Multi-shaft driving apparatus and fluid rotary apparatus

Abstract: A multi-shaft driving apparatus includes a plurality of motors each for rotating one of a plurality of shafts to be synchronously rotated, an encoder, provided for each motor, for detecting a rotational state of the shafts, a pulse generator for generating a pulse signal for rotating the shafts, and a motor control circuit, provided for each motor, for inputting the pulse signal for rotating the shafts and a pulse signal detected by the encoder and used as a feedback signal. The motor control circuit has a PLL control section and a rotational angle phasing section so that a rotational angle phasing control loop is generated to perform a rotational angle phasing operation by the rotational angle phasing section so to as place the shafts in position at a driving start and after performing the rotational angle phasing operation, a rising and steady control loop is generated to perform an operation from a rise state to a steady state by the PLL control section. A fluid rotary apparatus includes a plurality of rotors accommodated in a housing, a plurality of shafts each for rotating one of the rotors to be synchronously rotated, and a fluid sucking opening formed in the housing and a fluid discharge opening formed therein, in addition to the structure of the multi-shaft driving apparatus so that the volume change of a closed space formed by the rotors or by the rotors and the housing is utilized to suck and discharge fluid.

Description: BACKGROUND OF THE INVENTION The present invention relates to a fluid rotary apparatus. Conventionally, equipments are provided with the multi-shaft driving apparatus for driving a plurality of shafts synchronously by a plurality of motors. In order for the multi-shaft driving apparatus to rotate a plurality of shafts synchronously with a high accuracy, it is proposed that an encoder, a pulse generator and a motor control circuit are provided for each motor. The encoder detects the rotational state of the shafts. The pulse generator generates pulse signals for rotating the shafts. The motor control circuit, having a PLL control section, inputs the pulse signals outputted from the pulse generator and pulse signals fed back by the encoder as a result of the detection of the rotational state of the shafts. In the above construction, a PLL control loop which passes through the PLL control section is formed. According to the above multi-shaft driving apparatus, the shafts are driven synchronously in a steady state by the PLL control section, but they do not rotate synchronously in transient states such as rise time and fall time in the rotations of the shafts because any control such as PLL control is not performed. Vacuum technology is used in a very wide range from a technological field closely relating to daily life to a high technological field. Thus, vacuum technology is indispensable for technological progress. Recently, an oil-free dry pump which forms a clean vacuum has become noteworthy in view of the progress of semiconductor industry. The dry pump includes screw type, scroll type and claw type. A positive-displacement vacuum pump is normally used in a low vacuum degree ranging from the atmospheric pressure to 1,3332 - 0,13332 Pa (10 -2 - 10 -3 torr). The positive-displacement vacuum pump comprises a plurality of rotors accommodated in a housing; a plurality of driving shafts which rotates the rotors synchronously; and a fluid suction opening and a fluid discharge opening formed in the housing. Utilizing the volume change of a space formed by the rotors or by the housing and the rotors, the drive pump sucks and discharges fluid. In order to make the pump oil-free, the conventional pump comprises a timing gear for rotating a motor shaft for driving a plurality of rotors and the rotors synchronously; an oil chamber provided in a space accommodating a bearing; and a mechanical seal provided between the oil chamber and a space (suction chamber) formed by the rotors and the housing so as to prevent oil from penetrating into the space. However, according to the conventional pump of the above construction, it is necessary to periodically replace oil and the mechanical seal and in addition, it is difficult to prevent the leakage of oil from the oil chamber. The inventors of the present invention have already proposed a fluid rotary apparatus (oil-free vacuum pump) comprising two rotors synchronously rotated without contacting each other by the above-described multi-shaft synchronous control. However, the proposal does