WO2007007975A1 - Volumetric rotary pump - Google Patents

Volumetric rotary pump Download PDF

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Publication number
WO2007007975A1
WO2007007975A1 PCT/KR2006/002637 KR2006002637W WO2007007975A1 WO 2007007975 A1 WO2007007975 A1 WO 2007007975A1 KR 2006002637 W KR2006002637 W KR 2006002637W WO 2007007975 A1 WO2007007975 A1 WO 2007007975A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
subsidiary
fluid
rotating shafts
positive displacement
Prior art date
Application number
PCT/KR2006/002637
Other languages
French (fr)
Inventor
Chang Sik Youn
Original Assignee
Jinmyung21 Co., Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR10-2005-0060971 external-priority
Application filed by Jinmyung21 Co., Ltd filed Critical Jinmyung21 Co., Ltd
Publication of WO2007007975A1 publication Critical patent/WO2007007975A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12Rotary-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
    • F04C2/123Rotary-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 with radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038Shaft sealings specially adapted for rotary-piston machines or pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084Toothed wheels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00Manufacture
    • F04C2230/90Improving properties of machine parts
    • F04C2230/91Coating

Abstract

Disclosed herein is a rotary positive displacement pump for fluid compressors, which is small in size and is suitable for a large quantity of flow and a high head, and which shows excellent performance upon low-speed rotation and high-speed rotation. The pump is suitable for a large quantity of flow and a high head, is capable of moving a large quantity of fluid to a high position, and is operated by varying the volume, so that the pump is operated at high efficiency, thus preventing efficiency from being reduced upon low-speed rotation or high-speed rotation. The pump forms a completely balanced rotating mechanism, thus preventing vibrations from occurring due to unbalanced rotation of components even when rotating at high speed. Further, the pump solves the drawbacks occurring in different kinds of pumps upon both low-speed rotation and high-speed rotation, thus being used for various purposes and showing high performance.

Description

Description
VOLUMETRIC ROTARY PUMP
Technical Field
[1] The present invention relates, in general, to a rotary positive displacement pump and, more particularly, to a rotary positive displacement pump for fluid compressors, which is small in size and is suitable for a large quantity of flow and a high head, and which shows excellent performance upon low-speed rotation and high-speed rotation.
[2]
Background Art
[3] Generally, pumps are machines that are operated by power transmitted from a driving means, such as a motor, thus moving fluid. The pumps are typically classified into non-positive displacement pumps and positive displacement pumps. Non-positive displacement pumps convert energy in an unsealed state. The positive displacement pumps convert energy in a sealed state. Non-positive displacement pumps are constructed so that discharge pressure is reduced as the discharge quantity increases. Non-positive displacement pumps include a centrifugal pump, a diagonal flow pump, an axial flow pump, etc. according to the mechanism and construction. Meanwhile, the positive displacement pumps are constructed so that the discharge quantity is almost constant regardless the loading pressure, and include a piston pump, a plunger pump, a gear pump, a screw pump, a vane pump, etc.
[4] The positive displacement pump includes a cylinder which is provided with an intake valve and a discharge valve and has a predetermined volume. As a piston, a plunger, or a bucket rectilinearly reciprocates in the cylinder, a vacuum is created in the cylinder, thus drawing liquid into the cylinder. A required pressure acts on the liquid through the change in volume, thus providing static pressure energy to liquid and supplying the liquid.
[5] A rotary positive displacement pump is constructed such that a special type of rotor rotates in a casing. A gear pump, a vane pump, and a screw pump are kinds of rotary positive displacement pumps. The gear pump is operated such that meshed gears rotate in a casing, thus delivering liquid trapped between teeth of the gears and the wall of the casing from an intake pipe to a discharge pipe. The gear pump is usually used for moving oil, and has a small quantity of flow, but achieves pressure up to 25 to 30 MPa. The vane pump is operated such that moving vanes are moved in a radial direction by the rotation of a rotor, thus delivering liquid, in the same manner as the gear pump. The vane pump achieves pressure up to 40 MPa. The screw pump is operated by the engagement and rotation of two or three screw rods. The vane pump is usually used for moving oil, and can achieve pressure up to 20MPa.
