EP2551521A2 - Pumpe - Google Patents

Pumpe Download PDF

Info

Publication number
EP2551521A2
EP2551521A2 EP12177655A EP12177655A EP2551521A2 EP 2551521 A2 EP2551521 A2 EP 2551521A2 EP 12177655 A EP12177655 A EP 12177655A EP 12177655 A EP12177655 A EP 12177655A EP 2551521 A2 EP2551521 A2 EP 2551521A2
Authority
EP
European Patent Office
Prior art keywords
stage
shaft
pump
main drive
driving force
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP12177655A
Other languages
English (en)
French (fr)
Other versions
EP2551521A3 (de
Inventor
Phil Chan Rha
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Philtec Co Ltd
Original Assignee
Philtec 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 KR1020110075023A external-priority patent/KR101305394B1/ko
Priority claimed from KR1020120026107A external-priority patent/KR101305395B1/ko
Application filed by Philtec Co Ltd filed Critical Philtec Co Ltd
Publication of EP2551521A2 publication Critical patent/EP2551521A2/de
Publication of EP2551521A3 publication Critical patent/EP2551521A3/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • 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
    • F04C2/02—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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps

Definitions

  • the present invention relates to a double action rotary pump, which is intended to forcibly deliver fluid such as liquid or gas. More particularly, the present invention relates to a pump, in which spaces of cylinders are divided by a piston that has a pair of heads, each of which is provided inside a corresponding cylinder so as to be eccentric from the center of the cylinder such that each head rotates inside the cylinder.
  • the volumes of the divided spaces of the cylinders are repeatedly and alternately contracted and expanded in response to the rotation of the heads so that intake and exhaust operations of the cylinders are performed counteractively and continuously, thereby forcibly delivering fluid.
  • Such a pump generally includes a transmission unit and an operating unit in order to forcibly deliver fluid.
  • the transmission unit of the pump includes a pair of crank-type first and second shafts, which operates at uniform and non-uniform angular speeds using driving force that is transmitted from a motor via a power transmission system, which is realized by combining concentric and eccentric gears.
  • the operating unit is provided in series with the transmission unit so as to be connected to one side of the transmission unit.
  • the operating unit includes an intake port and an exhaust port on both sides thereof.
  • the operating unit also includes first and second cylinders, which are arranged in upper and lower positions, are divided from each other, and are connected to each other via a through-hole.
  • a piston in the operating unit, includes a pair of heads, each of which is provided in a corresponding one of the first and second cylinders using a corresponding one of the first and second shafts such that the each head is eccentric from the center of the corresponding cylinder.
  • the heads rotate at non-uniform angular speeds in a counteracting fashion while maintaining a distance between the shafts.
  • the piston also includes a connector, which extends through the through-hole and connects the heads to each other.
  • the volumes of spaces inside the cylinders, which are divided by the piston are repeatedly and alternately contracted and expanded in response to the rotation of the piston, so that the cylinders counteractively and continuously perform the intake and exhaust operations, thereby forcibly delivering fluid.
  • the angular speed of the heads varies depending on an angle of rotation in order to maintain the distance between the first and second shafts. That is, according to the mechanical principle, the distance between the first and second shafts essentially varies between non-uniform maximum and minimum distances when the first and second shafts operate in opposite directions.
  • variable long and short distances between the shafts are mutually corrected due to the operation at uniform and non-uniform angular speeds, so that an intended pumping operation is enabled.
  • one of the first and second shafts operates at non-uniform speeds. Due to the non-uniform angular operation that is intended to correct the distance between the shafts, the flow rate of fluid that is forcibly delivered is non-uniform, which is attributable to changes in the angular speed due to the maximum and minimum diameter portions between the eccentric gears. Describing in more detail, one of the first and second shafts rotates at a uniform speed since driving force from the outside is directly delivered thereto. In addition, the other one of the first and second shafts operates at a lowest speed by gradually slowing down its rotation in the vicinity of 90° and 270° depending on the maximum and minimum diameter portions between the eccentric gears.
