1345.629 九、發明說明： 【發明所屬之技術領域】 量測技術、油壓技術、液靜壓技術：本發明係一種量測加壓流 體通過液壓組件的節流係數及流阻所使用的量測儀，指一種由兩個 獨立的承载平台以及同一個供油的泵浦及流路系統、感測器信號 處理系統組成之量測儀，可應用於各種雙向作動之液壓組件；將兩 個獨立的負荷分別加載於承載平台時，待測液壓組件被分別獨立的 •調節兩個流道的作動壓力，以液壓組件上游及下游的壓力感測器量 測得到壓力差，以及流量感測器量測得到通過液壓組件的流量，將 壓力差除以流量’得到液壓組件之流阻。以溫度感測器量測組件流 路入口及出口之各別溫度，將溫度取平均值，得到對應的流體黏度 係數，以流阻之倒數與流體黏度相乘的運算’得到液壓組件兩個流 路分別，節流係數；因此本發明為利用壓力與流量關係，經量測壓 力、流量及溫度，根據流體動力原理，經數值計算得到液廢組件之 •流，及㈣係數’這些量測、計算、訊號處理及輸出，運用到電腦、 計算程式、及人機介面。 【先前技術】 在各式顧控制H具中，_裝置的目的，除作為調整工作流 大小外，：兼具緩衝來源端與負載端之間流嶋的 ^ ’因而節流係數與流阻即為液壓組件工作效能之指 T，之输術，多她流f敵技術’= 關於即流餘與流阻之制技術。如： 7 ^45629 :華民國專利公告第Π72374號，專利额：流量制裝置及其製 4方去’公告日期：2007/02/01，申請日期：2005/11/29。 專利摘要：代表圖如第〗圖所示，本發明係提出一種量測裝置， 二來量測-流體之—流量，該量測裝置包括—基座、—流道、及至 ^兩電子電路，其巾該流道設於該基座上，該流體在該流道中流動， 該流道具有至少二截面；以及至少二電子電路分別與該至少二截 =電性連接’該至少二電子電路係偵測對應之該至少二截面之訊號 ♦ Μ化’再據以計算該流體之該流量。該種量測裝置係_一微電子 機械系統製程製備。 中華民國專利公告第0〇549435號，專利名稱：多功能壓力量測裝置， 公告日期：2003/08/2卜申請日期：2002/07/30 專利摘要：代表圖如第2圖所示，一種壓力量測裝置，包括一 籃°十《亥差疆什上设有一尚壓接頭及一低壓力接頭；以及一閥件， 該閥件上設有一固定口、一第一切換口及一第二切換口，該固定口 φ 〃該向壓力接頭相通；當該固定口與該第一切換口連通時，與該高 壓力接頭所連通的壓力為待測的管内全壓，與該低壓力接頭所連通 的壓力為待測的管内靜壓，則差壓計所顯示的數值為管内動壓；當 該固定口與該第二切換口連通時，與該高壓力接頭所連通的壓力為 大氣壓，與該低壓力接頭所連通的壓力為待測的管内靜壓，則差壓 計所顯示的數值為相對壓力。 上述專利a為液壓組件之壓力與流量量測。雙向作動液壓組 件，因外負荷作用引致内部各別壓力獨立變動，為了在設計之際， 即已確認該液壓組件之流阻及節流係數，只使用壓力計與流量計， 8 1345629 無法獲得相關於兩側獨立壓力作用於液壓組件内部元件之效應，亦 未具備篁測雙壓力作用時節流係數及流阻之量測方法。 【發明内容】 當流體通過液壓組件内部小孔、微小縫隙、細長通孔、彎曲管 迢或曲折通道時，因流體本身之黏滯性及表面摩擦阻力而造成壓力 降，壓力降與流量的比值為流體流動所受到之流阻，流阻之倒數乘 鲁以黏度係數即為元件之流動通道之節流係數；待測液壓組件内部流 路因設計複雜造成節流係數差異甚大，以及流體於管路内因摩擦昇 溫造成黏度改變，則影響液壓組件的流阻特性。 雙向作動液壓組件為兩個來源的壓力作用於其感應元件上，而 產生所需控制流動之作用，因此供油進入液壓組件後，循兩條分開 的内部流路通過，以兩條不同之出口離開液壓組件，到達油腔，因 承載平台被獨立的施加負荷，致使承載平台所受負荷獨立的反饋作 鲁用之流量及壓力，經兩個内部流路之獨立油壓，而以不同的壓力作 用在液壓組件之内部感應元件上，感應元件用來自動調節及反饋承 載重量塊的負荷作用。 測量液壓組件之流阻及節流係數，使用同一組供油果浦及油箱 的供流路系統，供應壓力使工作流體經過供油分配器，分成相同供 壓之兩條入口流路進入待測液壓組件，通往承載平台與轴承座之間 的油腔而流出，當作用於承載平台的負荷改變時，承載平台與轴承 座之間之油腔虔力隨之改變，此油腔内的壓力會因液壓組件内之流 9 1345629 阻作用而比供油壓力降低。 备兩個來自油㈣回饋壓力同時作用在液壓組件之感應元件 夺其"IL動由供壓連續推動兩條獨立的内部流路流體通過該液壓組 件而攸負荷端之兩個驗流出，成觸立的兩個工傾力，並且兩 個流量繼續經由軸承座與承載平台之間的間隙而流出，因此液壓組 件的兩細立_部流路流量分㈣供壓及各別的工作壓力之差 β 乂及均為紅作壓力之差值的函數，並且此兩流量依據兩個工 作壓轉用在感應元件而改變，因此兩個内部流路之節流係數分別 為_組件内部流路及感應元件的設計幾何及尺寸的函數之正比係 數。 使用本發明量測液壓組件的流阻時，以兩個反績於感應元件之 工倾力之差值為參數，蚊此參數，崎賴組件其中—個流路 2壓力降，則此流路之塵力降除以流量得流路的流阻，保持兩 乍動堡力差為定值，連續的調整壓力降，因而得到流量隨壓力降之 ·=數以作動壓力差為參數。將兩個内部流路供壓紅作壓力的差值 2別除以各別的流量，得到液壓組件之兩條内部流路隨不同作動麼 力差而改變之流阻。 雙向作動之雜組件内部兩條流路的通道具有小孔時，液壓组 部流路的流量為切流路及出σ流路分別賴差，以及兩 可以得到兩内部流路 之㈣_雜函數，㈣量_部鱗之_平均溫度 侍至]黏度係數，以及測量得到的非線性函數， 因投計幾何及尺寸而定之節流係數。 本發明的系統係由兩個承載平台與側向贿平面轴承的組合 ^45629 輪承座、供油系潘及:¾路系統、感測器、信號處理系統所組成，承 载平台與側向雜平面轴承均製以由外連通至内側油腔的油孔，用 來保持油麼，兩承載平台分別與其側向靜好面軸承組裝在一起坐 落於轴承座，軸承座坐祕集域，無槽連接咖f，絲引油 回油箱；流路系統包含有供油泵浦、油箱、_器、細渡器、三點 、、且止回閥、蓄壓器與壓力表；從油箱經栗浦加壓的流體 經過雙向作動之液壓組件後，分成兩個流道流至各自連通承载平台 •=訊，產生流體繼支持承餅台的射，改變兩财載平台的 荷重，用來獨立的調整此流體靜壓。 加壓流體由系浦從油箱流出，首先通過流路系統的粗渡器及三 丄且一點組包含有濾清器、調壓閥、油霧器與壓力表，具有過據、 遞與心官路的功能，流路系統以止回晰止流體逆流 ，以洩壓 間认定最大額&壓力，並根缝力絲控概路祕巾流體的供油 壓力。供應流體接著通過蓄壓器，以穩定流體的壓力，再以細渡器 鲁細渡流體中的雜質後，經供油分配器以穩定的壓力分配於兩個流 =、’其-流路經流量分配器内毛細管節流器或其他型式的節流器調 即流體之壓力後，以分開的流路供往各獨立的側向支承靜壓平面轴 承’則乍為荷重平台側向定位之用，另一流路之流體經過雙向作動 之液=組件後，再分成兩個流路通往兩個承載平台的油腔，最後從 油腔机出至集油槽；以壓力感測器及流量感測器量測流體通過待測 液[’、且件之壓力差及流量，溫度感湘分職啦體待測液壓 組件二口之流體溫度與出口之流體溫度。 田負载作用於承載平台時，經油孔流入承載平台内與轴承座之 1345629 間的油膜形成流體靜壓，此流體靜壓隨承載平台上負載重量之變化 而改邊，與供應壓力相比較，因液壓組件内之流阻作用而產生壓力 降由壓力感測器1測流體通過待測液壓組件之進口壓力及出口壓 力，由流量感測器、溫度感測器分別量測流量及流體溫度，以訊號 擷取卡將類比訊號轉成數位訊號，擷取並傳輸至電腦，以電腦程式 計算待測液壓組件節流係數及流阻；信號之處理，執行量測參數調 正、校準、&十异結果及信號變化等顯示之輸出，均由人機介面執行。 k號處理系統分成硬體與軟體兩部分，硬體包含感測器、感測 器放大器、感測器連線、資料擷取卡、信號接線盒、排線與電腦； 軟體包含人機介面及計算程式，人機介面包括操作晝面、數值輸入 及量測參數設定輸入、量測信號及計算結果顯示操作；量測設定包 含有量測通道設定、歸零設定、敏感度設定、工作流體參數設定、 取樣頻率及解析條數設定；量測通道設定各感測器分別對應於訊號 擷取卡上之量測通道，以區別各感測器之電壓訊號所對應之通道。 【實施方式】 本發明所揭露之節流係數及流阻量測儀，依據「第3圖」至「第 8圖」來說明本發明之實施方式。 本發明實施方式根據的原理說明如第3圖所示，雙向作動液壓 組件30為兩個來源的壓力作用於其感應元件23上，而產生所需控 制流動之作用’因此供油進入液壓組件30後，循兩條分開的内部流 路231及232通過，以兩條不同之出口 241及242離開液壓組件3〇, 到達油腔251及252，因承載平台101及102被獨立的施加重量塊 12 1345629 151及152 ’致使承载平台101及102所受負荷獨立的反饋作用之流 量及壓力，經兩個内部流路231及232之獨立油壓，而以不同的壓 力作用在液壓組件30之内部感應元件23上’感應元件23用來自動 調節及反饋承載重量塊151及152的負荷作用，因此感應元件23之 設計以及液壓組件30及其内部流路等之設計，影響了液壓組件3〇 之流阻、節流係數以及其流體通過之工作性能。 測量液壓組件30之流阻及節流係數，使用同一組供油泵浦4〇 及油箱401的供流路系統，供應壓力使工作流體經過供油分配器 409，分成相同供壓之兩條入口流路2 n、2丨2進入待測液壓組件3〇， .到達承載平台101及102之軸承座121及122，經過軸承座121及 122之油腔251及252而流出，當負載由重量塊151及152作用於承 載平台101及102時，於承載平台ι〇1及1〇2之油腔251及252内 產生壓力，此油腔内的壓力會因液壓組件3〇内之流阻作用而比供油 壓力降低。 雙向作動液壓組件，將供壓供給的油壓轉換成兩個不同的工作 壓力，及不同的流量，供壓β流體之流量為總流量2，兩個作動壓 力分別為6及6 ’其對應之流量，分別為Q及02，因此 δ = Q + & 當雙向作動液壓組件30兩條内部流路231及232的通道為狹縫 及毛細管時，兩條内部流路231及232的流量分別為其入口流路 21卜212及出口流路241、242壓差化一⑴及化一⑸之正比函數， 且均為兩條出口流路Ml及242壓差ΔΡ〗2 =尸丨之函數，以及與 黏度係數成反比的函數，因此可以表示成 13 1345629 a=J(d)yi(AP12) β2 户2)Λ(ΔΡ12) 其中γ及久 數，1 6刀別為液壓元件30的兩個内部流路231及232之節流係 數，刀別為通過兩個内部流路231及232之流體平均黏度係 1及’2 (·)分別為尸1 _户2之兩個非線性函數。 —又向作動之液壓組件30内部兩條流路231及232的通道具有 φ 夺兩條内部流路231及232的流量則成為入口流路211、212 出"IL路24卜242分別的壓差叫=(d)及ΔΡ2=(d)， 以及兩條出口流路24卜242壓差叫=A 1的非線性函數，因此 表不成 Q\=~gMPuAPn)1345.629 Nine, invention description: [Technical field of invention] Measurement technology, hydraulic technology, hydrostatic pressure technology: The present invention is a measurement for measuring the throttling coefficient and flow resistance of a pressurized fluid through a hydraulic component Instrument, a measuring instrument consisting of two independent carrying platforms and the same oil pumping and flow system, sensor signal processing system, can be applied to a variety of two-way hydraulic components; two independent When the loads are respectively loaded on the carrying platform, the hydraulic components to be tested are independently independent. • The operating pressure of the two flow paths is adjusted, and the pressure difference is measured by the pressure sensors upstream and downstream of the hydraulic components, and the flow sensor amount is measured. The flow through the hydraulic assembly is measured, and the pressure difference is divided by the flow rate to obtain the flow resistance of the hydraulic component. The temperature sensor is used to measure the temperature of the inlet and outlet of the component flow path, and the temperature is averaged to obtain the corresponding fluid viscosity coefficient, and the operation of multiplying the flow resistance by the reciprocal of the flow resistance is obtained. The road separately has a throttling coefficient; therefore, the present invention utilizes the relationship between pressure and flow, measures the pressure, flow rate and temperature, according to the principle of fluid dynamics, numerically calculates the flow of the liquid waste component, and (4) the coefficient 'these measurements, Calculation, signal processing and output, applied to computers, computing programs, and human-machine interfaces. [Prior Art] In the various types of control H, the purpose of the device is, in addition to the size of the adjustment workflow, both the buffer source and the load end. Therefore, the throttle coefficient and the flow resistance are For the hydraulic components work efficiency refers to T, the transmission, more than her flow of enemy technology '= about the system of flow and flow resistance. Such as: 7 ^45629: Republic of China Patent Notice No. 72374, patent amount: flow system and its system 4 to go 'announcement date: 2007/02/01, application date: 2005/11/29. Patent Abstract: As shown in the figure, the present invention proposes a measuring device, which measures the flow rate of the fluid, and the measuring device comprises a base, a flow channel, and two electronic circuits. The flow channel is disposed on the base, the fluid flows in the flow channel, the flow channel has at least two cross sections; and at least two electronic circuits are electrically connected to the at least two sections respectively. The at least two electronic circuit systems Detecting the signal corresponding to the at least two cross-sections ♦ Deuteration is further calculated to calculate the flow rate of the fluid. The measuring device is prepared by a microelectromechanical system process. Republic of China Patent Notice No. 0549549, Patent Name: Multi-Function Pressure Measuring Device, Announcement Date: 2003/08/2 Application Date: 2002/07/30 Patent Abstract: Representative Figure as shown in Figure 2, The pressure measuring device comprises a basket of ten "there is a pressure joint and a low pressure joint on the sea; and a valve member, the valve member is provided with a fixed port, a first switching port and a second a switching port, the fixed port φ 〃 is connected to the pressure joint; when the fixed port is in communication with the first switching port, the pressure connected to the high pressure joint is the total pressure in the pipe to be tested, and the low pressure joint The connected pressure is the static pressure in the tube to be tested, and the value displayed by the differential pressure gauge is the dynamic pressure inside the tube; when the fixed port is in communication with the second switching port, the pressure connected to the high pressure joint is atmospheric pressure, and The pressure connected by the low pressure joint is the static pressure inside the pipe to be tested, and the value displayed by the differential pressure gauge is the relative pressure. The above patent a is the pressure and flow measurement of the hydraulic component. The hydraulic components are operated in both directions, and the internal pressures are independently changed due to the external load. In order to confirm the flow resistance and the throttling coefficient of the hydraulic components at the time of design, only the pressure gauge and the flowmeter are used, 8 1345629 cannot be related. The effects of independent pressure on the internal components of the hydraulic components on both sides, and the measurement method of the throttling coefficient and flow resistance when the double pressure is applied are not available. SUMMARY OF THE INVENTION When a fluid passes through a small hole, a small gap, an elongated through hole, a curved tube or a tortuous path inside a hydraulic component, the pressure drop due to the viscosity of the fluid itself and the surface frictional resistance, the ratio of the pressure drop to the flow rate For the flow resistance of the fluid flow, the reciprocal of the flow resistance multiplied by the viscosity