Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
  • F04C2/06—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of other than internal-axis type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions

Definitions

• the present invention relates, in general, to rotary pumps which pump fluid using suction force of rotor units that are rotated by drive motors and, more particularly, to a multiple rotary pump in which a drive motor is provided such that an output shaft of the drive motor is placed at an offset position, so that a rotational speed of the pump can be changed to a high or low speed, and in which an eccentric rotary body is moved in a space defined in each rotor unit, thus preventing a cross-plate from being damaged, and which ensures smooth rotation of the rotor units using a bearing means.
• pumps are machines which move fluid to another place, for example, from a low position to a high position.
• FIG. 1 illustrates a rotary pump in which an upper rotor unit 2, which is provided in an upper chamber 1, is coupled to a lower rotor unit 4, which is provided in a lower chamber 3, through a cross-plate 5.
• the distance between the upper rotor unit 2 and the lower rotor unit 4 becomes shortest.
• the distance between the upper rotor unit 2 and the lower rotor unit 4 becomes longest.
• the distance between the centers of the upper and lower rotor units 2 and 4, which are offset from the chambers is 175.2 mm.
• the distance between the upper rotor unit 2 and the lower rotor unit 4 is 61.2 mm.
• the distance between the centers of the upper and lower rotor units 2 and 4, which are offset from the chambers is 177.2 mm.
• the distance between the upper rotor unit 2 and the lower rotor unit 4 is 63.2 mm.
• the cross-plate 5 which couples the upper rotor unit 2 to the lower rotor unit 4, is a rigid body, the structure and operation of the rotary pump shown in FIGS. Ia and Ib cannot be realized. In other words, the length of the cross-plate 5 must be varied depending on the positions of the rotor units.
• a rotary pump was proposed in Korean Patent Application No. 1994-010299, entitled “double cylindrical pump”. As shown in FIG. 2, this pump is constructed such that a cross-plate 3 is inserted into a sliding slot 2 formed in a circumferential outer surface of a first sliding body 1 (hereinafter, referred to as an upper rotor unit) , and the cross-plate 3 is removably coupled to the upper rotor unit 1 and is integrally coupled to a second sliding body 4 (hereinafter, referred to as a lower rotor unit) .
• a first sliding body 1 hereinafter, referred to as an upper rotor unit
• a second sliding body 4 hereinafter, referred to as a lower rotor unit
• eccentric gears are used to constantly maintain the distance between upper and lower rotor units.
• this method is applied to a multiple rotary pump, the offset shafts rotate the upper rotor unit in a clockwise direction and rotate the lower rotor unit in a counterclockwise direction using the eccentric gears, thus generating torsional stress.
• the eccentric gears can be used in a rotary pump having a single structure, but, in the case that the eccentric gears are used in a multiple rotary pump, because the orientations of the rotor units coupled to the shafts are different, an acceleration section is varied by the eccentricity. Thus, the possibility of breakage of the rotor units is increased.
• an object of the present invention is to provide a multiple rotary pump which pumps fluid using suction force of rotor units rotated by a drive motor, and in which the drive motor is provided such that an output shaft of the drive motor is placed at an offset position, so that a rotational speed of the pump can be changed to high or low speed, and in which an eccentric rotary body is moved in a space defined in each rotor unit, thus preventing a cross- plate from being damaged, and which ensures smooth rotation of the rotor units using a bearing means.
• the present invention provides a rotary pump which has a drive motor and upper and lower chambers and pumps fluid both using rotor units moving along inner surfaces of the chambers and using a cross-plate.
• the rotary pump comprises: a drive motor provided at a predetermined position such that an output shaft thereof is disposed at an offset position, with an overload prevention unit provided on an end of the output shaft, the overload preventing unit having a helical motor gear; a clutch unit coupled to an end of the overload prevention unit; upper and lower chambers; rotor units provided in the respective upper and lower chambers such that power is transmitted through the clutch unit to the rotor units, each of the rotor units having an eccentric rotary body installed in each rotor unit and eccentrically rotated by each of a pair of rotating shafts and, with bearing means provided in each of the rotor units.
• the clutch unit which is a critical part of the present invention and is coupled to the overload prevention unit, may comprise: a first gear engaging with the helical motor gear, which is eccentrically positioned, the first gear being rotatably fitted over the rotating shaft, which is placed at a position opposite a direction in which the helical motor gear is offset, and a first subsidiary gear having a diameter smaller than a diameter of the first gear and integrally provided beneath the first gear; a second gear having a larger diameter and engaging with the first subsidiary gear, the second gear being rotatably fitted over the other rotating shaft, and a second subsidiary gear having a diameter smaller than the diameter of the second gear and integrally provided beneath the second gear; a third gear having a larger diameter and engaging with the second subsidiary gear, the third gear being rotatably fitted over the rotating shaft, and a third subsidiary gear having a diameter smaller than the diameter of the third gear and integrally provided beneath the third gear; a fourth gear having a larger diameter and engaging with the third subsidiary gear, the fourth gear being rotatably fitted over the
• first, second, third, fourth and fifth gears and the first, second, third, fourth and fifth subsidiary gears are fitted over the first and second shafts, bearings are interposed between the rotating shafts and the gears such that the gears are rotated at relatively low speeds with respect to the rotating shafts, and when the first and second main gears and are rotated at low speeds by the power transmitted from the drive gear, the rotor units are rotated at low speeds.
• the clutch unit comprises: a first gear engaging with the helical motor gear, which is eccentrically positioned, the first gear being rotatably fitted over the rotating shaft, which is placed at a position opposite a direction in which the helical motor gear is offset, and a first subsidiary gear having a diameter larger than a diameter of the first gear and integrally provided beneath the first gear; a second gear having a smaller diameter and engaging with the first subsidiary gear, the second gear being rotatably fitted over the other rotating shaft, and a second subsidiary gear having a diameter larger than the diameter of the second gear and integrally provided beneath the second gear; a third gear having a smaller diameter and engaging with the second subsidiary gear, the third gear being rotatably fitted over the rotating shaft, and a third subsidiary gear having a diameter larger than the diameter of the third gear and integrally provided beneath the third gear; a fourth gear having a smaller diameter and engaging with the third subsidiary gear, the fourth gear being rotatably fitted over the rotating shaft, and a fourth
• first, second, third and fourth gears and the first, second, third and fourth subsidiary gears are fitted over the first and second shafts, bearings are interposed between the rotating shafts and the gears such that the gears are rotated at relatively high speeds with respect to the rotating shafts, and when the first and second main gears are rotated by the power transmitted from the drive gear, the rotor units are rotated at high speeds.