  • the flow rate of fluid that is pumped varies depending on the angle of the shaft of the pump, i.e. the flow rate is the maximum at 0° and 180° and the minimum in the vicinity of 90° and 270°.
  • the flow rate of one of the first and second cylinders is fixed but the flow rate of the other one of the first and second cylinders varies between the maximum and the minimum. Consequently, the sum of the instantaneous flow rates that are pumped by the pump is not uniform.
  • the non-uniformity of the flow rate of fluid that is pumped is a main reason for surging that would cause a problem in the operation of the pump.
  • the surging of the pump causes a number of problems, which degrade the quality of the pump. Specifically, the surging creates noises and vibration, decreases the lifespan of devices, decreases the efficiency of the pump, and disables high-precision control over forced delivery, such as delivery at a fixed amount.
  • the power transmission system that includes the concentric or eccentric gears is composed of several stages that use at least two sets of shafts in addition to the first and second shafts. Therefore, the spatial arrangement of the power transmission system is difficult.
  • the configuration is complicated since several types of gears having large and small diameters are systematically and continuously associated with adjacent elements. Consequently, there are problems in that is difficult to fabricate the pump and that the cost of manufacture of the pump increases.
  • the power transmission system is composed of several stages, the distance of a power transmission route unnecessarily extends, thereby increasing the distance between an input and an output of driving force.
  • mechanical friction or load between mechanical elements in respective stages increases power loss, so that power that is consumed in the operation of the pump increases, thereby decreasing the operating efficiency of the pump. Therefore, the development of a technology that can overcome such problems is required.
  • Various aspects of the present invention provide a pump, in which driving force is distributed using a distribution stage and a delivery stage of a power transmission system, which is realized by combining concentric and eccentric gears, so that first and second shafts operate in counteractive non-uniform angular speeds. Accordingly, the sum of flow rates that are pumped by a piston at a predetermined time point can stay uniform, thereby enabling a fixed amount of fluid to be forcibly delivered, preventing surging, and improving the performance of the pump.
  • a pump in which first and second shafts of a transmission unit operate at non-uniform angular speeds using the power transmission system, which is realized by combining a worm, which moves like a pendulum, and a pair of eccentric worm gears, which are provided on both sides of the worm such that the worm is disposed in the middle between them. Accordingly, it is possible to simplify the structure, reduce the number of parts, and simplify the parts, thereby reducing the cost of manufacture.
  • a pump in which the power transmission system is realized by combining a minimum number of mechanical elements such that the length of a route along which power is transmitted and the stages of the power transmission system are decreased, thereby reducing mechanical friction and load. Accordingly, it is possible to reduce power consumption, increase the efficiency of operation, and improve the quality of the pump.
  • a double action rotary pump which is intended to forcibly deliver fluid such as liquid or gas.
  • the pump includes a transmission unit and an operating unit provided in series with the transmission unit.
  • the transmission unit operates at uniform or non-uniform angular speeds using driving force that is transmitted from a motor via a power transmission system, which includes a combination of concentric and eccentric gears.
  • a piston has a pair of heads, which rotate at non-uniform angular speeds in a counteracting fashion while maintaining the distance between shafts, and divides the spaces inside cylinders.
  • the volumes of the divided spaces of the cylinders are repeatedly and alternately contracted and expanded in response to the rotation of the piston, so that the cylinders counteractively and continuously perform intake and exhaust operations, thereby forcibly delivering fluid.
  • the structure of the power transmission system of the transmission unit is improved such that the sum of flow rates that are pumped by the piston at a predetermined time point stays uniform. Accordingly, a fixed amount of fluid can be forcibly delivered, thereby making it possible to prevent surging.
