CN102979719A - Pump - Google Patents
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- CN102979719A CN102979719A CN2012103414137A CN201210341413A CN102979719A CN 102979719 A CN102979719 A CN 102979719A CN 2012103414137 A CN2012103414137 A CN 2012103414137A CN 201210341413 A CN201210341413 A CN 201210341413A CN 102979719 A CN102979719 A CN 102979719A
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- axle
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- 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
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- 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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Rotary Pumps (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
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.
Description
The cross reference of related application
The application require on July 28th, 2011 application, application number is 10-2011-75023, and on March 14th, 2012 application, application number is the preference of the korean patent application of 10-2012-26107, the full content of above-mentioned application purpose is as a reference incorporated into herein.
Technical field
The present invention relates to a kind of double-action rotary pump, this rotary pump is intended to carry forcibly fluid, for example liquid or gas.More preferably, the present invention relates to a kind of pump, the space of cylinder body demarcates by piston in this pump, and this piston has the pair of pistons head, and each piston head is arranged in the corresponding cylinder body so that eccentric with the center of cylinder body, so that each piston head rotates in cylinder body.In this pump, the volume in the space that is divided out of cylinder body is compression and expansion repeatedly and alternately in response to the rotation of piston head, so that reaction ground but (counteractively) and carry out continuously suction and the discharging operation of cylinder body carries fluid thus forcibly.
Background technique
Be used for carrying the double-action rotary pump of the several types of fluid to be developed and to be used so far forcibly.This pump generally includes transmission unit and operating unit, in order to carry forcibly fluid.
The transmission unit of pump comprises the first axle and second axle of a pair of crankshaft, the first axle of described crankshaft and the second axle utilization operate with the angular velocity of consistent (uniform) or inconsistent (non-uniform) from the driving force of motor transmission by means of dynamic transfer system, and this dynamic transfer system is by realizing in conjunction with concentric gear and eccentricity gear.Operating unit and transmission unit in series arrange, thereby are connected with a side of supply unit.Operating unit comprises suction port and exhaust port in its both sides.Operating unit also comprises the first cylinder body and the second cylinder body, and described the first cylinder body and the second cylinder body are arranged in upper position and the lower position, mutually separate and interconnect via through hole.In addition, in operating unit, piston comprises the pair of pistons head, and each piston head utilizes the corresponding axis in the first axle and the second axle to be arranged in the corresponding cylinder body in the first and second cylinder bodies, so that each piston head is eccentric with corresponding cylinder body.Piston head rotates with inconsistent angular velocity by counteractive mode (in a counteracting fashion), keeps simultaneously distance between the described axle.This piston also comprises connector, and this connector extends by through hole and piston head is interconnected.The rotation of the volume response piston in the space in the cylinder body of being divided by piston and repeating and compression and expansion alternately, thus cylinder body reaction ground and carrying out continuously sucks and discharging operation, carries forcibly thus fluid.
According to the operating conditions that is used for the piston rotation, the angular velocity of piston head changes according to the angle of rotation, in order to keep the distance between the first axle and the second axle.In other words, according to Der Grundsatz der Maschinen, when the first axle and the second axle during along opposite direction operation, the distance between the first axle and the second axle changes between inconsistent ultimate range and minimum range basically.Yet in the pump of as above configuration, because with the inconsistent angular velocity operation of making peace, length and short distance variable between the axle can be proofreaied and correct each other, thereby so that desired pumping operation becomes feasible.
Yet, such pump operated in, one of them of the first axle and the second axle is with inconsistent speed operation.Because be intended to the inconsistent angle operation of the distance between the axis calibration, the flow of the fluid that therefore is forced to carry is inconsistent, the variation of the angular velocity that it causes owing to the minimum and maximum diameter parts between eccentricity gear.Illustrate in greater detail, owing to directly be transported to one of them of the first axle and the second axle from the driving force of outside, one of them of the first axle and the second axle is with consistent speed rotation.In addition, another in the first axle and the second axle according to the minimum and maximum diameter parts between the eccentricity gear by reduce gradually its near 90 ° and 270 ° rotational speed and with minimum speed operation.The flow of the fluid of pumping changes according to the angle of the axle of pump, and namely flow is located maximum at 0 ° and 180 °, and minimum near 90 ° and 270 °.By this way, the flow of one of them of the first and second cylinder bodies is fixed, but the flow of the another one cylinder body of the first and second cylinder bodies changes between minimum and maximum.Therefore, the summation by the instantaneous flow of pump institute pumping is inconsistent.
