CN105822629B - Hydraulic unit and method for operating a hydraulic unit - Google Patents
Hydraulic unit and method for operating a hydraulic unit Download PDFInfo
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- CN105822629B CN105822629B CN201511036291.0A CN201511036291A CN105822629B CN 105822629 B CN105822629 B CN 105822629B CN 201511036291 A CN201511036291 A CN 201511036291A CN 105822629 B CN105822629 B CN 105822629B
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- 238000000034 method Methods 0.000 title claims description 21
- 238000001816 cooling Methods 0.000 claims abstract description 171
- 230000007246 mechanism Effects 0.000 claims abstract description 109
- 239000002826 coolant Substances 0.000 claims description 89
- 239000003507 refrigerant Substances 0.000 claims description 37
- 239000002918 waste heat Substances 0.000 claims description 21
- 230000008569 process Effects 0.000 claims description 8
- 230000005855 radiation Effects 0.000 claims description 6
- 238000005086 pumping Methods 0.000 claims description 2
- 238000009835 boiling Methods 0.000 description 29
- 239000003921 oil Substances 0.000 description 20
- 238000010586 diagram Methods 0.000 description 12
- 238000012546 transfer Methods 0.000 description 11
- 238000001179 sorption measurement Methods 0.000 description 8
- 230000008859 change Effects 0.000 description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 238000013461 design Methods 0.000 description 5
- 239000010705 motor oil Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 230000001360 synchronised effect Effects 0.000 description 4
- 230000032258 transport Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 3
- 239000004576 sand Substances 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000013021 overheating Methods 0.000 description 2
- 230000007723 transport mechanism Effects 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 239000012212 insulator Substances 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/62—Cooling or heating means
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A hydraulic unit (100) is proposed, comprising an actuator mechanism (102) for driving the hydraulic unit (100), wherein the actuator mechanism (102) comprises a pump (104) and/or a motor (106). The hydraulic unit (100) has a cooling mechanism (108) thermally coupled to the actuator mechanism (102) for cooling the actuator mechanism (102).
Description
Technical Field
The present invention relates to a hydraulic unit, a corresponding hydraulic system, the use of waste heat of a corresponding hydraulic unit or of a corresponding hydraulic system, and a method for operating a hydraulic unit.
Background
In the prior art, heat is discharged along the surface of the component through a heat path (e.g., in the control unit, pump, motor, …), and heat is discharged along the surface (convectively and radiatively).
As these components are increasingly integrated into the system, the surface is reduced and hot spots are not located near the surface.
Disclosure of Invention
Against this background, with the solution proposed here, a hydraulic unit according to the main claim is proposed, as well as a hydraulic system using the hydraulic unit, an application of waste heat of the respective hydraulic unit or of the respective hydraulic system, and a method for driving the hydraulic unit. Advantageous embodiments can be derived from the respective dependent claims and the subsequent description.
For compact hydraulic units, overheating and local hot spots can be avoided by integration of the cooling mechanism. Advantageously, the power density of the hydraulic unit can be improved. At the same time, a uniform temperature ratio inside the system can be achieved.
The solution proposed here provides a hydraulic unit with an actuator mechanism for driving the hydraulic unit, wherein the actuator mechanism comprises a pump and/or an electric motor, characterized by a cooling mechanism thermally coupled to the actuator mechanism for cooling the actuator mechanism, wherein the cooling mechanism comprises a cooling circuit with a cooling line for a cooling medium and a conveying mechanism for conveying the cooling medium in the cooling line, wherein the cooling medium is a refrigerant.
The hydraulic unit can be any hydraulic unit, such as a unit, a motor-pump group (Sytronix), a hydraulic cylinder unit with a motor-pump group if necessary, or individual components such as pumps, valves, control boxes, cylinders, motors, etc. The hydraulic cylinder unit can be a hydraulic linear unit, a hydraulic compact shaft, in particular a hydraulic cylinder with an internal actuator mechanism, a motor-pump-hydraulic cylinder or a synchronous cylinder, in particular in a differential manner. The motor may be an electric motor. The motor may be designed to drive the pump. The pump is designed for pumping a hydraulic medium into a chamber of the hydraulic cylinder unit in order to move a piston of the hydraulic cylinder unit. The cooling device can be designed to cool the actuator device, additionally or alternatively to cool the hydraulic cylinder unit or a partial region of the hydraulic cylinder unit.
The cooling device may comprise a cooling circuit with a cooling line for a cooling medium and a conveying device for conveying the cooling medium in the cooling line. The cooling line can be a cooling line. In one embodiment, the cooling mechanism may include a plurality of cooling lines or cooling channels. The cooling medium can be a heat carrier or a cold carrier. The cooling medium may be used to output heat. Thus, a first section of the cooling line or of the cooling circuit can be provided on the actuator device, in particular on an outer surface of the actuator device. The cooling medium can thus transport thermal energy away from hot spots inside the hydraulic cylinder unit. The hot spot can be a spatially local heat sink. The conveying mechanism for conveying the cooling medium may be a coolant conveying unit or a cooling medium conveying unit.
The cooling medium is a refrigerant. The refrigerant may transfer heat in the refrigeration cycle against the thermal gradient, so that the ambient temperature may be higher than the temperature of the hydraulic unit to be cooled. The refrigerant may be applied without changing the pressure, for example in heat pipes, or also with changing the pressure, for example during a cycle of a refrigerator.
Furthermore, the cooling means can be designed to conduct a cooling medium to the outer surface of the hydraulic unit in order to dissipate the absorbed thermal energy by convection and additionally or alternatively by thermal radiation. Between the cooling means and the outer surface, an insulating member or insulating surface may be provided. The waste heat of the hot spots can thus be conveyed by targeted heat transfer to a cooling device, such as a large surface, a cooling body, a cooling unit or a heat exchanger.
The hydraulic unit may have a fan for generating an air flow over the surface of the cooling device and/or the heat exchanger and/or the radiator. A section or a partial region of the cooling device can thus advantageously be cooled, in particular by convection.
The cooling mechanism may have a mechanism for changing a system pressure of the cooling mechanism. The cooling device may in particular have a device for changing the system pressure of a cooling medium in the form of a coolant in the cooling line. The pressure of the cooling medium can thus be optimally adjusted for the transfer of enthalpy through the cooling medium.