  • the driving force is distributed using the distribution stage and the delivery stage of the power transmission system, which is realized by combining concentric and eccentric gears, so that the first and second shafts operate in counteractive non-uniform angular speeds. Consequently, the sum of flow rates that are pumped by the piston at a predetermined time point can stay uniform, thereby enabling a fixed amount of fluid to be forcibly delivered, preventing surging. Accordingly, it is possible to remove noises or vibration, thereby improving the endurance of devices and improving the performance of the pump.
  • the first and second shafts of the transmission unit operate at non-uniform angular speeds using the power transmission system, which is realized by combining the worm, which moves like a pendulum, and the pair of eccentric worm gears, which are provided on both sides of the worm such that the worm is disposed in the middle between them. Accordingly, it is possible to simplify the structure, reduce the number of parts, and simplify the parts, thereby reducing the cost of manufacture.
  • the power transmission system is realized by combining a minimum number of mechanical elements such that the length of the route along which power is transmitted and the stages of the power transmission system are decreased, thereby reducing mechanical friction and load. Accordingly, it is possible to reduce power consumption, increase the efficiency of operation, and improve the quality of the pump.
  • the amount of fluid that is pumped by the pump is maintained uniform, it is possible to precisely measure a flow rate and forcibly deliver a fixed amount of fluid, thereby enabling high-precision control over forced delivery.
  • FIG. 1 is a front cross-sectional view showing the structure of a pump according to one embodiment of the invention
  • FIG. 2 is a side cross-sectional view showing the structure of the pump according to one embodiment of the invention.
  • FIG. 3A and FIG. 3B are explanatory views showing a power transmission system that is applied to the pump according to an embodiment of the invention, in which FIG. 3A is a development view of transmission shafts, and FIG. 3B is a development view of transmission gears;
  • FIG. 4A to FIG. 4E are explanatory views showing the operation of the pump according to one embodiment of the invention, in which FIG. 4A shows the position in which the piston is positioned at a reference point 0°, FIG. 4B is the explanatory view in which the piston is rotated to a position around 90°, FIG. 4C is the explanatory view in which the piston is rotated to a position around 180°, FIG. 4D is the explanatory view in which the piston is rotated to a position around 270°, and FIG. 4E is an explanatory view in which the piston is rotated to a position around 360°;
  • FIG. 5A and FIG. 5B are explanatory views showing another embodiment of the power transmission system, which is applicable to the pump of the invention, in which FIG. 5A is a development view of transmission shafts, and FIG. 5B is a development view of transmission gears;
  • FIG. 6A and FIG. 6B are explanatory views showing a further embodiment of the power transmission system, which is applicable to the pump of the invention, in which FIG. 6A is a development view of transmission shafts, and FIG. 6B is a development view of transmission gears;
  • FIG. 7 is a partially cutaway front elevation view showing a pump according to another embodiment of the invention.
  • FIG. 8 is a cross-sectional view taken along line A-A in FIG. 7 ;
  • FIG. 9 is a cross-sectional view taken along line B-B in FIG. 7 ;
  • FIG. 10A to FIG. 10D are stepwise explanatory views showing the intake and exhaust processes of the pump according to another embodiment of the invention.
  • FIG. 1 and FIG. 2 show a pump according to an embodiment of the invention in detail.
  • the invention provides a double action rotary pump, which is intended to forcibly deliver fluid such as liquid or gas.
  • the pump of this embodiment generally includes a transmission unit 10 and an operating unit 20, which are surrounded by respective casings such that they are isolated from each other.
  • the transmission unit 10 includes a main drive shaft 11 in the central portion of the body thereof, the main drive shaft 11 receiving driving force from a motor or the outside, a pair of crank-type first and second shafts 12 and 13, which are arranged in parallel in the upper and lower positions.
  • the first and second shafts 12 and 13 are associated with the main drive shaft 11 and follow it via a power transmission system, which will be described later.
  • a power transmission system 30 includes a distribution stage 31, a delivery stage 32, and first and second input stages 33 and 34.
  • the core concept of the invention is characterized in delivering the driving force that is introduced to the main drive shaft 11 by distributing it using the distribution stage 31 and the delivery stage 32, so that respective first and second shafts 12 and 13 operate at non-uniform angular speeds in opposite directions. Due to this, the sum of flow rates that are pumped by the pump at a predetermined time point can stay uniform, so that fluid can be forcibly delivered.