[6] The conventional rotary positive displacement pump includes a lobular pump which delivers liquid according to the same principle as the gear pump. The lobular pump may be a gear pump, the teeth of which are reduced in number. In the lobular pump, rotors are engaged with each other such that one rotor cannot rotate the opposite rotor. Thus, the rotors are driven by an additional gear.
[7] The conventional rotary positive displacement pump can achieve a high head coefficient, and perform its original function even at a low speed. However, the conventional rotary positive displacement pump is problematic in that the quantity of flow is small, efficiency is lowered when it rotates at low speed, and noise and abrasion of the gear may occur during high-pressure and high-speed rotation.
[8] Thus, a high-performance pump which is capable of achieving a large quantity of flow, a high head, and high efficiency during both low-speed rotation and high-speed rotation is required.
[9] In order to satisfy the above-mentioned conditions, Korean Patent No. 127650 proposed a rotary positive displacement pump, which was invented by the same inventor, and which has already been registered. However, the rotary positive displacement pump is problematic in that efficiency is low due to lack of flow, shocks are applied to a casing when the rotor rotates, and the sealing ability thereof is poor. Thus, the present invention intends to improve on the patent, thus providing a rotor for a rotary positive displacement pump which is more efficient.
[10]
Disclosure of Invention
Technical Problem
[11] Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and an object of the present invention is to provide a rotary positive displacement pump for fluid compressors, which is small in size and is suitable for a large quantity of flow and a high head, and which shows excellent performance upon both low-speed rotation and high-speed rotation.
[12] Another object of the present invention is to provide a rotary positive displacement pump, which is suitable for a large quantity of flow and a high head, is capable of moving a large quantity of fluid to a high position, and is operated by varying the volume, so that the pump is operated at high efficiency, thus preventing efficiency from being reduced upon low-speed rotation or high-speed rotation, and which forms a completely balanced rotating mechanism, thus preventing vibrations from occurring due to unbalanced rotation of components even when rotating at high speed.
[13] A further object of the present invention is to provide a rotary positive displacement pump, which solves the drawbacks occurring in different kinds of pumps upon both low-speed rotation and high-speed rotation, thus being used for various purposes and showing high performance. Thus, the pump of this invention is usefully applied to various fluid machines which are small and require high performance.
[14]
Technical Solution
[15] In order to accomplish the objects, the present invention provides a rotary positive displacement pump, including a first cover unit having a fastening hole, with inlet space being defined in the first cover unit and an inlet port being defined in a center of the first cover unit; a subsidiary cover having a fastening member which is fastened to the fastening hole of the first cover unit via a pin or a bolt, with branch inlet ports being provided on upper and lower portions of the subsidiary cover and space being defined inside an inner wall such that ends of rotating shafts are inserted into the space; a main body having a rotor mounting hole in which a main rotor and a subsidiary rotor are mounted, with branch inlet ports and branch outlet ports being formed in left and right sides of upper and lower portions of the rotor mounting hole, and an O-ring seat being provided outside the rotor mounting hole; a second cover unit having a plurality of shaft holes in which the rotating shafts are inserted, with a bearing being installed in each of the shaft holes, the second cover having space therein for receiving power transmission means; the power transmission means including a first gear member fitted over a main shaft so as to transmit power to the rotating shafts mounted to the main rotor and the subsidiary rotor, and a second gear member and a third gear member engaging with the first gear member and mounted to the corresponding rotating shafts; the main rotor and the subsidiary rotor each having a rotor body mounted to each of the shafts rotating in a center of the main body, division protrusions provided on an outer circumferential surface of the rotor body and coated with an elastic material, and grooves formed between the division protrusions, with a plurality of leakage preventing protrusions being formed on the division protrusions at regular intervals; a sealing means including a sealing member which has a support metal ring provided in the main body through which the rotating shafts pass and which is embedded in a rubber rib, the rubber rib being provided with a cylindrical extension part, a spacer contacting the sealing member to discharge pressure fluid to the inlet port, and a plate being made of a metal material to prevent the removal of the sealing member and the spacer, and having a through hole for each of the rotating shafts to pass therethrough, the sealing member, the spacer, and the plate being sequentially coupled to each other; an oil pumping means including a body having a mounting hole which is formed at a predetermined position in the body such that the oil pumping means is mounted to the main body through the hole to surround an engaged part of the gear members which are mounted to the rotating shafts of the main rotor and the subsidiary rotor and transmit power, a fluid guide provided on a lower surface of the body, wings integrally provided on both sides of the body, and a fluid outlet hole formed in one of the wings in such a way as to be aligned with the center of the fluid guide; and a pressure maintaining means including a regulator screwed into an insert hole of the main body, an operator operated by a predetermined pressure, and a spring elastically installed between the regulator and the operator.
