CN1489672A - 在利用位移原理对液体加压或减压的设备和压力交换器中减少噪音和空蚀的方法 - Google Patents
在利用位移原理对液体加压或减压的设备和压力交换器中减少噪音和空蚀的方法 Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
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- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
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- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
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- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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- F15B21/008—Reduction of noise or vibration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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Abstract
一种在利用位移原理对流体加压或减压的设备和压力交换器中减少噪音和空蚀的方法,其中压力交换器的端盖中的至少一个设置有连接通道(14、17、18),在处于减压区(3)或加压区(4)内期间该连接通道实质上增加转子通道(15、16)中的流动介质的入口和出口。该方法包含不同的实施例,例如在通道(16)和相对的通道(15)之间设置有直接连接通道(14)。
Description
本发明涉及一种在利用位移原理工作的设备中减少噪音和空蚀的方法。当利用位移原理对一有限体积的液体极快加压时,将伴随产生噪音,或者当极快减压时,同样会产生噪音,但由于空蚀的原故噪音大大增强,空蚀还会损坏结构和缩短设备的寿命。
目前设备许多是已知的,其包括挪威专利Nos.161341、168548、306272中描述的液压泵、液压阀、液压致动器、液压马达和压力交换器,当其在过高的旋转频率或压力下使用时,其噪音水平便变得难以接受。实践中,因为在同一台设备内要同时完成两个过程的时间极其有限,故最后提到的那种设备特别容易受到这些工作条件的限制。
本发明的目的主要是提出一种对这些限制的敏感性大大减小的上述设备。
本发明方法的特别的特征呈现在权利要求书指出的技术特征中。
现在参看附图详细描述本发明。这些附图示意性地说明本发明如何在本发明的压力交换器中优选地实施。
图1示出了一压力交换器的端盖,其带有常规设计的高压口和低压口。
图2示出了转子旋转一周完成一个完整的工作过程中在不同位置处的经转子通道和端盖的横截面。
图3是假设流体为理想和不可压缩的且端盖上的孔口为对称的条件下,压力交换器工作过程中的转子通道压力和泄漏图。
图4是相同过程中用实际的可压缩或弹性流体工作时的压力和泄漏图。
图5示出了如何将本发明应用于压力交换器端盖上的一示例。
图6示出了本发明应用在压力交换器端盖上的另一实施例。
图1示一个具有高压口1和低压口2的对称端盖的全部主要元件。虽然图中孔口角域是一样的,但这并非必要并且在转子中与不同数目的通道结合可能是有利的。端盖上有两个密封区,其一为介于高压侧和低压侧之间的减压区3,另一为加压区4。根据转子通道按顺时针方向旋转的事实,所有转子通道都将从高压口1经过减压区3到低压口2,以便再经过加压区4又进入高压口1。此外,减压区3具有一入口边缘和一出口边缘6,相应地加压区4具有一入口边缘7和一出口边缘8。密封区3和4的角度延伸范围至少包含一个完整的转子通道及其径向壁元件。如果角度延伸范围较大,则密封区就具有一个附加区。减压区3具有的附加区用折线9表示,而加压区4具有的相应区用折线10表示。
