CN106555738B - 用于确定压力的装置 - Google Patents
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- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
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- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
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- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
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- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
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- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/126—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
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- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
- G01L5/26—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes for determining the characteristic of torque in relation to revolutions per unit of time
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
- H02P1/00—Arrangements for starting electric motors or dynamo-electric converters
- H02P1/16—Arrangements for starting electric motors or dynamo-electric converters for starting dynamo-electric motors or dynamo-electric converters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/04—Carter parameters
- F04B2201/0402—Lubricating oil temperature
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- F04B2203/00—Motor parameters
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- F04B2203/0201—Current
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- F04B2203/0207—Torque
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Abstract
用于确定通过借助于电动马达(31)驱动的泵(30)产生的压力(64)的装置(100),所述装置(100)设置用于基于内扭矩(114)和损失力矩(108)之差求得压力(64),其中,所述装置(100)还设置用于从马达电流(110)和马达常数(ke)中求得内扭矩(114)。
Description
技术领域
本发明涉及一种用于确定压力的装置、用于调节压力的调节机构以及用于运行泵的机构。
背景技术
泵在此理解为用于输送液体的机械仪器。液体-固体-混合物、泥以及具有极少气体份额的液体也落入其范围内。在泵设备的运行中,传动功转换成运送的液体的动能。
本装置尤其用于确定传动装置油附加泵(Getriebeoelzusatzpumpe)中的压力。在液压线路图中,所述传动装置油附加泵与主油泵并联。当主油泵断开或者具有极小的转速时,传动装置油附加泵应该维持压力。为此,传动装置油附加泵应该确保稳定的压力。
文件DE 10 2011 086 572 A1描述了一种用于转速可变地调节容积泵组的方法和调节设备。所述容积泵组包括容积泵和驱动装置,该驱动装置由电驱动马达和变频器构成。通过调节设备将容积泵的最终压力调节到最终压力额定值上,其中检测由驱动装置提供的状态值。通过调节设备从中求得最终压力。
发明内容
在此背景下提出了一种用于确定压力的装置、一种调节机构以及一种用于运行泵的机构。实施方式由以下说明书中获得。
介绍了用于确定通过借助于电动马达驱动的泵产生的压力的装置,其中该装置设置用于基于所述电动马达的内扭矩和所述电动马达的损失力矩之差来求得压力,其中该装置还设置用于从所述电动马达的马达电流和所述电动马达的马达常数中求得内扭矩,其中,所述装置设置用于从所述电动马达的温度和所述电动马达的马达转速中求得损失力矩。
在一种实施方式中,从温度、尤其油温以及马达转速中求得损失力矩。
此外可以提出,用特征曲线求得损失力矩。