The cooling mechanism may be coupled to the heat exchanger. The cooling mechanism may also have a heat sink. It is also advantageous if the cooling device has a throttle valve, in addition or alternatively a compressor. The cooling means may in particular have a throttle, in addition or alternatively, in order to vary the pressure of the cooling medium in the cooling circuit. The pressure of the cooling medium can be varied section by section. Thus, the pressure of the cooling medium in the first section of the cooling circuit may be different from the second pressure of the cooling medium in the second section of the cooling circuit.
The hydraulic unit may at least partially surround the actuator mechanism. The actuator mechanism may in particular be arranged inside the hydraulic unit. The movable cylinder of the hydraulic unit, in particular in the form of a hydraulic cylinder unit, can thus at least partially surround the actuator mechanism in the retracted state. The inner surface of the hydraulic unit or of the hydraulic cylinder unit can bear against the outer surface of the actuator mechanism. The cooling means may be at least partly arranged between an inner surface of the hydraulic unit or of the hydraulic cylinder unit and an outer surface of the actuator means.
The cooling mechanism may have at least one check valve located on the cooling circuit. The cooling circuit can thereby pass through the cylinder chambers of the hydraulic or hydraulic cylinder units. The supply device may in particular comprise at least one check valve and a cylinder chamber for supplying the cooling medium. The cooling medium can thus flow into the cylinder chamber via the inlet and out of the cylinder chamber via the outlet. This embodiment is possible not only in the case of an integrated design of the hydraulic cylinder, but also in the case of a (hydraulic) cylinder unit with an externally located motor-pump unit.
The cooling mechanism may have a volume compensation reservoir coupled to the cooling circuit for compensating the volume of refrigerant in the cooling circuit. Thus, for example, in the case of a change in the volume of the cooling circuit, which is caused, for example, by cylinder chambers in the cooling circuit having a changing volume, the volume compensation reservoir can be used to supply additional cooling medium or to temporarily store excess cooling medium. The cylinder chamber in the cooling circuit may be part of the conveying means. The cylinder chamber may thus also be referred to as a transfer chamber. This embodiment is possible not only in the case of an integrated design of the hydraulic cylinder, but also in the case of a (hydraulic) cylinder unit with an externally located motor-pump unit.
Furthermore, in one embodiment, the cooling medium may be a hydraulic medium. The leaking oil connection of the pump may in particular be coupled with a cooling circuit in order to provide a hydraulic medium. The leaking oil may thus be a hydraulic medium, for example. The hydraulic medium may be a hydraulic liquid or a fluid used to transfer energy and/or force in a hydraulic system. The hydraulic medium can thus be thermally stable, i.e. have a low temperature influence on the viscosity (whether dynamic or kinematic), have low compressibility and shear stability and low foam formation. This embodiment is not only possible in the case of an integrated design, but also generally for hydraulic units, motor-pump units and cylinder units with an externally located motor-pump unit.
A hydraulic system is proposed with one variant of the first hydraulic unit proposed here and at least one variant of the second hydraulic unit proposed here, which have a common cooling mechanism. It is thus possible to use one cooling mechanism for at least two hydraulic units. In this case, the first hydraulic unit and at least the second hydraulic unit are arranged in parallel or in series in a cooling circuit of the cooling unit. In one embodiment, an at least partially parallel arrangement of a plurality of hydraulic units is combined with an at least partially serial arrangement of a plurality of hydraulic units. Here, the parallel and series may relate to the arrangement of the hydraulic units in the cooling circuit.
It is proposed to use waste heat of variants of the hydraulic unit proposed here and/or to use waste heat of variants of the hydraulic system proposed here for further cooling processes and/or thermal processes, in particular by means of a refrigerator. Waste heat from the at least one hydraulic unit can thus be used for a cooling process or a thermal process, for example in order to drive an adsorption refrigerator. In this way, thermal energy utilization can be carried out not only for the hydraulic unit, but likewise, for example, for a hydraulic system or a Sytronix motor pump unit.
A method for operating a hydraulic unit is proposed, wherein the method comprises the following steps:
controlling the actuator mechanism; and
the actuator mechanism is cooled with a cooling mechanism coupled to the actuator mechanism.
The object of the invention can also be achieved quickly and efficiently with this design variant in the form of the method of the invention.
One aspect of the present invention is a cooling design for a hydraulic unit. For a hydraulic unit, the electric motor and the pump may be incorporated inside the cylinder of the hydraulic unit or the hydraulic cylinder unit. In one embodiment, a cooling medium or cooling channel is present here, which discharges heat from the electric motor and the pump.
In an alternative embodiment, the coolant is circulated in an inner casing surrounding the motor and the pump. Alternatively, the heat discharge may be performed here by a radiator or a heat exchanger.
In one embodiment, a coolant or refrigerant in the cooling mechanism may be utilized here. The cooling mechanism may thus be designed to use a coolant for cooling purposes, or alternatively a refrigerant. The refrigerant circuit can optionally have a throttle. The cooling circuit may thus have a plurality of refrigerant circuits.
In a special embodiment, a cylinder or a cylinder chamber of the hydraulic unit or the hydraulic cylinder unit or an auxiliary cylinder coupled to the hydraulic unit or the hydraulic cylinder unit can be used as the coolant supply unit.
In one embodiment, a hydraulic medium can optionally be used as cooling medium. The hydraulic medium can be tapped at the leakage oil connection or at the outlet of the pump.
The waste heat of the multiple shafts or hydraulic cylinder units can advantageously be combined and the heat can be utilized using process technology.
Drawings
The invention is described in detail below by way of example with reference to the accompanying drawings. Wherein:
FIGS. 1-4 are schematic diagrams of a hydraulic unit, respectively;
FIGS. 5-8 are simplified graphs of temperature trends, respectively;
FIGS. 9-10 are schematic diagrams of a hydraulic unit, respectively;
FIG. 11 is a simplified graph of temperature trend;
12-18 are schematic diagrams of a hydraulic unit according to one embodiment of the present invention, respectively;
FIGS. 19-22 are schematic views of an actuator mechanism, respectively;
FIG. 23 is a schematic diagram of a hydraulic unit;
24-26 are schematic diagrams of hydraulic systems, respectively;
FIG. 27 is a simplified diagram of an adsorption chiller and hydraulic system; and
FIG. 28 is a flow chart of a method.
Detailed Description
The same or similar components may be labeled with the same or similar reference numbers in the following figures. Furthermore, the drawings, descriptions thereof, and claims contain the general combination of features. The person skilled in the art will here know that these features can also be considered individually or in combination with other combinations not explicitly stated here.