not describe the method for synchronously rotating the rotors in starting and stopping the vacuum pump. From EP-A-0 382 029 a multi-spindle synchronous drive unit for synchronously driving a plurality of spindles is known which includes a plurality of motors for driving the spindles, respectively, a plurality of encoders for detecting rotational positions of the motors, respectively, which are, respectively, attached to the motors, a plurality of PLL control means for controlling drive of the motors, respectively, which receive, as feedback signals, detection signals of the encoders, respectively, a reference pulse oscillator for outputting a pulse signal and a plurality of multipliers which multiply into speed command pulse signals, the pulse signal by multiplication factors corresponding to rotational speed ratios of the spindles, respectively, so as to input the speed command pulse signals to the PLL control means, respectively. The use of this device with regard to a fluid rotary device is not disclosed in this application. Furthermore, a device for driving two machines synchronously with a predetermined phase angle is known from the German laid open document 21 63 474. In order to achieve this, a first operation phase during which the phase angles of each machine are measured and controlled is implemented. When the predetermined phase angle difference is obtained, the machines are driven synchronously by a common reference pulse. SUMMARY OF THE INVENTION Accordingly, an essential object of the present invention is to provide a fluid rotary apparatus capable of rotating a plurality of rotors synchronously without the rotors contacting each other in the start, steady state, and stop of the apparatus. In accomplishing these and other objects, according to the present invention, there is provided a fluid rotary apparatus comprising a plurality of rotors accommodated in a housing, a plurality of shafts each for rotating one of the rotors to be synchronously rotated, a plurality of motors each for rotating one of a plurality of the shafts to be synchronously rotated, an encoder provided for each motor for detecting the rotational state of the shafts, a pulse generator for generating a pulse signal for rotating the shafts, and a motor control circuit, provided for each motor for inputting a pulse signal detected by the encoder and used as a feedback signal to control the synchronization of the shafts wherein the motor control circuit has at least one PLL controller for performing a PLL control operation at a steady state after a rise time and before a fall time. There is further provided a fluid drawing opening and a fluid discharge opening which are formed in the housing wherein the volume change of a space formed by the rotors and the housing is utilized to draw and discharge fluid and wherein the pulse signals from the pulse generator are inputted in the motor control circuit. A preferred embodiment is contained in subclaim 2. According to the above-described construction, the fluid rotary apparatus may be applied to a positive-displacement vacuum pump. The pump does not require the provision.of a mechanical sliding portion which allows the shafts to be rotated synchronously both in the transient state (rise time and fall time) and in the steady state. That is, the pump does not require the supply of lubricating oil. Therefore, the pump is clean and the shafts rotate at a high speed, and in addition, the apparatus is durable. BRIEF DESCRIPTION OF THE DRAWINGS These and other objects and features of the present invention will become clear from the following description taken in conjunction with the preferred embodiments thereof with reference to the accompanying drawings, in which: Fig. 1 is a block diagram showing a multi-shaft driving apparatus according to an embodiment of the present invention; Fig. 2 is a sectional view showing a positive-displacement vacuum pump applied to a fluid rotary apparatus according to the present invention; Fig. 3 is a front view, showing a positive-displacement vacuum pump applied to a fluid rotary apparatus, in which a housing is broken away; Fig. 4 is a graph showing the number of rotations of shafts of the multi-shaft driving apparatus of Fig. 1 with respect to the elapse of drive time of the multi-shaft driving apparatus; and Fig. 5 is explanatory view showing a part of a screw of the positive-displacement vacuum pump of Fig. 2. DETAILED DESCRIPTION OF THE INVENTION Before the description of the present invention proceeds, it is to be noted that like parts are designated