CN105822629A - Hydraulic unit and method for operating hydraulic unit - Google Patents
Hydraulic unit and method for operating hydraulic unit Download PDFInfo
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- CN105822629A CN105822629A CN201511036291.0A CN201511036291A CN105822629A CN 105822629 A CN105822629 A CN 105822629A CN 201511036291 A CN201511036291 A CN 201511036291A CN 105822629 A CN105822629 A CN 105822629A
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- hydraulic pressure
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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
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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
- F15B21/08—Servomotor systems incorporating electrically operated control means
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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
- F15B21/14—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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- Fluid Mechanics (AREA)
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- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a hydraulic unit (100) with an actuator device (102) for operating the hydraulic unit (100), wherein the actuator device (102) comprises a pump (104) and / or a motor (106). The hydraulic unit (100) has a cooling device (108), which is thermally coupled to the actuator device (102) for cooling the actuator device (102).
Description
Technical field
The present invention relates to a kind of hydraulic pressure unit, a kind of corresponding hydraulic system, the application of a kind of used heat to corresponding hydraulic pressure unit or corresponding hydraulic system and a kind of method for driving hydraulic pressure unit.
Background technology
In the prior art, heat along assembly surface by (such as controlling unit, pump, motor ... in) discharge of heat path, and heat is along surface (convectively with radiation ground) discharge.
Owing to these assemblies are more and more integrated in systems, so reducing described surface, and focus is not near surface.
Summary of the invention
Under this background, use solution proposed here, propose a kind of hydraulic pressure unit according to main claim, a kind of use the hydraulic system of this hydraulic pressure unit, the application of a kind of used heat to corresponding hydraulic pressure unit or corresponding hydraulic system and a kind of method for driving hydraulic pressure unit.Useful design can be obtained by corresponding dependent claims and follow-up explanation.
For compact hydraulic pressure unit, can be by the integrated of cooling body be avoided overheated and hot localised points.It can be advantageous to improve the power density of hydraulic pressure unit.Simultaneously, it is possible to achieve the uniform temperature ratio of internal system.
Solution proposed here provides a kind of hydraulic pressure unit, it is with the actuation mechanism for driving hydraulic pressure unit, wherein, this actuation mechanism includes pump and/or motor, it is characterized in that the cooling body for cooling down actuation mechanism with actuation mechanism thermal coupling, wherein, this cooling body includes the cooling circuit with the cooling line for cooling medium and for carrying the conveying mechanism of the cooling medium in cooling line, wherein, cooling medium is a kind of cold-producing medium.
Hydraulic pressure unit can be arbitrary hydraulic pressure unit, such as unit, motor-pump-group (Sytronix), if desired with hydraulic cylinder unit or each assembly such as pump, valve, control chamber, cylinder, motor etc. of motor-pump-group.Hydraulic cylinder unit can be the linear unit of hydraulic pressure, the compact axle of hydraulic pressure, hydraulic cylinder, motor-pump-hydraulic cylinder or the synchronized cylinder especially with differential fashion particular with internally positioned actuation mechanism.Motor can be motor.Motor can be designed to drive pump.This pump is designed to hydraulic medium to be pumped in the chamber of hydraulic cylinder unit, in order to the piston of hydraulic cylinder unit is moved.Cooling body can be designed to cool down actuation mechanism, addedly or alternatively cooling hydraulic cylinder unit or the subregion of hydraulic cylinder unit.
Cooling body can include the cooling circuit with the cooling line for cooling medium and for carrying the conveying mechanism of the cooling medium in cooling line.Cooling line can be a kind of cooling pipe at this.In one embodiment, cooling body can include multiple cooling line or cooling duct.Cooling medium can be a kind of heat carrier or cold carrier at this.Cooling medium may be used for quantity of heat given up.Thus can be in actuation mechanism, particularly on the outer surface of actuation mechanism, cooling line or cooling circuit the first section is set.Cooling medium thus heat energy outwards can be carried from the focus within hydraulic cylinder unit.Here, focus can be at local heating spatially.Can be coolant supply unit or cooling medium supply unit for carrying the conveying mechanism of cooling medium.
Cooling medium is cold-producing medium.This cold-producing medium can transmit heat in kind of refrigeration cycle on the contrary with thermal gradient, thus ambient temperature can be higher than the temperature of hydraulic pressure unit to be cooled down.This cold-producing medium such as can be applied in heat pipe in the case of not changing pressure, or such as can also apply in the cyclic process of refrigerator in the case of changing pressure.
Additionally, cooling body can be designed to cooling medium to guide to the outer surface of hydraulic pressure unit, in order to by convection current and addedly or substitute and discharge absorbed heat energy by heat radiation.Between cooling body and outer surface, an insulating part or insulating surface can be set.Thus the used heat of focus can be transmitted by heat targetedly and be transported to the biggest surface of cooling body, cooling body, cooling unit or heat exchanger.
Hydraulic pressure unit can have the ventilation blower for producing air-flow on the surface of cooling body and/or heat exchanger and/or radiator.Thus can advantageously especially by convection current, one section or the subregion of cooling body be cooled down.
Cooling body can have the mechanism of the system pressure for changing cooling body.Cooling body particularly can be with the mechanism with the system pressure for changing the cooling medium as coolant of the form in cooling line.Thus can optimally adjust the pressure of cooling medium, for transmitting heat content by cooling medium.
Cooling body can couple with heat exchanger.Cooling body can also have radiator.It would also be beneficial that cooling body has choke valve, addedly or alternatively there is compressor.Here, cooling body particularly can have choke valve, addedly or alternatively there is choke valve, in order to the pressure of the cooling medium in change cooling circuit.Here, the pressure of cooling medium can change on segment-by-segment basis.Therefore, the pressure cooling medium in the first section of cooling circuit can be differently configured from the second pressure of the cooling medium in the second section of cooling circuit.
Hydraulic pressure unit can hold actuation mechanism at least in part.Actuation mechanism particularly can be arranged on the inside of hydraulic pressure unit.Therefore, the moveable cylinder of the particularly hydraulic pressure unit of hydraulic cylinder unit form can hold actuation mechanism at least in part when indentation.Hydraulic pressure unit or the inner surface of hydraulic cylinder unit can abut on the outer surface of actuation mechanism.Cooling body can be at least partially disposed on hydraulic pressure unit or between the inner surface of hydraulic cylinder unit and the outer surface of actuation mechanism.
