JP2880333B2 - Adjustment device for rotor pump timing gear - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a timing gear adjusting device which adjusts the amount of eccentricity of a timing gear for rotating a rotor of a rotor pump to prevent problems such as discharge pressure pulsation and abnormal noise.

[0002]

2. Description of the Related Art Conventionally, a non-contact type screw pump in which a male rotor and a female rotor provided in a casing rotate with a slight gap between their mutual tooth surfaces and pressurize and discharge fluid or the like in the casing. In Japanese Patent Application No. 02-417302, the present applicant has disclosed a clearance adjustment method for the purpose of appropriately securing the clearance between the rotor tooth surfaces and preventing the rotor tooth surfaces from contacting each other. In this method, a timing gear is connected to the rotor shaft of each of the male and female rotors, a driving force for rotating each rotor is transmitted to the timing gear, and the clearance between the rotor tooth surfaces is adjusted by adjusting the timing gear. In such a rotor pump, the tooth surface of one of the male and female drive-side rotors is brought into contact with the tooth surface of the free-sided rotor, and the drive-side rotor is rotated in the forward and reverse directions, respectively. Then, the free rotor on the other side is rotated to determine the backlash between the tooth surfaces of the entire tooth surface, and the rotor is set at a substantially central position of the backlash between the rotor tooth surfaces. For this reason, the mounting position of one of the timing gears can be adjusted with respect to the rotor shaft, and the timing gear is fixed to the rotor shaft at the position determined in the above-described manner, and the clearance between the tooth surfaces of each rotor is adjusted during rotation. It is made substantially uniform over the tooth surface. For this reason, in the case of the same proposal, the bolt mounting hole of one of the timing gears is formed as a long idle hole so that the mounting position can be changed with respect to the rotor shaft.

[0003]

However, in the above case,
Since the mounting position of the timing gear changes with respect to the rotor shaft, there is a problem that the center of the timing gear and the center of the rotor shaft are eccentric within the range of the coupling clearance, and a meshing transmission error occurs. For this reason, the clearance between the tooth surfaces of the rotor set at the time of rest also changes in synchronization with the timing gear, which is likely to cause problems such as discharge pressure pulsation and generation of fluctuation noise. Further, there is a problem that the timing gear itself generates a meshing sound due to the eccentricity. Conventionally, measures such as improving the gear accuracy or improving the accuracy of the joint between the gear and the rotor shaft have been taken against such a problem, and the efficiency has been poor.

[0004]

SUMMARY OF THE INVENTION In order to solve such a problem, the present invention provides a rotor pump having a timing rotor mounted on a shaft of a male rotor.
Gear gears so that the tooth surface does not contact the male rotor
A timing is attached to the axis of the female rotor arranged with a small gap.
Gears, and one timing gear
Drive both gears to rotate both rotors
Rotor pump with eccentricity to the other timing gear
In a rotary pump where the presence of
The timing gear can be moved in the direction perpendicular to the rotor shaft.
Move along a straight line connecting the centers of the axes,
Move the timing gear toward the other timing gear by a predetermined amount.
Equipped with a position correction actuator that can be pressed
Move forward and backward in the direction orthogonal to the straight line connecting the centers of the axes,
Press and hold the outer surface of one timing gear from both sides
A pair of guide actuators
The maximum deviation of the other timing gear driven by the
Based on the information on the core amount and its orientation,
Gear in the direction that the other timing gear moves away from the gear.
Command to rotate the tie a further 90 degrees, then the other tie
The gearing gear to the one timing gear by the maximum amount of eccentricity
Command to the position correction actuator
A rotor pump tie having a control mechanism
This is an adjustment device for the mining gear.

[0005]

[Action] Creates position correction actuator by command of control mechanism
Move the other timing gear to one timing gear
And push it out at that time.
Move straight by pinching the other timing gear
Can be done.

[0006] By modifying the eccentricity of Thailand Mingugia, it is possible to maintain the discharge pressure eliminates the fluctuation of the clearance between the tooth surfaces of the rotor constant. Further, abnormal noise is reduced.