[16]
Brief Description of the Drawings
[17] FIG. 1 is an exploded perspective view showing the construction of a rotary positive displacement pump, according to the present invention;
[18] FIG. 2 is a side sectional view showing the construction of the rotary positive displacement pump, according to the present invention;
[19] FIG. 3 is a front view showing the coupling structure of a main body and rotors, which are important parts of the invention;
[20] FIG. 4 is a perspective view showing the construction of a main rotor and a subsidiary rotor, which are important parts of the invention;
[21] FIG. 5 is a sectional view showing the coupling construction of the rotors;
[22] FIGS. 6 to 9 are sectional views showing leakage preventing protrusions formed on the main rotor and the subsidiary rotor, according to several embodiments of the present invention;
[23] FIGS. 10 to 13 are views illustrating other installation structures of the main rotor and the subsidiary rotors, which are important parts of the present invention;
[24] FIG. 14 is a sectional view showing an installation structure of a sealing means, which is an important part of the present invention;
[25] FIG. 15 is a perspective view showing the construction of a spacer;
[26] FIGS. 16 and 17 are sectional views showing the operation of the sealing means;
[27] FIG. 18 is a perspective view showing the construction of an oil pumping means, which is an important part of the present invention;
[28] FIG. 19 is a view showing the operation of the oil pumping means;
[29] FIG. 20 is an exploded perspective view showing a pressure maintaining means, which is an important part of the present invention;
[30] FIG. 21 is a sectional view showing the operation of the pressure maintaining means; and
[31] FIG. 22 is a sectional view showing the operation of the rotary positive displacement pump, according to the present invention. [32]
Mode for the Invention
[33] Hereinafter, the preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
[34] FIG. 1 is an exploded perspective view showing the construction of a rotary positive displacement pump, according to the present invention, and FIG. 2 is a side sectional view showing the construction of the rotary positive displacement pump, according to the present invention. Referring to the drawings, the rotary positive displacement pump 1 of this invention includes a first cover unit 10, a subsidiary cover 10a, a main body 30, a second cover unit 40, a power transmission means 50, a main rotor 61 and subsidiary rotors 62, a sealing means 70, an oil pumping means 80, and a pressure maintaining means 20. The first cover unit 10 has an inlet port 12 for supplying fluid, and the subsidiary cover 10a feeds the fluid to the space in which the rotors are installed. The main body 30 compresses the supplied fluid such that the fluid has a predetermined pressure. The second cover unit 40 temporarily stores the fluid fed through the subsidiary cover 10a. The power transmission means 50 functions to rotate the rotating shafts and the rotors. The main rotor 61 and the subsidiary rotors 62 compress the fed fluid, thus providing pressure to the fluid. The sealing means 70 returns lubricating oil which flows along the rotating shafts, thus preventing sticking and leakage. The oil pumping means 80 forcibly circulates the lubricating oil to bearings which support the rotating shafts, which rotate at high speeds. Further, the pressure maintaining means 20 keeps the pressure in the pump constant even when fluid is not being discharged.
[35] The first cover unit 10 includes fastening holes. Inlet space 11 is defined in the first cover unit 10, and the inlet port 12 is formed in the center of the first cover unit 10. The subsidiary cover 10a includes fastening members which are fastened to the fastening holes of the first cover unit 10 using pins or bolts. Branch inlet ports 1 Ia and 11a' are formed in the upper and lower portions of the subsidiary cover 10a, and space 12a is defined inside an inner wall for an end of each rotating shaft 53 to be inserted into the space.