Cooling body can have at least one check-valves being positioned on cooling circuit.Here, this cooling circuit can through hydraulic pressure unit or the cylinder chamber of hydraulic cylinder unit.Here, conveying mechanism particularly can include at least one check-valves and cylinder chamber, in order to conveying cooling medium.Cooling medium thus can be flowed in cylinder chamber via entrance, and via outlet from cylinder chamber flow out.This embodiment is not only feasible in the case of the integrated form make of hydraulic cylinder, and the most feasible when (hydraulic pressure) piston-cylinder unit is with externally-located motor-pump-group.
Cooling body can have the volume compensation reservoir coupled with cooling circuit, for compensating the volume of the cold-producing medium in cooling circuit.It is thus possible, for instance in the case of the stereomutation of cooling circuit, this such as causes because of the cylinder chamber of the volume with change in cooling circuit, it is possible to use this volume compensation reservoir provides additional cooling medium, or unnecessary cooling medium is kept in.Cylinder chamber in cooling circuit is in the part that this can be conveying mechanism.Thus cylinder chamber can also be referred to as conveyor chamber.This embodiment is not only feasible in the case of the integrated form make of hydraulic cylinder, and the most feasible when (hydraulic pressure) piston-cylinder unit is with externally-located motor-pump-group.
Additionally, in one embodiment, cooling medium can be hydraulic medium.The leakage machine oil joint of pump can couple with cooling circuit especially, in order to provides hydraulic medium.Leakage machine oil thus can be such as hydraulic medium.Hydraulic medium can be hydraulic fluid or for the energy transmitting in hydraulic system and/or the fluid of power.Thus hydraulic medium can be heat-staple, say, that viscosity (the most dynamically viscosity or motion viscosity) is had less temperature affects, has relatively low compressibility and shear stability and less formation of foam.This embodiment is not only feasible in the case of integrated form make, and the most feasible for hydraulic pressure unit, motor-pump-group and the piston-cylinder unit with externally-located motor-pump-group at large.
Proposing a kind of hydraulic system, it is with a modification of the first hydraulic pressure unit proposed here and at least one modification of the second hydraulic pressure unit of proposing here, and they have common cooling body.Thus can be that at least two hydraulic pressure unit uses a cooling body.Here, the first hydraulic pressure unit and at least the second hydraulic pressure unit are arranged in the cooling circuit of cooling body concurrently or serially.In one embodiment, multiple hydraulic pressure units the most parallel is arranged combined with the layout of at least part of serial of multiple hydraulic pressure units.Here, the deployment scenarios of the parallel and serial hydraulic pressure unit that can relate in cooling circuit.
Propose, the used heat of the modification of the hydraulic pressure unit that use proposes here, and/or use the used heat of the modification of the hydraulic system proposed here, for particularly by means of another cooling procedure and/or the thermal process of refrigeration machine.Thus the used heat from least one hydraulic pressure unit can be used for cooling procedure or thermal process, such as to drive adsorbent refrigerator.Not only for hydraulic pressure unit, and the most such as can carry out heat energy utilization for hydraulic test or Sytronix-motor-pump-unit in this way.
Proposing a kind of method being used for and driving the hydraulic pressure unit proposed here, wherein, the method has following steps:
Control actuation mechanism；With
Utilize the cooling body coupled with actuation mechanism to cool down actuation mechanism.
This design variant that can also utilize the method form of the present invention quickly and effectively realizes the purpose of the present invention.
One aspect of the present invention is the Cooling Design scheme of hydraulic pressure unit.For hydraulic pressure unit, motor and pump can be encased in the cylinder interior of hydraulic pressure unit or hydraulic cylinder unit.In one embodiment, there are cooling medium or cooling duct at this, its heat outwards discharges from motor and pump.
In the optional embodiment of one, coolant circulates in holding the inner shell of motor and pump.Alternatively, heat dissipation can be carried out by radiator or heat exchanger here.
In one embodiment, the coolant in cooling body or cold-producing medium can be utilized here.Thus can be designed to cooling body use coolant to cool down, or alternatively use cold-producing medium.Here, refrigerant loop can have choke valve selectively.Cooling circuit thus can have multiple refrigerant loop.
In a kind of specific implementation, hydraulic pressure unit or the cylinder of hydraulic cylinder unit or cylinder chamber or the assistant cylinder coupled with hydraulic pressure unit or hydraulic cylinder unit can be used as coolant supply unit.
In one embodiment, selectively hydraulic medium can be used as cooling medium.Here, hydraulic medium leaking on machine oil joint or can access at delivery side of pump.
Advantageously can by multiple axles or the used heat of hydraulic cylinder unit collect, and use process technology to utilize heat.
Accompanying drawing explanation
The present invention is the most exemplarily described in detail in detail.Wherein:
Fig. 1-Fig. 4 is respectively the schematic diagram of hydraulic pressure unit；
Fig. 5-Fig. 8 is respectively the curve chart of the simplification of temperature tendency；
Fig. 9-Figure 10 is respectively the schematic diagram of hydraulic pressure unit；
Figure 11 is the curve chart of the simplification of temperature tendency；
Figure 12-Figure 18 is respectively the schematic diagram of hydraulic pressure unit according to an embodiment of the invention；
Figure 19-Figure 22 is respectively the schematic diagram of actuation mechanism；
Figure 23 is the schematic diagram of hydraulic pressure unit；
Figure 24-Figure 26 is respectively the schematic diagram of hydraulic system；
Figure 27 is absorption cooler and the simplification figure of hydraulic system；With
Figure 28 is the flow chart of method.
Detailed description of the invention
Identical or similar parts can indicate identical or similar reference in following accompanying drawing.Additionally, these accompanying drawings and explanation and claims thereof contain total combination of multiple features.Here, one skilled in the art will appreciate that these features can also be investigated individually or combined with other combination not being expressly recited here.