by like reference numerals throughout the accompanying drawings. An embodiment as defined in claim 1 of the present invention will be described below with reference to Figs. 1 and 4. Fig. 1 is a block diagram showing the construction of a multi-shaft driving apparatus according to the embodiment. The apparatus comprises motors M1 and M2 each for driving shafts 1 and 2 to be synchronously rotated; motor control circuits 3 and 4 for controlling the motors M1 and M2, respectively; incremental encoders 5 and 6 and absolute encoders 7 and 8, for detecting the rotational state of the shafts 1 and 2, namely, rotational position thereof and rotational speed thereof; a pulse generator 9, positioned in a front stage of the motor control circuits 3 and 4, for generating pulse signals for rotating the shafts 1 and 2; and a CPU control circuit 10 for outputting control signals to the motor control circuits 3 and 4 and to the pulse generator 9. The motor control circuits 3 comprises a first PLL control circuit 31; a second PLL control circuit 32; a rotational angle phasing circuit 33; a driver section 34 consisting of a current amplifier; and a pulse extracting section 35. The motor control circuits 4 comprises a first PLL control circuit 41; a second PLL control circuit 42; a rotational angle phasing circuit 43; a driver section 44 consisting of a current amplifier; and a pulse extracting section 45. The "PLL control" means a phase-locked loop control. Pulse signals, generated by the pulse generator 9, for rotating the shafts 1 and 2 and pulse signals detected by the incremental encoders 5 and 6 serving as feedback signals are inputted to the first and second PLL control circuits 31, 32, 41, and 42 and the rotational angle phasing sections 33 and 43 via the pulse extracting sections 35 and 45. The following three control loops (1), (2), and (3) are generated. First PLL control loop (1) passes through the first PLL control circuits 31 and 41. Second PLL control loop (2) passes through the second PLL control circuits 32 and 42. Rotational angle phasing control loop (3) passes through the rotational angle phasing sections 33 and 43. Upon receipt of the output of the CPU control section 10, contacts of switching sections 36 and 46 are changed as follows to select a first state, a second state or a third state. When contacts 36a and 46a are connected with the CPU control section 10, the first state in which only the first PLL control loop (1) is generated is selected. When contacts 36b and 46b are connected therewith, the second state in which the second PLL control loop (2) and the rotational angle phasing control loop (3) are generated is selected. When contacts 36c and 46c are connected therewith, the third state in which only the rotational angle phasing control loop (3) is generated is selected. The PLL control circuits 31, 32, 41, and 42 detect the phase difference between the pulse signal, for rotating the shafts 1 and 2, outputted from the pulse generator 9 and the pulse signal detected by the incremental encoders 5 and 6 so that the frequency of both signals and the phase thereof are coincident with each other. The signal indicating the detected phase difference is used as a feedback control. For example, both pulse signals are inputted to the PLL control circuits 31, 32, 41, and 42 and a phase compensation is made by detecting the phase difference between both pulse signals by a phase comparator and by passing a signal indicating the phase difference through a low-pass filter. Since this method is known, the description thereof is omitted. Upon receipt of an instruction of the CPU control section 10, the pulse extracting sections 35 and 45 extract the instructed number of pulses from pulse signals, for rotating the shafts 1 and 2, outputted from the pulse generator 9. The signal outputted from the absolute encoders 7 and 8 are converted into a signal indicating the rotational position of the shafts 1 and 2 by counters 12 and 13, and then the converted signal is inputted to the CPU control section 10. The operation of the apparatus of the above construction is described below. Rise time 1 (Period of (I) of Fig. 4) First, the phase difference between the rotational angle of the shafts 1 and 2 is adjusted to a predetermined phase difference. In the motor control circuits 3 and 4, the state in which only the rotational angle phasing control loop (3) is generated is selected, i.e., the contacts 36c and 46c are selected. The CPU control section 10 issues to the pulse generator 9 an instruction of generating pulse signals, for