• Each of the rotor units which are another critical part of the present invention, may comprise: a cylindrical housing having a cylindrical shape with a diameter smaller than an inner diameter of each chamber, with a plurality of bearing seats formed in a circumferential inner surface of the cylindrical housing, and a space defined in the cylindrical housing; the eccentric rotary body having a diameter smaller than the inner diameter of the cylindrical housing and eccentrically fitted over each of the rotating shafts; and the bearing means seated into the bearing seats of the cylindrical housing.
• Both the cylindrical housing and the eccentric rotary body are provided in each of the upper and lower chambers, and the two cylindrical housings are coupled to each other through the cross-plate and are eccentrically rotated.
• each rotor unit may comprise: a cylindrical housing having a cylindrical shape with a diameter smaller than an inner diameter of each chamber, with a space defined in the cylindrical housing; the eccentric rotary body having a diameter smaller than the inner diameter of the cylindrical housing and eccentrically fitted over each of the rotating shafts, with a plurality of bearing seats formed in a circumferential outer surface of the eccentric rotary body; and the bearing means seated into the bearing seats of the eccentric rotary body.
• Both the cylindrical housing and the eccentric rotary body are provided in each of the upper and lower chambers, and the two cylindrical housings are coupled to each other through the cross-plate and are eccentrically rotated.
• each eccentric rotary body is in rolling contact with the a circumferential inner surface of each chamber, thus reducing friction between them, thereby ensuring smooth rotation of the rotor units.
• a space is defined between the chamber and the eccentric rotary body, thus solving a conventional problem in that a cross-plate is damaged by torsional stress and tensile force, thereby ensuring superior durability of the pump.
• FIG. 1 is a view showing a rotor unit of a conventional rotary pump
• FIG. 2 is a view showing a cross-plate inserted into a slide slot of a rotor unit of another conventional pump
• FIG. 3 is a view showing the operation of a rotor unit to illustrate the concept of the present invention
• FIG. 4 is a schematic view showing a reason that a cross-plate must be lengthened
• FIG. 5 is a sectional view showing a first embodiment of a clutch unit of the present invention
• FIG. 6 is a sectional view showing a second embodiment of a clutch unit of the present invention
• FIG. 7 is a sectional view showing a third embodiment of a clutch unit of the present invention
• FIG. 8 is a sectional view showing a fourth embodiment of a clutch unit of the present invention.
• FIGS. 9 and 10 are views showing the operation of the rotor unit according to the present invention.
• FIG. 11 is a view showing an enlargement of a first embodiment of the rotor unit of the present invention.
• FIG. 12 is a view of a cylindrical housing according to the first embodiment of the rotor unit of the present invention.
• FIG. 13 is a schematic view illustrating the operation of the rotor unit according to the first embodiment of the present invention.
• FIG. 14 is a view showing a modification of the rotor unit according to the first embodiment of the present invention.
• FIG. 15 is a view showing an enlargement of a second embodiment of the rotor unit of the present invention.
• FIG. 16 is a view showing an eccentric rotary body according to the second embodiment of the rotor unit of the present invention
• FIG. 17 is a view showing a modification of the rotor unit according to the second embodiment of the present invention.
• FIG. 18 is a schematic view illustrating the operation of the rotor unit according to the second embodiment of the present invention.
• FIG. 19 is schematic views showing installation of a bearing means according to the present invention.
• FIG. 20 is schematic views showing installation of the bearing means according to the present invention.
• FIG. 21 is a plan view of a pump according to the present invention.
• FIG. 22 is a view showing a duplex pump according to the present invention
• FIG. 23 is a view showing a triplex pump according to the present invention
• FIG. 24 is a view showing a quadruple pump according to the present invention.
• FIG. 25 is a view showing an example of a piping structure of the pump according to the present invention.
• FIG. 26 is a view showing another example of a piping structure of the pump according to the present invention.
• FIG. 27 is a view showing a further example of a piping structure of the pump according to the present invention.
• FIG. 28 is a view showing yet another example of a piping structure of the pump according to the present invention.
• FIG. 29 is a sectional view showing the construction of the quadruple pump according to the present invention.
• FIG. 30 is a perspective view of an overload prevention unit of the present invention.
• FIG. 31 is a sectional view showing the overload prevention unit coupled to an output shaft of a drive motor according to the present invention.
• the present invention is similar to the conventional art in that it is a rotary pump, which has a drive motor and upper and lower chambers, and in which a pumping operation is executed by movement both of rotor units, which rotate along the inner surface of the chambers, and of a cross-plate.
• an eccentric rotary body is provided in each rotor unit, and a gap is defined between the rotor unit and the eccentric rotary body. Thanks to the gap, the present invention does not require a variable length of the cross-plate, unlike the conventional art.
• another special feature of the present invention is characterized in that a rotational speed can be changed between a high speed and a low speed.
• the rotary pump of the present invention includes a pair of rotor units 200 which rotate in two circular chambers 30, in the same manner as that of the typical rotary pump.
• an upper rotor unit 200 (placed at an upper position when viewing the drawing) is rotated in a clockwise direction.
• a lower rotor unit 200 (placed at a lower position when viewing the drawing) is rotated in a counterclockwise direction. Therefore, as sequentially shown in the drawing, first, the rotor units 200 are oriented in a vertical direction while the upper rotor unit 200 contacts the uppermost point of the upper chamber 20. Next, the upper rotor unit 200 is rotated at 90° in a clockwise direction, so that the contact surface of the upper rotor unit 200 moves to a portion of the upper chamber 30 (placed at the upper position when viewing the drawing) which is spaced apart from the uppermost point at 90°.
