder Lage vom Scheitel zurück in die entgegengesetzte Richtung.In a further development that is easy to manufacture, a first winding or layer extends radially inwards in a direction of the axis of rotation up to an apex of the first winding or layer, is guided radially outwards there by an amount of at least one pipe diameter of the heat exchange device and extends with a second wrap or layer back from the apex in the opposite direction.

Die Wärmetauscheinrichtung kann sich teil- oder vollumfänglich um die Drehachse erstrecken, sodass ein im Gehäuseinnenraum, insbesondere im Ringraum beanspruchter Bauraum einer Komponente der Hydromaschine von der Wärmetauscheinrichtung umgangen ist.The heat exchange device can extend partially or completely around the axis of rotation, so that an installation space of a component of the hydraulic machine that is occupied in the housing interior, in particular in the annular space, is bypassed by the heat exchange device.

In einer Variante ist der Gehäuseinnenraum von einem Gehäuse begrenzt, das an einer gleichen Seite von einer um die Drehachse drehbaren Triebwelle, mit der die Zylinder-Kolbeneinheiten drehfest verbunden sind, und von einem Zulauf und oder einem Rücklauf der Wärmetauscheinrichtung durchgriffen ist.In one variant, the housing interior is delimited by a housing through which a drive shaft rotatable about the axis of rotation, with which the cylinder-piston units are non-rotatably connected, and an inlet and/or a return of the heat exchanger device pass through on the same side.

In einer Variante ist der Gehäuseinnenraum von einem Gehäuse begrenzt, das an einer gleichen Seite Anschlüsse des Hochdrucks und des Niederdrucks aufweist und von einem Zulauf und / oder einem Rücklauf der Wärmetauscheinrichtung durchgriffen ist.In one variant, the housing interior is delimited by a housing which has high-pressure and low-pressure connections on the same side and has an inlet and/or a return of the heat exchange device passing through it.

Vorzugsweise ist der Zulauf und / oder der Rücklauf außenseitig am Gehäuse gegen dieses abgedichtet. So ist die Dichtstelle einfach zugänglich, kontrollierbar und wartbar.The inlet and/or the return is preferably sealed against the housing on the outside. The sealing point is thus easily accessible, controllable and serviceable.

Ein hydraulisches Aggregat hat eine Hydromaschine, die gemäß wenigstens einem Aspekt der vorhergehenden Beschreibung ausgebildet ist. Dabei sind fest mit der Hydromaschine, insbesondere mit deren Gehäuse, zumindest verbunden: eine Antriebsmaschine, insbesondere eine Elektromaschine, über die ein Drehmoment an die Hydromaschine übertragbar ist, und ein Druckmittelbehälter, der mit dem Niederdruck und / oder Hochdruck der Hydromaschine verbindbar ist. Der Druckmittelbehälter kann je nach Ausgestaltung eines hydraulischen Kreises, in den die Hydromaschine einbindbar ist, als offener Tank (offener Kreislauf) oder Druckausgleichsbehälter (geschlossener Kreislauf) ausgebildet sein.A hydraulic unit has a hydraulic machine that is designed according to at least one aspect of the preceding description. At least one of the following is permanently connected to the hydraulic machine, in particular to its housing: a drive machine, in particular an electric machine, via which torque can be transmitted to the hydraulic machine, and a pressure medium tank, which can be connected to the low pressure and/or high pressure of the hydraulic machine. Depending on the configuration of a hydraulic circuit into which the hydraulic machine can be integrated, the pressure medium tank can be designed as an open tank (open circuit) or pressure equalization tank (closed circuit).

Ein derartiges Aggregat ist beispielsweise zur Druckmittelversorgung eines Hydrozylinders vorgesehen.Such a unit is provided, for example, for supplying pressure medium to a hydraulic cylinder.