Therefore, the fluid flow of pumping is inconsistent to be the main cause that causes pulsation, and the pulsation meeting brings problem in the operation of pump.
Pulse of pumps causes many problems, and these problems can reduce the quality of pump.Particularly, pulsation produce noise and vibration, reduction equipment working life, reduce the efficient of pump and in the ability of forced conveyance forfeiture highi degree of accuracy control (for example carrying with fixing amount).
In addition, in pump as described above, comprise that the dynamic transfer system of concentric gear or eccentricity gear is comprised of several levels, these levels are utilization at least two group axles except utilizing the first axle and the second axle.Therefore, the configuration of the space of dynamic transfer system is difficult.This structure is complicated, and this is owing to have the several types gear of major diameter and minor diameter and contiguous element system ground and and link continuously (associated with).Therefore, the problem of existence is to be difficult to make the manufacture cost increase of this pump and pump.
In addition, because dynamic transfer system is comprised of several level, the distance of power transmission distance is unnecessarily expanded, and has increased thus the distance between the input and output of driving force.In addition, mechanical friction or load have increased energy loss between the mechanical component in level separately, thereby the energy of pump operated middle consumption increases, and has reduced thus the operating efficiency of pump.Therefore need to be able to overcome the exploitation of the technology of these problems.
The information that discloses in this background technique of the present invention is only used for strengthening the understanding to background of the present invention, and should be as for this information structure admitting or any type of suggestion by prior art well known to those skilled in the art.
Summary of the invention
Each aspect of the present invention provides a kind of pump, in this pump, driving force utilizes the distribution stage of dynamic transfer system to distribute with carrying level, and dynamic transfer system is by realizing in conjunction with concentric gear and eccentricity gear, so that the first axle and the second axle operate with counteractive, inconsistent angular velocity.Therefore, the summation of the flow by the piston pumping predetermined time point can be consistent, thereby the fluid that guarantees fixed amount is forced to carry, prevents from pulsing and improved the operation of pump.
A kind of pump also is provided, wherein the first axle of supply unit and the second axle utilize dynamic transfer system to operate with inconsistent angular velocity, dynamic transfer system is by realizing in conjunction with worm screw and a pair of eccentric worm gear, described worm screw swings as pendulum, described a pair of eccentric worm gear is arranged on the both sides of worm screw, so that worm screw is arranged in the middle of these worm gears.Therefore so that can simplified structure, reduce the quantity of parts and simplify parts, reduce thus the cost of making.
A kind of pump also is provided, and wherein dynamic transfer system is by realizing in conjunction with the mechanical component of minimum number, thereby power transmission institute reduces mechanical friction and load thus along the level minimizing of length and the dynamic transfer system in path.Therefore, so that can reduce energy consumption, improve operating efficiency, and the quality of improving pump.
An aspect of of the present present invention provides a kind of double-action rotary pump, and this pump is intended to for the forced conveyance fluid, for example liquid or gas.This pump comprises supply unit and the operating unit that is connected in series with supply unit.Supply unit utilizes by the driving force of dynamic transfer system from the motor transmission and operates with consistent or inconsistent angular velocity, and dynamic transfer system comprises the combination of concentric gear and eccentricity gear.In operating unit, piston comprises the pair of pistons head, and piston head rotates simultaneously distance between the retainer shaft by counteractive mode with inconsistent angular velocity, and piston is divided the space in the cylinder body.The rotation of the volume response piston that is divided the space of cylinder body and repeating and compression and expansion alternately, thus cylinder body reaction ground and carrying out continuously sucks and discharging operation, carries forcibly thus fluid.The structure of the dynamic transfer system of supply unit improves so that the summation of the flow by the piston pumping is consistent in predetermined point of time.Therefore, the fluid of fixed amount can be carried forcibly, becomes possibility so that prevent pulsation thus.In addition, can also reduce the path length on power transmission institute edge and reduce the quantity of the level of dynamic transfer system by simplified structure, reduce thus mechanical friction or load.Therefore, become possibility so that increase the operating efficiency of pump with the quality of improving pump.
According to embodiments of the invention, driving force utilizes the distribution stage of dynamic transfer system and transmitting stage to distribute, described dynamic transfer system is by realizing in conjunction with concentric gear and eccentricity gear, so that the first axle and the second axle operate with counteractive, inconsistent angular velocity.Therefore, the summation of the flow by the piston pumping predetermined time point can be consistent, thus so that the fluid of fixed amount be forced to carry, thereby prevent pulsation.Therefore, can remove noise or vibration, can improve thus the fatigue resistance of equipment and improve pump performance.