• the lower rotor unit 200 (placed at the lower position when viewing the drawing) is rotated at 90° in a counterclockwise direction so that the contact surface thereof moves to a portion of the inner surface of the lower chamber 30 (placed at the lower position when viewing the drawing) which is spaced apart from the uppermost point at 270°.
• the upper rotor unit 200 is rotated in a clockwise direction until it reaches a portion of the upper chamber 30 spaced apart from the uppermost point at 180°.
• the lower rotor unit is rotated in a counterclockwise direction until it reaches a portion of the inner surface of the lower chamber 30 spaced apart from the uppermost point at 180°.
• the upper rotor unit 200 is rotated in a clockwise direction until it reaches a portion of the inner surface of the upper chamber 30 spaced apart from the uppermost point at 270°.
• the lower rotor unit is rotated in a counterclockwise direction until it reaches a portion of the inner surface of the lower chamber 30 spaced apart from the uppermost point at 90°.
• the rotor units 200 are returned to the first stage. This process is continuously repeated.
• the upper rotor unit 200 may be rotated in a counterclockwise direction, and the lower rotor unit 200 may be rotated in a clockwise direction.
• each rotor unit 200 is greatly reduced.
• the lower rotor unit 200 is rotated is a counterclockwise direction and reaches the portion of the inner surface of the lower chamber 30 spaced apart from the uppermost point at 270°.
• the length of the cross-plate is AK. Therefore, as demonstrated in the Pythagorean Theorem in that the length of the hypotenuse of a right-angled triangle is longest, the length of the cross-plate must be lengthened by any method.
• the conventional art has the structure such that the length of the cross-plate is varied while the diameter of the rotor unit 200 is constant.
• an eccentric rotary body 220 is provided in each rotor unit 200, and a space is defined around the eccentric rotary body in the rotor unit 200. The description of these is as follows.
• a drive motor 10 is provided at a predetermined position such that an output shaft 11 thereof is disposed at an eccentric position.
• An overload prevention unit 20 having a helical motor gear 12 is provided on an end of the output shaft 11.
• a clutch unit 100 is provided on an end of the overload prevention unit 20.
• chambers 30 are provided at upper and lower positions.
• the rotor units 200 which receive driving force from the clutch unit 100, are installed in the chambers 30.
• the eccentric rotary body 220 which has a bearing means 210 and is rotated by a rotating shaft Sl or S2, is installed in each rotor unit 200.
• the drive motor 10 is coupled to the pump such that the output shaft 11 thereof is positioned at a side of the center of the pump, that is, is eccentrically positioned with respect to the pump. Furthermore, the helical motor gear 12 is provided on the end of the output shaft to increase rotating friction.
• the clutch unit 100 is coupled to the helical motor gear 12.
• a high-speed clutch unit 100 or a low-speed clutch unit 100 which will be explained later herein, can be selectively provided.
• rotational force of the drive motor 10 is transmitted to the rotating shafts Sl and S2 through the clutch unit 100, after the rotational speed is changed to a high or low speed by the clutch unit 100.
• the eccentric rotary bodies 220 are rotated by the above-mentioned rotational force. At this time, the eccentric rotary bodies 220 can be smoothly rotated by the bearing means 210 during the fluid pumping operation.
• the clutch unit 100 is coupled to the overload prevention unit 20.
• a low-speed drive gear 110 which engages with the helical motor gear 12 that is eccentrically positioned, is fitted over the rotating shaft S2, which is placed at a position opposite the direction in which the helical motor gear 12 is offset.
• the low-speed drive gear 110 is locked to the rotating shaft S2 by a key.
• a first main gear 111 is fitted over the rotating shaft S2 below the low-speed drive gear 110 while being locked to the rotating shaft S2 by a key.
• a second main gear 112 which engages with the first main gear 111, is fitted over the other rotating shaft Sl and locked to the rotating shaft Sl by a key .
• the first main gear 111 is rotated by rotation of the low-speed drive gear 110 at a low speed.
• the second main gear 112, which engages with the first main gear 111, is rotated in an opposite direction.
• the drive motor 10 is provided such that the output shaft 11 thereof is inserted into the pump at an offset position, in detail, at a position offset towards the upper rotor unit 200 (located on the right when viewing the drawing) .
• the output shaft 11 may be eccentrically placed such that it is offset towards the lower rotor unit 200 (located on the left when viewing the drawing) .
• the reason that the output shaft 11 is placed such that it is offset towards the upper rotor unit 200 is to construct the present invention such that the rotational speed of the rotating shafts can be changed to a high or low speed. If the output shaft 11 is offset towards the upper rotor unit 200, a space defined between the output shaft 11 and the lower rotor unit 200 (located on the left when viewing the drawing) is greater than a space defined between the output shaft 11 and the upper rotor unit 200.
• the gear having a larger diameter can be applied in the larger space.
• the low-speed drive gear 110 is rotated at a low speed.
• the low-speed drive gear 110 having the large diameter, is rotated at a low speed.
• the rotating shaft S2 and the low-speed drive gear 110 are rotated at the same angular speed.
• the first main gear 111 is locked to the rotating shaft S2 by the key K below the low-speed drive gear 110. Therefore, revolutions of the low-speed drive gear 110 are also the same as that of the rotating shaft S2.
• the second main gear S2 which engages with the first main gear Sl, is locked to the other rotating shaft Sl by the key.
• the pump of the present invention may be used for pumping air as well as fluid, that is, may be applied to a pneumatic compressor.
• FIG. 6 illustrates a high-speed type of a second embodiment of the clutch unit 100 of the present invention.
• a high-speed drive gear 120 is provided at the narrower side in the spaces defined between the rotating shafts and the output shaft of the drive motor 10, which is offset to the right when viewing the drawing.
• This gear has a small diameter so that it can be rotated at a high speed.
• the high-speed drive gear 120 which engages with the helical motor gear 12 that is eccentrically positioned, is fitted over the rotating shaft Sl, which is placed at a predetermined position in the direction in which the helical motor gear 12 is offset.