Fig. 1 is the schematic diagram of the hydraulic cylinder unit 100 according to an embodiment.To illustrate at this, the general scheme proposed here is made by what the embodiment as hydraulic pressure unit of hydraulic cylinder unit was introduced.It will be apparent that the scheme to hydraulic pressure unit cooling proposed here is confined to use hydraulic cylinder unit the most at large.It is also conceivable to the solution proposed here to be such as applied to common hydraulic pressure unit, motor-pump-group (Sytronix), hydraulic cylinder unit, with motor-pump-group or the hydraulic cylinder unit of each assembly, each assembly described is such as pump, valve, control chamber, cylinder, motor or similar assembly.Thus to as follows by hydraulic cylinder unit as the explanation of the embodiment of hydraulic pressure unit, following understanding should be done, in order to summarily introduce solution proposed here, the only removable example only by the hydraulic cylinder unit with the cooling-part correspondingly coupled discloses the program, but solution proposed here utilizes one of aforementioned components or unit to replace hydraulic cylinder unit to work.
It it is the synchronized cylinder (Gleichgangzylinder) using differential (Differenzial) make for the hydraulic cylinder unit as hydraulic pressure unit 100 exemplarily selected as described below.This hydraulic cylinder unit (being provided with reference 100 for hydraulic pressure unit the most typically) has the actuation mechanism 102 for driving hydraulic cylinder unit 100.This actuation mechanism 102 includes pump 104 and for driving the motor 106 of pump 104.Actuation mechanism 102 is arranged in hydraulic cylinder unit 100 inner chamber.For cooling down cooling body 108 and actuation mechanism 102 thermal coupling of actuation mechanism 102.
In the embodiment shown in fig. 1, hydraulic cylinder unit 100 has main body 110 and the piston rod 112 guided at this main body 110 cathetus.Main body 110 has flange (Anflanschung) 114 in side.This hydraulic cylinder unit 100 is through appropriately designed so that piston rod 112 laterally can move relative to flange 114 side of main body 110.Main body 110 is through suitable molding, thus it provides for piston rod 112 and guides.Main body 110 and piston rod 112 are through suitable molding, thus provide four chambers K1, K2, K3, K4, wherein, hydraulic medium is pumped in corresponding chamber K1, K2, K3, K4, or pump out from corresponding chamber K1, K2, K3, K4, so that piston rod 112 moves.Chamber K1, K2, K3 arrange radially around actuation mechanism 102.Chamber K4 is formed with the end side surface relative with flange 114 of main body 110 by piston rod 112.
Pump 104 and motor 106 are positioned in the room of hydraulic cylinder unit 100, and working media (hydraulic oil) is transported in corresponding chamber K1, K2, K3 or K4.Thus piston rod 112 is applied power, and this piston rod is moved along shown direction 116.
Cooling body 108 includes the cooling circuit 118 with the cooling line 120 for cooling medium, and includes the conveying mechanism 122 for carrying the cooling medium in cooling line 120.Cooling line 120 provides for cooling medium and guides.In the embodiment shown in fig. 1, as conveying mechanism 122, the delivery pump 122 being arranged in cooling circuit 118 is employed.
Cooling body 108 can be designed to guide coolant, cold-producing medium or hydraulic medium as cooling medium.In a simple embodiment, ratio as shown in fig. 1, uses coolant as cooling medium.
Overwhelming majority thermal loss produces in motor 106 and pump 104.These thermal loss must first pass through two walls of main body 110 in the case of not having described cooling circuit 118 and arrive surface via the working media of hydraulic cylinder unit 100.Cooling body 108 provides additional heat dissipation, utilizes this cooling body can avoid the bigger resistance to heat of system, so avoid overheated.Thus the effect to reduce can be avoided to run.
By means of the cooling medium carried by delivery pump 122, the heat of other assembly within motor 106, pump 104 and hydraulic cylinder unit 100 can outwards be carried.
For being such as also referred to as the hydraulic cylinder unit 100 of hydraulic linear unit, hydraulic cylinder or motor-pump-hydraulic cylinder, it is internal that the pump 104 of actuation mechanism 102 and/or motor 106 are positioned at hydraulic cylinder unit 100.Cooling medium pump 104 and/or motor 106 and/or the used heat of other focus of internal system (such as valve) be transported away from arriving cooling body.Here, cooling body 108 has the mechanism 122 for carrying cooling medium.
Arrow Q represents that energy is incorporated into cooling body 108 from pump 104 and motor 106, and represents that energy is discharged outside to from cooling body 108.Energy introduces and carries out with the form of heat energy.
Fig. 2 show the schematic diagram of hydraulic cylinder unit 100.This hydraulic cylinder unit 100 can be an embodiment of the hydraulic cylinder unit 100 described in aforementioned figures.Fig. 2 corresponding to Fig. 1, difference is, cooling body 108 is designed to cooling medium to direct on the outer surface 224 of hydraulic cylinder unit 100, in order to discharge, by convection current and/or heat radiation, the heat energy absorbed.
In this embodiment, deliver coolant on the big surface 224 of hydraulic cylinder unit 100.Here, the heat energy of absorbed inside can be emitted into the external world by free convection and/or heat radiation.Such as, coolant can the most helically guide along cylindrical surface 224.This effect further can be strengthened by additional cooling ribs.
Fig. 3 show the schematic diagram of hydraulic cylinder unit 100.This hydraulic cylinder unit 100 can be an embodiment of the hydraulic cylinder unit 100 described in aforementioned figures.Fig. 3 corresponding to Fig. 2, difference is, is provided with ventilation blower 326 on outer surface 224, for producing air-flow on the surface of cooling body 108.
In this embodiment, heat energy is disposed to the surface of hydraulic cylinder unit 100 as the embodiment in Fig. 2.Here, compulsory air-flow is utilized such as to utilize ventilation blower 326-the most axially or radially to make land used-strengthen convection current.
In the case of surface is identical, this embodiment has the heat dissipating capacity of improvement.Owing to the temperature at focus is relatively low, this causes the efficiency of the assembly such as raising of motor 106.
Fig. 4 show the schematic diagram of hydraulic cylinder unit 100.Fig. 4 corresponding to Fig. 1, difference is, cooling body 108 couples with heat exchanger 428.
In this embodiment, heat energy is emitted into another cooling circuit 430 by heat exchanger 428.This embodiment has the heat dissipating capacity of maximum compared to the embodiment shown in Fig. 1 to Fig. 3, and can realize the highest power density.Can be further with the used heat of system at this.