In addition, according to embodiments of the invention, unanimously can accurately the measuring fluid and carry forcibly the fluid of fixed amount of the amount by keeping pump institute pumping fluid realizes that in forced conveyance highi degree of accuracy controls thus.
In addition, according to embodiments of the invention, the first axle of transmission unit and the second axle utilize dynamic transfer system to operate with inconsistent angular velocity, described dynamic transfer system is by realizing in conjunction with worm screw and a pair of eccentric worm gear, described worm screw moves as pendulum, and described eccentric worm gear is arranged on the both sides of worm screw so that worm screw medially setting between worm gear.Therefore, can simplified structure, reduce the quantity of parts and simplify parts, lowered thus manufacture cost.
In addition, according to embodiments of the invention, dynamic transfer system realizes by the mechanical component in conjunction with minimum number, thereby the level of the length in the path on power transmission institute edge and dynamic transfer system is reduced, and has reduced thus mechanical friction and load.Therefore, can reduce energy loss, improve operating efficiency, and improve the quality of pump.
In addition, according to embodiments of the invention, because the amount of the fluid by the pumping of pump institute is consistent, accurately measuring flow and carry forcibly the fluid of fixed amount is realized highi degree of accuracy control in forced conveyance thus.
Method and apparatus of the present invention has other characteristics and advantage, these characteristics and advantage will present in more detail in the accompanying drawings or illustrate, these accompanying drawings merge to herein, and in describing in detail below of the present invention, these accompanying drawings one are used from explains some principle of the present invention.
Description of drawings
Fig. 1 shows the normal cross-section figure according to the pump structure of the embodiment of the invention;
Fig. 2 shows the side cross-sectional view according to the pump structure of the embodiment of the invention;
Fig. 3 A and Fig. 3 B show the example view that is applied to according to the dynamic transfer system of the pump of the embodiment of the invention, and wherein Fig. 3 A is the plan of transmission axle, and Fig. 3 B is the plan of transmission gear;
Fig. 4 A shows example view according to the operation of the pump of the embodiment of the invention to Fig. 4 E, wherein Fig. 4 A shows piston and is positioned at 0 ° of position of locating of reference point, Fig. 4 B shows the example view that piston rotates to about 90 ° position, Fig. 4 C shows the example view that piston rotates to about 180 ° position, Fig. 4 D shows the example view that piston rotates to about 270 ° position, and Fig. 4 E shows the example view that piston rotates to about 360 ° position;
Fig. 5 A and Fig. 5 B show the other embodiment's of the dynamic transfer system that may be used in the pump of the present invention example view, and wherein Fig. 5 A is the plan of transmission axle, and Fig. 5 B is the plan of transmission gear;
Fig. 6 A and Fig. 6 B show the other embodiment's of the dynamic transfer system that may be used in the pump of the present invention example view, and wherein Fig. 6 A is the plan of transmission axle, and Fig. 6 B is the plan of transmission gear;
Fig. 7 shows the partial cut front view of pump according to another embodiment of the invention;
Fig. 8 is the cross-sectional view that the line A-A in Fig. 7 cuts open;
Fig. 9 is the cross-sectional view that the line B-B in Fig. 7 cuts open; With
Figure 10 A shows the according to other embodiments of the present invention suction of pump and the example view progressively of discharge process to Figure 10 D.
Embodiment
In detail with reference to each embodiment of the present invention, example is wherein illustrated in the accompanying drawings and is described below now.Fig. 1 and Fig. 2 show in detail the pump according to the embodiment of the invention.The invention provides a kind of double-action rotary pump, this pump is intended to the forced conveyance fluid, for example liquid or gas.
This embodiment's pump generally includes transmission unit 10 and operating unit 20, and described transmission unit 10 and operating unit 20 are surrounded by housing separately, so that they are isolated mutually.
At first, transmission unit 10 comprises: the main driving axle 11 in the middle body of its body, main driving axle 11 receive from motor or outside driving force; And the first axle 12 of a pair of crankshaft and the second axle 13, described the first axle 12 and the second axle 13 are arranged in upper position and the lower position abreast.The first axle 12 and the second axle 13 link with main driving axle 11 and are driven in described main driving axle via dynamic transfer system, and dynamic transfer system will described subsequently.