• the high-speed drive gear 120 is locked to the rotating shaft Sl by a key.
• a first main gear 121 is fitted over the rotating shaft Sl below the high-speed drive gear 120 while being locked to the rotating shaft S2 by a key.
• a second main gear 122 which engages with the first main gear 121, is fitted over the other rotating shaft S2 and locked to the rotating shaft S2 by a key.
• the first main gear 121 is rotated by rotation of the high-speed drive gear 120 at a high speed.
• the second main gear 122 which engages with the first main gear 121, is rotated in an opposite direction.
• the rotational speed of the high-speed drive gear 120 is slower than that of the output shaft of the drive motor 10.
• the upper rotating shaft Sl placed to the right when viewing the drawing
• the first main gear 121 is rotated at the same speed as that of the rotating shaft Sl.
• the rotating shaft S2 is also rotated at the same angular speed as that of the second main gear 122.
• the rotor units 200 which are coupled to the ends of the rotating shafts and form a single or multiple structure, are rotated by the rotation of the rotating shaft S2, thus executing the pumping operation.
• a third embodiment of the clutch unit 100 of the present invention will be explained herein below with reference to FIG. 7.
• a first gear 131 which engages with the helical motor gear 12 that is eccentrically positioned, is rotatably fitted over the rotating shaft S2, which is placed at a position opposite the direction in which the helical motor gear 12 is offset.
• a first subsidiary gear 132 having a diameter smaller than that of the first gear 131, is integrally provided beneath the first gear 131.
• a second gear 133 which has a relatively large diameter and engages with the first subsidiary gear 132, is rotatably fitted over the other rotating shaft Sl.
• a second subsidiary gear 134 having a diameter smaller than that of the second gear 133, is integrally provided beneath the second gear 133.
• a fifth gear 139 which has a relatively large diameter and engages with the fourth subsidiary gear 138, is rotatably fitted over the rotating shaft S2.
• a fifth subsidiary gear 140 having a diameter smaller than that of the fifth gear 139, is integrally provided beneath the fifth gear 139.
• a drive gear 144 which has a relatively large diameter and engages with the fifth subsidiary gear 140, is fitted over the rotating shaft Sl and locked to the rotating shaft Sl by a key K.
• first and second main gears 145 and 146 having the same diameter, are respectively fitted over and locked to the rotating shafts Sl and s2 using keys.
• first, second, third, fourth and fifth gears 131, 133, 135, 137 and 139 and the first, second, third, fourth and fifth subsidiary gears 132, 134, 136, 138 and 140 are fitted over the first and second shafts Sl and S2, bearings B are interposed between them such that the gears are smoothly rotated at low speeds with respect to the rotating shafts.
• the first and second main gears 145 and 146 are rotated at low speeds by the rotational force transmitted through the drive gear 144, thus rotating the rotor units 200 at low speeds.
• the first subsidiary gear 132 is integrally provided beneath the first gear 131.
• the first subsidiary gear 132 has a diameter smaller than the diameter of the first gear 131.
• the first subsidiary gear 132 engages with the second gear 133 fitted over the upper rotating shaft Sl (located on the right side when viewing the drawing) .
• the first subsidiary gear 132 has a relatively small diameter, and the diameter of the second gear 133 is larger than that of the first subsidiary gear 132. Hence, when the rotational force is transmitted from the first subsidiary gear 132 to the second gear 133, the number of revolutions decreases.
• the second subsidiary gear 132 is integrally provided beneath the second gear 133.
• the gears are integrated with each other, so that revolutions thereof are equal to each other.
• the second subsidiary gear 132 engages with the third gear 135 fitted over the rotating shaft S2.
• the third gear 135 has the diameter larger than that of the second subsidiary gear 132, so that the rotational speed is reduced when the rotational force is transmitted.
• the third subsidiary gear 136 having the diameter smaller than that of the third gear 135, is integrally provided beneath the third gear 135.
• the third gear 135 and the third subsidiary gear 136 are integrated with each other, revolutions thereof are equal to each other.
• the above-mentioned gear coupling structure is also applied throughout the fourth gear 137, the fourth subsidiary gear 138, the fifth gear 139 and the fifth subsidiary gear 140, so that the rotational speed is sequentially reduced.
• the fifth subsidiary gear 137 engages with the drive gear 144 having a relatively large diameter. The drive gear 144 is locked to the rotating shaft Sl.
• the right rotating shaft Sl is rotated by the rotation of the drive gear 144.
• bearings B are provided around the rotating shafts in the first, second, third, fourth and fifth gears 131, 133, 135, 137 and 139 and the first, second, third, fourth and fifth subsidiary gears 132, 134, 136, 138 and 140, they are smoothly rotated with respect to the rotating shaft to execute the functions of the speed reduction.
• the rotating shaft Sl is rotated only by rotation of the drive gear 144.
• the first main gear 145 which is located on the right (when viewing the drawing) , is rotated.
• the number of revolutions of the first main gear 145 is equal to those of the drive gear 144 and the upper rotating shaft Sl. Furthermore, the first main gear 145 engages with the second main gear 146. Hence, the second main gear 146 is rotated by the rotation of the first main gear 145 in a direction opposite that of the first main gear 145.
• the second main gear 146 is locked to the lower rotating shaft Sl by a key, so that the lower rotating shaft S2 is also rotated at the same rotational speed as that of the second main gear 146.
• the rotor units 200 which are coupled to the rotating shafts Sl and S2, are rotated by the rotation of the rotating shafts Sl and S2, thus executing the fluid pumping operation.
• sixth through eleventh gears and subsidiary gears may be additionally provided beneath the fifth gear 139 and the fifth subsidiary gear 140. That is, other gears may be provided in the clutch unit 100 in the same manner as the above-mentioned gear coupling structure. Then, the rotational speed can be further reduced while the rotational force is transmitted.
• the clutch unit 100 may be a structure in which the number of gears is less than the above embodiment, so as to reduce the degree of speed reduction.
• FIG. 8 A fourth embodiment of the clutch unit 100 of the present invention is shown in FIG. 8.