Fig. 5 to Fig. 8 is respectively the simplification figure of temperature curve 532,634,736,838.In cartesian coordinate system, the longitudinal axis marks temperature, transverse axis marks length of tube or the position of cooling line 120.Dotted line represents (constant) internal temperature TInternalOr TI(constant) external temperature TOutsideOr TA.Here, for the embodiment of the curve 532,634 shown in Fig. 5 and Fig. 7, use coolant, for the embodiment of the curve 736,838 shown in Fig. 6 and Fig. 8, use cold-producing medium.Fig. 5 and Fig. 6 is shown in the temperature curve 532,634 of the cooling medium inside hydraulic cylinder unit, Fig. 7 and Fig. 8 is shown in the temperature curve 736,838 of the cooling medium outside hydraulic cylinder unit.This hydraulic cylinder unit can be a modification in the embodiment shown in Fig. 1 to Fig. 4 of hydraulic cylinder unit 100.Curve 532 shown in Fig. 5 as straight line from relatively low external temperature TAInternal temperature T is extended to through shown tube sectionI.Mark average temperature difference Δ T.Curve 634 in Fig. 6 shows constant boiling temperature TBoilingOr TS, and, internal temperature TIWith boiling temperature TSBetween temperature difference Δ T be constant.Curve 736 shown in Fig. 7 as straight line from internal temperature TIRelatively low external temperature T is extended to through shown tube sectionA.Mark average temperature difference Δ T.Curve 838 in Fig. 8 shows constant boiling temperature TBoilingOr TS, and, external temperature TAWith boiling temperature TSBetween temperature difference Δ T be constant.
By improving the temperature of the cold-producing medium at cooling body targetedly, higher heat dissipating capacity will be realized.By reducing the temperature of the cold-producing medium at focus targetedly, realization is improved the efficiency (efficiency of copper loss owner of lost property motor to be determined, and straight line declines along with the rising of temperature) of such as motor.
The advantage carrying out, with concrete example, the inventive concept that place of matchmakers proposes below.Here, Fig. 5/Fig. 7 represents use coolant, Fig. 6/Fig. 8 represents use cold-producing medium:
The surface area (d=100mm, I=212mm) of motor-pump-group: AInternal=0.067m2；
The heat dissipating capacity of the pipe flowed through: αInternal=1500W/ (m2×K)；
The such as temperature of motor-pump-group: TInternal=80 DEG C；
Ambient temperature: TExtraneous=20 DEG C；
The boiling temperature of coolant: 70 DEG C；
MTD Δ T in the length range of pipe/tube section:
Fig. 5: Δ T=(80 DEG C-20 DEG C)/2=30 DEG C；
Fig. 6: Δ T=80 DEG C-70 DEG C=10 DEG C.
Thus obtaining in Fig. 5 such as flowing to the hot-fluid of cooling medium from motor-pump-group is PZu=A × α × Δ T=3015W.
Thus obtaining in Fig. 6 such as flowing to the hot-fluid of cooling medium from motor-pump-group is PZu=A × α × Δ T=1000W.
The surface area of such as radiator: AOutside=1m2；
The heat dissipating capacity of radiator: αOutside=20W/ (m2×K)；
MTD Δ T in the length range of radiator:
Fig. 5: Δ T=(80 DEG C-20 DEG C)/2=30 DEG C；
Fig. 6: Δ T=70 DEG C-20 DEG C=50 DEG C.
Thus obtain in Fig. 7 being such as P from cooling medium to extraneous hot-fluidAb=A × α × Δ T=600W.
Thus obtain in Fig. 8 being such as P from cooling medium to extraneous hot-fluidAb=A × α × Δ T=1000W.
Compared to cold-producing medium, for coolant, owing to temperature difference Δ T reduces, so, smaller to extraneous hot-fluid from radiator.Here, the heat energy of discharge plays the effect reducing temperature in radiator.For cold-producing medium, in radiator, the heat energy of discharge plays the effect changed from gaseous state or vaporous to the states of matter that liquid changes.Here, during whole states of matter changes, temperature all keeps constant.
Owing to flowing through pipe, the heat transfer coefficient α of inner side is significantly greater than outside (radiator uses natural way or forces mode convection current), so, drain into from inner side the hot-fluid that can discharge of maximum in outside apparently depend on outside heat transfer.In the case of A and α is constant, the heat transfer in outside can only be improved by improving temperature difference Δ T.
Fig. 7 shows, the flow velocity of coolant is the highest, and the temperature difference Δ T in outside is the biggest, and the temperature difference Δ T of inner side is the least.System reaches meansigma methods when coolant temperature is 70 DEG C.Here, PZu=PAb！Due to flow velocity so that a square ground rising is lost in the pipe friction of eddy current type, so the heat in introducing system increases.
Fig. 8 shows, the boiling temperature T of cold-producing mediumBoilingDepend on pressure.Constant when being 4 bar at system pressure, such as coolant SolkaneR123 has the boiling temperature of 70 DEG C.Owing to the temperature of inner side is 80 DEG C, the states of matter of coolant becomes gaseous state from liquid, and when temperature constant is 70 DEG C, heat energy increases.The process in outside is contrary.
Utilize cold-producing medium as coolant, even if in the case of flow velocity is relatively low, it is also possible to optimize heat dissipating capacity.So that pipe friction loss keeps less, and then the heat energy additionally introduced is made to keep less.
Cold-producing medium is used to be advantageously the heat budget of compact hydraulic test/hydraulic systemThere is provided and improve, and then improve the power density of system.Here, the thermal loss of system is advantageously collected, and can use the most further.Here, the stationary temperature (boiling temperature of cold-producing medium) along whole surface improves heat dissipating capacity.
But it is also shown for using the heat power principle of refrigeration machine, and the pressure of cold-producing medium does not change.Owing in the case of hydraulic axis is compact, heat transits to relatively low temperature levels (such as extraneous 20 DEG C) from higher temperature levels (80 DEG C of such as pump), so being avoided that the boiling point of the cold-producing medium making such as refrigeration machine because of pressure change changes.
Thus use the heat power principle of refrigeration machine, in order to make the surface temperature on whole surface keep identical, in the case of surface area is identical, thus improves heat dissipating capacity.