Eine hydraulische Achse hat demgemäß eine Hydromaschine, die gemäß wenigstens einem Aspekt der vorhergehenden Beschreibung. Dabei sind fest mit der Hydromaschine, insbesondere mit deren Gehäuse, zumindest verbunden: eine Antriebsmaschine, insbesondere Elektromaschine, über die ein Drehmoment an die Hydromaschine übertragbar ist, ein von der Hydromaschine mit Druckmittel versorgbarer Hydrozylinder und ein Steuerblock, insbesondere Ventilsteuerblock, zur Steuerung der Druckmittelversorgung. Ergänzend kann, wie bereits oben erwähnt, ein Tank oder ein Druckmittelbehälter, der mit dem Niederdruck und / oder Hochdruck der Hydromaschine verbindbar ist, vorgesehen sein.Accordingly, a hydraulic axle has a hydraulic machine which, according to at least one aspect of the preceding description. At least one of the following is permanently connected to the hydraulic machine, in particular to its housing: a drive machine, in particular an electric machine, via which torque can be transmitted to the hydraulic machine, a hydraulic cylinder that can be supplied with pressure medium by the hydraulic machine, and a control block, in particular a valve control block, for controlling the pressure medium supply . In addition, as already mentioned above, a tank or a pressure medium container that can be connected to the low pressure and/or high pressure of the hydraulic machine can be provided.

Mehrere Ausführungsbeispiele einer erfindungsgemäßen Hydromaschine und ihrer Wärmetauscheinrichtungen sind in den Zeichnungen dargestellt. Anhand der Figuren dieser Zeichnungen wird die Erfindung nun näher erläutert.Several exemplary embodiments of a hydraulic machine according to the invention and its heat exchange devices are shown in the drawings. The invention will now be explained in more detail on the basis of the figures in these drawings.

Es zeigen:

  • Figur 1 eine hydrostatische Axialkolbenpumpe in Schrägscheibenbauweise gemäß einem ersten Ausführungsbeispiel, in einem Längsschnitt,
  • Figur 2 eine hydrostatische Axialkolbenpumpe in Schrägscheibenbauweise gemäß einem zweiten Ausführungsbeispiel, in einem Längsschnitt,
  • Figur 3 eine zweites Ausführungsbeispiel einer Wärmetauscheinrichtung der Axialkolbenpumpe gemäß Figur 2 in einer perspektivischen Ansicht,
  • Figur 4 die Wärmetauscheinrichtung gemäß Figur 3 in einer Seitenansicht,
  • Figur 5 die Wärmetauscheinrichtung gemäß den Figuren 3 und 4 in einer Ansicht in Richtung der Längsachse,
  • Figur 6 ein drittes Ausführungsbeispiel einer Wärmetauscheinrichtung in einer perspektivischen Ansicht,
  • Figur 7 eine hydrostatische Axialkolbenpumpe gemäß einem dritten Ausführungsbeispiel mit der Wärmetauscheinrichtung gemäß Figur 6,
  • Figur 8 eine hydrostatische Axialkolbenpumpe gemäß einem vierten Ausführungsbeispiel in einem Längsschnitt,
  • Figur 9 eine Wärmetauscheinrichtung gemäß einem fünften Ausführungsbeispiel in einer Seitenansicht und einer Draufsicht, und
  • Figur 10 eine Wärmetauscheinrichtung gemäß einem sechsten Ausführungsbeispiel in einer Seitenansicht und in einer Draufsicht.
Show it:
  • figure 1 a hydrostatic axial piston pump in swash plate design according to a first embodiment, in a longitudinal section,
  • figure 2 a hydrostatic axial piston pump in swash plate design according to a second embodiment, in a longitudinal section,
  • figure 3 according to a second exemplary embodiment of a heat exchange device of the axial piston pump figure 2 in a perspective view,
  • figure 4 the heat exchange device according to figure 3 in a side view,
  • figure 5 the heat exchange device according to Figures 3 and 4 in a view in the direction of the longitudinal axis,
  • figure 6 a third embodiment of a heat exchange device in a perspective view,
  • figure 7 a hydrostatic axial piston pump according to a third embodiment with the heat exchange device according to figure 6 ,
  • figure 8 a hydrostatic axial piston pump according to a fourth embodiment in a longitudinal section,
  • figure 9 a heat exchange device according to a fifth exemplary embodiment in a side view and a top view, and
  • figure 10 a heat exchange device according to a sixth embodiment in a side view and in a plan view.