• a first gear 150 which engages with the helical motor gear 12 that is eccentrically positioned, is rotatably fitted over the rotating shaft S2, which is located at a position opposite the direction in which the helical motor gear 12 is offset.
• a first subsidiary gear 151 having a diameter larger than that of the first gear 150, is integrally provided beneath the first gear 150.
• a second gear 152 which has a relatively small diameter and engages with the first subsidiary gear 151, is rotatably fitted over the other rotating shaft Sl.
• a second subsidiary gear 153 having a diameter larger than that of the second gear 152, is integrally provided beneath the second gear 152.
• a third gear 154 which has a relatively small diameter and engages with the second subsidiary gear 153, is rotatably fitted over the rotating shaft S2.
• a third subsidiary gear 155 having a diameter larger than that of the third gear 154, is integrally provided beneath the third gear 154.
• a fourth gear 156 which has a relatively small diameter and engages with the third subsidiary gear 155, is rotatably fitted over the rotating shaft Sl.
• a fourth subsidiary gear 157 having a diameter larger than that of the fourth gear 156, is integrally provided beneath the fourth gear 156.
• a drive gear 158 which has a relatively small diameter and engages with the fourth subsidiary gear 157, is fitted over and locked to the rotating shaft S2 by a key K.
• first, second, third and fourth gears 150, 152, 154 and 156 and the first, second, third and fourth subsidiary gears 151, 153, 155 and 157 are fitted over the first and second shafts Sl and S2, bearings B are interposed between them such that the gears are smoothly rotated at high speeds with respect to the rotating shafts.
• the first and second main gears 160 and 161 are rotated at high speeds by the rotational force transmitted through the drive gear 158, thus rotating the rotor units 200 at high speeds .
• the first gear 150 is rotatably fitted over the lower rotating shaft S2 (located on the left when viewing the drawing) , and the first subsidiary gear 151, having a diameter smaller than that of the first gear 150, is integrally provided beneath the first gear 150.
• the first subsidiary gear 151 is rotated along with the first gear 150.
• the revolutions thereof are equal to each other.
• the second gear 152 which is fitted over the upper rotating shaft Sl (located on the right when viewing the drawing) , is rotated by the rotation of the first subsidiary gear 151.
• the second subsidiary gear 153 having a relatively large diameter, is integrated with the second gear 152, the number of revolutions of the second subsidiary gear 153 is equal to the number of revolutions of the second gear 152.
• the third gear 154 is rotatably fitted over the lower rotating shaft S2.
• the third subsidiary gear 155 having a large diameter is integrated with the third gear 154, so that their revolutions are equal to each other.
• the fourth gear 156 which is rotatably fitted over the upper rotating shaft Sl, engages with the third subsidiary gear 155.
• the rotational speed is increased when the power is transmitted between them.
• the fourth subsidiary gear 157 having a large diameter, is integrated with the fourth gear 156, so that the fourth gear 156 and the fourth subsidiary gear 157 are rotated at the same angular speed.
• the fourth subsidiary gear 157 engages with the drive gear 158 which has a small diameter and is locked to the lower rotating shaft S2 by the key. Therefore, the power is transmitted from the fourth subsidiary gear 157 having a large diameter to the drive gear 158 having a small diameter, so that the rotational speed is changed to high speed. Because the drive gear 158 is locked to the lower rotating shaft S2 (placed at the lower position when viewing the related drawing) by the key K, the rotating shaft S2 is rotated along with the drive gear 158.
• the first main gear 160 which is coaxial with the drive gear 158, is locked to the rotating shaft S2 by the key K, so that they are rotated at the same angular speed.
• the first main gear 160 engages with the second main gear 161, and the first and second main gears 160 and 161 have the same diameter.
• the second main gear 161 is rotated by rotation of the first main gear 160. At this time, they are rotated in directions opposite each other. Furthermore, because the second main gear 161 is locked to the rotating shaft Sl by the key K, the rotating shaft Sl is rotated by the rotation of the second main gear 161. As a result, the rotational speed of the rotating shaft S2 is changed to high speed by the clutch unit 100 of the fourth embodiment.
• the rotating shaft S2 rotates the rotor units 200 of the lower ends of the rotating shafts Sl and S2 in the state of being rotated at a high speed.
• first, second, third and fourth gears 150, 152, 154 and 156 and the first, second, third and fourth subsidiary gears 151, 153, 155 and 157 are rotatably coupled to the rotating shafts through the bearings B, thus executing only the function of a change of speed.
• fifth through tenth gears and subsidiary gears may be additionally provided below the fourth gear 156 and the fourth subsidiary gear 157 of FIG. 8 to further increase the rotational speed of the rotating shafts.
• the clutch unit 100 of the present invention has been explained.
• the rotor units 200 which are rotated by rotation of the rotating shafts Sl and S2 changed in speed by the clutch 100 and thus execute a function of pumping fluid, will be described in detail.
• the rotor unit 200 can be manufactured in shapes of two types of embodiments. A first embodiment of the rotor unit 200 is shown in FIGS. 9 through 12. A second embodiment of the rotor unit 200 is shown in FIGS. 15 and 16. First, the rotor unit 200 according to the first embodiment will be explained herein below.
• each rotor unit 200 of the present invention includes a cylindrical housing 230 which has a cylindrical shape with a diameter smaller than an inner diameter of the chamber 30.
• a plurality of bearing seats 231 is formed in a circumferential inner surface of the cylindrical housing 230.
• a space 235 is defined in the cylindrical housing 230.
• Each rotor unit 200 further includes an eccentric rotary body 220 which has a diameter smaller than the inner diameter of the cylindrical housing 230 and is eccentrically fitted over the rotating shaft Sl or S2.
• a bearing means 210 is seated into each bearing seat 231 of the cylindrical housing 230.
• Both the cylindrical housing 230 and the eccentric rotary body 220 are provided in each of the upper and lower chambers 30.
• the two cylindrical housings 230 are coupled to each other through a cross-plate 207 and are eccentrically rotated.