Fig. 9 show the schematic diagram of hydraulic cylinder unit 100.Fig. 9 corresponding to Fig. 1, difference is, cooling body 108 has the mechanism 940 of the system pressure for changing cooling body 108.The system pressure of the cooling medium in cooling line especially it is designed to adjust for changing the mechanism 940 of system pressure.
Utilize the mechanism 940 for changing system pressure, boiling point can be adjusted, and then adjust Δ T according to working condition and external conditionInternalWith Δ TOutside.Operating point thus elapse up or down.
Figure 10 show the schematic diagram of hydraulic cylinder unit 100.Figure 10 corresponding to Fig. 1, difference is, is provided with choke valve 1042 and compressor 1044 in cooling circuit 118.By choke valve 1042 and compressor 1044, cooling body 108 is designed to change the pressure of the cooling medium in cooling circuit, changes the most on segment-by-segment basis.It is divided at least two section or tube section thereby through choke valve 1042 and 1044 cooling circuits of compressor.
By means of the cold-producing medium carried by compressor 1044 and compress, the heat of other assembly within motor 106, pump 104 and hydraulic cylinder 100 can outwards carry.Owing to pressure raises, boiling temperature also raises, and through higher temperature difference Δ T, heat can be emitted into the external world.The pressure of cooled cold-producing medium is reduced, thus with relatively low (being adjusted) boiling temperature T by choke valve 1042BoilingIt is led to focus.There is the temperature absorption strengthened there.
Embodiment shown in Figure 10 have employed cold-producing medium, this cold-producing medium pump 104 and/or motor 106 and/or the used heat of other focus (such as valve) of system be transported away to cooling body.The compressor 1044 for changing refrigerant pressure it is integrated with and for changing the choke valve 1042 of refrigerant pressure in cooling circuit 118.
In the embodiment shown in fig. 10, a kind of cold-producing medium is have employed as cooling medium, its boiling point is between assembly temperature or tank temperature and ambient temperature, and used heat is transported to leave to cooling body from other focus (such as valve) of tank and/or pump 104 and/or motor 106 and/or system.The conveying mechanism 122 of cold-producing medium is have employed at this.
Figure 11 is the simplification figure of temperature curve 1146.In cartesian coordinate system, the longitudinal axis marks temperature, transverse axis marks length of tube or the position of cooling line 120.Dotted line represents (constant) internal temperature TInternalOr TI(constant) external temperature TOutsideOr TA.Here, for the embodiment shown in Figure 11, cold-producing medium is used.Figure 11 is shown in the temperature curve 1146 of the cold-producing medium inside hydraulic cylinder unit.This hydraulic cylinder unit can be the embodiment shown in Fig. 10 of hydraulic cylinder unit 100.Curve 1146 in Figure 11 shows constant boiling temperature TBoilingOr TS, and, internal temperature TIWith boiling temperature TSBetween temperature difference Δ T be constant.
The advantage carrying out, with concrete example, the inventive concept that place of matchmakers proposes below.The parameter not clearly stated can be learnt by previous cases.
The surface area (d=100mm, I=212mm) of motor-pump-group: AInternal=0.067m2；
The heat dissipating capacity of the pipe flowed through: αInternal=1500W/ (m2×K)；
The such as temperature of motor-pump-group: TInternal=80 DEG C；
Ambient temperature: TExtraneous=20 DEG C；
The boiling temperature of cold-producing medium: 63.7 DEG C；
MTD Δ T in the length range of pipe/tube section:
Figure 11: Δ T=80 DEG C-63.7 DEG C=16.3 DEG C.
Thus obtaining in Figure 11 such as flowing to the hot-fluid of cooling medium from motor-pump-group is PZu=A × α × Δ T=1630W.
PCompressor=340W.
The surface area of such as radiator: AOutside=1m2；
The heat dissipating capacity of radiator: αOutside=20W/ (m2×K)；
Boiling temperature: TBoiling=120 DEG C；
MTD Δ T in the length range of radiator:
Figure 11: Δ T=120 DEG C-20 DEG C=100 DEG C.
Thus obtain in Figure 11 being such as P from cooling medium to extraneous hot-fluidAb=A × α × Δ T=2000W.
For cold-producing medium, in radiator, the heat energy of discharge plays the effect changed from gaseous state or vaporous to the states of matter that liquid changes.Here, during whole states of matter changes, temperature all keeps constant.
Owing to flowing through pipe, the heat transfer coefficient α of inner side is significantly greater than outside (radiator uses natural way or forces mode convection current), so, drain into from inner side the hot-fluid that can discharge of maximum in outside apparently depend on outside heat transfer.In the case of A and α is constant, the heat transfer in outside can only be improved by improving temperature difference Δ T.
The boiling temperature T of cold-producing mediumBoilingDepend on pressure.By improving pressure, boiling temperature rises.Based on this, so that the cold-producing medium utilizing the compressor work introduced extraly to obtain heating is discharged with higher stationary temperature difference by cooling body.Thus can realize improving heat dissipation effect.Pressure is reduced by choke valve, so that boiling point is in relatively low temperature.This can realize the adjusted temperature difference Δ T on vaporizer, and this causes the heat absorbing capability improved.
Therefore, by changing boiling temperature, no matter in inside or in outside, heat dissipating capacity can be optimized.
Figure 12 show the schematic diagram of hydraulic cylinder unit 100.Figure 12 corresponding to Figure 10, difference is, choke valve 1042 and compressor 1044 are controlled.In this embodiment it is possible to change pressure by vaporizer (in inner side), and/or change pressure, the thus temperature in regulation refrigerant loop 118 by condenser (in outside).Thus heat dissipating capacity can be adjusted according to working condition and external condition.
Figure 13 show the schematic diagram of hydraulic cylinder unit 100.Figure 13 is corresponding to the combination of embodiment shown in Fig. 3 with embodiment shown in Figure 10.Cooling body 108 is designed to direct into cooling medium on the outer surface 224 of hydraulic cylinder unit 100, in order to discharge, by convection current and/or heat radiation, the heat energy absorbed.On hydraulic cylinder unit 100, outer surface 224 is provided with ventilation blower 326, for producing air-flow on the surface of cooling body 108.Between outer surface 224 and cooling body 108, outer surface 224 is provided with insulating part 1346.