[0007]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Timing Gear Adjustment of a Rotor Pump of the Present Invention
An embodiment of the apparatus will be described with reference to the accompanying drawings.
FIG. 1 is a longitudinal sectional view of a timing gear adjusting device of the present invention used in combination with a rotor clearance measuring device, FIGS. 2 and 3 are timing gear adjusting devices of the present invention, FIG. 2 is a plan view, and FIG. 3 is a sectional view taken along line AA of FIG.

First, a non-contact screw type rotor pump 1
The rotor pump 1 includes a female rotor 3 and a male rotor 4 in a casing 2 as shown in FIG.
The rotor surfaces of the female rotor 3 and the male rotor 4 are rotated with a small gap that does not make contact with each other, and pressurize and discharge fluid or the like in the casing 2.

Therefore, the female rotor 3 and the male rotor 4
Is provided with rotor shafts 5 and 6 as shafts, respectively. The rotor shafts 5 and 6 are supported by the casing 2, and the timing gears 7 and 8 are coupled to one end of the rotor shaft 5 extending outside the casing 2. ing. And among these timing gears 7,8, for example female rotor 3 side of the timing gear 7, adjustable position and become to the rotor shaft 5, via a large floating long hole of Ri diameter yo bolt 9, the rotor shaft 5 It is bolted to the flange. The rotational driving force of each rotor 3, 4 is
8 is transmitted. Incidentally, the number of teeth of the male rotor 3 is four, and the number of teeth of the female rotor 4 is five.

The rotor clearance measuring device 10 is for measuring the clearance between the tooth surfaces of the male and female rotors. The outline of the device and the measuring method will be outlined below.

A servomotor 11 for rotational drive is connected to the rotor shaft 6 of the male rotor 4.
Include rotary encoders 12 and 13 for detecting a rotation angle.
Is provided. The rotary encoders 12 and 13 and the servomotor 11 are connected to an arithmetic control unit 14 to perform arithmetic processing on signals from the rotary encoders 12 and 13 and to control the servomotor 11. Further, a display 15 and a printer 16 for displaying processed data are provided. The rotor shaft 5 on the female rotor 3 side is provided with a friction brake 18 and a rotor fixing brake 19.

The measuring method of the clearance between the tooth surfaces by such an apparatus is as follows. First, the rotor pump 1
It is set on the measuring device 10. At this time, the timing gear 7 on the side of the female rotor 3 is set to “ not fastened ” to the rotor shaft 5 so that the driving force is not transmitted from the timing gears 7 and 8. Then, after the tooth surface of the male rotor 4 is brought into contact with the tooth surface of the female rotor 3, the transmission error of the mesh between the two rotors is measured.

That is, the male rotor 4 is rotated forward and the female rotor 3 is rotated, and the rotary encoders 12 and 1 are rotated.
At 3, the rotation angles of both are measured. At this time, the rotation angle of the female rotor 3 with respect to the rotation angle of the male rotor 4 should rotate according to a certain fixed theoretical value, but the actual rotation angle has an error. Obtained as data 21.

If, for example, the rotation of the male rotor 4 is rotated five times and the forward rotation is stopped, the female rotor 3 is rotated four times, and all combinations of the respective tooth surfaces are completed. Then, if this data is represented in a graph, the measured value S in FIG.
1 (from a to b), and the drive rotor 4 shown on the horizontal axis
The transmission error of the driven rotor 3 (converted from the rotation angle error of the driven rotor 3 to the error amount in the backlash direction) shown on the vertical axis with respect to the rotation angle is represented by a waveform.

Next, the male rotor 4 is rotated in the reverse direction to bring the opposite tooth surfaces into contact. At this time, the distance from the floating gap B of the male rotor 4 to the height C indicates the backlash of the same portion. Then, by rotating the male rotor 4 backward by 5 rotations from this state and measuring the rotation angles of the rotors 3 and 4 to show the deviation from the theoretical value, the measured value S2 (from C to D) in FIG. 4 is obtained. The vertical interval between S1 and S2 indicates a backlash corresponding to each rotation angle. With the above, between the rotor tooth surfaces
End measurement of backlash.