  • the distribution stage 31, which is an eccentric gear, is provided on the main drive shaft 11, and supplies the driving force that is introduced through the main drive shaft 11 to the first and second shafts 12 and 13 by distributing the driving force.
  • the first input stage 33 which is a concentric gear, is provided on the first shaft 12, is associated with the distribution stage 31 of the main drive shaft 11 via the delivery stage 32, and receives the distributed driving force from the main drive shaft 11.
  • the second input stage 34 which is an eccentric gear, is provided on the second shaft 13, is associated with the distribution stage 31 of the main drive shaft 11, and receives the distributed driving force from the main drive shaft 11.
  • the driving force introduced through the main drive shaft 11 is distributed by the power transmission system 30, and the respective first and second shafts 12 and 13 counteractively operate at non-uniform angular speeds, thereby maintaining the distance between shaft ends according to the operating condition of the first and second shafts 12 and 13,
  • the delivery stage 32 is a converting element for driving the first and second shafts 12 and 13 in the opposite directions by converting the delivery of power and the direction in which driving force acts.
  • the delivery stage 32 is provided using an idle shaft 32a between the main drive shaft 11 and the first shaft 12, and includes an input section 32b and an output section 32c.
  • the input section 32b is an eccentric gear, is associated with the distribution stage 31 of the main drive shaft 11, and receives the driving force.
  • the output section 32c is a concentric gear, is associated with the first input stage 33, and transmits the driving force introduced through the input section 32b to the first input stage 33.
  • first and second cylinders 21 and 22 are arranged up and down along one vertical line, and are connected to each other by a through passage 23, which extends therebetween, thereby defining one space.
  • an intake port 24 and an exhaust port 25 are provided on both sides between the first and second cylinders 21 and 22 of the operating unit 20, in the direction that intersects the through passage 23 of the first and second cylinders 21 and 22.
  • fluid is taken in and exhausted through the intake port 24 and the exhaust port 25.
  • the piston 26, which operates using the first and second shafts 12 and 13, is provided inside the first and second cylinders 21 and 22.
  • the piston 26 includes a pair of heads 26a and 26b, which are provided eccentrically from the centers of the first and second cylinders 21 and 22, and rotate counteractively while maintaining the distance between the shafts due to the non-uniform angular speeds of the first and second shafts 12 and 13.
  • the heads 26a and 26b are connected to each other by a connector 26c, which passes through the through passage 23, thereby the piston 26 a unitary body.
  • the connector 26c has the function of connecting the heads 26a and 26b and the function of dividing (or partitioning) the cylinders 21 and 22.
  • the heads 26a and 26b stay in slide contact with the inner walls of the first and second cylinders 21 and 22, and divide the first and second cylinders 21 and 22, which define one space, respectively or to the right and left sections.
  • the volumes of the divided spaces in the respective cylinders 21 and 22 are repeatedly and alternately contracted and expanded in response to the rotation of the piston 26, so that the both cylinders 21 and 22 can perform the intake and exhaust operations in a counteractive and continuous fashion. Consequently, fluid can be forcibly delivered by a double action mechanism.
  • FIG. 4A shows the initial state of the operation of the pump, in which the piston 26 is positioned at 0° and is reached to the top dead point.
  • the second cylinder 22 is closed and the first cylinder 21 is opened, so that fluid is started to be taken into the divided left space via the intake port 24.
  • FIG. 4B shows the position in which the first head 26a of the piston 26 is rotated 90° in the clockwise direction and the second head 26b of the piston 26 is rotated 90° in the counterclockwise direction.
  • the divided left space of the first cylinder 21 is expanded, thereby continuing to take in fluid.
  • FIG. 4C shows the position in which the piston 26 is positioned at 180°, thereby reaching the bottom dead point.
  • the first cylinder 21 is closed while expanding to the maximum, thereby finishing the process of taking in fluid.
  • the second cylinder 22 is opened, and fluid is being taken into the divided left space of the second cylinder 22.
  • FIG. 4D shows the position in which the first head 26a of the piston 26 is rotated further about 270° in the clockwise direction while the second head 26b of the piston 26 is rotated further about 270° in the counterclockwise direction.