In this embodiment, deliver coolant on the big surface of hydraulic cylinder unit 100.Here, the heat energy of absorbed inside can be emitted into the external world by free convection or forced convertion and heat radiation.Such as, coolant can the most helically guide along cylindrical surface.
Figure 14 show the schematic diagram of hydraulic cylinder unit 100.Figure 14 corresponding to Figure 10, difference is, is provided with the single condenser 1448 with ventilation blower 326 in cooling circuit 118.
Figure 15 show the schematic diagram of hydraulic cylinder unit 100.Figure 15 corresponding to Figure 10, difference is, is provided with heat exchanger 428 in cooling circuit 118.
In this embodiment, heat energy is emitted into another cooling circuit 430 by heat exchanger 428.This embodiment has the heat dissipating capacity of maximum compared to the embodiment shown in Figure 12 to Figure 15, and can realize the highest power density.Can be further with the used heat of system at this.
Figure 16 show the schematic diagram of hydraulic cylinder unit 100.Figure 16 corresponding to Fig. 1, difference is, is provided with choke valve 1042 and two check-valves 1650,1652 in cooling circuit 118, and cooling circuit 118 is directed over chamber K1.Here, chamber K1 is used as compressor.
One aspect of present example is, uses cooling medium, it pump 104 and/or motor 106 and/or the used heat of other focus (such as valve) of system be transported away to cooling body.Cooling medium is carried and is carried out by the linear unit i.e. reciprocating motion of piston rod.Chamber K1 is a part for conveying mechanism 122.
If piston rod 122 moves right in the drawings, just suck cooling medium.If piston rod 122 is moved to the left in the drawings, cooling medium is just compressed, and carries towards cooling body.Its premise is compressible cooling medium.Two embodiments subsequently describe other design.
One embodiment shows the cooling circuit 118 on hydraulic cylinder 100, and it is with integrated pump 104 and/or motor 106.Here, cooling medium is carried out passive conveying by cylinder moving.
Advantageously, the temperature ratio of internal system is homogenized.Here, without extra conveying mechanism.
In the synchronized cylinder using differential fashion, chamber K2 with K3 and K4 area is identical, thus without chamber K1.This chamber K1 is currently used to carry cooling medium.Two check-valves 1650,1652 determine the flow direction.
Figure 17 show the schematic diagram of hydraulic cylinder unit 100.Figure 17 corresponding to Figure 16, difference is, cooling body has the volume compensation reservoir 1754 coupled with cooling circuit, for compensating the coolant volume in cooling circuit 118.In this embodiment, the reservoir 1754 for volume compensation is positioned in the pipeline 120 of cooling medium.Thus incompressible cooling medium can also be used here, such as pressure fluid (such as hydraulic oil, leakage machine oil).
Figure 18 show the schematic diagram of hydraulic cylinder unit 100.In this embodiment, a simple cylinder with differential effect 1856 is used to realize moving back and forth.Motor-pump-group 102 is positioned at the outside or inside of cylinder 1856.Owing to employing two chamber K5 and K6 herein for reciprocating motion, so being mounted with a single conveying cylinder 1858 concurrently, its piston rod 1860 couples with the piston rod 112 of hydraulic cylinder unit 100.Thus when piston rod 112 moves, the volume of conveying cylinder 1858 also changes, cooling medium flows in or out conveyor chamber K7 via check-valves 1650,1652, and this conveyor chamber is also referred to as cylinder chamber K7.
Follow-up embodiment shows a part for hydraulic test, and it such as includes the linear unit of tank, unit and hydraulic pressure.Here, the leakage machine oil of pump is used to cool down assembly such as motor.Advantageously achieve uniform temperature ratio in internal system.Advantageously, it is not necessary to extra conveying mechanism.Here, without the single conveying mechanism for cooling medium, because leakage machine oil is under pressure.
Figure 19 show the schematic diagram of actuation mechanism 102.This actuation mechanism 102 can be an embodiment of the actuation mechanism 102 shown in aforementioned figures.This actuation mechanism includes pump 104 and the motor 106 coupled with pump 104.Pump 104 is connected with tank 1964 by aspiration 1962.There is individual pressure piping 1966 to extend away from from pump 104, be used for driving hydraulic mechanism, the hydraulic cylinder unit 100 such as described in aforementioned figures.This pump has leakage machine oil joint 1967, stretches out, from this leakage machine oil joint, the leakage machine oil pipeline 1968 that a wound motor 106 stretches.Leakage machine oil pipeline 1968 is designed to absorb the heat of motor by means of the hydraulic medium as cooling medium guided in leakage machine oil pipeline 1968, and the hydraulic medium being heated is led back in tank 1964.
Hydraulic pressure unit 100 is made up of tank, pump 104 and motor 106, and it is changed into hydraulic power electrical power.The machine oil being positioned in tank 1964 is sucked up to pump 104 via aspiration 1962, and is discharged by pressure piping 1966 at a higher pressure.Most of pumps 104 have leakage machine oil joint 1967 due to drive mechanism or the gap of gear internal.Leakage machine oil also has the residual compression of 1-4 bar there, and is used for cooling down motor 106.Therefore, the heat power of motor 106 is entered in tank 1964 by leakage machine oil, and can be discharged by its surface.
Figure 20 show the schematic diagram of actuation mechanism 102.Figure 20 corresponding to Figure 19, difference is, on leakage machine oil pipeline 1968, is provided with the radiator 1448 with ventilation blower 326 between motor 106 and tank 1964.
Embodiment shown in Figure 20 is corresponding to the embodiment shown in Figure 19, and it is with the additional cooling body (radiator 1448 of band ventilation blower 326) of leakage machine oil.Here, the heat power with motor 106 of pump 104 is disposed to outside air, without entering in tank 1964.
Figure 21 show the schematic diagram of actuation mechanism 102.Figure 21 corresponding to Figure 19, difference is, on leakage machine oil pipeline 1968, is provided with heat exchanger 428 between motor 106 and tank 1964.
Embodiment shown in Figure 21 is corresponding to the embodiment shown in Figure 20, but with heat exchanger 428 as cooling body.Here, the heat power with motor 106 of pump 104 is disposed to the second cooling circuit.Thus heat power can be continued with.