[36] The main body 30 includes a rotor mounting hole 31 in which the main rotor 61 and the subsidiary rotor 62 are mounted. Branch inlet ports 32 and 32a' and branch outlet ports 33 and 33 a' are formed in left and right sides of the upper and lower portions of the rotor mounting hole 31. An O-ring seat is provided outside the rotor mounting hole 31. The branch inlet ports 32 and 32a of the main body are connected to the branch inlet ports 1 Ia and 1 Ia' of the subsidiary cover 10a. The branch outlet ports 33 and 33a are formed independently from the rotor mounting hole 31 and are connected to a discharge port 34.
[37] The second cover unit 40 is provided with a plurality of shaft holes 41 into which the rotating shafts 53 are inserted. The bearings 42 are installed in the corresponding shaft holes 41. Further, space 43 is defined in the second cover unit 40 to receive the power transmission means 50 therein.
[38] As shown in FIGS. 4 and 5, the main rotor 61 includes a rotor body 61a, division protrusions 61b, and grooves 61c, and each subsidiary rotor 62 includes a rotor body 62a, division protrusions 62b, and grooves 62c. The rotor body 61a, 62a is mounted to each rotating shaft 53 which rotates in a center of the main body 30. The division protrusions 61b, 62b are provided on the outer circumferential surface of the rotor body 61a, 62a, and are coated with an elastic material. The grooves 61c, 62c are formed between the division protrusions 61b, 62b. A plurality of leakage preventing protrusions 6 Id, 62d is provided on the division protrusions 61b, 62b at regular intervals.
[39] Meanwhile, as shown in FIGS. 6 to 9, the cross-section of each of the leakage preventing protrusions 6 Id, 62d provided on the main rotor 61 and the subsidiary rotors 62 is selected from among the group consisting of a semicircular cross-section, a triangular cross-section, and a trapezoidal cross-section.
[40] As shown in FIG. 1, the power transmission means 50 includes a first gear member
M-I which is fitted over a main shaft M to transmit power to the rotating shafts 53 to which the main rotor 61 and the subsidiary rotor 62 are secured. The power transmission means 50 also includes a second gear member 51 and a third gear member 52 which engage with the first gear member M- 1 and are mounted to the rotating shafts 53.
[41] As shown in FIGS. 1 and 14, the sealing means 70 includes sealing members 70a, spacer members 70b, and a plate 70c, which are sequentially coupled to each other. Each sealing member 70a includes a support metal ring 71 which is positioned between the main shaft M and the main body 30 through which the rotating shafts 53 pass, and which is embedded in a rubber rib 72, and a cylindrical extension part 72-1 which is provided on the rubber rib 72. Each spacer 70b is in contact with the corresponding sealing member 70a, and discharges oil to the outside. The plate 70c is made of a metal material, and functions to prevent the removal of the sealing members 70a and the spacers 70b, with through holes being formed in the plate 70c such that the rotating shafts 53 can pass through the plate 70c.
[42] As shown in FIG. 15, each spacer 70b includes a spacer body 7Ob-I. An inclined surface 70b-2 is provided along an end of the spacer body 7Ob-I, and a through hole is formed in the body plate such that the main shaft and the rotating shafts pass through the body plate. A plurality of projections 70b-3 is formed on the surface of the spacer body 7Ob-I at regular intervals, and spaces 70b-4 are defined between the projections 70b-3.
[43] As shown in FIGS. 18 and 19, the oil pumping means 80 includes a body 81. A mounting hole is formed at a predetermined position in the body 81 such that the oil pumping means is mounted to the main body 30 through the hole to surround the engaged part of the gear members 51 and 52 which are mounted to the rotating shafts 53 of the main rotor 61 and the subsidiary rotors 62 and transmit power. A fluid guide 82 is provided on the lower surface of the body 81, and wings 83 are integrally provided on both sides of the body 81. Further, a fluid outlet hole 85 is formed in one of the wings 83 in such a way as to be aligned with the center of the fluid guide 83.
[44] Meanwhile, an elongate guide groove 84 is formed on the inner surface of each of the wings 83. One end of the guide groove 84 is connected to the fluid guide 82.