  • the divided right space of the first cylinder 21 is contracted, thereby starting to exhaust fluid that is taken in through the exhaust port 25.
  • the divided left space of the second cylinder 22 is expanded, so that the process of taking in fluid is continued.
  • FIG. 4E shows the position in which the first head 26a of the piston 26 is rotated further 360° in the clockwise direction while the second head 26b of the piston 26 is rotated further about 360° in the counterclockwise direction, so that the piston 24 returns to the position of FIG. 4A .
  • the space of the first cylinder 21 is in the middle between the intake operation and the exhaust operation, and the amount of exhaust is the maximum.
  • the space of the second cylinder 22 is expanded to the maximum, thereby finishing the process of taking in fluid.
  • no fluid is taken into or exhausted from the space of the second cylinder 22.
  • the first cylinder 21 starts to take in fluid while the second cylinder 22 starts to exhaust fluid in contrast. Consequently, the first and second cylinders 21 and 22 alternately perform the intake and exhaust operations, thereby enabling an intended pumping operation.
  • FIG. 5A and FIG. 5B show another embodiment of the power transmission system of the pump of the invention.
  • the power transmission system 130 of this embodiment connects a pair of the crank-type first and second shafts 12 and 13 to each other.
  • the first and second shafts 12 and 13 are arranged in parallel in upper and lower positions about the main drive shaft 11, which receives driving force from a motor or the outside.
  • the power transmission system 130 includes a distribution stage 131, a delivery stage 132 and first and second input stages 133 and 134.
  • each of the distribution stage 131 and the delivery stage 132 is configured as an eccentric gear or any eccentric member, such as a sprocket or a chain.
  • the distribution stage 131 which is an eccentric gear, is provided on the main drive shaft 11, and supplies driving force that is introduced through the main drive shaft 11 to the first and second shafts 12 and 13 by distributing the driving force.
  • the first input stage 133 which is an eccentric sprocket, is provided on the first shaft 12, is associated with the distribution stage 131 via the delivery stage 132 of the chain, and receives the distributed driving force from the main drive shaft 11.
  • the second input stage 134 which is an eccentric gear, is provided on the second shaft 13, is associated with the distribution stage 131 of the main drive shaft 11, and receives the distributed driving force from the main drive shaft 11.
  • the driving force received via the main drive shaft 11 is distributed via the power transmission system 130, so that the first and second shafts 12 and 13 counteractively operate at non-uniform angular speeds in order to maintain the distance between the shafts according to the operating condition of the first and second shafts 12 and 13.
  • the distribution stage 131 includes a first transmission element 131a, which is an eccentric gear, and a second transmission element 131b, which is an eccentric sprocket.
  • FIG. 6A and FIG. 6B show a further embodiment of the power transmission system of the pump of the invention.
  • the power transmission system 230 of this embodiment connects a pair of the crank-type first and second shafts 12 and 13 to each other.
  • the first and second shafts 12 and 13 are arranged in parallel in upper and lower positions about the main drive shaft 11, which receives driving force from a motor or the outside.
  • the power transmission system 230 includes a distribution stage 231, a delivery stage 232 and first and second input stages 233 and 234.
  • each of the distribution stage 231 and the delivery stage 232 is configured as, for example, a concentric or eccentric gear or chain that has a large or small size.
  • the distribution stage 231 which is an eccentric gear, is provided on the main drive shaft 11, and supplies driving force that is introduced through the main drive shaft 11 to the first and second shafts 12 and 13 by distributing the driving force.
  • the input stage 233 which is a concentric gear, is provided on the first shaft 12, is associated with the distribution stage 131 via the delivery stage 132 of the chain, and receives the distributed driving force from the main drive shaft 11.
  • the second input stage 234, which is an eccentric gear, is provided on the second shaft 13, is associated with the distribution stage 131 of the main drive shaft 11, and receives the distributed driving force from the main drive shaft 11.
  • the driving force received via the main drive shaft 11 is distributed via the power transmission system 230, so that the first and second shafts 12 and 13 counteractively operate at non-uniform angular speeds in order to maintain the distance between the shafts according to the operating condition of the first and second shafts 12 and 13