Next, the timing gears 7, 8 are operated in the same procedure.
Measure the backlash between. That is, the timing gear 7 that has not been engaged before is “ coupled ” to the rotor shaft 5.
If the timing gear 7 on the driving side rotates the timing gear 7 on the driven side, the data of the measured value P1 is obtained by the forward rotation and the data of the measured value P2 is obtained by the reverse rotation. The vertical interval between P1 and P2 indicates the backlash at each rotation angle. This allows for backlash between timing gears.
End the measurement.

As described above, when the backlash between the tooth surfaces of the rotor and the backlash between the timing gears are measured,
The backlash area between the timing gears (the area surrounded by P1 and P2) can be freely moved and adjusted within the backlash area between the rotor tooth faces (the area surrounded by S1 and S2), and the position where the rotor tooth faces do not contact. The timing gear can be positioned at the same time.

Incidentally, the timing gear adjusting device 22 of the present invention uses the transmission error of the timing gear shown in FIG.
That is, it is intended to smooth the unevenness of the measured values P1 and P2.

That is, the transmission error of the timing gear is affected by the eccentricity of the gear more than the influence of the tooth groove runout, the tooth profile accuracy, etc., as shown in FIG. It also appears that large undulations are repeated periodically. In FIG. 4, the measured values P1 and P2 are large.
The cause of the undulation is the amount of eccentricity of the gear.
The effect on transmission error when gear eccentricity is e
Consider FIG.

FIG. 6 is a diagram for explaining the relationship between the eccentricity of the gear and the transmission error. In FIGS. 6A and 6B, r is the pitch circle radius of the driven gear A, and L is the rotation of both rotor rotating shafts. A straight line connecting the centers, O indicates the rotation center of the rotor shaft, Q indicates the rotation center of the gear A, and e indicates the amount of eccentricity of the gear . Gear A
Since the rotation center Q does not match, gear A
When rotated, the rotation center Q of the gear A is centered on the rotation center O.
Around the circle having the radius e. Rotating during turning
As a typical pattern of the heart Q, the center of rotation Q is straight in FIG.
The state when it reaches a line perpendicular to the line L, as shown in FIG.
The state when the turning center Q reaches the straight line L is shown. Destination
When the amount of eccentricity e is in a phase perpendicular to the straight line L, the retardation angle β of the driven gear A is calculated by the equation shown in FIG. The delay amount a on the pitch circle of A coincides with the eccentricity e.

Next, in the state shown in FIG. (B) rotated 90 degrees from the state shown in FIG. (A), the eccentric direction coincides with the direction of the straight line L. At this time, the retardation angle β of the driven gear A and the gear A The delay amount a on the pitch circle is a value shown in the figure. Here, θ is the pressure angle of the gear.

Accordingly, when the gear having such an eccentric amount e rotates, the amount of retardation on the pitch circle draws a curve as shown in FIG. 7C, and the maximum amount of retardation is a right angle in the state of FIG. It should show the phase value e. It is considered that the influence of the eccentricity also appears on the transmission errors of the measured transmission error transmission values P1 and P2 shown in FIG. That is, it is considered that the maximum fluctuation width b of the transmission error shown in FIG. 4 is obtained, and this value b is halved to correspond to the value e in FIG. 6C.

From the above considerations, in order to correct the amount of eccentricity of the gear, the largest one among the periodic fluctuations of the transmission error is searched, and the gear is shifted in the eccentric direction by half of the amount. It can be seen that it is better to move.

The configuration of the timing gear adjusting device 22 for adjusting the amount of eccentricity will now be described with reference to FIGS.

This timing gear adjusting device 22 is a position correcting actuator 2 capable of pressing the driven side timing gear 7 toward the drive side timing gear 8.
3, and a pair of guide actuators 24, 24 as guide means for pressing and holding both side surfaces of the timing gear 7, and the pressing directions of the position correction actuator 23 and the guide actuator 24 are orthogonal to each other.