coefficient is the throttling coefficient of the flow channel of the component; the internal flow path of the hydraulic component to be tested is greatly different due to the complicated design, and the fluid is in the tube. The viscosity change caused by the friction heating in the road affects the flow resistance characteristics of the hydraulic components. The two-way actuating hydraulic assembly acts on the sensing element from two sources of pressure to create the desired control flow, so that after the oil enters the hydraulic assembly, it passes through two separate internal flow paths, with two different outlets. Leaving the hydraulic components and reaching the oil chamber, the load is independently applied by the load-bearing platform, so that the independent feedback of the load on the load-bearing platform is used for the flow and pressure of the use, and the independent oil pressure of the two internal flow paths is at different pressures. Acting on the internal sensing element of the hydraulic component, the sensing element is used to automatically adjust and feedback the load acting on the weight block. Measuring the flow resistance and throttling coefficient of the hydraulic components, using the same supply flow system for the oil and the fuel tank, supplying the pressure so that the working fluid passes through the oil supply distributor, and is divided into two inlet flow paths of the same pressure to enter the test The hydraulic component flows out to the oil chamber between the bearing platform and the bearing housing. When the load for the load bearing platform changes, the oil chamber pressure between the bearing platform and the bearing housing changes, and the pressure in the oil chamber changes. It will be lower than the supply pressure due to the resistance of the flow in the hydraulic assembly 9 1345629. Prepare two inductive components from the oil (four) feedback pressure and act on the hydraulic components. The IL is continuously pressurized by the pressure supply. Two independent internal flow paths are passed through the hydraulic component and the two ends of the load rejection are formed. Two working forces are struck, and the two flows continue to flow out through the gap between the bearing housing and the load bearing platform, so the two vertical flow portions of the hydraulic assembly are divided into four (4) pressure supply and respective working pressures. The difference β 乂 is a function of the difference between the red pressures, and the two flows are changed according to the two working pressures used in the sensing element, so the throttling coefficients of the two internal flow paths are respectively _ component internal flow paths and The proportional coefficient of the design geometry and the function of the dimensions of the sensing element. When the flow resistance of the hydraulic component is measured by the present invention, the difference between the two working forces of the sensing element is taken as a parameter, and the parameter of the mosquito, the pressure drop of the flow channel 2 of the component, is the flow path. The dust force is reduced by the flow resistance of the flow path, and the difference between the two turbulences is maintained as a constant value, and the pressure drop is continuously adjusted, so that the flow rate decreases with the pressure drop as the parameter. The difference between the pressures of the two internal flow paths for the pressure red is divided by the respective flow rates, and the flow resistances of the two internal flow paths of the hydraulic components change with different actuation forces are obtained. When the channel of the two flow paths in the two-way operation has a small hole, the flow rate of the flow path of the hydraulic group is the difference between the flow path and the σ flow path, and the two internal flow paths can be obtained. , (four) quantity _ part of the scale _ average temperature served to] viscosity coefficient, and the measured nonlinear function, the throttle coefficient due to the geometry and size of the survey. The system of the present invention is composed of a combination of two bearing platforms and lateral bristle plane bearings, a 45629 wheel bearing seat, an oil supply system pan: a 3⁄4 way system, a sensor, and a signal processing system, and the carrying platform and the lateral miscellaneous The plane bearing is made of oil hole that communicates from the outside to the inner oil chamber to keep the oil. The two bearing platforms are assembled with the lateral static surface bearing respectively, and are seated in the bearing housing. Connect the coffee f, the silk oil returns to the fuel tank; the flow system includes the oil pump, the fuel tank, the _, the finer, the three points, and the check valve, the accumulator and the pressure gauge; from the tank through the Lipu After the pressurized fluid passes through the two-way hydraulic component, it is divided into two flow channels