Gemäß Figur 1 hat ein erstes Ausführungsbeispiel einer hydrostatischen Axialkolbenpumpe 1 ein Gehäuse 2 mit einem ringförmigem Gehäusemantel 4, der stirnseitig einerseits von einem Durchtriebdeckel 6 und andererseits von einem Anschlussdeckel 8 verschlossen ist. Im Gehäuse 2 ist über Wälzlager 10, 12 eine Triebwelle 14 drehbar gelagert. Drehfest mit der Triebwelle 14 verbunden ist eine Zylindertrommel 16, in die entlang einem konzentrisch zur Drehachse 18 angeordneten Teilkreis eine Vielzahl von Zylinderbohrungen parallel zur Drehachse 18 eingebracht ist. In der jeweiligen Zylinderbohrung ist ein hydrostatischer Arbeitskolben 20 axialverschieblich geführt und seitens des Gehäusedeckels 6 an einer fest im Gehäuse 2 angeordneten Schrägscheibe 22 gleitend abgestützt. Im Bereich des Anschlussdeckels 8 ist zwischen der Zylindertrommel 16 und dem Anschlussdeckel 8 eine von Durchgangsausnehmungen (nicht dargestellt) durchsetzte Steuerscheibe 24 angeordnet. Die Durchgangsausnehmung (Drucknieren) sind dabei in Druckmittelverbindung mit einem Hochdruckanschluss 26 und einem Niederdruckanschluss 28 des Anschlussdeckels 8.According to figure 1 a first exemplary embodiment of a hydrostatic axial piston pump 1 has a housing 2 with an annular housing shell 4, which is closed at the front on the one hand by a drive-through cover 6 and on the other hand by a connection cover 8. A drive shaft 14 is rotatably mounted in the housing 2 via roller bearings 10 , 12 . A cylinder drum 16 is connected in a rotationally fixed manner to the drive shaft 14 , in which a plurality of cylinder bores are introduced parallel to the axis of rotation 18 along a pitch circle arranged concentrically to the axis of rotation 18 . A hydrostatic working piston 20 is guided in an axially displaceable manner in the respective cylinder bore and is slidably supported on the part of the housing cover 6 on a swash plate 22 fixedly arranged in the housing 2 . In the area of the connection cover 8, a control disk 24 penetrated by through-holes (not shown) is arranged between the cylinder drum 16 and the connection cover 8. The through-hole (pressure kidneys) are in fluid communication with a high-pressure connection 26 and a low-pressure connection 28 of the connection cover 8.

Bei Drehung der Triebwelle 14, und damit der Zylindertrommel 16, sind die hydrostatischen Arbeitsräume über ihre zu den Anschlüssen 26, 28 weisenden Mündungen alternierend mit Hoch- und Niederdruck verbunden.When the drive shaft 14, and thus the cylinder drum 16, rotates, the hydrostatic working chambers are alternately connected to high and low pressure via their ports pointing to the connections 26, 28.

Im Gehäuse 2 ist ein Gehäuseinnenraum 30 ausgebildet. Radial zwischen der Zylindertrommel 16 und einer Gehäuseinnenwandung 32 ist ein Ringraum 34 ausgebildet. In diesem und um die Drehachse 18 erstreckt sich eine wendelförmige Wärmetauscheinrichtung 36 zur Abfuhr thermischer Energie aus dem Gehäuse 2. Wie vorbeschrieben liegt der heißeste und verlustbehaftetste Punkt in einem hydraulischen Kreislauf in der hydrostatischen Axialkolbenpumpe 1. Durch die im Ringraum 34 angeordnete Wärmetauscheinrichtung 36 wird die thermische Energie genau an diesem Punkt an ein in der Wendel strömendes Kühlmittel, beispielsweise Wasser, übertragen. Dadurch ist ein ΔT an dieser Stelle sehr hoch und der Wärmeübergangskoeffizient α ebenfalls. Damit kann auf kleiner Wärmetauschfläche eine große Wärmemenge übertragen werden. In Folge entfällt ein bedeutend größerer Wärmetauscher, der extern zur Verfügung gestellt werden müsste. Auf diese Weise kann sowohl bei den Investitionskosten als auch den Betriebskosten eine Ersparnis erzielt werden. Außerdem lassen sich unmittelbar temperaturbedingte Verschleißerscheinungen an der hydrostatischen Axialkolbenpumpe minimieren, da diese immer im optimalen Temperaturbereich betrieben werden kann.A housing interior 30 is formed in the housing 2 . An annular space 34 is formed radially between the cylinder drum 16 and an inner wall 32 of the housing. In A helical heat exchange device 36 for dissipating thermal energy from the housing 2 extends around this axis and around the axis of rotation 18. As described above, the hottest and most lossy point in a hydraulic circuit is in the hydrostatic axial piston pump 1. The heat exchange device 36 arranged in the annular space 34 heats the thermal Energy is transferred at precisely this point to a coolant flowing in the coil, for example water. As a result, a ΔT is very high at this point and so is the heat transfer coefficient α. This means that a large amount of heat can be transferred over a small heat exchange surface. As a result, there is no longer a significantly larger heat exchanger that would have to be provided externally. In this way, savings can be achieved both in terms of investment costs and operating costs. In addition, direct temperature-related wear and tear on the hydrostatic axial piston pump can be minimized, since it can always be operated in the optimum temperature range.