Main driving axle 11 and the first axle 12 and the second axle 13 link each other by dynamic transfer system, dynamic transfer system is large by utilizing/little with one heart or eccentricity gear or analog obtain suitable transfer ratio in conjunction with several types.In an example, shown in Fig. 3 A and Fig. 3 B, dynamic transfer system 30 comprises distribution stage 31, carries level the 32 and first input stage 33 and the second input stage 34.
Core concept of the present invention is characterised in that, carry the driving force that is incorporated into main driving axle 11 by utilizing distribution stage 31 and 32 pairs of driving forces of conveying level to distribute, thereby corresponding the first axle 12 and the second axle 13 are in opposite direction with inconsistent angular velocity operation.Just because of this, the summation of the flow by the pumping of pump institute can be consistent in predetermined point of time, thereby fluid can be carried forcibly.
Illustrate in greater detail, distribution stage 31 is eccentricity gear, and described distribution stage 31 is arranged on the main driving axle 11, and by the driving force of introducing by means of main driving axle 11 is distributed driving force is provided to the first axle 12 and the second axle 13.The first input stage 33 is concentric gear, and described first end enters level 33 and is arranged on the first axle 12, and it links with the distribution stage 31 of main driving axle 11 via carrying level 32, and receives the driving force from the distribution of main driving axle 11.The second input stage 34 is eccentricity gear, and described the second input stage 34 is arranged on the second axle 13, links with the distribution stage 31 of main driving axle 11, and receives driving force from the distribution of main driving axle 11.Distributed by dynamic transfer system 30 by the driving force that main driving axle 11 is introduced, and corresponding the first axle 12 and the second axle 13 be with the operation of inconsistent angular velocity reaction ground, keeps distance between the axle head according to the operating conditions between the first axle 12 and the second axle 13 thus.
Here, carrying level 32 is conversion element, and this conversion element is used for by the conveying of switching energy and the direction of driving force effect the first axle 12 and the second axle 13 being driven in opposite direction.Carry level 32 by between main driving axle 11 and the first axle 12, using pony axle (idle shaft) 32a to arrange, and comprise input part 32b and output 32c.Input part 32b is eccentricity gear, links with the distribution stage 31 of main driving axle 11, and receives driving force.Output 32c is concentric gear, links with the first input stage 33, and will be delivered to the first input stage 33 by the driving force that input part 32b introduces.
In addition, operating unit 20 in series is arranged on a side of transmission unit 10.In operating unit 20, the first cylinder body 21 and the second cylinder body 22 arrange along a vertical line and up and down, and be connected to each other by penetrating via 23, and described penetrating via 23 extends between the first cylinder body 21 and the second cylinder body 22, limits thus a space.
In addition, suction port 24 and exhaust port 25 direction of between the first cylinder body 21 of operating unit 20 and the second cylinder body 22, intersecting along the penetrating via 23 with the first cylinder body 21 and the second cylinder body 22 and being arranged on the both sides.Suction and the discharging operation of response piston, fluid sucks and discharges by suction port 24 and exhaust port 25, and suction and the discharging operation of described piston will be described later.
Utilize the piston 26 of the first axle 12 and 13 operations of the second axle to be arranged in the first cylinder body and the second cylinder body.Piston 26 comprises a pair of pistons 26a and 26b, and the center deviation heart of described piston head and the first cylinder body 21 and the second cylinder body 22 arranges, and because the angular velocity of the first axle 12 and the second axle 13 is inconsistent, the rotation of piston head reaction ground is distance between the retainer shaft simultaneously.Piston head 26a and 26b interconnect by means of the connector 26c by penetrating via 23, and piston 26 is an integral body thus.Here, connector 26c has the effect of connection piston head 26a and 26b and the effect of division (or separation) cylinder body 21 and 22.
In piston 26, the inwall of piston head 26a and 26b and the first cylinder body 21 and the second cylinder body 22 keeps sliding contact, and demarcates the first cylinder body 21 and the second cylinder body 22 that limits respectively a space, or is divided into right side part and left part.The rotation of the spatial volume response piston 26 that is divided in separately cylinder body 21 and cylinder body 22 and repeating and compression and expansion alternately sucks and discharging operation so that two cylinder bodies 21 and 22 can be carried out with adverse effect and continuous mode.Therefore fluid can pass through the double action mechanical system forced conveyance.
To Fig. 4 E, the explanation of the operating process of pump according to this embodiment of the invention will be provided with reference to figure 4A.Fig. 4 A shows pump operated original state, and wherein piston 26 is positioned at 0 ° and arrival top dead.Here, the second cylinder body 22 is closed and the first cylinder body 21 is opened, thereby fluid begins to enter the leftward space that is divided via suction port 24.