rotating the shafts 1 and 2, of a low frequency. In addition, based on the signal indicating the rotational position detected by the absolute encoders 7 and 8, the CPU control section 10 controls the pulse extracting sections 35 and 45 so that the pulse generator 9 outputs a necessary number of pulses to the motor control circuits 3 and 4. Thus, the phase difference between the rotational angle of the shafts 1 and 2 is adjusted to the predetermined phase difference. Rise time 2 (Period of (II) of Fig. 4) The number of rotations of the shafts 1 and 2 is increased to that of the steady state with the phase difference between the rotational angle of the shafts 1 and 2 kept at the predetermined phase difference. In the motor control circuits 3 and 4, the state in which the second PLL control loop (2) and the rotational angle phasing control loop (3) are generated in parallel is selected, i.e., the contacts 36b and 46b are selected. The frequency of the pulse signal, for rotating the shafts 1 and 2, outputted from the pulse generator 9 is gradually increased. The second PLL control loop (2) does not have a fast response to a great fluctuation of the frequency of the pulse signal and consequently, the second PLL control loop (2) alone is incapable of keeping the initially set phase difference between the rotational angle of the shafts 1 and 2. The rotational angle phasing control loop (3) has the following function. That is, the rotational angle phasing sections 33 and 43 having a deviation counter, respectively monitor the output of the incremental encoders 5 and 6 and instantly correct the deviation of the phase difference between the rotational angle of the shafts 1 and 2, thus accurately following the rise of the frequency of the pulse signal. That is, the rotational angle phasing control loop (3) performs the speed control of f/V conversion system. Thus, in cooperation of the second PLL control loop (2) and the rotational angle phasing control loop (3), the shafts 1 and 2 can be synchronously rotated with a high accuracy even in the transient state. Steady drive (Period of (III) of Fig. 4) When the number of rotations of the shafts 1 and 2 has become the number of the steady state, in the motor control circuits 3 and 4, the state in which only the first PLL control loop (1) is generated is selected, i.e., the contacts 36a and 46a are selected. In the steady state, the frequency of the pulse signal for rotating the shafts 1 and 2 is almost constant. Therefore, even though the rotational angle phasing control loop (3) does not function, the phase difference between the rotational angle of the shafts 1 and 2 is kept at the predetermined phase difference. Another reason the rotational angle phasing control loop (3) is not allowed to operate in the steady state is as follows: In the steady state, an optimum control may be made by slightly varying the predetermined phase difference between the rotational angle of the shafts 1 and 2. To this end, the pulse extracting sections 35 and 45 extract a necessary number of pulses from the pulse signal for rotating the shafts 1 and 2. But if the rotational angle phasing control loop (3) functions, the varied phase difference returns to the predetermined phase difference. That is, the predetermined phase difference cannot be varied. Fall time (Period of (IV) of Fig. 4) When the operation is to be stopped, the rotations of the shafts 1 and 2 are stopped with the phase difference between the rotational angle of the shafts 1 and 2 kept at the predetermined phase difference. In the motor control circuits 3 and 4, the state in which the second PLL control loop (2) and the rotational angle phasing control loop (3) are generated in parallel is selected, i.e., the contacts 36b and 46b are selected. The frequency of the pulse signal for rotating the shafts 1 and 2 is gradually decreased. The second PLL control loop (2) has a fast response to a slight fluctuation of the frequency of the pulse signal, but does not have a fast response to a great fluctuation of the frequency thereof and consequently, the second PLL control loop (2) alone is incapable of keeping the predetermined phase difference between the rotational angle of the shafts 1 and 2 at the predetermined phase difference. The rotational angle phasing control loop (3) has the following function. That is, the rotational angle phasing sections 33 and 43 having a deviation counter, respectively monitor the output of the incremental encoders 5 and 6 and instantly correct the deviation of the phase difference between the rotational