Application of SolidWorks & AMESim based Updated Simulation Technique to Back-flow Analysis of Trochoid Hydraulic Pump for Lubrication

Transcription

1 Application of SolidWorks & AMESim based Updated Simulation Technique to Back-flow Analysis of Trochoid Hydraulic Pump for Lubrication Seung Won Jeong #, Won Jee Chung #, Man Su Kim #, Myung Sik Kim* # School of Mechatronics, Changwon National University, South Korea 1 dongnegosu@gmail.com 2 wjchung@changwon.ac.kr 3 subek@naver.com * Flutek, 6 Gongdan-ro 98beon-gil, Seongsan-gu, Changwon-si, Gyeongsangnam-do, South Kore 4 mskim@flutek.co.kr Abstract In this paper, we deal with the Gerotor pump which will be referred to as trochoid pump, hereinafter since it has been widely used for the transmission part of a automobile. Usually, the simulation of trochoid pump has utilized a professional analysis program or language such as CFD (specifically CFX ) or C-code (e.g. C++) which is not an easy tool for a field engineer. But the field engineer based on his experience has a hurdle in modifying the flow model according to the need of a customer. To cope with this problem, in the paper of Kim et al. [3] in WORLDCOMP 2012 (CSC 2012), we have presented how to establish the flow model of a trochoid pump by using the most popular 3- dimensional (or 3D) modeling tool SolidWorks and a hydraulic analysis program AMESim. For this model, we have figured out the clearance problem which was neglected in the paper of Kim et al. [3]. In this paper, we will update Kim s flow model in order to solve the clearance problem by incorporating Jang s formulation [4] into the SolidWorks model. The practical excellence of updated simulation technique proposed in this paper will be verified to be compared with experimental results. Keywords lubrication pump, trochoid pump, clearance, simulation technique, viscosity of hydraulic fluid, experimentation I. INTRODUCTION As for the environmental issues of transportation equipment, research and development has been recently focused on high fuel efficiency. The control of the engine (or transmission) of vehicle, as a method for sustaining high fuel efficiency during the stable running of a vehicle, is required. In order to maintain normal performance and durability of the engine (or transmission), a lubrication device for preventing internal friction which can result in overheating is necessary. Usually the output power of engine is used to the lubrication device in the range of about 25-30%. Nowadays a (fixed displacement) internal gear pump using the modified curve of sphere gear is used for a lubrication device in the viewpoint of market. The internal gear pump can be divided into two kinds, i.e., Gerotor pump and Partition pump. In this paper, we deal with the Gerotor pump which will be referred to as trochoid pump, hereinafter since it has been widely used for the transmission part of a automobile. The terminology of trochoid is derived from a trochoidal tooth profile as shown in Fig.3. A sample of a trochoid pump is shown in Fig.1, which can be used for the transmission of a commercial vehicle. Fig. 1 Trochoid Pump The trochoid pump is composed of outer rotor and inner rotor as shown in Fig. 2. This means that it has simple structure. Owing to the development of sintering technology, any profile of rotor can be manufactured and then can be easily assembled. Especially the relative motion between outer and inner rotors is small for a trochoid pump. Pump efficiency can be maintained for long operation. These points explain the wide use of trochoid pump as a hydraulic source for the lubrication of transmission or engine. In previous papers including Yang et al. [1] and Nam et al. [2], the simulation of trochoid pump has utilized a professional analysis program or language such as CFD (specifically CFX ) or C-code (e.g. C++) which is not an easy tool for a field engineer. This software tool can realize mesh and then make a flow model. But the field engineer