  • the distribution stage 231 includes a first transmission element 231a, which is a concentric gear, and a second transmission element 231b.
  • the second transmission element 231b is configured by sequentially arranging an input section 231b-1, which is a small eccentric gear, a delivery section 231b-2, which is a concentric gear, and an output section 231b-3, which is a large eccentric gear.
  • the delivery stage 232 is a converting element for driving the first and second shafts 12 and 13 in the opposite directions by converting the delivery of power and the direction in which driving force acts.
  • the delivery stage 232 is provided using an idle shaft 232a between the main drive shaft 11 and the first shaft 12.
  • An eccentric idle gear 232b is associated with the delivery section 231b-2 of the distribution stage 231 of the main drive shaft 11, and receives the driving force.
  • the delivery stage 232 is associated with the first input stage 233, and redirects the driving force that is introduced through the idle gear 232b to the first input stage 233.
  • the second input stage 234 includes a first input section 234a, which is a concentric gear associated with the first transmission element 231a of the distribution stage 231 of the main drive shaft 11; a delivery section 234b, which is associated with the input section 231b-1 of the second transmission element 231b of the distribution stage 231; and a second input section 234c, which is associated with the output section 231b-3 of the second transmission element 231b of the distribution stage 231.
  • the power transmission system 230 is configured such that it transmits power as required by exchanging driving force between the first shaft 12 and the second shaft 13 via the main drive shaft 11 and between the main drive shaft 11 and the second shaft 13.
  • FIG. 7 , FIG. 8 and FIG. 9 show a pump according to another embodiment of the invention. This embodiment is different from the foregoing embodiment in that the structure of the power transmission system of the transmission unit of the pump.
  • the pump of this embodiment includes a transmission unit 320 and an operating unit 330, which are isolated from each other on both sides inside a casing 310.
  • the pump also has a motor 340.
  • a pair of crank-type first and second shafts 322 and 324 are arranged in parallel, and operate at non-uniform angular speeds using the driving force that is delivered from the motor 340 via a power transmission system.
  • first and second cylinders 336 and 337 are arranged on the same horizontal line, and are connected to each other by a through-hole 335, thereby defining one space.
  • an intake port 332 and an exhaust port 334 are provided in the upper and lower portions.
  • first and second cylinders 336 and 337 are provided with a piston 338, which includes a pair of heads 338a and 338b.
  • the heads 338a and 338b are provided inside the first and second cylinders 336 and 337 using the first and second shafts 322 and 324, such that they are eccentric from the centers of the first and second cylinders 336 and 337.
  • the heads 338a and 338b rotate counteractively while maintaining the distance between the shafts of eccentric portions due to non-uniform angular speeds.
  • the piston 338 also includes a connector 338c, which extends through the through-hole 335 so as to connect the heads 338a and 338b.
  • the heads 338a and 338b stay in slide contact with the inner walls of the first and second cylinders 336 and 337, and divide the first and second cylinders 336 and 337, which define one space, respectively or to the right and left sections.
  • the volumes of the divided spaces in the respective cylinders 336 and 337 are repeatedly and alternately contracted and expanded in response to the rotation of the piston 338, so that the both cylinders 336 and 337 can perform the intake and exhaust operations in a counteractive and continuous fashion. Consequently, fluid can be forcibly delivered by a double action mechanism.
  • the connector 338c has the function of connecting the first and second heads 338a and 338b to each other and the function of a separator sheet that divides the respective spaces of the first and second cylinders 336 and 337 from each other.
  • the number of mechanical elements of the power transmission system of the transmission unit 320 is significantly reduced, thereby simplifying the structure, decreasing the route along which power is delivered, and decreasing mechanical friction or resistance.
  • the power transmission system 323 of the transmission unit 320 of this embodiment includes a worm 323a and a pair of eccentric worm gears 323b and 323c.
  • One end of the worm 323a extends further, thereby forming a rod having a predetermined length.
  • the terminal of the rod of the worm 323a is fixed by a support piece 323a-1, which is coupled with the upper section of the casing 310, such that the driving force from the output shaft 342 of the motor 340 is transmitted thereto.
  • the other end of the worm 323a forms a free end,