Fig. 1 is a schematic view of a hydraulic cylinder unit 100 according to an embodiment. It is to be noted here that the generic solution proposed here is described with the aid of an embodiment of the hydraulic cylinder unit as a hydraulic unit. It is clear that the solution proposed here for cooling the hydraulic unit is not generally limited to the use of hydraulic cylinder units. It is also conceivable to apply the solution proposed here, for example, to a conventional hydraulic unit, a motor-pump group (Sytronix), a hydraulic cylinder unit with a motor-pump group or individual components, such as pumps, valves, a control box, cylinders, motors or the like. The following description of an embodiment with a hydraulic cylinder unit as hydraulic unit is therefore to be understood as follows, which, for the purpose of summarizing the solution proposed here, is disclosed only by way of an exchangeable example of a hydraulic cylinder unit with a correspondingly coupled cooling element, but which can also be operated with one of the aforementioned assemblies or assemblies instead of a hydraulic cylinder unit.
The hydraulic cylinder unit as the hydraulic unit 100 exemplarily selected for the following description is a synchronous cylinder (gleichangzylinder) adopting a differential (differential) configuration. The hydraulic cylinder unit (hereinafter, representatively, a hydraulic unit is provided with reference numeral 100) has an actuator mechanism 102 for driving the hydraulic cylinder unit 100. The actuator mechanism 102 includes a pump 104 and a motor 106 for driving the pump 104. The actuator mechanism 102 is disposed in the inner chamber of the hydraulic cylinder unit 100. A cooling mechanism 108 for cooling the actuator mechanism 102 is thermally coupled to the actuator mechanism 102.
In the exemplary embodiment shown in fig. 1, the hydraulic cylinder unit 100 has a main body 110 and a piston rod 112 guided in a straight line in the main body 110. The body 110 has a flange (An flanschung)114 on one side. The hydraulic cylinder unit 100 is designed appropriately so that the piston rod 112 can move laterally with respect to the flange 114 side of the main body 110. The body 110 is suitably shaped so that it provides a guide for the piston rod 112. The body 110 and the piston rod 112 are suitably shaped so as to provide four chambers K1, K2, K3, K4, wherein hydraulic medium is pumped into the respective chamber K1, K2, K3, K4 or out of the respective chamber K1, K2, K3, K4, thereby moving the piston rod 112. The chambers K1, K2, K3 are arranged radially around the actuator mechanism 102. The chamber K4 is formed by the piston rod 112 and the end side of the body 110 opposite the flange 114.
The pump 104 and the motor 106 are located in the inner chamber of the hydraulic cylinder unit 100 and deliver the working medium (hydraulic oil) to the respective chamber K1, K2, K3 or K4. Thereby applying a force to the piston rod 112 and causing the piston rod to move in the direction 116 as shown.
The cooling means 108 comprise a cooling circuit 118 with a cooling line 120 for a cooling medium and comprise a conveying means 122 for conveying the cooling medium in the cooling line 120. The cooling circuit 120 provides guidance for the cooling medium. In the embodiment shown in fig. 1, a delivery pump 122 arranged in the cooling circuit 118 is used as the delivery mechanism 122.
The cooling means 108 may be designed to conduct a coolant, a refrigerant or a hydraulic medium as cooling medium. In a simple embodiment, such as shown in fig. 1, a coolant is used as the cooling medium.
Most of the heat loss is generated in the motor 106 and the pump 104. Without the cooling circuit 118, these heat losses must first reach the surface through the two walls of the body 110 and via the working medium of the hydraulic cylinder unit 100. The cooling mechanism 108 provides an additional heat drain, by means of which a large thermal resistance of the system and thus overheating can be avoided. Thus avoiding operation with reduced efficiency.
With the aid of the cooling medium supplied by the supply pump 122, heat of the motor 106, of the pump 104 and of other components inside the hydraulic cylinder unit 100 can be supplied to the outside.
For a hydraulic cylinder unit 100, which is also referred to as a hydraulic linear unit, a hydraulic cylinder or a motor-pump-hydraulic cylinder, for example, the pump 104 and/or the motor 106 of the actuator mechanism 102 are located inside the hydraulic cylinder unit 100. The cooling medium transports waste heat of the pump 104 and/or of the motor 106 and/or other hot spots (e.g., valves) inside the system away to the cooling mechanism. Here, the cooling means 108 has means 122 for conveying a cooling medium.
Arrow Q indicates introduction of energy from the pump 104 and the motor 106 into the cooling mechanism 108, and indicates discharge of energy from the cooling mechanism 108 to the outside. The energy introduction takes place in the form of thermal energy.
Fig. 2 is a schematic view of the hydraulic cylinder unit 100. The hydraulic cylinder unit 100 may be one embodiment of the hydraulic cylinder unit 100 described in the foregoing drawings. Fig. 2 corresponds to fig. 1 with the difference that the cooling means 108 is designed to guide a cooling medium onto the outer surface 224 of the hydraulic cylinder unit 100 in order to dissipate the absorbed thermal energy by convection and/or thermal radiation.
In this embodiment, coolant is delivered to the large surface 224 of the hydraulic cylinder unit 100. Here, the internally absorbed thermal energy may be discharged to the outside by natural convection and/or thermal radiation. For example, the coolant may be directed helically along the cylindrical surface 224 as shown. This effect can be further enhanced by additional cooling ribs.
Fig. 3 is a schematic view of the hydraulic cylinder unit 100. The hydraulic cylinder unit 100 may be one embodiment of the hydraulic cylinder unit 100 described in the foregoing drawings. Fig. 3 corresponds to fig. 2, with the difference that a fan 326 is arranged on the outer surface 224 for generating an air flow over the surface of the cooling element 108.
In this embodiment, the thermal energy is discharged to the surface of the hydraulic cylinder unit 100 as in the embodiment of fig. 2. The convection is enhanced here by means of a forced air flow, for example by means of a fan 326, for example acting radially or axially.
This embodiment has an improved heat discharge capability with the same surface. This results in improved efficiency of components such as the motor 106 due to the lower temperature at the hot spot.
Fig. 4 is a schematic view of the hydraulic cylinder unit 100. Fig. 4 corresponds to fig. 1, except that cooling mechanism 108 is coupled to heat exchanger 428.