The pressing stroke of the position correcting actuator 23 can be controlled by a control mechanism (not shown). A pair of guide actuators 24, 24 facing each other with the timing gear 7 interposed therebetween are connected to, for example, the same air drive source 25. Then, the timing gear 7 is pressed from both side surfaces with uniform pressure.

The adjustment of the gear set position by the timing gear adjusting device 22 is performed as follows. First, as described above, the timing gear 7 is set by the timing gear 8.
To determine the phase and the amount of the maximum swing b of the transmission error from the measured values P1 and P2 as shown in FIG. At this time, the phase of the gear should be in a direction in which the eccentric direction is orthogonal to a straight line connecting both rotation axes, as shown in FIG.

Then, by rotating the timing gear 7 by 90 degrees from the phase at which the maximum swing width b appears, the eccentric direction can be made coincident with the straight line connecting the centers of both rotating shafts. At this time, a direction in which the eccentric direction is away from the other timing gear 8 is selected.

Next, in this state, the guide actuators 24, 24 are operated to press and hold both side surfaces of the timing gear 7, and then, the fastening between the rotor shaft 5 and the timing gear 7 is released (the bolt 9 is removed) . Then, the stroke of the position correction actuator 23 is operated, and a half of the maximum runout width b is obtained.
After the timing gear 7 is pushed and moved by an amount (eccentric amount e), it is fastened to the rotor shaft 5 again by the bolt 9 .

When the transmission error of the timing gear is confirmed, smooth trajectories P1 and P2 are obtained as shown in FIG. That is, the amount of eccentricity can be adjusted very easily.

[0031]

As described above, the apparatus for adjusting the timing gear of the rotor pump according to the present invention can correct the position by the command of the control mechanism.
Activate the actuator and move the other timing gear
Extruded toward the timing gear of
The other timing gear is sandwiched by the guide actuator
Can be moved straight. Timing gi
By correcting the eccentricity of the rotor, the clearance between the rotor tooth
And the discharge pressure can be kept constant.
You. Further, abnormal noise is reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a timing gear adjusting device of the present invention used in combination with a rotor clearance measuring device.

FIG. 2 is a plan view of the timing gear adjusting device of the present invention.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a graph of a conventional example showing an engagement transmission error between a rotor and a timing gear.

FIG. 5 is a graph of the present invention showing a meshing transmission error between a rotor and a timing gear.

FIG. 6 is an explanatory diagram for explaining a relationship between eccentricity of a gear and a transmission error amount.

[Explanation of symbols]

1 ... rotor pump , 3 ... female rotor , 4 ... male rotor ,
5 , 6 ... rotor shaft , 7 , 8 ... timing gear , 10 ... rotor clearance measurement device , 22 ... timing gear adjustment device , 23 ... position correction actuator , 24 ... guide actuator , e ... eccentricity.

Claims (1)

(57) [Claims] 1. A time axis is attached to a shaft of a male rotor of a rotor pump .
Gear teeth so that the tooth surface does not contact the male rotor
To the axis of the female rotor , which is arranged with a very small gap .
Imming gears are connected, and one timing gear
A rotor pump that rotates both rotors by driving a timing gear.
The other timing gear is moved in the direction perpendicular to the rotor shaft in the rotary pump in which the eccentric amount is assumed to exist.
Capable constitute, Bei position correction actuator which can be pressed a predetermined amount toward the forward and backward movement along a straight line connecting the centers of the axes and one of the timing gears to the other of the timing gears
For example, to move forward and backward in the direction perpendicular to the straight line connecting the centers of the respective axes且
Press and hold the outer surface of one timing gear from both sides
A pair of guide actuators, and the other timing driven by the one timing gear
Based on the information of the maximum eccentric amount of gear and its azimuth,
The other timing gear is far from one timing gear
Issue an instruction to rotate both gears further 90 degrees in the direction
Next, move the other timing gear to one tie by the maximum amount of eccentricity.
Command to push the gear toward the
An adjustment device for a timing gear of a rotor pump, comprising a control mechanism for emitting to an eta .