to flow to the respective supporting platform. The fluid is generated to support the bearing platform, and the load of the two financial platforms is changed for independent adjustment. This hydrostatic pressure. The pressurized fluid flows out of the fuel tank by the pump, first through the roughing device of the flow system and the three-way and one-point group contains the filter, the pressure regulating valve, the oil mister and the pressure gauge, which has the basis, the hand and the heart The function of the road, the flow system to stop the flow of the fluid to stop the flow, to determine the maximum amount of pressure and pressure, and to control the oil supply pressure of the fluid. The supply fluid then passes through the accumulator to stabilize the pressure of the fluid, and then the impurities in the fluid are finely branched, and then distributed to the two streams via the oil distributor with a stable pressure =, 'the flow path The capillary restrictor or other type of restrictor in the flow distributor is adjusted to be the pressure of the fluid, and is supplied to the independent laterally supported hydrostatic plane bearing by separate flow paths, which is used for lateral positioning of the load platform. After the fluid of the other flow path passes through the two-way operation liquid=component, it is divided into two flow paths to the oil chamber of the two bearing platforms, and finally from the oil chamber to the oil collecting tank; the pressure sensor and the flow sensing The measuring fluid passes through the liquid to be tested [', and the pressure difference and flow rate of the parts, and the temperature senses the temperature of the fluid to be measured and the fluid temperature of the outlet. When the field load acts on the load-bearing platform, the oil film flows into the oil film through the oil hole and forms a hydrostatic pressure between the oil film and the 1345629 of the bearing seat. The hydrostatic pressure changes with the load weight on the load-bearing platform, compared with the supply pressure. The pressure drop caused by the flow resistance in the hydraulic component is measured by the pressure sensor 1 through the inlet pressure and the outlet pressure of the hydraulic component to be tested, and the flow sensor and the temperature sensor respectively measure the flow rate and the fluid temperature. The analog signal is converted into a digital signal by the signal capture card, captured and transmitted to the computer, and the throttle coefficient and flow resistance of the hydraulic component to be tested are calculated by the computer program; the signal processing is performed, and the measurement parameter adjustment, calibration, & The output of the display of the ten different results and signal changes is performed by the human machine interface. The k processing system is divided into two parts: hardware and software. The hardware includes sensors, sensor amplifiers, sensor connections, data capture cards, signal junction boxes, cables and computers. The software includes human-machine interface and Calculation program, man-machine interface includes operation surface, numerical input and measurement parameter setting input, measurement signal and calculation result display operation; measurement setting includes measurement channel setting, zero setting, sensitivity setting, working fluid parameter Setting, sampling frequency and number of parsing settings; measuring channel setting each sensor corresponds to the measuring channel on the signal capture card to distinguish the channel corresponding to the voltage signal of each sensor. [Embodiment] The throttling coefficient and the flow resistance measuring instrument disclosed in the present invention will be described based on "3rd" to "8th drawing". DESCRIPTION OF THE PREFERRED EMBODIMENTS According to the principles of the present invention, as shown in FIG. 3, the two-way actuating hydraulic assembly 30 applies two sources of pressure to its sensing element 23 to produce the desired control flow. Thus, the oil supply enters the hydraulic assembly 30. Thereafter, the two separate internal flow paths 231 and 232 pass, leaving the hydraulic assembly 3〇 at two different outlets 241 and 242, reaching the oil chambers 251 and 252, since the load platforms 101 and 102 are independently applied with the weight blocks 12 1345629 151 and 152 'the flow and pressure causing the load-independent feedback of the load-bearing platforms 101 and 102 to be independent of the internal oil pressure of the two internal flow paths 231 and 232, and acting on the internal pressure of the hydraulic component 30 with different pressures The sensing element 23 on the component 23 is used to automatically adjust and feedback the load acting on the weight 151 and 152. Therefore, the design of the sensing component 23 and the design of the hydraulic component 30 and its internal flow path affect the flow of the hydraulic component 3 