• each of the rotor units 200 comprises the cylindrical housing 230, the eccentric rotary body 220 and the bearing means 210 provided in the cylindrical housing 230, such that the two rotor units 200 are placed in the respective chambers 30.
• the rotor units 200 are placed in the chambers 30 which communicate with an inlet BC and an outlet BD are formed.
• Each chamber 30 has a genuine circular cross- section.
• Each of the rotor units has the plurality of bearing seats 231.
• Needle roller bearings or ball bearings are seated into the bearing seats 231 such that the rotor unit 200 is smoothly eccentrically rotated.
• the eccentric rotary bodies 220 of the rotor units 200 are fitted over the respective rotating shafts Sl and S2, which are coupled to the clutch unit 100.
• each eccentric rotary body 220 is eccentrically fitted over each rotating shaft Sl, S2 but not coaxially fitted over it.
• the eccentric rotary bodies 220 move along the circumferential inner surfaces of the chambers 30 in order to draw and discharge fluid into and from the pump.
• each rotating shaft Sl, S2 is coaxially provided in each chamber 30, and each eccentric rotary body 220 is eccentrically fitted over each rotating shaft Sl, S2.
• a moving track of a portion of the eccentric rotary body 220 which is farthest from the rotating shaft is configured in a predetermined shape. That is, the moving track is formed along the circumferential inner surface of the chamber 30.
• the needle roller bearings or ball bearings are seated into the bearing seats 231 formed in the circumferential inner surface of the cylindrical housing
• the circumferential outer surface of the eccentric rotary body 220 is in rolling contact with the needle roller bearings or ball bearings, while the eccentric rotary body 220 is rotated. Meanwhile, the eccentric rotary body 220 is provided in each of the upper and lower rotor units 200.
• the eccentric rotary body 220 fitted over the upper rotating shaft Sl is also rotated in a clockwise direction, as shown in FIGS. 9 and 10.
• the lower eccentric rotary body 220 is rotated in a counterclockwise direction, so that the contact surface of the lower rotor unit 200 moves to a portion of the inner surface of the lower chamber 30 which is in a 9 o'clock direction, that is, the portion angularly spaced apart from the uppermost point at 270°.
• the contact surface of the upper rotary unit 200 moves to the lowermost portion of the upper chamber 30 which is in a 6 o'clock direction, that is, the portion angularly spaced apart from the uppermost point at 180°.
• the lower eccentric rotary body 220 is also further rotated in a counterclockwise direction, so that the contact surface of the lower rotary unit 200 moves to a portion of the inner surface of the lower chamber 30 which is in a ⁇ o'clock direction, that is, the portion angularly spaced apart from the uppermost point at 180° (see, the first view of FIG. 10) .
• the contact surface of the upper rotary unit 200 moves to the lowermost portion of the upper chamber 30 which is in a 9 o'clock direction, that is, the portion angularly spaced apart from the uppermost point at 270°.
• the lower eccentric rotary body 220 is also further rotated in a counterclockwise direction, so that the contact surface of the lower rotary unit 200 moves to a portion of the inner surface of the lower chamber 30 which is in a 3 o'clock direction, that is, the portion angularly spaced apart from the uppermost point at 90°.
• the process is returned to the first step. As such, the process is continuously repeated, so that fluid is pumped by movement of the rotor units 200.
• the distance between the contact point between the upper eccentric rotary body 220 and the upper cylindrical housing 230 and the contact point between the lower eccentric rotary body 220 and the lower cylindrical housing 230 is shortest, as described above with reference to FIG. 4.
• the distance between the rotating shafts Sl and S2, over which the eccentric rotary bodies 220 are fitted, are constant without being varied.
• the contact points between the eccentric rotary bodies 220 and the cylindrical housings 230 of the upper and lower rotor units 200 are farthest away from each other.
• the present invention is designed such that the diameter of each eccentric rotary body 220 is smaller than the inner diameter of each cylindrical housing 230.
• the space 235 is defined between them such that the eccentric rotary body 220 is movable in the space 235.
• the distance difference is compensated for by the space 235 while each eccentric rotary body is rotated in the space 235 of each cylindrical housing 230.
• the bearing seats 231 are formed in the inner surface of the cylindrical housings 230, and it is constructed such that the bearing seats 231 have different depths.
• the bearing seats 231 are symmetrically formed along the inner surface of the cylindrical housing 230 and have different depths which are deeper in the order of Gxa ⁇ G3a ⁇ G2a ⁇ GIa ⁇ Gya.
• the bearing seat Gya which is formed at the uppermost position of the cylindrical housing 230, is deepest.
• the bearing seat GIa which is formed at a position spaced apart from the uppermost position at a predetermined angular interval, is shallower than the bearing seat Gya.
• the depths of the remaining bearings are shallower in the order of G2a > G3a > Gxa.
• a track along which the eccentric rotary body 220 contacts the ball bearings or needle roller bearings protruding from the inner surface of the cylindrical housing 230, has at an upper portion thereof an elliptical shape and at a lower portion thereof a circular shape having a relatively small curvature, as shown in FIG. 13.
• the rotor unit 200 moves while the distance difference induced in the cross-plate 207 of the rotor unit 200 is compensated for by the space 235 defined in the rotor unit 200.
• the eccentric rotary body 220 is placed at positions corresponding to the bearing seats Gxa, in other words, when the eccentric rotary body 220 is placed in between a 3 o'clock direction and a 9 o'clock direction, the eccentric rotary body 220 contacts the ball bearings or needle roller bearings which protrude to greater heights from the inner surface of the cylindrical housing 230.
• the bearing seats Gya, GIa, G2a, G3a and Gxa are symmetrical with each other based on a Y-axis.
• the bearing seats formed at an upper portion are symmetrical based on the Y-axis, and the remaining bearing seats Gxa formed at a lower portion have the same depth.
• the bearing seats are formed in shapes and to depths shown in FIG. 11.
• the above-mentioned effect may be realized both by bearing seats, having different diameter, and by ball bearings, which have the diameters corresponding to the bearing seats and are seated into the bearing seats.