angle of the shafts 1 and 2, thus accurately following the fall of the frequency of the pulse signal. Thus, in cooperation of the second PLL control loop (2) and the rotational angle phasing control loop (3), the shafts 1 and 2 can be synchronously rotated with a high accuracy even in the fall time. The CPU control section 10 monitors the signal, indicating the phase difference between the rotational angle of the shafts 1 and 2, detected by the absolute encoders 7 and 8 in the rise time and fall time of the shafts 1 and 2. If the CPU control section 10 detects a deviation in the phase difference between the rotational angle of the shafts 1 and 2, the CPU control section 10 controls the pulse extracting sections 35 and 45 so as to correct the frequency and phase of the pulse signal for rotating the shafts 1 and 2 and the deviated phase difference in the phase difference between the rotational angle of the shafts 1 and 2. In the above embodiment, the motor control circuits 3 and 4 have two PLL control circuits 31 and 32, and two PLL control circuits 41 and 42, respectively, but the motor control circuits 3 and 4 may include one PLL control circuit 32 and 42, respectively so that the output of the PLL control circuits 32 and 42 is directly connected to the contact 36a and 46a, respectively. The multi-shaft driving apparatus shown in Fig. 1 allows the shafts to be rotated synchronously not only in the steady state, but also in the transient state. Thus, the apparatus can be utilized in a wide range. A fluid rotary apparatus to which the above embodiment is applied is described below with reference to Figs. 2 and 3. Figs. 2 and 3 show a positive-displacement vacuum pump according to an embodiment of the present invention. Fig. 2 is a sectional view of the pump. Fig. 3 is a front view, showing the positive-displacement vacuum pump, in which a housing is broken away. The vacuum pump comprises a first bearing chamber 111 accommodating a first rotary shaft 102 vertically and a second bearing chamber 112 accommodating a second rotary shaft 103 vertically. Cylindrical rotors 104 and 105 are mounted on upper portions of the shafts 102 and 103, respectively. Screws 142 and 152 are formed on the peripheral surfaces of the rotors 104 and 105, respectively so that the screws 142 and 152 engage each other. The engagement portion of the screws 142 and 152 is denoted by (A). That is, a space formed by the concave (groove) and convex of the engagement portion (A) of the screws 142 and 152 and the housing 101 changes its volume cyclically with the rotation of the shafts 102 and 103. Thus, fluid sucking and discharging operations are performed. As shown in Figs. 2 and 3, gears 144 and 154 for preventing the contact of the screws 142 and 152 are formed on the peripheral surfaces of the rotors 104 and 105 at the lower end thereof. A solid lubricating film is formed on the gears 144 and 154 so that the metal of the gears 144 and 154 are capable of withstanding a small degree of contact. A gap (backlash) δ 2 between the engagement portion of the gears 144 and 154 is set to be smaller than a gap (backlash) δ 1 between the engagement portion (A) of the screws 142 and 152 formed on the peripheral surfaces of the rotors 104 and 105, respectively. The gears 144 and 154 do not contact each other when the shafts 102 and 103 are synchronously and smoothly rotating. If they are not rotating synchronously, the gears 144 and 154 contact each other, thus preventing the contact of the screws 142 and 152. The amount of backlashes δ 1 and δ 2 is too small to be accurately processed for practical use. The total amount of fluid leakage during one process of the pump is proportional to the period of time required in the process. Therefore, while the shafts 102 and 103 are rotating at a high speed, the performance of the pump such as ultimate vacuum degree can be sufficiently maintained even though the backlash δ 1 is made to be comparatively large. Accordingly, the dimension of the backlashes δ 1 and δ 2 necessary for preventing the collision of the screws 142 and 152 can be reliably obtained by rotating the shafts 1 and 2 at a high speed even though the processing accuracy of the screws is not high. A gas suction opening 114 and a gas discharge opening 115 are provided upstream and downstream of the engagement portion (A) of the housing 101, respectively. The shafts 102 and 103 are supported by a non-contact type static pressure bearing, which is described below, provided in internal spaces 145 and 155 of the rotors 104 and 105. That is, a thrust