Resistance, throttling coefficient and the performance of its fluid passage. Measuring the flow resistance and the throttling coefficient of the hydraulic assembly 30, using the same set of oil supply pump 4 and the supply flow system of the fuel tank 401, the supply pressure is passed through the oil supply distributor 409, and divided into two inlets of the same pressure supply. The flow paths 2 n, 2 丨 2 enter the hydraulic component 3 待 to be tested, reach the bearing seats 121 and 122 of the bearing platforms 101 and 102, and flow out through the oil chambers 251 and 252 of the bearing housings 121 and 122 when the load is from the weight When 151 and 152 are applied to the carrying platforms 101 and 102, pressure is generated in the oil chambers 251 and 252 of the carrying platforms ι〇1 and 1〇2, and the pressure in the oil chamber is caused by the flow resistance in the hydraulic assembly 3 Lower than the oil supply pressure. The two-way hydraulic component converts the oil pressure supplied by the pressure into two different working pressures, and different flow rates, and the flow rate of the pressurized β fluid is the total flow rate 2, and the two operating pressures are 6 and 6 ' respectively. The flow rates are Q and 02, respectively, so δ = Q + & When the passages of the two internal flow paths 231 and 232 of the two-way hydraulic component 30 are slits and capillaries, the flow rates of the two internal flow paths 231 and 232 are respectively The inlet flow path 21 212 and the outlet flow paths 241, 242 are differentially proportional to one (1) and one (5), and are the function of the pressure difference ΔΡ 2 = corpse of the two outlet flow paths M1 and 242, and A function inversely proportional to the viscosity coefficient, so it can be expressed as 13 1345629 a=J(d)yi(AP12) β2 household 2)Λ(ΔΡ12) where γ and the number of hours, 16 6 are the two internal parts of the hydraulic component 30 The throttle coefficients of the flow paths 231 and 232 are two nonlinear functions of the fluid average viscosity system 1 and '2 (·) passing through the two internal flow paths 231 and 232, respectively. - the flow path of the two flow paths 231 and 232 inside the hydraulic assembly 30 is φ. The flow rates of the two internal flow paths 231 and 232 become the pressures of the inlet flow paths 211, 212 and the "IL road 24 242" respectively. The difference between = (d) and Δ Ρ 2 = (d), and the two outlet flow paths 24 242 pressure difference is called = A 1 nonlinear function, so the table does not become Q\=~gMPuAPn)
Qi =~g2(AP2,APl2) _ 其中h及分別為兩條内部流路231及232之節流係數，外及〜為 兩條内部流路231及232之流體黏度係數，幻㈠及心㈠分別為兩個 壓差、△户 12及△尸2、APi2的非線性函數。 當兩個來自油腔25卜252的回饋壓力A及巧同時作用在液壓組 件30之感應元件23時，其流動由供壓巧連續推動兩條獨立的内部 流路0及&流體通過該液壓組件30而從負荷端之兩個油腔251及 252流出，成為獨立的兩個工作壓力户 1及户2，並且兩個流量^及^繼 續經由軸承座121及122與承载平台101及102之間的間隙而流出， 14 1345629 因此液壓組件30的兩條獨立的内部流路23 i、232流量別 為供壓以各獅I作勤$、&之差似及均為兩工作壓力之乃 及Α差值的函數，並且此兩流量依據兩個讀壓力^與&作用在感 應元件23而改變，因此兩個内部流路別及Μ2之節流係數^及^ 分別為雜組件30内部流路23卜232及感應元件23的設計幾何及 尺寸的函數/ι(·)及Λ(·)之正比係數。Qi =~g2(AP2,APl2) _ where h and the throttle coefficients of the two internal flow paths 231 and 232, respectively, and ~ are the fluid viscosity coefficients of the two internal flow paths 231 and 232, phantom (1) and heart (1) They are nonlinear functions of two differential pressures, Δ household 12 and △ corpse 2, and APi2. When the two feedback pressures A from the oil chambers 25 252 and the sensing elements 23 of the hydraulic assembly 30 act simultaneously, the flow is continuously pushed by the pressure supply by two independent internal flow paths 0 and & The assembly 30 flows out of the two oil chambers 251 and 252 at the load end to become two independent working pressure households 1 and 2, and the two flows ^ and ^ continue through the bearing blocks 121 and 122 and the carrying platforms 101 and 102. The gap between the two flows out, 14 1345629. Therefore, the flow of the two independent internal flow paths 23 i, 232 of the hydraulic assembly 30 is the pressure for each lion I to work as a divergence, and the difference between them is the two working pressures. And the function of the difference value, and the two flow rates are changed according to the two read pressures ^ & acting on the sensing element 23, so the throttle coefficients of the two internal flow paths and Μ2 are respectively the internal components of the hybrid component 30 The flow path 23 232 and the design geometry of the sensing element 23 and the function of the dimensions / () and Λ (·) proportional coefficient.