• the bearing seats 231 have different diameters which are larger in the order of
• each bearing means which is seated into each bearing seat, has the same diameter as that of the associated bearing seat.
• each bearing means such as ball bearings or needle roller bearing, protrudes from the bearing seat is varied depending on the diameter of the bearing means.
• the heights at which the ball bearings protrude are higher in the same order as that of the bearing seats, the diameters of which are larger in the order of Mya ⁇ MIa ⁇ M2a ⁇ M3a ⁇ Mxa.
• bearing means 210 may be seated into the bearing seats 231.
• ball bearings or needle roller bearings may be used as the bearing means 210.
• each bearing seat 2321 If ball bearings are used as the bearing means, a plurality of ball bearings is seated into each bearing seat 231. If needle roller bearings, each having a predetermined length, are used as the bearing means, a single needle roller bearing is seated into each bearing seat 231.
• the ball bearings be used for pumping fluid, such as water having a low viscosity
• the needle roller bearings be used for pumping fluid, such as mud having a high viscosity
• each rotor unit 200 includes a cylindrical housing 230 which has a cylindrical shape with a diameter smaller than an inner diameter of the chamber 30.
• a space 260 is defined in the cylindrical housing 230.
• Each rotor unit 200 further includes an eccentric rotary body 220 which has a diameter smaller than the inner diameter of the cylindrical housing 230 and is eccentrically fitted over the rotating shaft Sl or S2.
• a plurality of bearing seats 271 is formed in a circumferential outer surface of each eccentric rotary body 220.
• a bearing means 210 is seated into each bearing seat 271 of the eccentric rotary body 220.
• Both the cylindrical housing 230 and the eccentric rotary body 220 are provided in each of the upper and lower chambers 30.
• the two cylindrical housings 230 are coupled to each other through a cross-plate 207 and are eccentrically rotated.
• the general construction of the rotor unit 200 according to the second embodiment, except for the bearing seats formed in the circumferential outer surface of the eccentric rotary body 220, remains the same as the rotor unit 200 according to the first embodiment.
• the bearing means 210 is seated into each bearing seat 271 of the eccentric rotary bodies 220.
• the bearing means 210 serves to ensure smoother rotation of each eccentric rotary body 220 in each cylindrical housing 230.
• the bearing seats 271 are symmetrically formed in the outer surface of the eccentric rotary body 220 and have different depths, which are deeper in the order of Fya ⁇ F3a ⁇ F2a ⁇ FIa ⁇ Fxa.
• the bearing seats 271 are formed along the circumferential outer surface of the eccentric rotary body 220 and spaced apart from each other at regular angular intervals. As shown in FIG. 16, of the bearing seats 271, the bearing seats Fxa are deepest.
• bearing seats Fxa which are formed at positions spaced apart from the uppermost point at 90°, are deepest.
• the remaining bearing seats which are formed at positions spaced apart from each other at regular angular intervals, are shallower in the order of FIa > F2a > F3a > Fya.
• the bearing seats Fxa are deepest, and the bearing seats Fya are shallowest.
• each bearing seat 271 which are formed in the outer surface of the eccentric rotary body 220 at symmetrical positions based on the center of the eccentric rotary body 220 (at positions spaced apart from each other at 180°), have the same depth. Therefore, when the bearing means 210 is seated into each bearing seat 271, it is configured in a shape shown in FIG. 15.
• the protruding height of the bearing means (the ball bearings or the needle roller bearing) , which is seated into the bearing seat Fxa which is in a 3 o'clock direction, that is, formed in the eccentric rotary body 220 at a position spaced apart from the uppermost point at 90°, is lowest.
• the protruding height of the bearing means 210 (the ball bearings or the needle roller bearing) , which is seated into the bearing seat Fya which is in a 12 o'clock direction, that is, formed in the eccentric rotary body 220 at the uppermost position, is highest.
• FIG. 17 a modification of the second embodiment is shown in FIG. 17.
• This modification in which bearing seats have different diameters and bearing means seated into the bearing seats also have different diameters, has the same effect as that of the second embodiment.
• This modification is as follows.
• the bearing seats 271, which are formed in each eccentric rotary body, have diameters which are larger in the order of Nya ⁇ NIa ⁇ N2a ⁇ N3a ⁇ Nxa.
• Each bearing means, which is seated into each bearing seat has the same diameter as that of the associated bearing seat.
• the bearing seats are symmetrically formed along the circumferential outer surface of the eccentric rotary body.
• This modification has the same outline as that of the above-mentioned embodiment and, thus, the effect thereof is also equal to the above-mentioned embodiment.
• the outline of the eccentric rotary body which is defined by the bearing means will be explained herein below.
• the outline of the eccentric rotary body which is defined by connecting the outermost points of the ball bearings or needle roller bearings that protrude from the bearing seats 271, is configured in an elliptical shape.
• the eccentric rotary body 220 having the elliptical outline is eccentrically fitted over the rotating shaft, which is rotated in place.
• the ball bearings or needle roller bearing which is seated into the uppermost bearing seat Fya, mainly contacts the inner surface of the cylindrical housing.
• the eccentric rotary body When the eccentric rotary body is rotated at 90° and thus enters the state of the second view of FIG. 18, it is configured in an elliptical shape having a horizontal major axis.
• the bearing seat Fya has the shallowest depth, the height at which the ball bearings or needle roller bearing protrudes from the bearing seat is highest. Thereby, when the eccentric rotary body is in the above- mentioned state, the eccentric rotary body most securely pushes downwards the cylindrical housing.
• the eccentric rotary body serves to reliably close the passage formed below it, thus maximizing the pumping performance of the pump.
• ball bearings or needle roller bearings can be used as the bearing means 210 according to the second embodiment, in the same manner as that of the first embodiment. Furthermore, it is preferred that angular intervals, at which the ball bearings or needle roller bearings are spaced apart from each other, are determined depending on a difference between the diameter of the space 235 of the cylindrical housing 230 and the outer diameter of the outline of the eccentric rotary body 220. To easily illustrate this concept, FIG. 19 shows the elements with an exaggerated size difference between them.
• the contact points P and T are very close.