bearing is constituted by supplying compressed gas from orifices 116 to the upper and lower surfaces of the disks 121 and 131 formed on the shafts 102 and 103, respectively, and a radial bearing is composed by supplying compressed gas from orifices 117 to the peripheral surface of the shafts 102 and 103. The utilization of clean nitrogen gas equipped in a semi-conductor factory as compressed gas is capable of making the pressure inside the internal spaces 145 and 155 accommodating a motor higher than the atmospheric pressure. Thus, reactive gas which is corrosive and easily produces sediment can be prevented from penetrating into the internal spaces 145 and 155. Instead of the static pressure bearing, the bearing may be composed of a magnetic bearing which is also of a non-contact type and as such oil-free. Therefore, the shafts 102 and 103 are capable of rotating at a high speed. If a ball bearing is used in the bearing portion (chamber) and lubricating oil is used to lubricate the ball bearing, a gas verge mechanism utilizing nitrogen gas is capable of preventing the penetration of lubricating oil into a fluid actuation chamber. Both the shafts 102 and 103 are rotated at a speed as high as tens of thousands of rpm by AC servo motors 107 and 106 provided each in a lower portion of the shafts 102 and 103. Encoders 108 and 109 are provided on the lower ends of the shafts 102 and 103 and correspond to the encoders 5,6,7, and 8 in Fig. 1. The operation of the vacuum pump will be described below. First, in driving the vacuum pump, the phase difference between the rotational angles of the shafts 102 and 103 is adjusted to a predetermined phase difference under the control of the rotational angle phasing control loop (3) so that the center line of the convex or concave of the screw 142 and that of concave or convex of the screw 152 align with each other. The phase difference in the rotational angle between the shafts 1 and 2 can be adjusted to the predetermined phase difference by the gears 144 and 154. Subsequently, the number of the rotations of the shafts 102 and 103 is increased to that of the steady state with the phase difference in the rotational angle between the shafts 102 and 103 kept at the predetermined phase difference. The number of the rotations of the shafts 102 and 103 smoothly rises to that of the steady state in an accurate accordance with the number of rotations instructed by the pulse signal, for rotating the shafts 102 and 103, outputted from the pulse generator 9 without the gears 144 and 154 (screws 142 and 152) contacting each other. This is the above-described rise time operation of the multi-shaft driving apparatus. Alternatively, the first part of the rise time operation can be performed by the rotation of the gears 144 and 154 (screws 142 and 152). In the steady drive, the shafts 102 and 103 are rotated synchronously with a high accuracy by the first PLL control loop (1). In stopping the vacuum pump, with the phase difference between the rotational angles of the shafts 102 and 103 kept at the predetermined phase difference, the rotation of the shafts 102 and 103 can be stopped in an accurate accordance with the number of rotations instructed by the pulse signal for rotating the shafts 102 and 103 without the contact of the gears 144 and 154 (screws 142 and 152). This is the above-described fall time operation of the multi-shaft driving apparatus. As described above, the vacuum pump is capable of rotating the shafts 102 and 103 or the screws 142 and 152 synchronously with a high accuracy not only in the steady state, but also in the transient state. That is, according the vacuum pump to which the present invention applies, the shafts 102 and 103 are not rotated synchronously by a timing gear. Therefore, it is unnecessary to use lubricating oil or an oil seal in the timing gear. Consequently, a clean vacuum without oil can be obtained. Since a mechanical sliding portion is not provided, the shafts 102 and 103 can be rotated at a high speed and in addition, the vacuum pump does not make a big noise and is durable. Further, the shafts 102 and 103 can be rotated at a higher speed and the pump can be compact by supporting the shafts 102 and 103 by the static gas bearing. The fluid rotary apparatus shown in Fig. 2 may be applied to a positive-displacement vacuum pump. The pump does not require the provision of a mechanical sliding portion which allows the shafts to be rotated synchronously both in the transient state (rise time and fall time) and in the steady state. That is, the pump does not