μ阻之疋義為流動壓力降除以流量，因此流體通過雙向壓力作 動的液[組件30 ’麵條道+只有狹縫及毛細管時，祕内部流 路231及232的流阻彼此獨立，分別計算如下： 以及 -因此’使用本發明量測液壓組件3G的流阻時，以兩個反饋於感 件23之工作壓力之差值e—a為參數α，固定此參數α，改變 液壓、’且件3G射-鑛路之勤降，則此流路之動降除以流量得 到該，路的流阻’保持兩作動壓力差為定值，連續的調整壓力降， 因而％Ί減壓力降之函數以作祕力差為參數。將兩個内部流 路加及232供遷C與工作壓力6及？2的差值分別 除以f別的流量β及&，得到液壓组件3〇之兩條内部流路23i及 、=不同作動勤差而改變之流阻，⑽阻之倒數與流體黏度相乘 的運算仔到液壓組件3〇兩條内部流路231及232分別的節流係數。 又向作動之液壓組件3〇内部兩條流路231及况的通道具有小 1345629 孔時，液壓組件30兩條内部流路231及232的流量^及込為入口 流路211、212及出口流路24卜242分別的壓差M、^，以及兩 出口流路24卜242之壓差叫的非線性函數，由測量兩内部流路 23卜232之流體平均溫度得到黏度係數a及&，以及測量得到的非 線性函數&(^，叫）及《2(λρ2，δρ12)，可以得到兩内部流路231 及232因设計幾何及尺寸而定之節流係數a及&，計算如下： n=___Β〇ι__The meaning of μ resistance is the flow pressure drop divided by the flow rate, so the fluid is operated by the bidirectional pressure [component 30 'noodles + only slits and capillaries, the flow resistance of the internal flow paths 231 and 232 are independent of each other, respectively As follows: and - therefore, when using the present invention to measure the flow resistance of the hydraulic component 3G, the difference e-a of the two working pressures fed back to the sensing member 23 is the parameter α, the parameter α is fixed, and the hydraulic pressure is changed, and The 3G shot-mining of the mine road, the flow of the flow is reduced by the flow rate, the flow resistance of the road 'maintains the pressure difference between the two actuations, the pressure is continuously adjusted, so the pressure drop is reduced. The function takes the difference of the secret force as a parameter. Add two internal flow paths to 232 for C and work pressure 6 and? The difference between 2 is divided by the flow rate β and & respectively, and the two internal flow paths 23i of the hydraulic component 3〇 and the flow resistance changed by different operating divergence are obtained, and (10) the reciprocal of the resistance is multiplied by the fluid viscosity. The operation is performed to the hydraulic component 3, and the throttle coefficients of the two internal flow paths 231 and 232, respectively. When the two internal flow paths 231 and the passages of the hydraulic unit 3 are operated with a small 1345629 hole, the flow rates of the two internal flow paths 231 and 232 of the hydraulic component 30 are the inlet flow paths 211, 212 and the outlet flow. The differential pressures of the pressure difference M, ^, and the pressure difference between the two outlet flow paths 24 and 242 of the roads 24 and 242 are obtained by measuring the average temperature of the fluids of the two internal flow paths 23 and 232 to obtain the viscosity coefficients a and & And the measured nonlinear function & (^, call) and "2 (λρ2, δρ12), can obtain the throttle coefficients a and & of the two internal flow paths 231 and 232 due to the design geometry and size, calculated as follows : n=___Β〇ι__
g^AP^AP^ γ2=_thQl ^2(ΔΡ2,ΔΡ12) 本發明實施方式的系統如第4圖所示，係由供棘浦及流路系 統、感測器、信號處理系統、以及兩獨立的承載平台1〇1及ι〇2與 側向靜壓平面軸承ln及112組裝在—起，分触落在軸承座⑵ =12j之上’轴承座坐落在集油槽13之内，以回油管μ連接至油 箱；流路系統包含有泵浦40、油箱、粗濾器4〇2、細渡器彻、 三點組404、_閥4〇5、止回閥4〇6、蓄壓器術盘壓力表傾· 感測器包含有溫度感測器3η、312、313、314，流量感測器321 : 322與壓力感測器33卜332、341、342。 卜本發明的實施方式如第5⑻圖所示的承载平台10與兩個側向靜 =平面轴承u及11G以螺絲組合在—喊⑽構造坐落在轴承座 2座12坐落在無槽14的底板上，回辭13連接於集油槽 ，^槽收集由承載平台m、靜壓平面轴承112之内表面與轴承 '卜表面之間關隙流出之流體，經由回油管丨4將流體回到 16 1345629 油箱401，再被泵浦加壓進入油路循環。 承載平台ίο内部結構的實施例如第s(b)圖所示，承載平台川 内部製有油孔連接外側的進油孔1〇7與内側的内油孔⑽；承載平台 10曰之内側設製油腔1G4、回油溝1G6，油腔1G4的形狀依加工製造的 考星不限制為矩幵/或其他任何指定的幵3狀也可以僅以内油孔⑽ 作為油腔之用，承载平台1G可以使用單—油腔、雙油腔四油腔或 更多的油腔，每-油腔均須有獨立的油孔連接至供油，兩承載平台 鲁的油腔數目相等，且待測液驗件的數目不大於油腔數目，但使用 的油腔數目愈多’油腔的最大壓力愈低，且因承載平台1G面積增大 造成不平衡時，而須增加油腔數目；側向靜壓平面轴承n及110也 在内。随有油孔18及内側製有油腔105，也可以使用單油腔或多油 腔或無油腔僅設以油孔，而且側向及正向油腔數可以任意的組合， 唯須使承載平台10與側向靜壓平面軸承u及11〇的組合在轴承座 上保持平衡，承載平台10使用的油腔數超過丨時，選擇部分或全部 % 油腔作為量測用，承载平台10或側向靜壓平面軸承11及110使用 多油腔時，每一油腔均須有獨立的節流器調節供油壓力，在流量分 配器20中，分配供油經獨立的節流器至每一個油腔。 本發明實施方式的之實體構造如第6圖所示，供應流體由供油 系統的泵浦40加壓後，自油箱401流出，首先通過粗濾器4〇及三 點組404，三點組包含有濾清器、調壓閥、油霧器與壓力表，具有過 濾、調壓與潤滑管路的功能；流路系統以止回閥4〇6防止流體逆流， 以/¾壓閥405設定最大額定壓力，並根據壓力表4〇8來控制流路系 統中流體的供油壓力A。供應流體接著通過蓄壓器4〇7，以穩定流 1345629 體的壓力，再以細濾器403細濾流體中的雜質後，經供油分配器4〇9 以穩定的壓力分配於兩個流路，其一流路經流量分配器20内毛細管 節流器或其他型式的節流器22調節流體之壓力後，以分開的流路供 往各獨立的側向靜壓平面軸承m、112，以作為承載平台側向定位 之用’另一流路之流體經過雙向作動之液壓組件3〇後，再分成兩個 流道通往各別對應之承載平台101及102的油腔，以壓力感測器 331 332、341、342及流量感測器321、322量測流體通過待測液壓 • 組件30之壓力差及流量’溫度感測器311、312、313、314分別量 測流體通過待測液壓組件3〇入口之流體溫度與出口之流體溫度。 當負載作用於承載平台101時，承載平台1〇1内之油腔形成壓 力，此壓力與供應壓力相比較，因液壓組件3〇内之流阻作用而產生 壓力降。由流量、壓力 '溫度感測器量測，隨承載平台上負载重量 之變化’量測系統供油壓力、流體通過待測液壓組件3〇之進口壓力、 出口壓力、流量及出入口之流體溫度，以訊號擷取卡將類比訊號轉 φ 成數位訊號，擷取並傳輸至電腦503，以數值程式計算待測液壓組件 節流係數及流阻。 信號處理系統分成硬體與軟體兩部分，硬體實施例如圖7所示， 以溫度感測器311-314、流量感測器321及322、壓力感測器331_334 得到的信號’經由信號接線盒5(U、排線502、資料擷取卡、至電腦 5〇3 ;軟體包含有人機操作介面及程式碼，人機介面包括操作晝面、 數值輸入及參數輸入設定操作、及計算結果顯示操作。 於所有的感測器輸出端各跨接一個電阻601-610，將輪出電壓轉 換為電腦503所能接受之電壓範圍後輸出，由於電阻6〇1·6ι〇在製 1345629 造生產時會產生誤差，使電壓量測前存在—偏壓誤差，所以必須於 量測前將感測器量測輸出的偏差記錄，歸零奴中輸人此偏差，於 量測時須將感測器所產生的偏差扣除。 感測器所量測得之電壓訊號，以排線5〇2傳輸至信號接線盒 5(H ’再連接至電腦503中之資料擷取卡，排線5〇2 _外界雜訊干 擾電壓訊號，傳輸排線502上之接線分別對應至電腦5〇3中資棚 取卡之各㈣通道。透過龍練卡，各感㈣之類比信號轉換為 數位信號，將訊號乘以校準常數，成為供油壓力、作用於待測液壓 組件30之感應元件23的工作壓力，以及分別通過液壓組件3〇兩條 流路之流料練。將壓力及流量代人式計算，得到通過待 測液壓組件3G之祕祕之流阻，流體減職溫度之變化已事先 7於電腦程式中’平均溫度為出σ溫與入口溫度之平均值，由電 知私式根據平均溫度計算兩流路之雜平触麟數，將流體黏度 係數代入流阻分母計算，得到兩條流路分別的節流係數。 又 1345629 【圖式簡單說明】 第1圖先前技術流量量測裝置及其製造方法之代表圖。 第2圖先前技術多功能壓力量測裝置之代表曰。 第3圖本發明實施方式之原理圖。 第4圖本發明實施方式之系統圖。 組合圖。 第5⑻圖本發明之承餅纽其側向靜壓平面軸承與轴承座 第5(b)圖承載平台及其側向靜壓平面軸承之構造圖。 第6圖本發明實施方式之實體構造圖。 第7圖本發明之信號量測及處理實施例說明圖。