2 based on his experience has a hurdle in modifying the flow model according to the need of a customer. To cope with this problem, in the paper of Kim et al. [3] in WORLDCOMP 2012 (CSC 2012), we have presented how to establish the flow model of a trochoid pump by using the most popular 3- dimensional (or 3D) modeling tool SolidWorks and a hydraulic analysis program AMESim. For this model, we have figured out the clearance problem which was neglected in ref. [3], so as to be explained in detail in Section 2. In this paper, we have updated Kim s flow model in order to solve the clearance problem by incorporating Jang s formulation [4] into the SolidWorks model. The practical excellence of updated simulation technique proposed in this paper will be verified to be compared with experimental results. II. THEORETICAL DESIGN OF TROCHOID PUMP [4] In Kim et al. [3], the clearance (specifically the distance between inner rotor and outer rotor as depicted in Fig. 2) can be turned out to '0 ', which can be accepted in theoretical sense. But, in practical sense, the rotation between inner rotor and outer rotor cannot occur because there is no hydraulic fluid in the clearance and thereby the rotors get jammed between each other. Thus we have utilized Jang s theory [4] to treat with this clearance problem. Figure 2 shows a schematic diagram of the trochoid pump mainly used, where this pump is composed of the outer rotor and inner rotor. The outer rotor is designed from a trochoid shape of the tooth of inner rotor and thereby can have an arc/oval/sinusoidal shape. Specifically the inner rotor is drawn by using an arc with almost the same radius. Moreover the number of robes for the outer rotor is one more than the that of inner rotor. A coaxial drive is used by inserting the shaft of the pump into the center of inner rotor. Thus the trochoid pump has the constant eccentric distance of e between the inner rotor and the outer rotor, which can result in pumping by changing the intaking volume of hydraulic fluid as shown in Fig. 2. Fig. 3 Profile of trochoid curve Defining N by Eq. (1), (1) then the basic trochoid curve in [4] can be given by Eqs. (2) and (3) : (2) (3) where is the rotation angle of rolling circle and the rotation angle of basic circle, resulting in the following relationship: (4) Defining K as (5) then we have the final (modified) trochoid trajectory (X, Y) by Eq. (6) : Fig. 2 drawing of inner and outer rotor Basically we have exploited the design formulation of trochoid profile proposed by Jang et al. [4]. Referring to Fig. 3, R r is the radius of rolling circle, while R c is the radius of the basic circle. R z denotes the radius of idle circle for a trochoid curve. (6)

3 Unfortunately, Kim et al. [3] has based on only Eq. (6), which cannot treat with the actual problem of clearance 0. Specifically, clearance 0 means that there is no hydraulic fluid in the clearance and thereby both the inner and outer rotors get jammed. In the meanwhile, to cope with clearance 0 problem in this paper, we have used the eccentricity denoted by e as follows: where R Inouter and R InInner are defined in Fig. 2, respectively. Then R z can be determined by Eq. (8) : where R r is usually given by a design engineer. Figure 3 means that field engineers who are familiar with SolidWorks can draw easily the trochoid model by using SolidWorks based on Eqs. (6) and (8) not by virtue of C- code which is difficult for the engineers. Specifically, using the motion analysis module of SolidWorks, the rolling circle can be rotated based on the basic circle in order to generate trochoid curve as shown in Fig. 3. Only the basic condition, R r > e, should be satisfied. Next, when the circle of trace of wheel is made to be rotated according to the trochoid curve through the motion analysis module of SolidWorks, the shape of inner rotor can be designed as shown in Fig. 4. Finally the pump configuration which is designed by using a trochoid tooth profile is shown in Fig. 5. (7) (8) III. FLOW FIELD AREA MODELLING [3] USING SOLIDWORKS The flow field area modeling technique using SolidWorks is almost similar to that of Kim et al. [3]. In this section we will briefly explain this technique. As shown in Eq. (10), the dispensing flow rate Q pump of the positive displacement pump can be obtained by using the change of flow volume displ per w pump one rotation and the rotational angular speed. Especially displ can be expressed by Eq. (11) because the thickness H of trochoid pump is constant. In Eq. (11), Area denotes the cross-sectional area of flow rate while q indicates rotation angle. Now we need the data of area change darea according to rotation angle, i.e. dq by using SolidWorks as a CAD (Computer Aided Design) tool. Then, how to obtain the flow rate of the trochoid pump is as follows. Q pump = (10) displ w pump dv darea displ = = H dq dq 3 é m ù ê ú ërad û (11) The data of area change ( darea ) can be obtained by