require the supply of lubricating oil. Therefore, the pump is clean and the shafts (rotors) rotate at a high speed, and in addition, the apparatus is durable. Additionally, the apparatus can include a vacuum degree setting means 160 for setting the vacuum degree in a discharge space and a vacuum degree detecting means 161 for detecting the vacuum degree therein. The frequency of the pulse signal indicating the number of rotations of the shafts 102 and 103 is varied according to the difference between a set vacuum degree and a detected vacuum degree. The number of rotations of the rotors 104 and 105 may be varied according to the detected vacuum degree in the discharge space. Thus, the number of rotations of the rotors 104 and 105 can be accurately controlled and consequently, gas can be accurately discharged in a wide vacuum range from a low vacuum degree to a high vacuum degree. Therefore, gas discharge performance can be controlled with a high accuracy. For example, the control of the pressure in the vacuum chamber can be facilitated without using a butterfly valve. The fluid rotary apparatus is capable of discharging gas and controlling pressure with a high accuracy without providing the vacuum pump with a flow rate controlling equipment, for example, a butterfly valve. As shown in Fig. 5, normally, the phase difference between the rotational angles of the shafts 102 and 103 is adjusted to the predetermined phase difference so that the center line of the convex or concave of the screw 142 and that of the concave or convex of the screw 152 align with each other. But in order to increase gas discharge efficiency in the steady state, it is preferable that the center line of the convex or concave of the screw 142 and that of the concave or convex of the screw 152 do not align with each other (for example, rotational angle difference of the shafts 102 and 103 is set to approximately 0.01°.) At this time, the pulse extracting sections 35 and 45 extract a necessary number of pulses from the pulse signal for rotating the shafts 102 and 103. The pulse extracting sections 35 and 45 are provided both in the motor control circuits 3 and 4 so that the center line of the convex or concave of the screw 142 and that of the concave or convex of the screw 152 do not align with each other in both backward and forward directions. In order to change the rotational angle difference of the shafts 102 and 103 as fine as 0.01°, an encoder having approximately 10,000 light transmitting slits per 360° (one rotation) is preferably used to obtain pulses of 40,000 resolutions, namely, four times as great as 10,000. Thus, 360°/40000 = 0.01°

Claims: A fluid rotary apparatus comprising: a plurality of rotors (104, 105) accommodated in a housing (101); a plurality of shafts (1, 2; 102, 103) each for rotating one of the rotors (104, 105) to be synchronously rotated; a plurality of motors (M1, M2; 106, 107) each for rotating one of a plurality of the shafts (1, 2; 102, 103) to be synchronously rotated; an encoder (5, 6; 108, 109) provided for each motor (M1, M2; 106, 107) for detecting the rotational state of the shafts (1, 2; 102, 103); a pulse generator (9) for generating a pulse signal for rotating the shafts (1, 2; 102, 103); and a motor control circuit (3, 4), provided for each motor (M1, M2; 106, 107), for inputting a pulse signal detected by the encoder (5, 6; 108, 109) and used as a feedback signal to control the synchronization of the shafts (1, 2; 102, 103) wherein the motor control circuit (3, 4) has at least one PLL controller (31, 32, 41, 42) for performing a PLL control operation at a steady state after a rise time (II) of the rotational speed of the shafts and before a fall time (IV) thereof, characterized in that a fluid drawing opening (114) and a fluid discharge opening (115) is formed in the housing (101) wherein the volume change of a space formed by the rotors (104, 105) and the housing (101) is utilized to draw and discharge fluid, and that the pulse signals from the pulse generator (9) are inputted in the motor control circuit (3, 4). The fluid rotary apparatus as claimed in claim 1, wherein the motor control circuit (3, 4) has a rotational angle phasing controller (33, 43) for performing a rotational angle phasing operating at the rise time (II) and the fall time (IV).

Inventors: HASEGAWA MIKIO, MARUYAMA TERUO, HASEGAWA, MIKIO, MARUYAMA, TERUO
Applicants: MATSUSHITA ELECTRIC IND CO LTD, MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD.
Application year: 1992
Main classification: G05D13
IPC codes: H02P5, F04C25