[45] As shown in FIGS. 1 and 21, the pressure maintaining means 20 includes a regulator 21, an operator 23, and a spring 22. The regulator 21 is screwed to an insert hole 35 of the main body 30. The operator 23 is operated by a predetermined pressure. The spring 22 is elastically mounted between the regulator 21 and the operator 23.
[46] Referring to FIGS. 10 to 13, the main rotor 61 and the subsidiary rotors 62, the rotating shafts 53 and the branch inlet ports 32 and 32a and the branch outlet ports 33 and 33a may be formed to be symmetrical to a vertical central line of the main body 30. The division protrusions may be formed on the main rotor 61 and the subsidiary rotors 62 to correspond to the rotation ratio. Alternatively, the subsidiary rotors may be arranged at an angle of 120° relative to one main rotor.
[47] The operation of this invention, constructed as described above, is as follows. That is, as shown in FIGS. 1 to 22, when the main shaft M acting as an input end is rotated, the first gear member M-I fitted over the main shaft M is rotated, and the second gear member 51 and the third gear member 52 engaging with the first gear member are rotated. Thereby, the rotating shafts 53 to which the main rotor 61 and the subsidiary rotors 62 are mounted are rotated.
[48] In such a state, fluid is fed through the inlet port 12 formed in the first cover unit
10. Subsequently, the fluid is filled in the inlet space which is defined by the coupling of the first cover unit 10 to the subsidiary cover 10a. The fluid flows through the branch inlet ports 11a and 11a' formed in the subsidiary cover 10a, so that the fluid is fed into the main body 30.
[49] In a detailed description, when the fluid passing through the branch inlet ports 11a and 11a' is supplied to the fluid storage space 31 of the main body 30, the fluid is compressed by the main rotor 61 and the subsidiary rotors 62, so that the fluid has a predetermined pressure.
[50] When the main rotor 61 and the subsidiary rotors 62 are rotated, the fluid is compressed at places where the division protrusions 61b of the main rotor 61 contact the division protrusions 62b of the subsidiary rotors 62. The fluid compressing process is performed by repeating the following operation. That is, the division protrusions 61b of the main rotor 61 pass over the division protrusions 62b of the subsidiary rotors 62, and thereafter, the following division protrusions enter the grooves 61c and 62c. Subsequently, the following division protrusions enter the following grooves.
[51] The fluid supplied through such a process is fed to the branch outlet ports 33 and
33a by the grooves 61c of the main rotor 61. Thus, the fluid is delivered from the branch inlet ports 32 and 32a to the branch outlet ports 33 and 33a. When such a process is repeated, the pumping action is performed through feeding.
[52] According to the present invention, the main rotor 61 and the subsidiary rotors 62 are shaped such that the subsidiary rotors maintain a contact line with a circle forming an important part of the main rotor, thus reducing friction and shocks generated during the rotation of the rotors, and enhancing a sealing ability.
[53] Further, when gaps are formed between the main rotor 61 and the subsidiary rotors
62, the subsidiary rotors 62 and the main body 30, or the main rotor 61 and the main body 30, pressure is lowered due to leaking backflow, and efficiency is reduced due to the reduction in flow. Therefore, in order to solve this problem, leakage preventing protrusions 6 Id, 62d made of an elastic material are formed at predetermined positions on the outer surface of each of the rotors, thus preventing gaps from forming during operation, therefore improving the performance of the pump.
[54] Therefore, an increase in the sealing ability improves the performance of the rotary positive displacement pump and prolongs the lifespan of the pump.
[55] Meanwhile, the plurality of leakage preventing protrusions 6 Id and 62d are parallelly formed on the main rotor 61 and the subsidiary rotors 62 to be spaced apart from each other by a predetermined interval, as shown in FIG. 5. The cross-section of each leakage preventing protrusion is selected from among a semi-circular cross- section, a triangular cross-section, or a trapezoidal cross-section. Such a shape increases the sealing ability, thus improving the performance of the rotary positive displacement pump, and prolonging the lifespan of the pump.
[56] Further, various constructions are appropriately selected according to various installation and usage conditions depending on the construction of the main body 30, thus achieving maximum efficiency.