using angular velocity ratio of trochoid pump. It can be performed by changing the area through the rotation of each rotor according to the rotation ratio of inner and outer rotors. The speed ratio can be determined by Eq. (12) according to the number of outer rotor lobes (or teeth) (N lobe ): (12) w where out ( w in ) (inner) rotor. denotes the angular velocity of outer Fig. 4 Generation of Inner Rotor Shape Fig. 5 Designed trochoid pump When the drawings of the inner and outer rotors are completed, flow field area modeling can be done through the element conversion technique of SolidWorks as shown in Fig. 6 where inlet and outlet are simplified. In specific, the sketch of 3 parts, i.e., inner rotor, outer rotor and inlet/outlet, are first designated as BLOCKs by using BLOCK technique of SolidWorks. Then the flow field area (to be explained later) can be modeled by performing the PROTRUSION BASE (similar to PAD technique of Solidworks ) technique of SolidWorks. Consequently 7 models of flow field area are designated as shown in Fig. 6. Now, the area change of one flow field should be investigated according to Eq. (12) (in other words, according to the rotation of inner rotor BLOCK). Specifically, while making inlet and outlet BLOCK fixed, the outer rotor BLOCK is rotated based on Eq. (12) as the inner rotor BLOCK is rotated, by using FORMULA EDIT technique of SolidWorks. In every rotation, the area of one flow field can be changed in

4 shape according to the rotation angle of inner rotor as shown in Fig. 7. Thus the area change of one flow field between inlet and outlet can be depicted as a graph of Fig. 8 which will be used later for the simulation of trochoid pump using AMESim. In a similar manner to Fig. 8, the area change of outlet and inlet flow field can be also obtained as shown in Fig. 9. IV INTERNAL FLOW ANALYSIS The objective of hydraulic circuit modeling for trochoid pump using AMESim is to realize flow and then simulate backflow so as to control the flow rate control of trochoid pump. In case of hydraulic circuit modeling of only one flow field for trochoid pump, the area change data of Fig. 8 and the thickness of rotor can be made equivalent with an 1- dimensional piston model as shown in Fig. 10. Fig. 6 Flow field modeling using SolidWorks Fig dimensional piston model of one flow field using AMESim Fig. 7 Area change of one flow field according to rotation angle of inner rotor (shape) Fig. 8 Area change of one flow field according to rotation angle of inner rotor Fig. 9 Area change of outlet and inlet flow field Hydraulic circuit modeling of trochoid pump is required to show the volume generated at the location of each particular angle when the inner rotor comes in contact with the outer rotor. This can be carried out at the location of each phase change, i.e., 360 /N lobe. Finally N lobe models are generated similarly as Fig.10 and connected each other as shown in Fig. 11. The factors that can be simply controlled in real time through the formation of the AMESim hydraulic circuit of a trochoid pump include: the rotation speed of pump, the shape angle of inlet and outlet, gap between outer rotor and pump casing, and gap between inner rotor and outer rotor. In backflow simulation, these control factors are important for the flow rate control of trochoid pump. Especially, from the viewpoint of a field engineer, AMESim is more uselful for this back-flow simulation, compared with a traditional analysis software of fluid mechanics, i.e., CFD, because CFD needs the renewal of mesh modeling every time each control factor has a different value while AMESim needs only the input values of control factors without any change of hydraulic circuit modeling. In some cases, cavitation occurs at low velocity resulting from decreasing suction force due to the characteristics of lubricating hydraulic fluid, not high-velocity revolution. However, as the difference at low velocity is negligible, the present study compares a simulation-based method with an actual operation case to do research needed in the field. This paper is intended to reduce the budget for experimentation as well as trial and error via the simulation-based estimation, provided the confidence level of the case compared falls within the error range. The simulation for the outlet part shows the hydraulic variation from the inside of the stabilized domain excluding the transitional condition at the time of initial response as in Fig. 12.