图2a-d示出每个具有尾通道壁或后通道壁12和首通道壁或前通道壁13的转子通道11从高压口向低压口运动的循环。起始位置2a是当后通道壁12的前缘到达减区压3的入口边缘5的时刻,此时通道压力P2a相当于高压区中的压力HP。在此位置上,泄漏量最大,Q1经过前通道壁13受到最大流动阻力以及压差HP-LP(高压-低压)的作用。当转子通道的后壁12到达减压区3的位置上时,泄漏量减小,Q2受到愈益增大的流动阻力,直到转子通道到达位置2b上时为止,在该位置,两种泄漏受到相同的流动阻力,通道压力P2b相当于两个端口之间压差的一半。因为流动介质是理想的,并且在工作过程中流动介质既不蓄积,也不释放,故可假定两种泄漏量任何时候都相等。此种状态要一直保持到转子通道到达下个位置2C时为止,在该位置上,前通道壁13的前缘与出口边缘6重合。这时开始了另一状态,其导致转子通道内的压力逐渐减小,泄漏量逐渐增大以及对于泄漏流Q1的阻力逐渐下降,直到通道在位置2d处与低压口连通时为止。
图2e-h示每个转子通道从低压口向高压口运动的循环。起始位置2e是当转子通道后壁12的前缘和加压区的入口边缘7重合并且通道压力P2e相当于低压口中的压力的时刻。在此位置上,泄漏流Q3经过前通道壁13受到了大的流动阻力和压差HP-LP的作用。当转子通道的后壁12到达减压区的位置上时,泄漏流Q4受到愈益增加的流动阻力作用,直到通道到达位置2f时为止,在该位置处,两种泄漏流的流动阻力相等,而转子通道具有的压力P2f相当于两个端口之间压差的一半,即(HP-LP)/2。此种状态保持不变,直到转子通道到达下一个位置2g时为止,在该位置处,前通道壁13的前缘和出口边缘8重合。这标志着另一种状态的开始,其中转子通道内的压力逐渐增加,并且泄漏量Q4、Q3逐渐增加,直到通道在位置2h中与高压口连通为止。
图3为图2a-h所示一个转子通道完成整个工作过程中的理想压力图,其基于带有相反对称的通道的转子以及角度延伸范围相等的对称端口。该图表示两条相互间隔180°的通道,其中一条通道加压,而另一条则同时减压。该图还表示不同位置上不可压缩的理想流体介质的相对泄漏量大小。在此条件下,泄漏流Q在转子通道的端面和端盖的端面之间的间隙中建立起平衡,而且与Q=压差/流动阻力成比例。
此公式能用来对图示泄漏流进行量化分析。其清楚且明确地表明:当后通道壁12的后缘通过减压区3的入口边缘5时,转子通道中的压力逐渐降到高压口和低压口之间压差的一半。当转子通道的径向壁元件12和13完全位于减压区3内时,泄漏量Q1和Q2也逐渐减少到一半。相反的一转子通道从低压口运动到高压口,经历了和前面一转子通道相反的工作过程,压力逐渐增加到等于前面一转子通道压力的一半。泄漏量Q3和Q4在开始时最大,当后通道壁12的后缘通过加压区4的入口边缘7时逐渐减小到一半。当前通道壁13通过出口边缘8时,通道内压力增加到高压的全值,而泄漏量Q3和Q4要增加一倍。
图4示出了在使用实际弹性流体介质(即水)时压力交换器工作过程的压力图。其主要区别在于转子通道从高压侧输送流动介质,该流动介质受压缩并含有在通道与低压口连通前必须释放的额外体积,这要求泄漏量Q1和Q2不相等。由于被封闭且逐渐释放的额外体积,转子通道内的压力降极小,这产生一连续的高泄漏流量Q1和一迅速减小的泄漏流量Q2,此泄漏流Q2在压差逐渐增大的同时经过通道的后壁12重新填充转子通道。流动阻力增加很快,结果当转子的通道的壁元件12和13位于加压区4内的同时,Q2达到非常低的最小值,此后仅逐渐增加,直至其达到和理想情况下同样的最大值。该转子通道的前壁13经常受到高压差作用,并且当其前缘通过减压区的入口边缘6时,开始一个剧烈的工作过程,在此过程中,压力仅逐渐下降,而泄漏量Q1由于流动阻力大大减小而迅速增加。在该过程期间,存在大的危险,即空蚀和无法接受的噪音等级。在加压时,工作过程部分地相反并且有所不同。在此情况下,流动介质起初受到来自高压侧泄漏流Q3的作用,该泄漏流不会立即导致通道内的压力迅速增加,这是因为一部分体积由压缩所吸收,并且其压力曲线LP-HP如图中所示。这种情况还有一个结果便是泄漏量Q4虽未达到同样的量,但它一直大大低于Q3,直到转子通道差不多达到高压侧时为止,在此处相对较高的压差加上快速减小的流动阻力导致泄漏量Q4大量增加。此处还要补充一点:转子的旋转速度需要工作过程的效果的增加,因为当通道减压时,同向流动的泄漏流Q1和Q2接受较高的体积流,然而当转子通道加压时,反向流动的泄漏流Q3和Q4则减少了。这一点和实践经验符合:只有在减压区3中才可看到因空蚀而造成的破坏。
图5示出了一应用于压力交换器端盖上的本发明实施例。该提出的实施例基本上包含避免高泄漏量Q1和Q4的最大值的各种方法,因为Q1和Q4的高的最大值被认为是设备内存在较高压力和贯通流动时引起高噪音等级和空蚀破坏的原因。根据本发明,一种方法是在至少一个端盖上设置连接通道14。当两个具有壁元件12和13的通道在减压区3和加压区4内时,该通道14允许来自相对通道15和16的流体介质转移,其结果为使工作过程大致和理想压力图相当。在减压或加压时,即使每个通道都和连接通道1 4相通,也只有极短的时间存在同时连接,以允许压力平衡或均衡以及流体介质的转移。在通道16的后壁基本上已通过入口边缘5以及通道15的后壁紧接着通过入口边缘7之后,或者在两个通道同时处于与减压区3及加压区4密封接合的情况下,这种情况发生。此种通过连接通道14的同时连接在通道15的前壁到达高压口的位置之前或在通道16的前壁到达低压口的位置上之前便中断了。