In this embodiment, the thermal energy is discharged through a heat exchanger 428 to another cooling circuit 430. This embodiment has the maximum heat removal capability compared to the embodiment shown in fig. 1 to 3 and can achieve a very high power density. The waste heat of the system can be further utilized here.
Fig. 5-8 are simplified diagrams of temperature profiles 532, 634, 736, 838, respectively. In a cartesian coordinate system, the temperature is plotted on the vertical axis and the tube length or the position of the cooling circuit 120 is plotted on the horizontal axis. The dotted line indicates the (constant) internal temperature TInner partOr TIAnd (constant) external temperature TExterior partOr TA. Here, a coolant is used for the embodiment of the curves 532, 634 shown in fig. 5 and 7 and a refrigerant is used for the embodiment of the curves 736, 838 shown in fig. 6 and 8. Fig. 5 and 6 show temperature curves 532, 634 of the cooling medium inside the hydraulic cylinder unit, and fig. 7 and 8 show temperature curves 736, 838 of the cooling medium outside the hydraulic cylinder unit. This hydraulic cylinder unit may be a modification of the embodiment of the hydraulic cylinder unit 100 shown in fig. 1 to 4. The curve 532 shown in fig. 5 is taken as a straight line from the lower outside temperature TAExtends through the pipe section shown to an internal temperature TI. The average temperature difference Δ T is indicated. Curve 634 in FIG. 6 shows a constant boiling temperature TBoiling of waterOr TSAnd, an internal temperature TIWith boiling temperature TSThe temperature difference Δ T therebetween is constant. The curve 736 shown in FIG. 7 is taken as a straight line from the internal temperature TIExtends through the pipe section shown to a lower external temperature TA. The average temperature difference Δ T is indicated. Curve 838 in FIG. 8 shows a constant boiling temperature TBoiling of waterOr TSAnd, an external temperature TAWith boiling temperature TSThe temperature difference Δ T therebetween is constant.
By a targeted increase in the temperature of the refrigerant at the cooling means, a higher heat removal capacity is achieved. By a targeted reduction of the temperature of the refrigerant at the hot spot, an improvement of e.g. the efficiency of the motor will be achieved (the copper loss mainly determines the efficiency of the motor and decreases linearly with increasing temperature).
The advantages of the proposed inventive concept are presented below in a specific example. Here, fig. 5/7 show the use of a coolant, and fig. 6/8 show the use of a refrigerant:
surface area of motor-pump group (d 100mm, I212 mm): a. theInner part＝0.067m2；
Heat removal capacity of the tubes flowing through: alpha is alphaInner part＝1500W/(m2×K)；
For example, the temperature of the motor pump group: t isInner part＝80℃；
Outside temperature: t isOutside world＝20℃；
Boiling temperature of coolant: 70 ℃;
average temperature difference Δ T over the length of the tube/tube section:
FIG. 5: Δ T ═ (80 ℃ to 20 ℃)/2 ═ 30 ℃;
FIG. 6: Δ T80-70 ℃ ═ 10 ℃.
This results in a heat flow P in fig. 5, for example from the motor pump group to the cooling mediumZu＝A×α×ΔT＝3015W。
This results in a heat flow P in fig. 6, for example from the motor pump group to the cooling mediumZu＝A×α×ΔT＝1000W。
Surface area of the heat sink, for example: a. theExterior part＝1m2；
Heat discharge capacity of radiator: alpha is alphaExterior part＝20W/(m2×K)；
Average temperature difference Δ T over the length of the radiator:
FIG. 5: Δ T ═ (80 ℃ to 20 ℃)/2 ═ 30 ℃;
FIG. 6: delta T70-20 deg.C 50 deg.C.
This results in a heat flow P in fig. 7, for example from the cooling medium to the environmentAb＝A×α×ΔT＝600W。
This results in a heat flow P in fig. 8, for example from the cooling medium to the environmentAb＝A×α×ΔT＝1000W。
Since the temperature difference Δ T is reduced for the coolant compared to the refrigerant, the heat flow from the radiator to the outside is always small. Here, the heat energy discharged in the radiator plays a role of lowering the temperature. For the refrigerant, the heat energy discharged in the radiator functions as a change of the state of matter from a gaseous or vapor state to a liquid state. Here, the temperature remains constant throughout the change in the state of matter.
Since the heat transfer coefficient α is significantly greater on the inside than on the outside (the heat sink convects in a natural or forced manner) due to the flow through the tubes, the maximum dischargeable heat flow from the inside to the outside is significantly dependent on the heat transfer on the outside. With a and a constant, the heat transfer on the outside can only be improved by increasing the temperature difference Δ T.
Fig. 7 shows that the higher the flow rate of the coolant, the larger the temperature difference Δ T on the outer side, and the smaller the temperature difference Δ T on the inner side. The system reaches an average at a coolant temperature of 70 ℃. Here, P isZu＝PAb| A The amount of heat introduced into the system increases because the flow rate can cause the vortex tube friction losses to rise squared.
FIG. 8 shows the boiling temperature T of the refrigerantBoiling of waterDepending on the pressure. At a constant system pressure of 4 bar, for example, the coolant Solkane R123 has a boiling temperature of 70 ℃. Since the temperature of the inner side is 80 ℃, the state of the coolant changes from liquid to gas, and the heat energy increases at a constant temperature of 70 ℃. The process is reversed for the outer side.
Using a refrigerant as a coolant, the heat rejection capacity can be optimized even at low flow rates. This allows the tube friction losses and thus the additional thermal energy introduced to be kept low.
Use of refrigerant to advantageously provide heat budget for compact hydraulic equipment/systems
Improvements are provided that in turn increase the power density of the system. The heat losses of the system are advantageously combined here and can be used further if required. Here, a constant temperature (boiling temperature of the refrigerant) along the entire surface improves the heat discharging capability.
But also shows the thermodynamic principle using a refrigerator without the pressure of the refrigerant changing. Since the heat is transferred from a higher temperature level (e.g. 80 ℃ of the pump) to a lower temperature level (e.g. 20 ℃ of the outside) with a compact hydraulic shaft, a change in the boiling point of a refrigerant, such as a refrigerator, due to a change in pressure can be avoided.
The thermodynamic principle of the refrigerator is thus adopted so that the surface temperature remains the same over the entire surface, thereby improving the heat discharge capacity with the same surface area.