5 Fig. 11 Connected N lobe hydraulic circuit modeling of trochoid pump using AMESim pressure falls below 0 due to the momentary pressure drop upon the fluid going out. This moment is considered a backflow, implying the loss of flow. In Fig. 13, compared with that of Kim et al. [3], the back-flow is more observable, where the pressure rises due to the hydraulic fluid stuck in the rotor slots and it sharply drops upon the hydraulic fluid moving out. Normally, the following two approaches have been used to reduce the back-flow by decreasing the pulsation in existing pumps. The first approach is to apply a notch to the rotor, causing a little leakage to occur in advance in a closed space, to lessen the sharp increase in pressure and reduce the backflow. The second approach is to decrease the flow loss by varying the discharge angles of the hydraulic fluid touching the pump cover where the rotor meets the outlet housing. For the notch-related approach, it has been proved that it is hard to take a formulaic approach to the area representing the notch part. Moreover, it is hard to apply a notch to an actual trochoid pump, which has no room for a notch. As this approach is not consistent with the objective of seeking a method for enabling field engineers to access with ease, the second approach is used for the present study. With the second approach, to reduce the flow loss, the angle of the hydraulic fluid discharged from the rotor to the pump cover has been varied by 1 from 0, i. e., 1, 2, 3, 4 and 5. As shown in Fig. 14, the back-flow effect is smallest at 4. The variation of the discharge angle where the pump cover comes into contact with the hydraulic fluid lessens the backflow, and thus effectively decreases the overall leakage between the inner and outer rotors. This simulation-based reduction of the flow loss is applied to the pump design and then verified with experimentation. Fig. 12 Hydraulic pressure change at the outlet Fig. 14 Flow rate according to discharging angle of outlet Fig. 13 Flow loss occurred at back-flow As in Fig. 13, upon the rotor rotating, the pressure surges right before the lubricating fluid moves out. Then, the fluid The effects of varying viscosity of hydraulic fluid on efficiency in overall flow is also analyzed with AMESim for the hydraulic circuit model of Fig. 11. In general, SAE (Society of Automative Engineers)-defined 80W~90W (W denotes the unit of viscosity at -35 C) lubricating fluid is used as the hydraulic fluid for the trochoid pump. Another normal hydraulic fluid, ISO (International Organization Standardization) VG32 46 is also used, which is more of a gear hydraulic fluid with high viscosity than a lubricating hydraulic fluid. The hydraulic fluid with high viscosity can be used at a high temperature, e.g. 80~90 C maximum, whereas

6 the lubricating hydraulic fluid for the trochoid pump can be used only at 60C and below. Yet, there is no need to use the gear hydraulic fluid with high viscosity as lubrication is the main function of the hydraulic fluid. Figure 15 shows the simulation result of pressure according to the varying viscosity of the lubricating hydraulic fluid. Figure 16 represents the varying outlet flow in line with the outlet pressure as the viscosity changes. It is possible to infer from the graphs the internal flow loss according to the viscosity effect. Figure 15 shows the varying pressure over time with the viscosity of hydraulic fluid being 20cP (centi Poise) above (see Fig. 15-(a)) and 5cP below (see Fig. 15-(b)) the reference level of 10cP. No difference in the variation of pressure is found in line with the difference in viscosity in Fig. 15. But in Fig.16-(a) the higher the viscosity, the bigger the difference in flow, leading to loss. In Fig. 16-(b), the lower the viscosity, the less the difference in flow loss below 10cP. Yet, according to Won s et al. [7], it would be better not to use a lubricating hydraulic fluid with viscosity below 30cP considering rust protection and performance of the hydraulic fluid. An experimentation is conducted in collaboration with Yongdong Tech, Ltd. in Korea, in order to find out how the optimal effects found in the simulation work in an actual pump in comparison with existing pumps. Figures 17 and 18 show the actual experimental testing set-up