[57] Meanwhile, as shown in FIGS. 10 to 13, the geometrical shape of each of the main rotor and the subsidiary rotors is determined depending on the size ratio or rotation ratio of the main rotor to the subsidiary rotors. According to the number of grooves formed on the subsidiary rotors and the number of division protrusions formed on the main rotor, a 5 X 10 type construction, a 4 X 8 type construction, or other types of con- structions may be formed. Further, the shape of the grooves of each rotor may be changed according to the rotation ratio of the main rotor to the subsidiary rotors.
[58] In other words, the shape of the main rotor 61 is changed according to the rotation ratio of the main rotor 61 to the subsidiary rotors 62 or the number of division protrusions. The shape of the subsidiary rotors is determined according to the shape of the main rotor. The reason for this is because the subsidiary rotors must be rotated while in contact with the main rotor. That is, there is only one shape of each of the subsidiary rotors that is appropriate for the shape of the main rotor according to the above-mentioned basic characteristics.
[59] FIGS. 10 to 13 are partial sectional views showing various states where the main rotor 61 and the subsidiary rotors 62 are installed in the main body 30, according to several embodiments of the present invention. The rotation ratio of the main rotor 61 to the subsidiary rotors 62 is set to 1:2. Further, in order to allow the main rotor 61 and the subsidiary rotors 62 to rotate without interference between the division protrusions 61b of the main rotor 61 and the grooves 62c of the subsidiary rotors 62, the number of grooves 62c of the subsidiary rotors 62 and the number of division protrusions 61b of the main rotor 61 must have a ratio of 1:2. Thus, if the number of grooves 62c of each subsidiary rotor 62 is five, the number of division protrusions 61c of the main rotor 61 is ten.
[60] According to another embodiment of the invention, one main rotor 61 and two subsidiary rotors 62 for the main rotor are provided. The volume defined in the groove 61c between neighboring division protrusions 61b formed on the main rotor 61 serves as space for feeding the fluid.
[61] According to a further embodiment of the invention, the number of grooves 62c of each subsidiary rotor 62 is four, and the number of division protrusions 61b of the main rotor 61 is eight. Further, the number of main rotors 61 is two and the number of subsidiary rotors 62 is four.
[62] According to a further embodiment of the invention, the numerical ratio of the grooves 61c and 62c to the division protrusions 61b to 62b is changed according to the ratio of the rotation speed. That is, if the number of grooves 62c of each subsidiary rotor 62 is three and the number of division protrusions 61b of the main rotor 61 is six, the number ratio is 1:2.
[63] The branch inlet ports 32 and 32a through which fluid is fed and the branch outlet ports 33 and 33a through which the fluid is discharged are formed on both sides of the main body 30 to which the subsidiary rotors 62 are mounted. A contact part is provided between one subsidiary rotor 62 and another subsidiary rotor 62, so that the outermost part of the main rotor 61 is in close contact with the outermost part of each subsidiary rotor 62. Thereby, the main rotor and the subsidiary rotors are rotated while maintaining an airtight condition.
[64] Since the rotating shafts 53 are rotated at high speeds when fluid is discharged, the lubricating oil may leak. However, the leakage of the lubricating oil is prevented by the sealing means 70. The sealing means 70 is operated as follows. That is, as shown in FIGS. 16 and 17, high pressure caused by the rotation of the rotors causes leakage out of the through holes of the rotating shafts 53, which are formed in the plate 70c and the spacers 70b. Thus, the cylindrical extension part 72-1 of each rubber rib 72 is compressed and deformed under high pressure. However, since the support metal ring 71 is present, rubber moves in the direction of the arrow F. Since pressure is applied from the sealed fluid to the extension part 72-1 of the rubber rib, the internal stress of the rubber is concentrated on the portion right above a sliding contact part. Thereby, pressure is increased.
[65] As shown in FIG. 16, the increased pressure tends to move outwards due to the centrifugal force of the rotating shafts 53. In this case, the increased pressure is transferred to a hermetic fluid chamber having pressure lower than the fluid pressure of the sealing member 70a, which results from the leakage of oil through the outlet space 70b-4 formed between neighboring projections 70b-3 of each spacer 70b.