Da die Wärme auf diese Weise am "heißesten Ort" eines hydrostatischen Kreislaufs übertragen wird, kann die mittels dem Kühlwasser abgeführte thermische Energie gut weitergenutzt werden, da ihr Temperaturniveau besonders weit oberhalb der Umgebungstemperatur hoch ist. Auf diese Weise kann beispielsweise sekundär eine Warmwasserversorgung mit Wärme versorgt werden. Dies kann beispielsweise durch eine 3-Wege-Schaltung umgesetzt werden, in der das Kühlwasser in der Wärmetauscheinrichtung 36 solange zirkuliert, bis ein ausreichendes ΔT erreicht ist.Since the heat is transferred in this way at the "hottest place" of a hydrostatic circuit, the thermal energy dissipated by means of the cooling water can be used further, since its temperature level is particularly high above the ambient temperature. In this way, for example, a hot water supply can be supplied with heat on a secondary basis. This can be implemented, for example, by a 3-way circuit in which the cooling water circulates in the heat exchange device 36 until a sufficient ΔT is reached.

Durch den möglichen Entfall des externen Wärmetauschers entfällt auch die bereits weiter oben angesprochene, auf der relativ anfälligen Technik des Rohrbündelwärmetauschers oder Plattenwärmetauschers basierende, Fehlerquelle.Due to the possible omission of the external heat exchanger, the source of error already mentioned above, which is based on the relatively vulnerable technology of the tube bundle heat exchanger or plate heat exchanger, also no longer applies.

Auf eine weitergehende Erläuterung des grundlegenden Aufbaus und der grundlegenden Funktionsweise der hydrostatischen Axialkolbenmaschine 1 gemäß Figur 1, sowie der folgenden Ausführungsbeispiele, wird an dieser Stelle verzichtet, da dies hinreichend aus dem Stand der Technik bekannt ist. Die genannten Vorteil gelten auch für die folgenden Ausführungsbeispiele.On a more detailed explanation of the basic structure and the basic operation of the hydrostatic axial piston machine 1 according to figure 1 , as well as the following exemplary embodiments, are omitted at this point since this is sufficiently known from the prior art. The advantages mentioned also apply to the following exemplary embodiments.

Figur 2 zeigt eine hydrostatische Axialkolbenpumpe 101 gemäß einem zweiten Ausführungsbeispiel. Ein Unterschied zum ersten Ausführungsbeispiel gemäß Figur 1 ist dabei, dass sich die Wärmetauscheinrichtung 136 von derjenigen gemäß Figur 1 unterscheidet. Sie ist zwar ebenfalls als Wendel ausgestaltet, jedoch liegen die einzelnen Windungen der Wendel in Axialrichtung aneinander an. Zudem sind in Figur 2 ein Zulauf 38 und ein Rücklauf 40 der Wärmetauscheinrichtung 136 dargestellt. Beide 38, 40 durchsetzen den Gehäusedeckel 6 und sind an dessen Außenseite (nicht dargestellt) gegen das Gehäuse 2 abgedichtet. Durch den Zulauf 38 strömt in der Wendel der Wärmetauscheinrichtung 136 Kühlwasser ein und nimmt auf seinem Weg durch die Wendel bis zum Rücklauf 40 von dem im Gehäuseinnenraum 134 turbulent durchwirbelten Leckageöl Wärme auf. figure 2 shows a hydrostatic axial piston pump 101 according to a second embodiment. A difference from the first embodiment according to figure 1 is in that the heat exchange device 136 of that according to figure 1 differs. Although it is also designed as a coil, the individual windings of the coil are in contact with one another in the axial direction. In addition, figure 2 an inlet 38 and a return 40 of the heat exchange device 136 are shown. Both 38, 40 pass through the housing cover 6 and are sealed against the housing 2 on its outside (not shown). Cooling water flows through the inlet 38 into the coil of the heat exchange device 136 and, on its way through the coil to the return 40 , absorbs heat from the turbulent leakage oil in the housing interior 134 .