Fig. 9 is a schematic view of the hydraulic cylinder unit 100. Fig. 9 corresponds to fig. 1, with the difference that the cooling means 108 has means 940 for varying the system pressure of the cooling means 108. The means 940 for varying the system pressure are designed in particular to adjust the system pressure of the cooling medium in the cooling line.
The boiling point can be adjusted using a mechanism 940 for changing the system pressure, and thus the Δ T can be adjusted according to the operating conditions and the external conditionsInner partAnd Δ TExterior part. The working point is thus upwardOr pushed downward.
Fig. 10 is a schematic view of the hydraulic cylinder unit 100. Fig. 10 corresponds to fig. 1 with the difference that a throttle valve 1042 and a compressor 1044 are provided in the cooling circuit 118. The cooling means 108 are designed for varying the pressure of the cooling medium in the cooling circuit, in particular section by section, by means of a throttle 1042 and a compressor 1044. The cooling circuit is thus divided into at least two sections or pipe sections by means of the throttle 1042 and the compressor 1044.
With the refrigerant being delivered and compressed by the compressor 1044, heat of the motor 106, the pump 104, and other components inside the hydraulic cylinder 100 can be delivered to the outside. As a result of the pressure increase, the boiling temperature also increases and heat can be discharged to the outside via a higher temperature difference Δ T. The pressure of the cooled refrigerant is reduced by throttle 1042, thereby boiling at a lower (adjusted) boiling temperature TBoiling of waterIs directed to the hot spot. Where enhanced temperature absorption occurs.
The embodiment shown in fig. 10 employs a refrigerant that transports waste heat of the pump 104 and/or of the motor 106 and/or of other hot spots of the system (e.g., valves) away to the cooling mechanism. A compressor 1044 for changing the refrigerant pressure and a throttle 1042 for changing the refrigerant pressure are integrated in the cooling circuit 118.
In the embodiment shown in fig. 10, a refrigerant with a boiling point between the temperature of the assembly or tank and the ambient temperature is used as the cooling medium, and waste heat is transported away from the tank and/or pump 104 and/or motor 106 and/or other hot spots of the system (e.g., valves) to the cooling mechanism. Here, a refrigerant conveying mechanism 122 is employed.
Fig. 11 is a simplified diagram of temperature curve 1146. In a cartesian coordinate system, the temperature is plotted on the vertical axis and the tube length or the position of the cooling circuit 120 is plotted on the horizontal axis. The dotted line indicates the (constant) internal temperature TInner partOr TIAnd (constant) external temperature TExterior partOr TA. Here, for the embodiment shown in fig. 11, a refrigerant is employed. Fig. 11 shows a temperature curve 1146 of the refrigerant inside the hydraulic cylinder unit. This hydraulic pressureThe cylinder unit may be the embodiment of the hydraulic cylinder unit 100 shown in fig. 10. The curve 1146 in FIG. 11 shows a constant boiling temperature TBoiling of waterOr TSAnd, an internal temperature TIWith boiling temperature TSThe temperature difference Δ T therebetween is constant.
The advantages of the proposed inventive concept are presented below in a specific example. Parameters not explicitly described may be derived from the foregoing examples.
Surface area of motor-pump group (d 100mm, I212 mm): a. theInner part＝0.067m2；
Heat removal capacity of the tubes flowing through: alpha is alphaInner part＝1500W/(m2×K)；
For example, the temperature of the motor pump group: t isInner part＝80℃；
Outside temperature: t isOutside world＝20℃；
Boiling temperature of refrigerant: 63.7 ℃;
average temperature difference Δ T over the length of the tube/tube section:
FIG. 11: Δ T80-63.7 ℃ ═ 16.3 ℃.
This results in a heat flow P in fig. 11, for example from the motor pump group to the cooling mediumZu＝A×α×ΔT＝1630W。
PCompressor＝340W。
Surface area of the heat sink, for example: a. theExterior part＝1m2；
Heat discharge capacity of radiator: alpha is alphaExterior part＝20W/(m2×K)；
Boiling temperature: t isBoiling of water＝120℃；
Average temperature difference Δ T over the length of the radiator:
FIG. 11: Δ T120-20 ℃ ═ 100 ℃.
This results in a heat flow P in fig. 11, for example from the cooling medium to the environmentAb＝A×α×ΔT＝2000W。
For the refrigerant, the heat energy discharged in the radiator functions as a change of the state of matter from a gaseous or vapor state to a liquid state. Here, the temperature remains constant throughout the change in the state of matter.
Since the heat transfer coefficient α is significantly greater on the inside than on the outside (the heat sink convects in a natural or forced manner) due to the flow through the tubes, the maximum dischargeable heat flow from the inside to the outside is significantly dependent on the heat transfer on the outside. With a and a constant, the heat transfer on the outside can only be improved by increasing the temperature difference Δ T.
Boiling temperature T of refrigerantBoiling of waterDepending on the pressure. By increasing the pressure, the boiling temperature rises. On the basis of this, the refrigerant heated by the additionally introduced compressor work can be discharged with a high constant temperature difference by means of the cooling mechanism. Thereby, an improved heat discharging efficiency can be achieved. The pressure is reduced by means of a throttle valve, whereby the boiling point is at a lower temperature. This enables an adjusted temperature difference Δ T across the evaporator, which results in an increased heat absorption capacity.
Thus, by varying the boiling temperature, both internally and externally, the heat rejection capacity can be optimized.
Fig. 12 is a schematic view of the hydraulic cylinder unit 100. Fig. 12 corresponds to fig. 10, with the difference that the throttle valve 1042 and the compressor 1044 are controllable. In this embodiment, the temperature in the refrigerant circuit 118 can be adjusted by varying the pressure with the evaporator (on the inside) and/or by varying the pressure with the condenser (on the outside). The heat discharge capacity can thus be adjusted according to the operating conditions and the ambient conditions.
Fig. 13 is a schematic view of the hydraulic cylinder unit 100. Fig. 13 corresponds to a combination of the embodiment shown in fig. 3 and the embodiment shown in fig. 10. The cooling means 108 is designed to guide a cooling medium onto the outer surface 224 of the hydraulic cylinder unit 100 in order to dissipate the absorbed thermal energy by convection and/or thermal radiation. On the hydraulic cylinder unit 100, a ventilator 326 is provided on the outer surface 224 for generating an air flow on the surface of the cooling mechanism 108. Between the outer surface 224 and the cooling mechanism 108, an insulator 1346 is provided on the outer surface 224.