[66] At this time, high-pressure fluid escaping from the outlet space is rapidly discharged along the inclined surface 70b-2 from the spacer 70b. The discharged high- pressure fluid flows along a path defined in the main body 30 to the branch inlet ports 11a and 1 Ia', so that pressure acting on the sealing member is reduced, thus preventing the high-pressure fluid from leaking into the lubricating oil and prolonging the lifespan of the sealing means 70.
[67] Meanwhile, pressure is increased at the side of each sealing member 70a by the high-pressure fluid, so that each sealing member 70a and each spacer 70b may be dislodged from the main body. This is prevented by the plate 70c.
[68] The bearings 42 supporting the rotating shafts 53 are protected as follows. As shown in FIGS. 4 to 9, when the gear members 51 and 52 rotate, a vacuum is created at the position where the gear members 51 and 52 disengages from each other, thus performing a drawing action. Thereby, the fluid guide 82 of the body 81 is filled with oil.
[69] The oil in the fluid guide 82 of the body 81 is pressurized by the rotation of the gear members 51 and 52. The oil, having a predetermined pressure, is conveyed to the fluid outlet hole 85. That is, the oil is pushed and discharged through the fluid outlet hole 85 by oil which is supplied by the engagement of the gear members 51 and 52 between the outer circumference of the gear members 51 and 52 and the body 81.
[70] Thus, when the gear members 51 and 52, which are mounted to the rotating shafts
53 of the main rotor 61 and the subsidiary rotors 62 and transmit power, are rotated, oil present between the gear members 51 and 52 is compressed, so that the oil has a predetermined pressure. In such a state, the oil discharged through the fluid outlet hole 85 flows along the path, and is supplied to each bearing, thus providing a cooling and lubricating effect, thereby preventing the bearing from being damaged.
[71] Meanwhile, the elongate guide groove 84 is formed on the inner surface of each wing 83, and an end of the guide groove 84 is connected to the fluid guide 82. Thereby, when the gear members 51 and 52 rotate, oil flows to the guide groove 84 due to the increased pressure. The oil is fed to the fluid guide 82 by continuously generated pressure. The oil fed to the fluid guide 82 is discharged through the fluid outlet hole 85.
[72] As such, when the fluid is supplied and discharged at a predetermined pressure, the pump of this invention is connected to a nozzle connected to the discharge port. Afterwards, when the outlet of the nozzle is closed for a while, the internal pressure of the pump is increased.
[73] For example, since the main rotor 61 and the subsidiary rotors 62 are continuously operated to compress the fluid, the fluid remains at the discharge port 34, and thus the hydraulic pressure is increased. In this case, when the pressure exceeds a predetermined pressure, the pressure of the discharge port is diverted to the inlet port, thus preventing the pressure from increasing.
[74] The increase of pressure is prevented as shown in FIGS. 20 to 22. That is, when the operator 23 is pressurized by the pressure, the operator 23 is moved backwards and compresses the spring 22. The bypass passage 35 is opened by the operator 23 which moves backwards. At this time, the main body communicates with the inlet port via the bypass passage 35, so that some of the fluid, having a predetermined pressure, is returned to the inlet port, thus preventing the rise of pressure.
[75] Meanwhile, when the closed nozzle is opened, the compressing force of the operator is released. Thereby, the operator closes the bypass passage using the elastic force of the spring, thus preventing the leakage of pressure.
[76]
Industrial Applicability
[77] As described above, the present invention provides a rotary positive displacement pump for fluid compressors, which is small in size and is suitable for a large quantity of flow and a high head, and which shows excellent performance upon both low- speed rotation and high-speed rotation.
[78] Second, the present invention provides a rotary positive displacement pump, which is suitable for a large quantity of flow and a high head, is capable of moving a large quantity of fluid to a high position, and is operated by varying the volume, so that the pump is operated at high efficiency, thus preventing efficiency from being reduced upon low-speed rotation or high-speed rotation, and which forms a completely balanced rotating mechanism, thus preventing vibrations from occurring due to unbalanced rotation of components even when rotating at high speed.
[79] Third, the present invention provides a rotary positive displacement pump, which solves the drawbacks occurring in different kinds of pumps upon both low-speed rotation and high-speed rotation, thus being used for various purposes and showing high performance. Thus, the pump of this invention is usefully applied to various fluid machines which are small and require high performance.