Figure 22 show the schematic diagram of actuation mechanism 102.Figure 22 corresponding to Figure 19, difference is, leakage machine oil pipeline 1968 separates from pressure piping 1966, and is provided with choke valve 1042 between the section of wound motor 106 stretching, extension of pressure piping 1966 and leakage machine oil pipeline 1968.
Embodiment shown in Figure 22 is corresponding to the embodiment shown in Figure 19, but with choke valve 1042 on pressure piping.Owing to the most each pump has leakage machine oil joint, so, volume flow can be produced in pressure piping by choke valve 1042.
Figure 23 show the schematic diagram of hydraulic cylinder unit 100.Figure 23 corresponding to Fig. 1, difference is, cooling circuit 118 is through pump 104.Thus achieve in hydraulic cylinder unit 100 proposed scheme at the aspect shown in Figure 17 to Figure 22.
This example show the synchronized cylinder using differential configuration mode.Pump and motor are positioned in its inner chamber, and working media (hydraulic engine oil) is transported in corresponding chamber K1, K2, K3 or K4.Thus piston rod is applied power, and piston rod is moved along shown direction.
The thermal loss of the overwhelming majority produces in motor and pump.In the case of being difficult the cooling circuit shown in redness, described thermal loss must first pass around two walls and the working media arrival surface through hydraulic cylinder.Owing to not having big thermal resistance, in the case of without additional heat dissipation, system can be overheated, thus must be with the power work reduced.Leakage machine oil due to pump still has the residual compression of 1-4 bar, so, described leakage machine oil is used to cool down motor.The heat power with motor of pump arrives cooling body thereby through leakage machine oil.
Figure 24 show the schematic diagram of hydraulic system 2470.This hydraulic system 2470 has three hydraulic cylinder units 100.These hydraulic cylinder units 100 can be the modification of the hydraulic cylinder unit 100 described in aforementioned figures respectively.The cooling line 120 of cooling body 108 has radiator 1448 and ventilation blower 326.Here, cooling line 120 is through suitable molding so that these hydraulic cylinder units 100 are flow through concurrently.Therefore, three hydraulic cylinder units 100 have a common cooling body 108.
In the embodiment shown in Figure 24, hydraulic system 2470 includes the linear unit 100 such as hydraulic cylinder unit 100 of multiple hydraulic pressure.Cooling circuit 118 absorbs the heat of multiple linear unit 100.Alternatively, such as can be with a rearmounted adsorbent refrigerator.In this case, radiator 1448 is replaced with heat exchanger.
The heat budget that aforementioned concepts is compact hydraulic system 2470 provides to be improved.This power density causing improve system.The thermal loss of system 2470 is caught, and can use the most further.
The thermal loss of the overwhelming majority of compact axle (Kompaktachse) 100 produces on pump 104 and motor 106.Described used heat is delivered to cooling body from compact axle 100, such as with the radiator 1448 of ventilation blower 326 by cooling circuit 118.
Figure 25 show the schematic diagram of hydraulic system 2470.This figure corresponding to Figure 24, difference is, hydraulic cylinder unit 100 is arranged in series in cooling circuit 118.
This embodiment thus corresponding to the embodiment of Figure 24, but work the most concurrently, but work serially.
Figure 26 show the schematic diagram of hydraulic system 2470.This figure corresponding to Figure 24, difference is, replaces radiator and ventilation blower, and cooling circuit 118 has heat exchanger 428.Generally, this heat exchanger 428 is used to utilize used heat such as the mechanism heated for water.
Figure 27 show the simplification figure of adsorbent refrigerator 2772 and hydraulic system 2470.This hydraulic system 2470 can be the embodiment in the hydraulic system 2470 shown in Figure 24 to Figure 26.Adsorbent refrigerator 2772 couples with cooling load 2774 such as switch cubicles and recoverable cooler 2776.In one embodiment, hydraulic system 2470 is designed to control steam turbine 2778.
Under a lot of applicable cases, such as when controlling steam turbine, multiple axles 100 are arranged with being spatially near.These axles are connected with each other by a central cooling circuit 118.Alternatively, collected heat energy can be continued with here, such as, in adsorbent refrigerator 2772, be used for cooling down such as switch cubicle 2774.
The most exemplarily describe controlling combustion gas and possible utilization to the used heat of compact axle 100 during steam turbine.In this applications, under multiple compact axles 100 are positioned at the ambient temperature of at most 80 DEG C in combination.These compact axles 100 can work under the temperature conditions of at most 100 DEG C.
First the heat energy of each compact axle 100 collect by means of cooling circuit 118, and is transported to adsorbent refrigerator 2772.The thermal power of described 20kW can be changed into the cooling power of 12kW now, wherein it is desired to discharge the heat of 32kW in recoverable cooler 2776.Utilize the heat of this 12kW, such as, can at ambient temperature switch cubicle 2774 etc. be cooled down, and without extra refrigeration machine.Generally be emitted into the external world 20kW loss thermal power thus can be changed into 12kW can use cooling power.
For described example, for example with following values:
The power of axle: 15kW；
The efficiency of axle: 0.7；
The fully loaded degree of axle: 50%；
The used heat of axle: 2.25kW；
The quantity of axle: 9；
All used heat :-20kW.
Figure 28 is the flow chart of method 2890.According to an embodiment of the invention for driving the method 2890 of hydraulic pressure unit to include the step 2892 for controlling actuation mechanism and for utilizing the cooling body coupled with actuation mechanism to cool down the step 2894 of actuation mechanism.
Embodiment described here make use of trend, the trend of compact driving that dispersion drives, utilizes the trend of the power density of the trend of used heat and the higher of system.
Shown embodiment is only exemplarily to be chosen, and can be mutually combined.