In this embodiment, the coolant is supplied to a large surface of the hydraulic cylinder unit 100. Here, the internally absorbed thermal energy may be discharged to the outside through natural convection or forced convection and thermal radiation. For example, the coolant may be directed helically along the cylindrical surface as shown.
Fig. 14 is a schematic view of the hydraulic cylinder unit 100. Fig. 14 corresponds to fig. 10, with the difference that a separate condenser 1448 with a fan 326 is provided in the cooling circuit 118.
Fig. 15 is a schematic view of the hydraulic cylinder unit 100. Fig. 15 corresponds to fig. 10 with the difference that a heat exchanger 428 is provided in the cooling circuit 118.
In this embodiment, the thermal energy is discharged through a heat exchanger 428 to another cooling circuit 430. This embodiment has the maximum heat discharge capacity and can achieve a very high power density compared to the embodiments shown in fig. 12 to 15. The waste heat of the system can be further utilized here.
Fig. 16 is a schematic view of the hydraulic cylinder unit 100. Fig. 16 corresponds to fig. 1 with the difference that a throttle valve 1042 and two check valves 1650, 1652 are provided in the cooling circuit 118 and the cooling circuit 118 is led through the chamber K1. Here, the chamber K1 functions as a compressor.
One aspect of the present embodiment is the use of a cooling medium that transports waste heat of the pump 104 and/or of the motor 106 and/or of other hot spots of the system (e.g., valves) away to the cooling mechanism. The cooling medium is conveyed by the reciprocating movement of the linear unit, i.e. the piston rod. The chamber K1 is part of the transport mechanism 122.
If piston rod 122 moves rightward in the drawing, the cooling medium is sucked. If the piston rod 122 is moved to the left in the figure, the cooling medium is compressed and conveyed towards the cooling mechanism. Provided that a compressible cooling medium is present. The two following examples describe further embodiments.
One embodiment illustrates a cooling circuit 118 on the hydraulic cylinder 100 with an integrated pump 104 and/or motor 106. In this case, the cooling medium is passively conveyed by the cylinder movement.
Advantageously, the temperature ratio inside the system is homogenized. No additional conveying means are required here.
In the differential mode of the synchronous cylinder, the chambers K2 and K3 are the same area as K4, and therefore chamber K1 is not required. This chamber K1 is now used to convey the cooling medium. Two check valves 1650, 1652 determine the flow direction.
Fig. 17 is a schematic view of the hydraulic cylinder unit 100. Fig. 17 corresponds to fig. 16, with the difference that the cooling mechanism has a volume compensation reservoir 1754 coupled to the cooling circuit for compensating the coolant volume in the cooling circuit 118. In this exemplary embodiment, an accumulator 1754 for volume compensation is located in the line 120 for the cooling medium. Thus, incompressible cooling media, such as pressure fluids (e.g. hydraulic oil, leakage oil) can also be used here.
Fig. 18 is a schematic view of the hydraulic cylinder unit 100. In this embodiment, a simple differential cylinder 1856 is used to effect the reciprocating motion. The motor-pump-set 102 is located outside or inside the cylinder 1856. Since two chambers K5 and K6 are used here for the reciprocating movement, a single delivery cylinder 1858 is mounted in parallel, the piston rod 1860 of which is coupled to the piston rod 112 of the hydraulic cylinder unit 100. Thus, when the piston rod 112 moves, the volume of the delivery cylinder 1858 also changes, and the cooling medium flows via the check valves 1650, 1652 into or out of the delivery chamber K7, which is also referred to as the cylinder chamber K7.
The subsequent embodiments show a part of a hydraulic device, which for example comprises a tank, a set and a hydraulic linear unit. Here, the leaking oil of the pump is used to cool components such as the electric motor. A uniform temperature ratio is advantageously achieved within the system. Advantageously, no additional transport mechanism is required. Here, no separate supply for the cooling medium is required, since the leaking oil is under pressure.
Fig. 19 is a schematic view of the actuator mechanism 102. The actuator mechanism 102 may be one embodiment of the actuator mechanism 102 shown in the previous figures. The actuator mechanism includes a pump 104 and a motor 106 coupled to the pump 104. The pump 104 is connected to the tank 1964 by a suction line 1962. A pressure line 1966 extends from the pump 104 for actuating a hydraulic mechanism, such as the cylinder unit 100 described in the preceding figures. The pump has a leaking oil connection 1967 from which extends a leaking oil line 1968 that extends around the motor 106. The leaking engine oil line 1968 is designed to absorb heat of the electric machine by means of the hydraulic medium conducted in the leaking engine oil line 1968 serving as a cooling medium, and to conduct the heated hydraulic medium back into the tank 1964.
The hydraulic unit 100 is comprised of a tank, a pump 104 and a motor 106, which converts electrical power into hydraulic power. Oil located in the tank 1964 is drawn to the pump 104 via a suction line 1962 and drained at a higher pressure via a pressure line 1966. Most pumps 104 have a leaking oil connection 1967 due to clearances within the transmission or gears. The leaking oil has a residual pressure of 1-4 bar there and is used to cool the electric machine 106. Thus, the thermal power of the motor 106 enters the canister 1964 through the leaking oil and may be discharged through its surface.
Fig. 20 shows a schematic view of the actuator mechanism 102. Fig. 20 corresponds to fig. 19, except that a radiator 1448 with a fan 326 is provided between the motor 106 and the tank 1964 in the leaking oil line 1968.
The embodiment shown in fig. 20 corresponds to the embodiment shown in fig. 19 with an additional cooling mechanism (radiator 1448 with fan 326) that leaks oil. Here, the thermal power of the pump 104 and the motor 106 is discharged to the outside air without entering the tank 1964.
Fig. 21 is a schematic view of the actuator mechanism 102. Fig. 21 corresponds to fig. 19, except that a heat exchanger 428 is provided between the motor 106 and the tank 1964 in the leaking engine oil line 1968.
The embodiment shown in fig. 21 corresponds to the embodiment shown in fig. 20, but with a heat exchanger 428 as the cooling mechanism. Here, the thermal power of the pump 104 and of the motor 106 is discharged to the second cooling circuit. And thus the thermal power can be continuously utilized.