• the diameter of the eccentric rotary body 220 becomes smaller, the distance between the contact points is reduced.
• the diameter of the eccentric rotary body 220 is large to the degree similar to the size of the space 235 of the cylindrical housing 230, when the eccentric rotary body 220 is rotated along the inner surface of the cylindrical housing 230 from the state in which the uppermost ball bearing or needle roller bearing P contacts the inner surface of the cylindrical housing 230, a subsequent contact point becomes the point T of FIG. 20.
• the distance between the adjacent contact points P and T is increased compared to the case of FIG. 19.
• the number of required ball bearings or needle roller bearings is increased.
• the number of required ball bearings or needle roller bearings is reduced.
• the chamber 30 have a multiple structure, as shown in FIGS. 21 through 29. That is, in the present invention, one through ten pairs of upper and lower chambers 30, each having the rotor unit 200 therein, may be constructed in a row to form a multiple structure.
• ⁇ multiple structure' means that several rotor units 200 and chambers 30 may be provided on each of the upper and lower rotating shafts .
• a plurality of chambers 30 is disposed in a row. Separation plates are interposed between the chambers 30, so that the chambers 30 are divided.
• the upper rotors units 200 and the lower rotor units 200, which are provided in the chambers 30, are respectively fitted over the single upper rotating shaft Sl and the single lower rotating shaft S2.
• the upper rotors units 200 and the lower rotor units 200, which are fitted over the upper and lower rotating shafts Sl and S2 and are provided in the chambers 30, are arranged such that they differ in phase.
• the upper and lower rotating shafts Sl and S2 receive power from the drive motor through the clutch unit.
• Each of the upper and lower rotor units 200 has the structure of the rotor unit 200 described above according to the first or second embodiment .
• the multiple rotary pump of the present invention because no torsional stress is applied to the upper rotating shaft Sl and the lower rotating shaft S2, even when the upper and lower rotor units 200, which are respectively provided on the upper and lower rotating shafts Sl and S2 and have different phases, are rotated, they are not damaged. Furthermore, even if the upper and lower rotating shafts Sl and S2 are rotated at high speeds, because they are stable, the upper and lower rotor units 200 can be stably rotated at high speeds.
• manifolds may be coupled to inlets BC and outlets BD of the chambers 30.
• a mixture ratio of two or more kinds of fluid, which is drawn into the chambers 30 and discharge from the chambers 30, can be controlled.
• a first manifold CQ is coupled to inlets BC of first, second and third chambers CA, CB and CC, and a separate inlet pipe CF is coupled to an inlet BC of a fourth chamber CD.
• objective fluid is drawn into the first, second and third chambers CA, CB and CC through the first manifold, while diluent (water or chemical) is drawn into the fourth chamber CD through the inlet pipe.
• diluent water or chemical
• Both the objective fluid and the diluent are discharged from the chambers 30 through a second manifold CT coupled to the outlets of the chambers 30. Therefore, a mixture ratio of diluent to objective fluid to be discharged through the second manifold CT can be constantly controlled.
• the multiple rotary pump may be constructed such that a third manifold DA is coupled to the inlets of the first and second chambers CA and CB and a fourth manifold DB is coupled to the inlets of the third and fourth chambers CC and CD.
• the reference character CT denotes a second manifold coupled to the outlets of the chambers.
• the multiple rotary pump may be constructed such that a fifth manifold FA is coupled to the outlets BD of the first, second and third chambers CA, CB and CC and a separate outlet pipe FB is coupled to the outlet of the fourth chamber CD or, alternatively, a sixth manifold GA is coupled to the outlets BD of the first and second chambers and a seventh manifold GB is coupled to the outlets BD of the third and fourth chambers CC and CD.
• the overload prevention unit 20 is provided between the output shaft of the drive motor 10 and the clutch shaft, as shown in FIGS. 4, 5, 6, 30 and 31.
• the overload prevention unit 20 comprises a plurality of ball seats 21, which are formed in a circumferential outer surface of an end of the output shaft of the drive motor 10, and a coupler 24 which is coupled to the clutch unit 100, with a receiving space 22 defined in the coupler 24.
• the output shaft 11 is inserted into the receiving space 22.
• a plurality of ball insertion holes 23 are formed along a sidewall of the coupler 24 at positions corresponding to the ball seats 21.
• a cover ring 26 which is made of synthetic resin, is fitted over a circumferential outer surface of the coupler 24 to prevent balls 25 from being undesirably removed.
• each ball 25 is inserted into each ball insertion hole 23 and seated into each ball seat 21.
• the balls 25 are covered with the cover ring 26.
• the balls 25 are removed from the ball seats while pushing outwards the cover ring 26, thus preventing power from being transmitted.
• the end of the output shaft of the drive motor is tapered, and the ball seats 21 are formed in the circumferential outer surface of the end of the output shaft.
• the helical motor gear 12 is provided on an end of the coupler 24, which has the receiving space 22 into which the end of the output shaft of the drive motor 10 is inserted.
• the coupler 24 reliably couples the drive motor to the clutch unit 100 such that, when the drive motor 10 is rotated, power is securely transmitted.
• the coupler 24 which couples the clutch unit to the output shaft of the drive motor, can no longer rotate and must submit to the overload.
• the overload is increased, the balls push the cover ring 26 made of synthetic resin outwards and are thus removed from the ball seats.
• the present invention can solve a problem of breakage in the clutch unit 100, which has been frequently induced in the conventional pump.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Rotary Pumps (AREA)
• Applications Or Details Of Rotary Compressors (AREA)

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• 2005
  • 2005-11-23 CN CNA2005800484723A patent/CN101124404A/zh active Pending
  • 2005-11-23 EP EP05821225A patent/EP1831549A1/en not_active Withdrawn
  • 2005-11-23 WO PCT/KR2005/003968 patent/WO2006071003A1/en active Application Filing
  • 2005-11-23 US US11/794,459 patent/US20080124228A1/en not_active Abandoned
  • 2005-11-23 KR KR1020050112327A patent/KR100651669B1/ko not_active IP Right Cessation
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