亦可设想,通过为至少一个端盖设置独立且低流动阻力的连接通道17和18,将相应过程分开,即将减压和加压分别分开以实现本发明。每条通道17、18通向一高压口或一低压口,从而使在上述状态下流入或流出通道的流动大大增加。这可通过例如端盖中的设计成具有较短密封壁的长通道而实现,从而允许较高的泄漏量,但没有在低压口的出口间隙中产生空蚀的危险。此外,也可以用单独的或串联的管嘴实现通道和端口之间的连接。用此种方式将过程分开可以进一步降低噪音等级,这是因为这将可能产生一相移,从而减小图3和图4压力图中所示同时进行相反工作产生的谐振。本发明亦可结合不同数目的转子通道、不同尺寸的通道、同时处于减压或加压的更多通道以及具有不同角度延伸范围的不对称端口,以便优化本发明的效果。
Claims (5)
1.一种在利用位移原理对流体加压或减压的设备和压力交换器中减少噪音和空蚀的方法,其特征在于,压力交换器的端盖中的至少一个设置有连接通道(14、17、18),在处于减压区(3)或加压区(4)内期间该连接通道实质上增加转子通道(15、16)中的流动介质的入口和出口。
2.按照权利要求1所述的在利用位移原理对流体加压或减压的设备和压力交换器中减少噪音和空蚀的方法,其特征在于,至少一个端盖中的连接通道(14)布置成用于相对的通道(15、16)之间的直接连通,并且当所述通道同时在减压区(3)和加压区(4)内时该连接通道(14)提供压力平衡。
3.按照权利要求1所述的在利用位移原理对流体加压或减压的设备和压力交换器中减少噪音和空蚀的方法,其特征在于,至少一个端盖设置有分开的、流动阻力低的连接通道(17、18),该通道在所述阶段期间连接端口和转子通道(15、16)并分别允许加压和减压的相移。
4.按照权利要求1和3所述的在利用位移原理对流体加压或减压的设备和压力交换器中减少噪音和空蚀的方法,其特征在于,连接通道(17、18)非常长并具有一分别紧靠高压口和低压口的短密封表面,由此允许高的泄漏量。
5.按照权利要求1和3所述的在利用位移原理对流体加压或减压的设备和压力交换器中减少噪音和空蚀的方法,其特征在于,所述转子通道(15、16)在处于减压区(3)和加压区(4)内期间经流动阻力低的管嘴分别与该高压口及该低压口连接,由此提供压力平衡并且减少被认为是导致噪音和空蚀的原因的泄漏流(Q1和Q4),或者在第二实施例中设置有分开的、流动阻力低的连接通道(17、18),该通道在所述阶段期间连接端口和转子通道(15、16)并分别允许加压和减压的相移。
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NO20001877 | 2000-04-11 | ||
PCT/NO2001/000165 WO2001077529A2 (en) | 2000-04-11 | 2001-04-11 | Method for reducing noise and cavitation in machines and pressure exchangers which pressurize or depressurize fluids by means of the displacement principle |
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GB0319042D0 (en) * | 2003-08-13 | 2003-09-17 | Univ Surrey | Osmotic energy |
DE102004025289A1 (de) | 2004-05-19 | 2005-12-08 | Ksb Aktiengesellschaft | Rotations-Druckaustauscher |
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- 2001-04-11 DK DK01966776T patent/DK1276991T3/da active
- 2001-04-11 WO PCT/NO2001/000165 patent/WO2001077529A2/en active IP Right Grant