Wie bei allen Ausführungsbeispielen erweist sich die durch die Zylindertrommel 16 im Ölbad des Gehäuseinnenraumes 30 erzeugte Turbulenz als vorteilhaft für den Wärmeübergangskoeffizient der Wärmetauscheinrichtung 136. Durch die engere Anordnung der Wendeln der Wärmetauscheinrichtung 136 ist eine Wärmestromdichte, verglichen mit dem ersten Ausführungsbeispiel gemäß Figur 1, erhöht.As in all exemplary embodiments, the turbulence generated by the cylinder drum 16 in the oil bath of the housing interior 30 proves to be advantageous for the heat transfer coefficient of the heat exchange device 136. Due to the narrower arrangement of the coils of the heat exchange device 136, a heat flow density is greater than in the first exemplary embodiment figure 1 , elevated.

Die Figuren 3 bis 5 zeigen die Wärmetauscheinrichtung 136 gemäß Figur 2 in einer perspektivischen, einer Seiten- und einer Draufsicht. Der vergleichsweise kurze Zulauf 38 erstreckt sich parallel zur Drehachse 18 und ist im rechten Winkel, bezogen auf die Drehachse 18 in Umfangsrichtung, abgewinkelt. In Folgendem verläuft die Wendel mit aneinander anliegende Windungen in Richtung der Drehachse 18 und umfänglich um diese herum, bis an einem Scheitel der Wärmetauscheinrichtung 136 das Wendelrohr tangential ausläuft und wieder im rechten Winkel, parallel zur Drehachse 18 abgewinkelt ist und als Rücklauf 40 zurückgeführt ist.the Figures 3 to 5 show the heat exchange device 136 according to FIG figure 2 in a perspective, a side and a plan view. The comparatively short inlet 38 extends parallel to the axis of rotation 18 and is angled at a right angle relative to the axis of rotation 18 in the circumferential direction. The coil then runs with adjacent turns in the direction of the axis of rotation 18 and circumferentially around it until the coil tube runs out tangentially at an apex of the heat exchange device 136 and is angled again at right angles, parallel to the axis of rotation 18 and is fed back as a return 40.

Figur 6 zeigt ein drittes Ausführungsbeispiel einer Wärmetauscheinrichtung 236, das auf der wendelförmigen Wärmetauscheinrichtung 36 gemäß Figur 1 aufbaut. Im Unterschied zu dieser weist die Wärmetauscheinrichtung 236 in Radialrichtung zwei Lagen oder Wicklungen, anstatt nur einer, auf. Wie bereits das erste Ausführungsbeispiel 36 weisen die einzelnen Windungen in Richtung der Drehachse 18 einen Abstand zueinander auf. Auf diese Weise kann das turbulente Ölbad im Gehäuseinnenraum 30 auch die Zwischenräume zwischen den Windungen erreichen. Ausgehend von einem Zulauf 38 erstrecken sich innenliegende Windungen umfänglich und in Richtung zu der Achse 18 mit konstantem Wicklungsdurchmesser bis hin zu einem Scheitel der Wärmetauscheinrichtung 36. Hier wird der Durchmesser der Wicklung auf einen größeren Radius erweitert und die Windungen werden in umgekehrter Richtung entlang der Drehachse 18 umfänglich um diese zurückgeführt. So ergeben sich zwei Wicklungen oder Lagen. Die außenliegende Wicklung läuft als Rücklauf 40 wieder auf der Seite des Zulaufs 38, parallel zu diesem, aus. figure 6 shows a third exemplary embodiment of a heat exchange device 236, which is based on the helical heat exchange device 36 according to FIG figure 1 builds up. In contrast to this, the heat exchange device 236 has two layers or windings in the radial direction instead of just one. As in the first exemplary embodiment 36 , the individual windings are spaced apart from one another in the direction of the axis of rotation 18 . In this way, the turbulent oil bath in the housing interior 30 can also reach the spaces between the windings. Starting from an inlet 38, internal windings extend circumferentially and in the direction of the axis 18 with a constant winding diameter up to a crest of the heat exchange device 36. Here the diameter of the winding is expanded to a larger radius and the windings are returned circumferentially about the axis of rotation 18 in the reverse direction. This results in two windings or layers. The external winding runs out as a return 40 on the side of the inlet 38, parallel to this.