  • the worm 323a is interposed between the worm gears 323b and 323c, which will be describe below, and is guided by a guide rail that is provided in the lower portion of the casing 310 such that it moves like a pendulum.
  • the worm gears 323b and 323c are engaged with both sides of the worm 323a, such that the worm 323a is disposed in the middle between the worm gears 323b and 323c.
  • the worm gears 323b and 323c are eccentrically provided on the first and second shafts 322 and 324, respectively.
  • the worm 323a moves like a pendulum between the eccentric worm gears 323b and 323c while supplying driving force from the motor 340 to the worm gears 323b and 323c by distributing it.
  • a flexible delivery element 350 is provided between the output shaft 342 and worm 323a in order to transmit the driving force of the motor 340.
  • the delivery element 350 may be implemented as an elastic or resilient flexible material, such as a coil spring, a rubber material, or the like, which receives variation or changes between the output shaft 342 of the fixed motor 340, which is mounted on the casing 310, and the movable worm 323a, which moves like a pendulum inside the casing 310.
  • FIG. 10A shows the initial state of the operation of the pump in which the piston 338 is positioned at 0° and is reached to the top dead point.
  • the second cylinder 337 is closed and the first cylinder 336 is opened, so that fluid is started to be taken into the divided lower space of the first cylinder 336 via an intake port 332.
  • FIG. 10B shows the position in which the first head 338a of the piston 338 is rotated 90° in the clockwise direction and the second head 338b of the piston 338 is rotated 90° in the counterclockwise direction.
  • the divided lower space of the first cylinder 336 is expanded, thereby continuing the process of taking in fluid.
  • the second cylinder 337 in the closed state is opened, thereby starting to take fluid into the lower divided space.
  • FIG. 10C shows the position in which the piston 338 is positioned at 180°, thereby reaching the bottom dead point.
  • the first cylinder 336 is closed while expanding to the maximum, thereby finishing the process of taking in fluid.
  • fluid is being taken into the divided lower space of the second cylinder 337.
  • FIG. 10D shows the state in which the first head 338a of the piston 338 is rotated further about 270° in the clockwise direction while the second head 338b of the piston 338 is rotated further about 270° in the counterclockwise direction.
  • the divided lower space of the first cylinder 336 is contracted, thereby starting to exhaust fluid that is taken in through the exhaust port 334.
  • the divided lower space of the second cylinder 337 is expanded, so that the process of taking in fluid is continued.
  • the first head 338a of the piston 338 is rotated further 360° in the clockwise direction while the second head 338b of the piston 338 is rotated further about 360° in the counterclockwise direction, so that the piston 338 returns to the position of FIG. 10A .
  • the space of the first cylinder 336 is in the middle between the intake operation and the exhaust operation, and the amount of exhaust is the maximum.
  • the space of the second cylinder 337 is expanded to the maximum, thereby finishing the process of taking in fluid.
  • no fluid is taken into or exhausted from the space of the second cylinder 336.
  • the piston 338 rotates inside the cylinders 336 and 337 so that the first cylinder 336 takes in fluid while the second cylinder 337 exhausts fluid.
  • the first and second cylinders 336 and 337 alternately and repeatedly perform the intake operation and the exhaust operation, so that an intended pumping operation can be performed.
  • a double action rotary pump forcibly delivers fluid such as liquid or gas.
  • a transmission unit operates at uniform or non-uniform angular speeds using driving force transmitted from a motor via a power transmission system.
  • An operating unit is provided in series with the transmission unit.
  • a piston of the operating unit has a pair of heads, which rotate at non-uniform angular speeds in a counteracting fashion while maintaining the distance between shafts, and divides the spaces inside cylinders.
  • the volumes of the divided spaces of the cylinders are repeatedly and alternately contracted and expanded in response to the rotation of the piston, so that the cylinders counteractively and continuously perform intake and exhaust operations, thereby forcibly delivering fluid.
  • the structure of the power transmission system is improved such that the sum of flow rates that are pumped by the piston at a predetermined time point stays uniform.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
EP12177655.3A 2011-07-28 2012-07-24 Pumpe Withdrawn EP2551521A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020110075023A KR101305394B1 (ko) 2011-07-28 2011-07-28 펌프
KR1020120026107A KR101305395B1 (ko) 2012-03-14 2012-03-14 펌프