Fig. 22 is a schematic view of the actuator mechanism 102. Fig. 22 corresponds to fig. 19, except that a leaking oil line 1968 branches off from the pressure line 1966, and a throttle valve 1042 is provided between the pressure line 1966 and the section of the leaking oil line 1968 that extends around the motor 106.
The embodiment shown in fig. 22 corresponds to the embodiment shown in fig. 19, but with a throttle 1042 in the pressure line. Since not every pump has a leakage oil connection, a volume flow can be generated in the pressure line by means of the throttle 1042.
Fig. 23 is a schematic view of the hydraulic cylinder unit 100. Fig. 23 corresponds to fig. 1, with the difference that the cooling circuit 118 passes through the pump 104. The aspect of the proposed solution shown in fig. 17 to 22 is thus realized in the hydraulic cylinder unit 100.
This embodiment shows a synchronized cylinder in a differential configuration. The pump and the motor are located in their inner chambers and deliver the working medium (hydraulic oil) to the respective chamber K1, K2, K3 or K4. Thereby exerting a force on the piston rod and causing the piston rod to move in the direction shown.
The vast majority of heat loss occurs in the motor and pump. Without the cooling circuit shown in red, the heat loss must first reach the surface via the two walls and via the working medium of the hydraulic cylinder. Without a large thermal resistance, the system would overheat without additional heat removal and therefore would have to operate at reduced power. Since the leaking oil of the pump still has a residual pressure of 1-4 bar, said leaking oil is used to cool the motor. The thermal power of the pump and of the motor thus reaches the cooling mechanism by leaking oil.
Fig. 24 shows a schematic diagram of a hydraulic system 2470. The hydraulic system 2470 has three hydraulic cylinder units 100. These hydraulic cylinder units 100 may be modifications of the hydraulic cylinder units 100 described in the foregoing drawings, respectively. The cooling circuit 120 of the cooling mechanism 108 has a radiator 1448 and a fan 326. Here, the cooling lines 120 are suitably shaped such that the hydraulic cylinder units 100 are flowed through in parallel. Therefore, the three hydraulic cylinder units 100 have one common cooling mechanism 108.
In the embodiment shown in fig. 24, the hydraulic system 2470 includes a plurality of hydraulic linear units 100, such as hydraulic cylinder units 100. The cooling circuit 118 absorbs heat of the plurality of linear units 100. Alternatively, for example, an adsorption refrigerator can be placed downstream. In this case, the radiator 1448 is replaced with a heat exchanger.
The foregoing concept provides an improvement in the heat budget of the compact hydraulic system 2470. This results in an increase in the power density of the system. The heat losses of the system 2470 are pooled and can be further used as needed.
A significant portion of the heat loss of the compact shaft (Kompaktachse)100 occurs at the pump 104 and the motor 106. The waste heat is conveyed from the compact shaft 100 via the cooling circuit 118 to a cooling device, for example a radiator 1448 with the fan 326.
Fig. 25 shows a schematic diagram of a hydraulic system 2470. This figure corresponds to fig. 24, with the difference that the hydraulic cylinder units 100 are arranged in series in the cooling circuit 118.
This embodiment thus corresponds to the embodiment of fig. 24, but does not work in parallel, but in series.
Fig. 26 shows a schematic diagram of a hydraulic system 2470. This figure corresponds to fig. 24 with the difference that instead of a radiator and a ventilator, the cooling circuit 118 has a heat exchanger 428. Generally, the heat exchanger 428 is a mechanism for utilizing waste heat, such as for heating water.
Fig. 27 shows a simplified diagram of adsorption chiller 2772 and hydraulic system 2470. The hydraulic system 2470 may be the embodiment of the hydraulic system 2470 shown in fig. 24-26. Adsorption chiller 2772 is coupled to a cooling load 2774, such as a switchgear and return chiller 2776. In one embodiment, the hydraulic system 2470 is designed to control the steam turbine 2778.
In many applications, such as for example in the control of steam turbines, a plurality of shafts 100 are arranged spatially close to one another. The shafts are interconnected by a central cooling circuit 118. Optionally, the collected thermal energy can be used further here, for example in an adsorption refrigerator 2772 for cooling, for example, a switch cabinet 2774.
The possible utilization of the waste heat of the compact shaft 100 in the control of gas and steam turbines is described here by way of example. In this application, a plurality of compact axles 100 in combination are located at an ambient temperature of at most 80 ℃. These compact shafts 100 can operate at temperatures up to 100 ℃.
The thermal energy of the individual compact shafts 100 is first collected by means of the cooling circuit 118 and fed to the adsorption refrigerator 2772. The 20kW thermal power can now be converted into 12kW cooling power, wherein 32kW of heat needs to be dissipated in the return cooler 2776. With this 12kW of heat, for example, the switch cabinet 2774 or the like can be cooled at ambient temperature without an additional refrigerator. The lost thermal power of 20kW, which is normally discharged to the outside, can thus be converted into a usable cooling power of 12 kW.
For the example, the following values are taken, for example:
power of the shaft: 15 kW;
efficiency of the shaft: 0.7;
full load of shaft: 50 percent;
waste heat of the shaft: 2.25 kW;
number of shafts: 9;
total waste heat: -20 kW.
Fig. 28 is a flow chart of method 2890. This method 2890 for driving a hydraulic unit according to an embodiment of the invention comprises a step 2892 for controlling the actuator mechanism and a step 2894 for cooling the actuator mechanism with a cooling mechanism coupled to the actuator mechanism.
The embodiments described herein take advantage of the trend toward distributed drive, compact drive, waste heat, and higher power density of the system.
The embodiments shown are merely exemplary and may be combined with one another.