Figur 7 zeigt ein drittes Ausführungsbeispiel einer hydrostatischen Axialkolbenpumpe 201, das sich vom zweiten Ausführungsbeispiel gemäß Figur 2 im Wesentlichen durch die veränderte Wärmetauscheinrichtung 236 gemäß Figur 6 unterscheidet. figure 7 shows a third embodiment of a hydrostatic axial piston pump 201, which differs from the second embodiment according to figure 2 essentially by the modified heat exchange device 236 according to figure 6 differs.

Ein viertes Ausführungsbeispiel einer erfindungsgemäßen hydrostatischen Axialkolbenpumpe 301 zeigt Figur 8. Vom Ausführungsbeispiel gemäß Figur 7 unterscheidet sich es durch die abgewandelte Wärmetauscheinrichtung 336. Diese ist nun, anstatt wendelförmig, ondulierend ausgestaltet. Dabei ist ein Kranz von sich abwechselnd parallel zur Drehachse 18 erstreckenden und umfänglich abgewinkelten Abschnitten so aneinander gereiht, dass sich das Rohr der Wärmetauscheinrichtung 336 alternierend in Umfangsrichtung um die Drehachse 18 erstreckt. Auf diese Weise kann ein von den bisher gezeigten Ausführungsbeispielen abweichendes Temperaturprofil der Temperaturdifferenz ΔT realisiert werden.A fourth exemplary embodiment of a hydrostatic axial piston pump 301 according to the invention is shown figure 8 . According to the embodiment figure 7 it differs in the modified heat exchange device 336. This is now undulating instead of helical. A ring of circumferentially angled sections extending alternately parallel to the axis of rotation 18 is lined up in such a way that the tube of the heat exchange device 336 extends alternately in the circumferential direction around the axis of rotation 18 . In this way, a temperature profile of the temperature difference ΔT that deviates from the previously shown exemplary embodiments can be implemented.

Ein ganz ähnlich aufgebautes Ausführungsbeispiel einer Wärmetauscheinrichtung 436 zeigt Figur 9. Vom Ausführungsbeispiel gemäß Figur 8 unterscheidet sich die Wärmetauscheinrichtung 436 dadurch, dass vergleichsweise wenige ondulierende Abschnitte vorgesehen sind.A very similarly constructed embodiment of a heat exchange device 436 is shown figure 9 . According to the embodiment figure 8 the heat exchange device 436 differs in that comparatively few undulating sections are provided.

Ein letztes Ausführungsbeispiel einer Wärmetauscheinrichtung 536 zeigt Figur 10. Diese erstreckt sich stufenweise wendelförmig und hat zudem einen rechteckigen Querschnitt der Wendeln. Diese verlaufen abschnittsweise waagerecht, das heißt in einer Ebene, deren Normale die Drehachse 18 ist, und sind durch gegen die Ebenen jeweils angestellte Abschnitte miteinander verbunden. Auf diese Weise ergibt sich eine im Prinzip stufen- und wendelförmig gewickelte Wärmetauscheinrichtung.A final embodiment of a heat exchange device 536 shows figure 10 . This extends helically in steps and also has a rectangular cross-section of the filaments. These run horizontally in sections, that is to say in a plane whose normal is the axis of rotation 18, and are connected to one another by sections which are respectively set against the planes. In this way, a heat exchange device wound in a stepped and helical manner results in principle.

Offenbart ist eine Hydromaschine mit einem Gehäuseinnenraum, in dem ein Triebwerk angeordnet ist, über das mechanische Energie in hydraulische Energie, und / oder umgekehrt, leckagebehaftet wandelbar ist. Dabei ist im Gehäuseinnenraum eine Wärmetauscheinrichtung zur Abfuhr eines Wärmestroms der Leckage zumindest abschnittsweise angeordnet.Disclosed is a hydraulic machine with a housing interior space in which an engine is arranged, via which mechanical energy can be converted into hydraulic energy and/or vice versa, subject to leakage. There is one in the housing interior Heat exchange device for dissipating a heat flow of the leakage arranged at least in sections.