Publications (2)

Publication Number Publication Date
EP2551521A2 true EP2551521A2 (de) 2013-01-30
EP2551521A3 EP2551521A3 (de) 2013-12-25

Family

ID=46603597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12177655.3A Withdrawn EP2551521A3 (de) 2011-07-28 2012-07-24 Pumpe

Country Status (3)

Country Link
US (1) US20130028779A1 (de)
EP (1) EP2551521A3 (de)
CN (1) CN102979719A (de)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1041606A (en) * 1912-02-27 1912-10-15 Emil Dembowsky Engine.
CH282182A (fr) * 1946-10-07 1952-04-15 Eureka Williams Corp Pompe.
JPS58152189A (ja) * 1982-03-08 1983-09-09 Kazuichi Ito 無脈動回転ポンプ
KR970009955B1 (ko) * 1994-05-11 1997-06-19 나필찬 쌍원통 펌프
KR100449312B1 (ko) * 1996-11-11 2004-11-26 라필찬 쌍원통임펠러형펌프
KR20030010453A (ko) * 2001-07-24 2003-02-05 이기만 한쌍의 용적실을 갖는 용적형 펌프 및 이의 조립방법
KR20070006444A (ko) * 2005-07-08 2007-01-11 삼성테크윈 주식회사 범프 형성 방법 및 전도성 볼 정렬 장치
KR20070064444A (ko) * 2005-12-17 2007-06-21 나필찬 무맥동 쌍원통펌프
US8042331B2 (en) * 2008-04-01 2011-10-25 GM Global Technology Operations LLC On-demand hydraulic pump for a transmission and method of operation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Also Published As

Publication number Publication date
US20130028779A1 (en) 2013-01-31
CN102979719A (zh) 2013-03-20
EP2551521A3 (de) 2013-12-25

Similar Documents

Publication Publication Date Title
AU2004217638B2 (en) Compressor
CN101881272A (zh) 变量叶片泵
KR102677305B1 (ko) 로터리 압축기
KR101588956B1 (ko) 트윈 타입 지로터 펌프
KR20130011656A (ko) 스크롤 압축기
JP5278775B2 (ja) 油供給装置
JP2002256891A (ja) 内燃機関用燃料ポンプ
CN115898835A (zh) 一种恒流计量泵
EP2551521A2 (de) Pumpe
CN108087264B (zh) 无脉动高阶椭圆形凸轮泵
JP2009036137A (ja) 可変容量型ベーンポンプ
KR101305394B1 (ko) 펌프
CN108799100A (zh) 可实现消除液压脉动的设计方法及装置
CN218816898U (zh) 一种恒流计量泵
JP2022517576A (ja) 水素ガス圧縮装置
JP2009085213A (ja) 内接ギヤポンプ
JP2021110318A (ja) 可変容量オイルポンプ
RU55050U1 (ru) Устройство для перекачивания газожидкостных смесей при технологических операциях в скважинах
JP2002202018A (ja) 燃料ポンプ
JPH10122129A (ja) アキシャルピストン型油圧ポンプ
JP2009068421A (ja) 流体吸入吐出装置
JP7042099B2 (ja) ポンプ装置
JP2019124216A (ja) 流体ポンプ
CN218862834U (zh) 一种无脉冲双串联液压隔膜计量泵
KR102451043B1 (ko) 쌍원통 펌프

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 11/00 20060101ALI20131121BHEP

Ipc: F04C 2/06 20060101ALI20131121BHEP

Ipc: F16H 47/00 20060101ALI20131121BHEP

Ipc: F04B 9/02 20060101AFI20131121BHEP

Ipc: F04C 29/00 20060101ALI20131121BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20140626