List of numerals
100 hydraulic pressure units, hydraulic cylinder unit
102 actuation mechanism
104 pumps
106 motors
108 cooling bodies
110 main bodys
112 conveying mechanisms
114 flanges
116 directions, moving direction
118 cooling circuits
120 cooling lines
122 conveying mechanisms
K1 chamber, cylinder chamber, conveyor chamber
K2 chamber, cylinder chamber
K3 chamber, cylinder chamber
K4 chamber, cylinder chamber
224 outer surfaces, surface
326 ventilation blowers
428 heat exchangers
430 cooling circuits
532 temperature curves
634 temperature curves
736 temperature curves
838 temperature curves
TInternalInternal temperature
TOutsideExternal temperature
Δ T temperature difference
940 for changing the mechanism of the system pressure of cooling body
1042 choke valves
1044 compressors
1146 temperature curves
1448 radiators, condenser
1650 check-valves
1652 check-valves
1754 volume compensation reservoiies
1856 cylinders
1858 conveying cylinders
1860 piston rods
K5 chamber, cylinder chamber
K6 chamber, cylinder chamber
K7 chamber, cylinder chamber, conveyor chamber
1962 aspiration
1964 tanks
1966 pressure pipings
1967 leakage machine oil joints
1968 leakage machine oil pipelines
2470 hydraulic systems
2772 adsorbent refrigerators
2776 recoverable coolers
2778 steam turbines
2890 methods
2892 rate-determining steps
2894 cooling steps
Claims (14)
1. a hydraulic pressure unit (100), with being used for driving the actuation mechanism (102) of hydraulic pressure unit (100), wherein, this actuation mechanism (102) includes pump (104) and/or motor (106), it is characterized in that the cooling body (108) being used for cooling down actuation mechanism (102) with actuation mechanism (102) thermal coupling, wherein, this cooling body (108) includes the cooling circuit (118) with the cooling line (120) for cooling medium and is used for carrying the conveying mechanism (122) of the cooling medium in cooling line (120), wherein, cooling medium is a kind of cold-producing medium.
2. hydraulic pressure unit (100) as claimed in claim 1, wherein, cooling body (108) is designed to cooling medium to guide the outer surface (224) to hydraulic cylinder unit (100), in order to discharge absorbed heat energy by convection current and/or heat radiation.
3. the hydraulic pressure unit (100) as according to any one of the claims, wherein, has the ventilation blower (326) for producing air-flow on the surface of cooling body (108).
4. the hydraulic pressure unit (100) as according to any one of the claims, wherein, cooling body (108) has the mechanism (940) of the system pressure for changing cooling body (108), especially for the mechanism (940) of the system pressure of the coolant as cooling medium changed in cooling line (120).
5. hydraulic pressure unit (100) as claimed in claim 4, wherein, cooling body (108) has choke valve (1042) and/or compressor (1044).
6. the hydraulic pressure unit (100) as according to any one of the claims, wherein, cooling body (108) couples with heat exchanger (428), and/or cooling body (108) has radiator (1445), wherein, particularly ventilation blower (326) and this radiator mating reaction.
7. the hydraulic pressure unit (100) as according to any one of the claims, wherein, hydraulic pressure unit (100) holds actuation mechanism (102) at least in part, and actuation mechanism (102) is more particularly set on the inside of hydraulic pressure unit (100).
8. the hydraulic pressure unit (100) as according to any one of the claims, wherein, cooling body (108) has at least one check-valves (1650,1652) being positioned on cooling circuit (118), wherein, this cooling circuit (118) is through the cylinder chamber (K1 of hydraulic pressure unit (100)；K7), wherein, conveying mechanism (122) particularly includes at least one check-valves (1651,1652) and cylinder chamber (K1；K7), in order to conveying cooling medium.
9. the hydraulic pressure unit (100) as according to any one of the claims, wherein, cooling body (108) has the volume compensation reservoir (1754) coupled with cooling circuit (118), for compensating the volume of the cooling medium in cooling circuit (118).
10. the hydraulic pressure unit (100) as according to any one of the claims, wherein, cooling medium is hydraulic medium, wherein, leakage machine oil joint (1967) of pump (104) couples with cooling circuit (118) especially, in order to provide hydraulic medium.
11. 1 kinds of hydraulic systems (2470), with the first hydraulic pressure unit (100) any one of with good grounds the claims with according at least one second hydraulic pressure unit (100) any one of the claims, they have common cooling body (108).
12. hydraulic systems (2470) as claimed in claim 10, wherein, the first hydraulic pressure unit (100) and at least the second hydraulic pressure unit (100) are arranged in the cooling circuit (118) of cooling body (108) concurrently and/or serially.
13. according to the used heat of the hydraulic pressure unit (100) any one of claim 1 to 11 and/or the application that uses the used heat according to the hydraulic system (2470) any one of claim 10 to 11, for particularly by means of another cooling procedure and/or the thermal process of refrigeration machine (2772).
14. 1 kinds are used for driving the method (2890) according to the hydraulic pressure unit (100) any one of claim 1 to 13, and wherein, the method (2890) has following steps:
Control (2892) actuation mechanism (102)；With
The cooling body (108) coupled with actuation mechanism (102) is utilized to cool down (2894) actuation mechanism (102).
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014226665 | 2014-12-19 | ||
| DE102014226665.3 | 2014-12-19 | ||
| DE102015206236.8A DE102015206236A1 (en) | 2014-12-19 | 2015-04-08 | Hydraulic unit and method for operating a hydraulic unit |
| DE102015206234 | 2015-04-08 | ||
| DE102015206234.1 | 2015-04-08 | ||
| DE102015206236.8 | 2015-04-08 |
Publications (2)
| Publication Number | Publication Date |
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| CN105822629A true CN105822629A (en) | 2016-08-03 |
| CN105822629B CN105822629B (en) | 2021-05-04 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201511036291.0A Active CN105822629B (en) | 2014-12-19 | 2015-12-19 | Hydraulic unit and method for operating a hydraulic unit |
| CN201511036292.5A Active CN105715625B (en) | 2014-12-19 | 2015-12-19 | Hydraulic cylinder unit |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201511036292.5A Active CN105715625B (en) | 2014-12-19 | 2015-12-19 | Hydraulic cylinder unit |
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| CN (2) | CN105822629B (en) |
| IT (2) | ITUB20159614A1 (en) |
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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 |
|---|---|
| CN105822629B (en) | 2021-05-04 |
| ITUB20159614A1 (en) | 2017-06-18 |
| CN105715625B (en) | 2021-04-23 |
| ITUB20159396A1 (en) | 2017-06-18 |
| CN105715625A (en) | 2016-06-29 |
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