Offenbart sind weiterhin ein hydraulisches Aggregat und eine hydraulische Achse, die jeweils die Hydromaschine aufweisen.Also disclosed are a hydraulic unit and a hydraulic axle, each of which has the hydraulic machine.

BezugszeichenlisteReference List

1; 101; 201; 3011; 101; 201; 301
hydrostatische Axialkolbenpumpehydrostatic axial piston pump
22
GehäuseHousing
44
Gehäusemantelhousing jacket
66
Gehäusedeckelhousing cover
88th
Anschlussdeckelconnection cover
10, 1210, 12
Wälzlagerroller bearing
1414
Triebwelledrive shaft
1616
Zylindertrommelcylinder drum
1818
Drehachseaxis of rotation
2020
Arbeitskolbenworking piston
2222
Schrägscheibeswashplate
2424
Steuerscheibecontrol disc
2626
Hochdruckanschlusshigh pressure connection
2828
Niederdruckanschlusslow pressure connection
3030
Gehäuseinnenraumhousing interior
3232
Gehäuseinnenwandunghousing inner wall
34; 134; 234; 33434; 134; 234; 334
Ringraumannulus
36; 136; 236; 336; 436; 53636; 136; 236; 336; 436; 536
Wärmetauscheinrichtungheat exchange device

Claims (11)

  1. Hydraulic machine having a housing interior (30) and a group of hydrostatic working chambers mounted therein so as to be rotatable about an axis of rotation (18), said working chambers, upon rotation of the group, being connectable in an alternating manner to a high pressure (26) and to a low pressure (28) of the hydraulic machine and having a leakage into the housing interior (30), in which a heat exchanger device (36; 136; 236; 336; 436; 536) is accommodated, characterized in that a wall of the heat exchanger device (36; 136; 236; 336; 436; 536) is formed by a tube.
  2. Hydraulic machine according to Claim 1, wherein the heat exchanger device (36; 136; 236; 336) at least in sections occupies an annular chamber (34; 134; 234; 334) which extends between a housing inner wall (32; 132; 232; 332) and the hydrostatic cylinder/piston units bounding the working chambers.
  3. Hydraulic machine according to Claim 2, wherein the annular chamber (32; 132; 232; 332) extends in the direction of the axis of rotation (18) and around the latter, in particular predominantly in a cylindrical or conical or oval manner.
  4. Hydraulic machine according to one of Claims 1 to 3, wherein the axis of rotation (18) is engaged around by the heat exchanger device (36; 136; 236; 336) in an annular manner, in particular in a circular manner, or in a polygonal manner, in particular in a square or hexagonal or octagonal manner.
  5. Hydraulic machine according to one of the preceding claims, wherein a fluid is arranged in a single phase or in two phases in the heat exchanger device (36; 136; 236; 336) .
  6. Hydraulic machine according to one of the preceding claims, wherein the heat exchanger device (36; 136; 236; 536) extends at least in sections helically or spirally around the axis of rotation (18) and in the direction of the axis of rotation (18).
  7. Hydraulic machine according to one of the preceding claims, wherein the heat exchanger device (336; 436) extends at least in sections in an undulating manner around the axis of rotation (18) and in the direction of the axis of rotation (18).
  8. Hydraulic machine according to one of the preceding claims, wherein the heat exchanger device (236) extends with at least two windings or layers in a direction radially with respect to the axis of rotation (18).
  9. Hydraulic machine according to one of the preceding claims, with a housing (2, 4, 6, 8) which bounds the housing interior and through which passes, on an identical side (6), a drive shaft (14) which is rotatable about the axis of rotation (18) and to which the cylinder/piston units are connected for rotation therewith, and a feed (38) and a return (40) of the heat exchanger device (136; 336), or which, on an identical side, has connections of the high pressure and of the low pressure and through which a feed and a return of the heat exchanger device pass.
  10. Hydraulic assembly having a hydraulic machine which is designed according to one of the preceding claims, wherein at least the following are fixedly connected to the hydraulic machine: a drive machine, in particular electric machine, via which a torque can be transmitted to the hydraulic machine, and a pressure medium container which is connectable to the low pressure and/or high pressure of the hydraulic machine.
  11. Hydraulic axle having a hydraulic machine which is designed according to one of Claims 1 to 9, wherein at least the following are fixedly connected to the hydraulic machine: a drive machine, in particular electric machine, via which a torque can be transmitted to the hydraulic machine, a hydraulic cylinder which can be supplied with pressure medium by the hydraulic machine, and a control block, in particular valve control block, for controlling the pressure medium supply.
EP19700638.0A 2018-01-11 2019-01-07 Hydraulic machine, hydraulic assembly having the hydraulic machine, and hydraulic axle having the hydraulic machine Active EP3737862B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018200345.9A DE102018200345A1 (en) 2018-01-11 2018-01-11 Hydromachine, hydraulic aggregate with hydromachine, and hydraulic axis with hydromachine
PCT/EP2019/050202 WO2019137862A1 (en) 2018-01-11 2019-01-07 Hydraulic machine, hydraulic assembly having the hydraulic machine, and hydraulic axle having the hydraulic machine