所介绍的装置尤其构造用于容积泵。该容积泵可以构造为齿轮泵、尤其构造为齿环泵。其它的容积泵类型是叶轮泵。表明了在容积泵中通过扭矩确定实际压力很好地起作用,尤其在齿环泵或者说摆线泵中。在齿环泵或者说摆线泵中,外面的空心轮类似于滑动轴承作用,并且在较大的运行范围内在部件之间发生液体摩擦。这使得实际压力的确定比较精确地起作用。一旦相反出现混合摩擦,例如在叶片泵中在较大的工作范围内的情况就是如此,那么实际压力的确定变得不精确。因此,齿轮泵或者说摆线泵的使用有利于用于实际压力的所描述的确定。
在另一实施方式中,所介绍的装置用于确定通过摆线泵产生的压力。
该装置可以设置用于确定用于压力调节的实际压力。该实际压力在这种情况下是用所介绍的装置确定的压力。
此外,介绍了一种用于调节通过泵产生的压力的调节机构,其具有调节器,该调节器基于额定压力和实际压力之间的差求得调节参数,其中该调节机构拥有用于确定实际压力的装置,其中前面所述类型的装置用作该装置。在一种实施方式中,PI调节器用作调节器。
此外,介绍了一种用于运行泵的机构,其具有所描述类型的调节机构、用于实施预控制的单元(例如速度斜坡)以及用于在调节机构和用于实施预控制的单元之间进行切换的开关。
所介绍的用于确定压力的装置实现了确保稳定的压力。此外,用该装置还能在没有压力传感器的情况下进行压力调节。所介绍的装置下面特别结合压力调节进行描述。然而该装置不限制于该应用并且总是能够在需要确定压力时使用。
附图说明
本发明的其它优点和设计方案从说明书和附图中获得。当然,前面所述的以及后面还要解释的特征不仅能够以相应说明的组合进行使用,而且也能够以其它组合或者单独地进行使用,而不离开本发明的范围。
本发明根据附图中的实施方式示意性地示出,并且参照附图示意性地和详细地进行描述。在附图中:
图1以框图示出了所提出的调节机构的实施方式的结构,
图2以框图示出了用于压力确定的装置的实施方式,
图3示出了用于确定损失力矩的特征曲线的图形图示,
图4示出了摆线泵,以及
图5示出了具有泵的传动装置的示意图。
具体实施方式
图1示出了整体用附图标记10表示的调节机构的结构或者说构造。该图示示出了调节器12,在该情况下是PI调节器,用于预控制的速度斜坡(Speedrampe)14,八度的IIR过滤器16,压力模型(Druckmodell)20,限制器22,提前角过滤器24,旋转场发生器26,其中包含带有电动马达31的泵30的调节对象28,平均值形成器(Mittelwertbilder)32,模拟-数字-转换器34(将表征通过电动马达31的电流的信号输入模拟-数字-转换器),用于将时间换算成角度的单元36,四度的IIR过滤器38,集成器(Integrierer)40,八度的IIR过滤器42(将表征转速的信号、尤其在转子位置信号或者霍尔信号的两种交替之间的时间间隔输入八度的IIR过滤器),两度的IIR过滤器44,因子1/t 46(其将霍尔信号的交替之间的时间间隔换算成速度值n),例如通过LIN总线50提供用于温度的值T的模数48,以及提供马达常数ke的模数ke 52。此外,所述图示示出了用于在速度斜坡14和调节器12之间进行切换的开关80,其中根据IIR过滤器16的输出信号或者根据通过压力模型20产生的实际压力信号64实现切换。
将额定压力62和实际压力64输入元件60中。从中计算调节偏差ΔP 66。将转速n68输入速度斜坡14中,并且该速度斜坡与供给电压VS连接。该参数也输入限制器22中。
因为压力调节在运行的开始也许尽可能缓慢地使电动马达加速,所以为了快速起动而使用速度斜坡14,其实现了预控制。该速度斜坡14以最大的或者说至少较大的电流消耗起动所述电动马达31。基于估算的实际压力实现速度斜坡14与调节器12之间的切换,如果实际压力例如小于额定压力的90%,那么激活所述速度斜坡。如果实际压力例如大于额定压力的97%,那么激活所述调节器。调节器12的因子、尤其PI调节器的增强因子(Verstärkungsfaktor)能够在试验台上求得。
所述电动马达31能够通过在微控制器上实施的软件进行触发。在此,可以正弦整流地(sinuskommutiert)实现马达触发,因为这种电动马达是特别安静的。可以用正弦状的电压实现电动马达31的触发,然而也可以使用具有电流调节器的磁场定向的调节(FOR)。该FOR调节在触发时是有利的,因为电动马达可以更快地作出响应。所述调节机构10典型地压力调节地运行。
此外,可以与转速同步地实现霍尔沿之间的时间间隔换算成角度增量(Winkelinkrement)。时间同隔可以在每次第二PWM中断时增加。此外,当前角度的计算可以每100μs进行。在此,在每次PWM中断中实现对霍尔传感器的询问。因此,不是时间同步地实现过滤,而是根据转速或者说霍尔沿实现过滤。
图2以框图示出了用于确定压力的装置,其整体用附图标记100表示。该图示示出了特征曲线102,油温104和马达转速106输入其中。从中获得了损失力矩MV 108。
在此,油温104例如可以在泵30中测量,其也可以在传动装置中使用时在其它位置上、例如在传动装置的传动装置油底壳(Getriebeoelwanne)中进行测量并且输入用于确定压力的装置中。在汽车中也可以通过LIN总线(局部互联网络)输入温度值。
转速n例如可以以min-1(rpm)为单位进行说明。
所述马达常数ke要么可以为了相应的结构系列假定成相同的,要么可以为每个单个的电动马达进行校正。为了较高的精度,所述马达常数ke可以作为温度的函数进行说明,因为其取决于温度。
要注意的是,不测量压力,而是基于马达转速、马达电流以及油温来确定压力。在此,实际压力是泵出口上确定的施加的压力。所述油温例如是油池温度,其例如通过LIN总线报告给调节机构。所述摆线泵或者说齿轮泵的压力差ΔP通过下述进行计算:
ΔP=Mth·C (1)
所述因子C在此是取决于泵的常数,并且Mth是理论上的扭矩,其引起压力的产生并且因此也可以称作压力力矩。
理论上的扭矩Mth从内扭矩Mi和损耗力矩MV中借助于下述得出:
Mth=Mi-MV (2)
确定的内扭矩Mi从下述获得:
Mi=31/2/2·Kemax(1+(Tamb-20)·Temp_Koeff)·I (3)
在此示例性的是:
符号 | 说明 | 单位 | 值 | 注释 |
Ke<sub>max</sub> | 马达常数 | Vs/rad | 0.022749 | 以测量技术求得 |
I | 测量的马达电流 | A | ||
T<sub>amb</sub> | 油温(LIN) | ℃ | ||
T<sub>emp_Koeff</sub> | 倒置的温度系数 | %/K | -0.11 | 数据页值 |
表格1
作为马达电流I,可以测量通过线圈装置的电流,或者测量最终阶段中相应于该电流的电流或者说测量在直流马达中直流中间回路中的电流。
对于取决于泵的常数来说,从下述获得:
置换容积或者说腔室容积Vth相应于液体量在泵的一次旋转中输送的容积。用于测试的泵的腔室容积例如为Vth=2.21 10-6m3。以测试技术在70℃时求得泵参数。
确定特征曲线
图3示例性地示出了用于损失力矩MV的特征曲线102。仅仅说明了特征曲线102的少数点,并且在实际中-根据所希望的精度以及所希望的工作范围-使用更多的点。
用于损失力矩MV的特征曲线102例如可以在试验台上求得。此外,起动多个取决于转速和温度的取样位置,并且测量压力差ΔP,电动马达的转速n以及马达电流I。
借助于等式(1)可以在取样位置上计算理论上的扭矩Mth,并且借助于等式(3)计算内扭矩Mi。借助于等式(2)能够从理论上的扭矩Mth和内扭矩Mi中确定损失力矩MV,并且作为特性曲线的部分进行保存。
在此,所述损失力矩MV几乎线性地取决于转速并且对数地取决于温度。
用泵进行试验,并且实现了3.0巴到4.2巴范围内的实际压力所需的精度。
图4示例性示出了摆线泵30的构造。泵30的转子具有内齿轮302和外齿环303,外齿环的内齿部与内齿轮啮合。齿轮302和齿环303是彼此偏心布置的,并且它们具有不同数量的齿。由此齿轮302和齿环303以不同的转速转动,使得在这些齿之间的空腔在转动时在最大容积和最小容积之间变化。泵30具有流体入口304和流体出口305。流体入口304通过未示出的通道与齿轮302的端侧和齿环303的端侧在其中在预先给定的转动方向的情况下空腔变大的区域中保持流体连接,并且因此形成负压,且流体出口305通过未示出的通道与齿轮302的端侧和齿环303的端侧在其中在预先给定的转动方向的情况下空腔变小的区域中保持流体连接,并且因此形成超压,以便由此将待输送的流体挤压出来。
图5示出了具有壳体的传动设备的可行的示意性结构,在所述壳体中在下面设置了传动装置油360。本质上的机械的传动装置354必须在运行中以传动装置油360来润滑。为此,设置了第一传动装置油主泵350,其由传动装置354通过设备352机械地驱动,并且传动装置油360通过管路358泵送至传动装置354。但传动装置油主泵350仅在传动装置354运动时起作用。在传动装置354的静止状态中,机械驱动的传动装置油主泵未激活,并且传动装置354的润滑尤其在传动装置354起动时未可靠地保证。因此设置了通过电动马达30能驱动的传动装置油附加泵31,并且这可以在需要时通过管路356和止回阀357将传动装置油360泵送到管路358中并且由此泵送到传动装置354中。止回阀357设置用于禁止传动装置油从泵350流到泵31中。泵送至传动装置354的传动装置油360随后再次向下流回并且可以重新向上被泵送。泵31当然可替换地可以用作为传动装置油主泵。
当然,在本申请文件的范围内可以进行多种多样的改进和改型。如此,例如可以通过大量特征曲线值定义特征曲线KF 102,其为油温104和马达转速106分配了损失力矩MV108。然而函数MV=KF(T_104, n_106)也可以作为近似等式进行说明,或者可以内插在少数预先给出的值之间。
在前面几页上描述的各个参数要么可以为了所有的结构系列统一地确定,要么通过针对结构系列的每个泵装置进行的测试来确定。后者例如在确定马达常数ke时是有利的,因为其在不同的马达之间会显著变化。
在图1中示出的整体构造包含当然有利、但并非强制必需的大量细节。因此过滤器可以例如是其它装置或者在相应良好的信号的情况下完全取消。电动马达的触发的精确类型也可以以其它方式实现,如其对于本领域技术人员已知的那样。
Claims (9)
1.用于确定通过借助于电动马达(31)驱动的泵(30)产生的压力(64)的装置(100),其中,所述装置(100)设置用于基于所述电动马达(31)的内扭矩(114)和所述电动马达(31)的损失力矩(108)之差求得压力(64),其中,所述装置(100)还设置用于从所述电动马达(31)的马达电流(110)和所述电动马达(31)的马达常数(ke)中求得内扭矩(114),其中,所述装置设置用于从所述电动马达(31)的温度(104)和所述电动马达(31)的马达转速(68)中求得损失力矩(108)。
2.按权利要求1所述的装置,其设置用于以特征曲线(102)求得损失力矩。
3.按权利要求1所述的装置,其构造用于容积泵(30)。
4.按权利要求3所述的装置,其构造用于齿环泵(30)。
5.按权利要求4所述的装置,其构造用于摆线泵(30)。
6.按权利要求1所述的装置,其设置用于确定用于压力调节(12)的实际压力(64)。
7.用于调节通过泵(30)产生的压力(64)的调节机构(10),其具有调节器(12),所述调节器基于额定压力(62)和实际压力(64)之间的差求得调节参数,其中,所述调节机构(10)拥有用于确定实际压力的装置(100),其中按权利要求1到6中任一项所述的装置(100)用作所述装置(100)。
8.按权利要求7所述的调节机构,其中,PI调节器用作调节器(12)。
9.用于运行泵的机构,具有
-按权利要求7或8所述的调节机构(10),
-用于实施预控制的单元(14),以及
-用于在所述调节机构(10)和所述用于实施预控制的单元(14)之间进行切换的开关(80)。
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