g^AP^AP^ γ2=_thQl ^2(ΔΡ2, ΔΡ12) The system of the embodiment of the present invention is shown in Fig. 4, which is provided by a spine pump and a flow path system, a sensor, a signal processing system, and two independent systems. The bearing platforms 1〇1 and ι〇2 are assembled with the lateral static pressure plane bearings ln and 112, and are placed on the bearing housing (2) = 12j. The bearing housing is located inside the oil collecting groove 13 to return the oil pipe. μ is connected to the fuel tank; the flow system includes pump 40, fuel tank, strainer 4〇2, fine-passer, three-point group 404, _valve 4〇5, check valve 4〇6, accumulator plate The pressure gauge tilt sensor includes temperature sensors 3n, 312, 313, 314, flow sensors 321 : 322 and pressure sensors 33 332, 341, 342. The embodiment of the present invention is as shown in Fig. 5 (8). The load bearing platform 10 and the two lateral static = planar bearings u and 11G are combined by screws in a shouting (10) configuration. The bearing seat 2 is seated on the bottom plate of the grooveless 14 Above, the remark 13 is connected to the oil collecting trough, and the trough collects the fluid flowing out from the bearing platform m, the inner surface of the hydrostatic plane bearing 112 and the bearing surface, and returns the fluid to the fluid through the oil return pipe 丨4. The oil tank 401 is pumped into the oil circuit to be circulated. Carrying platform ίο The internal structure is implemented as shown in the figure s(b). The bearing platform is internally formed with an oil inlet hole 1〇7 and an inner oil hole (10) on the outer side of the oil hole connection; Cavity 1G4, oil return groove 1G6, oil chamber 1G4 shape is not limited to the shape of the test star, or any other specified 幵3 shape, or only the inner oil hole (10) can be used as the oil chamber. The load platform 1G can be used. Use single-oil chamber, double oil chamber, four oil chambers or more oil chambers, each oil chamber must have independent oil holes connected to the oil supply, the number of oil chambers of the two bearing platform Lu is equal, and the liquid to be tested The number of pieces is not more than the number of oil chambers, but the more the number of oil chambers used, the lower the maximum pressure of the oil chamber, and the imbalance of the 1G area of the load bearing platform, the number of oil chambers must be increased; the lateral static pressure The plane bearings n and 110 are also included. With the oil hole 18 and the oil chamber 105 on the inner side, it is also possible to use a single oil chamber or a multi-oil chamber or an oil-free chamber with only oil holes, and the number of lateral and forward oil chambers can be arbitrarily combined, only The combination of the bearing platform 10 and the lateral static pressure plane bearings u and 11〇 is balanced on the bearing housing. When the number of oil chambers used by the bearing platform 10 exceeds 丨, part or all of the oil chamber is selected for measurement, and the bearing platform 10 is used. Or when the lateral hydrostatic plane bearings 11 and 110 use multiple oil chambers, each oil chamber must have a separate throttle to adjust the oil supply pressure. In the flow distributor 20, the oil is distributed through a separate throttle to Every oil chamber. The solid structure of the embodiment of the present invention is as shown in Fig. 6. After the supply fluid is pressurized by the pump 40 of the oil supply system, it flows out from the oil tank 401, first through the strainer 4〇 and the three-point group 404, and the three-point group includes There are filters, pressure regulating valves, oil misters and pressure gauges, which have the functions of filtering, regulating and lubricating the pipelines; the flow system uses the check valves 4〇6 to prevent the fluid from flowing backwards, and the /3⁄4 pressure valve 405 is set to the maximum. The pressure is rated and the supply pressure A of the fluid in the flow path system is controlled according to the pressure gauge 4〇8. The supply fluid then passes through the accumulator 4〇7 to stabilize the pressure of the flow body 1345629, and then finely filters the impurities in the fluid with the fine filter 403, and then distributes the two flow paths through the oil supply distributor 4〇9 with a stable pressure. The first-class road is adjusted by the capillary restrictor or other type of restrictor 22 in the flow distributor 20 to adjust the pressure of the fluid, and is supplied to the independent lateral hydrostatic plane bearings m, 112 by separate flow paths. The lateral displacement of the load bearing platform is carried out by the fluid flow of the other flow path through the two-way hydraulic component 3, and then divided into two flow passages to the oil chambers of the respective corresponding load-bearing platforms 101 and 102 to the pressure sensor 331 The 332, 341, 342 and flow sensors 321 and 322 measure the pressure of the fluid through the hydraulic component to be tested and the flow rate 'temperature sensors 311, 312, 313, 314 respectively measure the fluid passing through the hydraulic component to be tested 3 The fluid temperature at the inlet and the fluid temperature at the outlet. When the load