List of reference numerals
100 hydraulic unit and hydraulic cylinder unit
102 actuator mechanism
104 pump
106 electric machine
108 cooling mechanism
110 main body
112 conveying mechanism
114 flange
116 direction and moving direction
118 cooling circuit
120 cooling pipeline
122 conveying mechanism
K1 cavity, cylinder cavity and conveying cavity
K2 cavity, cylinder cavity
K3 cavity, cylinder cavity
K4 cavity, cylinder cavity
224 outer surface, surface
326 ventilator
428 heat exchanger
430 cooling circuit
532 temperature profile
634 temperature profile
736 temperature curve
838 temperature curve
TInner partInternal temperature
TExterior partOutside temperature
Delta T temperature difference
940 mechanism for varying system pressure of cooling mechanism
1042 throttle valve
1044 compressor
1146 temperature curve
1448 radiator and condenser
1650 check valve
1652 check valve
1754 volume compensating accumulator
1856 Cylinder
1858 conveying cylinders
1860 piston rod
K5 cavity, cylinder cavity
K6 cavity, cylinder cavity
K7 cavity, cylinder cavity and conveying cavity
1962 suction line
1964A pot
1966 pressure line
1967 leakage engine oil joint
1968 leakage engine oil pipeline
2470 Hydraulic System
2772 adsorption refrigerator
2776 Return cooler
2778 steam turbine
2890 method
2892 control step
2894 Cooling step
Claims (19)
1. A hydraulic unit (100) with an actuator mechanism (102) for driving the hydraulic unit (100), wherein the actuator mechanism (102) comprises a pump (104) and a motor (106), wherein the motor (106) is designed for driving the pump (104), and wherein, the pump (104) is designed for pumping a hydraulic medium into a cavity of the hydraulic unit (100) in order to move a piston of the hydraulic unit (100), characterized by a cooling mechanism (108) thermally coupled to the actuator mechanism (102) for cooling the actuator mechanism (102), wherein the cooling device (108) comprises a cooling circuit (118) with a cooling line (120) for a cooling medium and a conveying device (122) for conveying the cooling medium in the cooling line (120), wherein the cooling medium is a refrigerant.
2. The hydraulic unit (100) as claimed in claim 1, wherein the cooling mechanism (108) is designed for directing a cooling medium to an outer surface (224) of the hydraulic unit (100) for expelling the absorbed thermal energy by convection and/or thermal radiation.
3. The hydraulic unit (100) as claimed in any one of the preceding claims, having a ventilator (326) for generating an air flow over the surface of the cooling means (108).
4. The hydraulic unit (100) as claimed in claim 1 or 2, wherein the cooling mechanism (108) has a mechanism (940) for changing a system pressure of the cooling mechanism (108).
5. The hydraulic unit (100) as claimed in claim 4, wherein the cooling mechanism (108) has a throttle valve (1042) and/or a compressor (1044).
6. The hydraulic unit (100) as claimed in claim 3, wherein the cooling mechanism (108) is coupled with the heat exchanger (428) and/or the cooling mechanism (108) has a radiator (1445).
7. The hydraulic unit (100) of claim 1 or 2, wherein the hydraulic unit (100) at least partially surrounds the actuator mechanism (102).
8. The hydraulic unit (100) as claimed in claim 1 or 2, wherein the cooling mechanism (108) has at least one check valve (1650, 1652) on a cooling circuit (118), wherein the cooling circuit (118) passes through a cylinder chamber (K1; K7) of the hydraulic unit (100).
9. The hydraulic unit (100) as claimed in claim 1 or 2, wherein the cooling mechanism (108) has a volume compensation reservoir (1754) coupled to the cooling circuit (118) for compensating a volume of the cooling medium in the cooling circuit (118).
10. The hydraulic unit (100) according to claim 1 or 2, wherein the cooling medium is a hydraulic medium.
11. The hydraulic unit (100) as claimed in claim 1 or 2, wherein the cooling mechanism (108) has a mechanism (940) for changing the system pressure of the coolant as cooling medium in the cooling line (120).
12. The hydraulic unit (100) as set forth in claim 6, wherein a ventilator (326) cooperates with the radiator.
13. The hydraulic unit (100) of claim 7, wherein the actuator mechanism (102) is disposed inside the hydraulic unit (100).
14. The hydraulic unit (100) as recited in claim 8, wherein the delivery mechanism (122) comprises at least one check valve (1651, 1652) and a cylinder chamber (K1; K7) for delivering the cooling medium.
15. The hydraulic unit (100) as claimed in claim 10, wherein a leaking oil connection (1967) of the pump (104) is coupled with the cooling circuit (118) for providing the hydraulic medium.
16. A hydraulic system (2470) with a first hydraulic unit (100) according to any one of the preceding claims and at least one second hydraulic unit (100) according to any one of the preceding claims, which have a common cooling mechanism (108).
17. The hydraulic system (2470) of claim 16, wherein the first hydraulic unit (100) and the at least second hydraulic unit (100) are arranged in parallel and/or in series in a cooling circuit (118) of the cooling mechanism (108).
18. Use of waste heat of a hydraulic unit (100) according to any one of claims 1 to 15 and/or of waste heat using a hydraulic system (2470) according to any one of claims 16 to 17 for another cooling process and/or a thermal process by means of a refrigerator (2772).
19. A method (2890) for driving a hydraulic unit (100) according to any one of claims 1-15, wherein the method (2890) has the steps of:
controlling (2892) an actuator mechanism (102); and
the actuator mechanism (102) is cooled (2894) with a cooling mechanism (108) coupled with the actuator mechanism (102).
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014226665.3 | 2014-12-19 | ||
| DE102014226665 | 2014-12-19 | ||
| DE102015206234 | 2015-04-08 | ||
| DE102015206236.8A DE102015206236A1 (en) | 2014-12-19 | 2015-04-08 | Hydraulic unit and method for operating a hydraulic unit |
| DE102015206236.8 | 2015-04-08 | ||
| DE102015206234.1 | 2015-04-08 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105822629A CN105822629A (en) | 2016-08-03 |
| CN105822629B true CN105822629B (en) | 2021-05-04 |
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|---|---|---|---|
| CN201511036292.5A Active CN105715625B (en) | 2014-12-19 | 2015-12-19 | Hydraulic cylinder unit |
| CN201511036291.0A Active CN105822629B (en) | 2014-12-19 | 2015-12-19 | Hydraulic unit and method for operating a hydraulic unit |
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| CN201511036292.5A Active CN105715625B (en) | 2014-12-19 | 2015-12-19 | Hydraulic cylinder unit |
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| TWI702345B (en) * | 2019-06-13 | 2020-08-21 | 高明鐵企業股份有限公司 | Preloaded structure of gravity-compensated linear drive device |
| CN116658491B (en) * | 2023-07-27 | 2023-09-22 | 湖南协力液压有限公司 | Low-impact hydraulic cylinder dynamic control method and system based on fluid resistance optimization |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN105822629A (en) | 2016-08-03 |
| ITUB20159614A1 (en) | 2017-06-18 |
| ITUB20159396A1 (en) | 2017-06-18 |
| CN105715625B (en) | 2021-04-23 |
| CN105715625A (en) | 2016-06-29 |
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