Publications (2)

Publication Number Publication Date
EP3737862A1 EP3737862A1 (en) 2020-11-18
EP3737862B1 true EP3737862B1 (en) 2022-06-22

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EP19700638.0A Active EP3737862B1 (en) 2018-01-11 2019-01-07 Hydraulic machine, hydraulic assembly having the hydraulic machine, and hydraulic axle having the hydraulic machine

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US (1) US11619214B2 (en)
EP (1) EP3737862B1 (en)
CN (1) CN111566346B (en)
DE (1) DE102018200345A1 (en)
WO (1) WO2019137862A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102021202489A1 (en) 2021-03-15 2022-09-15 Robert Bosch Gesellschaft mit beschränkter Haftung Cooling module for a hydraulic machine, hydraulic machine with it, and hydraulic unit

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Publication number Priority date Publication date Assignee Title
US1764753A (en) * 1926-09-30 1930-06-17 Fairbanks Morse & Co Fluid-compressing means
DE2703686A1 (en) 1977-01-29 1978-08-10 Bosch Gmbh Robert Variable volume high pressure hydraulic pump - has separate throttled circuit for cooling and lubricating oil supplied to main pump
DE9411163U1 (en) 1994-07-09 1995-12-21 O & K Orenstein & Koppel Ag, 13581 Berlin Device for cooling at least one traction pump and / or at least one traction motor of a hydrostatic traction drive
JP3626236B2 (en) 1995-02-22 2005-03-02 株式会社竹内製作所 Hydraulic circuit for motor
TW504546B (en) * 2000-10-17 2002-10-01 Fisher & Amp Paykel Ltd A linear compressor
US7799221B1 (en) * 2008-01-15 2010-09-21 Macharg John P Combined axial piston liquid pump and energy recovery pressure exchanger
CN101684783A (en) * 2008-09-28 2010-03-31 海特克液压有限公司 Plunger pump
CN102128186A (en) * 2011-03-24 2011-07-20 莱芜钢铁股份有限公司 Water and air double-cooled hydraulic cylinder
DE102011054623A1 (en) * 2011-10-11 2013-04-11 Linde Material Handling Gmbh Hydrostatic axial piston machine has cooling space that is sealed at cylinder block in relation to piston projection space extending axially between eccentric disc and piston recesses in cylinder block
DE102012000986B3 (en) * 2012-01-22 2013-05-23 Arburg Gmbh + Co Kg Hydraulic device with a tempering device
CN103939414A (en) * 2014-05-08 2014-07-23 无锡市长江液压缸厂 Quick water cooling waterproof sleeve oil cylinder
JP2016017430A (en) * 2014-07-07 2016-02-01 Ｋｙｂ株式会社 Hydraulic rotating machine
CN105201816B (en) * 2015-09-07 2017-03-22 福州大学 Self-cooling structure for cylinder of swashplate type plunger pump
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CN106678117B (en) * 2016-12-30 2018-10-19 天津市双象工程液压件有限责任公司 A kind of buffering hydraulic cylinder

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DE102018200345A1 (en) 2019-07-11
US11619214B2 (en) 2023-04-04
CN111566346B (en) 2023-05-30
US20200340460A1 (en) 2020-10-29
WO2019137862A1 (en) 2019-07-18
CN111566346A (en) 2020-08-21
EP3737862A1 (en) 2020-11-18

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