acts on the load bearing platform 101, the oil chamber in the load bearing platform 1〇1 forms a pressure which, in comparison with the supply pressure, causes a pressure drop due to the flow resistance in the hydraulic assembly 3〇. Measured by flow rate, pressure 'temperature sensor, with the change of load weight on the load platform', measure the system oil supply pressure, the inlet pressure of the fluid passing through the hydraulic component to be tested, the outlet pressure, the flow rate and the fluid temperature of the inlet and outlet. The analog signal is converted into a digital signal by the signal capture card, captured and transmitted to the computer 503, and the throttle coefficient and flow resistance of the hydraulic component to be tested are calculated by a numerical formula. The signal processing system is divided into two parts: a hardware and a software. The hardware is implemented as shown in FIG. 7. The signals obtained by the temperature sensors 311-314, the flow sensors 321 and 322, and the pressure sensor 331_334 are transmitted via a signal junction box. 5 (U, cable 502, data capture card, to computer 5〇3; software includes man-machine interface and code, man-machine interface including operation panel, numerical input and parameter input setting operation, and calculation result display operation A resistor 601-610 is connected across all the sensor outputs, and the output voltage is converted to a voltage range acceptable to the computer 503. The output is generated when the resistor 6〇1·6ι〇 is manufactured in 1345629. The error is generated, so that there is a bias error before the voltage measurement. Therefore, the deviation of the sensor measurement output must be recorded before the measurement, and the deviation is input to the slave. In the measurement, the sensor must be used. The generated deviation is deducted. The voltage signal measured by the sensor is transmitted to the signal junction box 5 with the cable 5〇2 (H' is connected to the data capture card in the computer 503, and the cable is 5〇2 _ outside Noise interference voltage signal, transmission cable 502 The wirings correspond to the (4) channels of the computer's 5 〇3 sheds. Through the dragon card, the analog signals of each sense (4) are converted into digital signals, and the signals are multiplied by the calibration constants to become the oil supply pressure. The working pressure of the sensing element 23 of the hydraulic component 30 is measured, and the flow of the two flow paths is respectively measured by the hydraulic component 3. The pressure and the flow rate are calculated on a human basis to obtain the flow resistance of the hydraulic component 3G to be tested. The change of the fluid demotion temperature has been previously 7 in the computer program. 'The average temperature is the average value of the σ temperature and the inlet temperature. The average temperature is calculated according to the average temperature. The fluid viscosity is calculated. The coefficient is substituted into the flow resistance denominator to obtain the throttling coefficient of the two flow paths. 1345629 [Simple description of the drawing] Fig. 1 Representative diagram of the prior art flow measuring device and its manufacturing method. 3 is a schematic diagram of an embodiment of the present invention. Fig. 4 is a system diagram of an embodiment of the present invention. Combination diagram. Fig. 5(8) is a side view of the present invention. FIG. 6 is a structural diagram of a load bearing platform and a lateral static pressure plane bearing thereof. FIG. 6 is a structural view of an embodiment of the present invention. FIG. 7 is a diagram showing a signal measurement and processing embodiment of the present invention. Illustrating.
20 1345629 【主要組件符號說明】 承載平台 10 ' 101 ' 102 油腔 104 、 105 回油溝 106 進油孔 107 内油孑L 18、108 側向靜壓平面軸承 11 > 110 ' 111 ' 112 軸承座 12、m、 122 集油槽 13 回油管 14 重量塊 151 ' 152 流量分配器 20'21 節流器 22 入口流路 211 ' 212 感應元件 23 内部流路 231 ' 232 出口流路 241 ' 242 油腔 251 > 252 液壓組件 30 溫度感測器 311 ' 312 ' 313 流量感測器 321 ' 322 壓力感測器 331 ' 332'333 系浦 40 油箱 401 細濾器 403 三點組 404 洩壓閥 405 止回閥 406 蓄壓器 407 壓力表 408 供油分配器 409 "is戒接線盒 501 排線 502 電腦 503 電阻 601-610 314 33420 1345629 [Description of main component symbols] Load bearing platform 10 ' 101 ' 102 Oil chamber 104 , 105 Oil return groove 106 Oil inlet hole 107 Internal oil 孑 L 18, 108 Lateral static pressure plane bearing 11 > 110 ' 111 ' 112 Bearing Seat 12, m, 122 Oil sump 13 Oil return pipe 14 Weight 151 ' 152 Flow distributor 20'21 Tractor 22 Inlet flow path 211 ' 212 Inductive element 23 Internal flow path 231 ' 232 Outlet flow path 241 ' 242 Oil chamber 251 > 252 Hydraulic Assembly 30 Temperature Sensor 311 ' 312 ' 313 Flow Sensor 321 ' 322 Pressure Sensor 331 ' 332' 333 Department 40 Fuel Tank 401 Fine Filter 403 Three Point Group 404 Pressure Relief Valve 405 Valve 406 Accumulator 407 Pressure gauge 408 Oil distributor 409 "is junction box 501 Cable 502 Computer 503 Resistance 601-610 314 334