Claims

Claims
[1] A rotary positive displacement pump, comprising: a first cover unit having a fastening hole, with inlet space being defined in the first cover unit and an inlet port being defined in a center of the first cover unit; a subsidiary cover having a fastening member which is fastened to the fastening hole of the first cover unit via a pin or a bolt, with branch inlet ports being provided on upper and lower portions of the subsidiary cover and space being defined inside an inner wall such that ends of rotating shafts are inserted into the space; a main body having a rotor mounting hole in which a main rotor and a subsidiary rotor are mounted, with branch inlet ports and branch outlet ports being formed in left and right sides of upper and lower portions of the rotor mounting hole, and an O-ring seat being provided outside the rotor mounting hole; a second cover unit having a plurality of shaft holes in which the rotating shafts are inserted, with a bearing being installed in each of the shaft holes, the second cover having space therein for receiving power transmission means; the power transmission means, comprising: a first gear member fitted over a main shaft so as to transmit power to the rotating shafts mounted to the main rotor and the subsidiary rotor; and a second gear member and a third gear member engaging with the first gear member and mounted to the corresponding rotating shafts; the main rotor and the subsidiary rotor each having a rotor body mounted to each of the shafts rotating in a center of the main body, division protrusions provided on an outer circumferential surface of the rotor body and coated with an elastic material, and grooves formed between the division protrusions, with a plurality of leakage preventing protrusions being formed on the division protrusions at regular intervals; sealing means, comprising: a sealing member which has a support metal ring provided in the main body through which the rotating shafts pass and which is embedded in a rubber rib, the rubber rib being provided with a cylindrical extension part; a spacer contacting the sealing member to discharge pressure fluid to the inlet port; and a plate being made of a metal material to prevent the removal of the sealing member and the spacer, and having a through hole for each of the rotating shafts to pass therethrough, the sealing member, the spacer, and the plate being sequentially coupled to each other; oil pumping means, comprising: a body having a mounting hole which is formed at a predetermined position in the body such that the oil pumping means is mounted to the main body through the hole to surround an engaged part of the gear members which are mounted to the rotating shafts of the main rotor and the subsidiary rotor and transmit power; a fluid guide provided on a lower surface of the body; wings integrally provided on both sides of the body; and a fluid outlet hole formed in one of the wings in such a way as to be aligned with the center of the fluid guide; and pressure maintaining means, comprising: a regulator screwed into an insert hole of the main body; an operator operated by a predetermined pressure; and a spring elastically installed between the regulator and the operator. [2] The rotary positive displacement pump according to claim 1, wherein the branch inlet ports are connected to the rotor mounting hole, and the branch outlet ports are formed independently from the rotor mounting hole.
[3] The rotary positive displacement pump according to claim 1, wherein a cross- section of each of leakage preventing protrusions formed on the main rotor and the subsidiary rotor is selected from a group consisting of a semi-circular shape, a triangular shape, and a trapezoidal shape. [4] The rotary positive displacement pump according to claim 1, wherein the spacer comprises: a spacer body; an inclined surface provided along an end of the spacer body; a through hole formed in a center of the spacer body such that each of the rotating shafts passes through the spacer body; a plurality of projections provided on a surface of the spacer body at regular intervals; and spaces defined between the protrusions. [5] The rotary positive displacement pump according to claim 1, wherein each of the wings has on an inner surface thereof an elongate guide groove, one end of the guide groove being connected to the fluid guide. [6] The rotary positive displacement pump according to claim 1, wherein the main rotor and the subsidiary rotor, the rotating shafts and the branch inlet ports and the branch outlet ports are symmetrically formed with respect to a vertical central axis of the main body.
PCT/KR2006/002637 2005-07-07 2006-07-06 Volumetric rotary pump WO2007007975A1 (en)

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KR1020050060971A KR100552597B1 (en) 2005-07-07 2005-07-07 Volumetric rotary pump

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KR101964049B1 (en) 2017-12-06 2019-04-01 태일엔지니어링 주식회사 Rotary positive displacement pump having a backflow protection
KR102145566B1 (en) * 2019-10-25 2020-08-18 주식회사 덕양에코 Positive displacement pump for recirculating leaking fluids and increasing watertight effect
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