and the separate parts after the experimental testing, respectively, so as to check any breakage and leakage from inner and outer rotors. Especially the checking list designated by KIMM (Korea Institute of Machinery and Materials, a governmental research institute in Korea) are tested in the experiment, which lasts for a total of 1,500 hours at 1500RPM and 55~60C. Table 1 compares the actual measurements of varying flows between the reference pump and the one whose outlet structure is modified via simulation and thereby manufactured. The flow in the closed section inside the pump and that in the open path connected to the tank are marked. The measurements for the open flow path are marked in brackets. As for the varied angles at the outlet, efficiency changes over time. That is, the longer the duration of use, the higher the benefits. The flow increases by a small margin, which is negligible. (a) (b) Fig. 15 Graph of outlet pressure according to viscosity Fig. 17 Experimental testing set-up (a) (b) Fig. 16 Graph of outlet flow according to outlet pressure V EXPERIMENTATION Fig. 18 Separate parts after the experiment

7 Effcie ncy 85% 91% Pass Table 1 Experimental values of different progression Accumulated Flow rate(cc) Efficiency (%) Noise (db) time Before After Change difference Comparison (22.4) (22.6) (25.8) (22.7) (22.6) (22.9) (20.0) (19.9) (20.1) (20.0) (19.9) (20.1) (19.9) (19.8) (19.6) (19.8) (20.0) (19.9) (19.1) (19.5) (19.2) (19.5) (18.7) (19) (18.7) (18.7) (18.6) (18.6) (18.6) (18.5) (18.6) 23.7 (18.5) Table 2 compares the result of 1500-hour experiment of the prototype trochoid pump with the pump acceptance criteria of KIMM. Overall, the flow efficiency of the trochoid pump decreases over time. Still, its efficiency is 6% higher than the criteria. Also, noise is lower than the criteria by 6dB, which indicates the stability of the design. Item Flow rate Table 2 Evaluation results of experimental testing Acceptance Criteria Testing Data of Yongdong Tech Pass/Unpass (cc) 23.7(cc) Pass Noise 85dB 79dB Pass VI CONCLUSIONS This paper provides a methodology for extracting the design data throughout a design software SolidWorks, based on the existing trochoid pump design equations which are used by hydraulic field engineers. In the paper of Kim et al. [3] in WORLDCOMP 2012 (CSC 2012), we have presented how to establish the flow model of a trochoid pump by using the most popular 3-dimensional modeling tool SolidWorks and a hydraulic analysis program AMESim. For this model, we have figured out the clearance problem which was neglected in ref. [3]. In this paper, we have updated Kim s flow model in order to solve the clearance problem by incorporating Jang s formulation [4] into the SolidWorks model. Through simulation results, this paper propose how to reduce the flow loss based according to the angle adjustment of the outlet of the trochoid pump. This proposal has been verified by using actual experimental results, which confirms that the design through the adjustment of outlet angle can increase flow rate. Hence this paper can be contributed to the prototyping of a trochoid pump by reducing the cost that can result from a trial-and-error design. VII ACKNOWLEDGEMENT This research is financially supported by Changwon National University in 2013 ~ VIII REFERENCE [1] S. Y. Yang, S. J. Cha, Simulation of Gavitating Flow in a Gerotor Oil Pump, Journal of Flud Machinery, The Korean Society of Automotive Engineers, Autumn Conference, pp. 152 ~ 158, [2] K. W. Nam, S. H. Jo and J. I. Park, Numerical simulation in the engine lubricating gerotor oil pump, The Korea Society of Mechanical Engineers, Vol. 30, pp ~ 1025, 2006 [3] M. S, Kim, W. J. Chung, S. W. Jeong, and J. Y. Jeon, Methodology for simulation of trochoid pump, Journal of the KSMTE, Vol. 22, No. 3, pp. 465~471, 2013 [4] J. S. Jang, J. W. Lee, D. C. Han, and M. R. Jo, A Study on Tooth Design Program Development of Gerotor Pump/Motor, Journal of KSTLE, Vol. 12, No. 3, pp. 100~106, [5] B. J. Kim, S. H. Seung, and S. H. Yoon, Flow Analysis and Port optimization of Gerotor Pump Using Commercial CFD Code, Journal of KSME, Vol. 60, No. 11, pp. 709~714, C. S. Won, N. G. Hur, and S. H. Kwon, Flow Analysis of Automotive Oil Pump of Gerotor Type, Journal of KSFM, Vol. 6, No. 4, pp. 7~13, 2003.