- 2001-04-11 AT AT01966776T patent/ATE330121T1/de active
- 2001-04-11 IL IL15226701A patent/IL152267A/xx not_active IP Right Cessation
- 2001-04-11 AU AU9333901A patent/AU9333901A/xx active Pending
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- 2001-04-11 CN CN018109977A patent/CN1489672B/zh not_active Expired - Lifetime
- 2001-04-11 ES ES01966776T patent/ES2266244T3/es not_active Expired - Lifetime
- 2001-04-11 AU AU2001293339A patent/AU2001293339B2/en not_active Expired
- 2001-04-11 EP EP01966776A patent/EP1276991B1/en not_active Expired - Lifetime
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CN102606548A (zh) * | 2012-03-23 | 2012-07-25 | 大连理工大学 | 径流式射流气波增压器 |
CN102606548B (zh) * | 2012-03-23 | 2014-07-23 | 大连理工大学 | 径流式射流气波增压器 |
CN104704274A (zh) * | 2012-08-16 | 2015-06-10 | 芙罗服务管理公司 | 流体交换装置、压力交换器和相关方法 |
CN104704274B (zh) * | 2012-08-16 | 2017-11-07 | 芙罗服务管理公司 | 流体交换装置、压力交换器和相关方法 |
CN104373396A (zh) * | 2013-08-15 | 2015-02-25 | 丹佛斯公司 | 液压机,特别是液压压力交换器 |
US9556736B2 (en) | 2013-08-15 | 2017-01-31 | Danfoss A/S | Hydraulic machine, in particular hydraulic pressure exchanger |
CN106103890A (zh) * | 2013-10-03 | 2016-11-09 | 能量回收股份有限公司 | 带有液压能传递系统的frac系统 |
CN107795448A (zh) * | 2016-08-29 | 2018-03-13 | 罗伯特·博世有限公司 | 液压静力轴向柱塞机 |
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EP1276991B1 (en) | 2006-06-14 |
EP1276991A2 (en) | 2003-01-22 |
NO312563B1 (no) | 2002-05-27 |
AU9333901A (en) | 2001-10-23 |
US20020025264A1 (en) | 2002-02-28 |
NO20001877L (no) | 2001-02-01 |
DK1276991T3 (da) | 2006-10-02 |
CN1489672B (zh) | 2012-11-07 |
NO20001877D0 (no) | 2000-04-11 |
ATE330121T1 (de) | 2006-07-15 |
ES2266244T3 (es) | 2007-03-01 |
IL152267A (en) | 2005-12-18 |
US6540487B2 (en) | 2003-04-01 |
WO2001077529A3 (en) | 2002-08-08 |
DE60120679T2 (de) | 2007-06-14 |
WO2001077529A2 (en) | 2001-10-18 |
IL152267A0 (en) | 2003-05-29 |
DE60120679D1 (de) | 2006-07-27 |
AU2001293339B2 (en) | 2007-01-04 |
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