The second piston head 26b that the first piston head 26a that Fig. 4 B shows piston 26 is rotated in a clockwise direction 90 ° and piston 26 is the position at half-twist place in the counterclockwise direction.Here, the leftward space that is divided of the first cylinder body 21 expands, thereby continues to suck fluid.
Fig. 4 C shows piston 26 and is positioned 180 ° of positions of locating to arrive thus bottom dead center.The first cylinder body 21 is closed when expanding into maximum, has finished thus the process that sucks fluid.Contrast simultaneously ground, the second cylinder body 22 is opened, and fluid is drawn into the leftward space that is divided of the second cylinder body 22.
The first piston head 26a that Fig. 4 D shows piston 26 is further rotated about 270 ° along clockwise direction, the second piston head 26b of piston 26 is further rotated about 270 ° position in the counterclockwise direction simultaneously.The leftward space that is divided of the first cylinder body 21 is compressed, begins to discharge thus the fluid of suction by floss hole 25.Contrast simultaneously ground, the leftward space that is divided of the second cylinder body 22 expands, and continues so that suck the process of fluid.
The first piston head 26a that Fig. 4 E shows piston 26 is further rotated 360 ° along clockwise direction, the second piston head 26b of piston 26 is further rotated about 360 ° position in the counterclockwise direction simultaneously, thereby piston 26 returns the position of getting back to Fig. 4 A.In this, the space of the first cylinder body 21 is in the centre that sucks operation and discharging operation, and discharge amount is maximum.Contrast ground, the space of the second cylinder body 22 expand into maximum, has finished thus the process that sucks fluid.Here, do not have fluid to suck the space of the second cylinder body or discharge from the space of the second cylinder body.
Along with the piston 26 that is in this state continues to carry out the pumping procedure that the position with Fig. 4 A begins, the first cylinder body 21 begins to suck fluid, at this moment contrasts ground the second cylinder body 22 and begins to discharge fluid.Therefore, the first cylinder body 21 and the second cylinder body 22 are alternately carried out and are sucked and discharging operation, realize thus desired pumping operation.
Fig. 5 A and Fig. 5 B show the other embodiment of the dynamic transfer system of pump of the present invention.Embodiment before similar, this embodiment's dynamic transfer system 130 interconnects a pair of crankshaft the first axle 12 and the second axle 13.The first axle 12 and the second axle 13 are arranged in upper position and the lower position around main driving axle 11 abreast, and main driving axle receives from motor or outside driving force.Dynamic transfer system 130 comprises distribution stage 131, carries level the 132 and first input stage 133 and the second input stage 134.Here, each in distribution stage 131 and the conveying level 132 is configured to eccentricity gear or any eccentric component, for example sprocket wheel or chain.
Illustrate in greater detail, distribution stage 131 is eccentricity gear, and this distribution stage 131 is arranged on the main driving axle 11, and by the time driving force introduced by means of main driving axle 11 distribute driving force be provided to the first axle 12 and the second axle 13.The first input stage 133 is eccentric chain-wheel, and this first input stage 133 is arranged on the first axle 12, links via conveying level 132 and the distribution stage 131 of chain, and receives driving force from the distribution of main driving axle 11.The second input stage 134 is eccentricity gear, and this second input stage 134 is arranged on the second axle 13, links with the distribution stage 131 of main driving axle 11, and receives driving force from the distribution of main driving axle 11.Therefore, distribute by means of dynamic transfer system 130 via the driving force that main driving axle 11 receives, so that the first axle 12 and the second axle 13 are with inconsistent angular velocity reaction ground operation, so that according to the distance between the operating conditions retainer shaft of the first axle 12 and the second axle 13.
Here, distribution stage 131 comprises the first transfer element 131a and the second transfer element 131b, and this first transfer element is eccentricity gear, and this two transfer element is eccentric chain-wheel.
Fig. 6 A and Fig. 6 B show the other embodiment of the dynamic transfer system of pump of the present invention.Embodiment before similar, this embodiment's dynamic transfer system 230 interconnects the first axle 12 and second axle 13 of a pair of crankshaft.The first axle 12 and the second axle 13 are arranged in upper position and the lower position around main driving axle 11 abreast, and main driving axle receives from motor or outside driving force.Dynamic transfer system 230 comprises distribution stage 231, carries level the 232 and first input stage 233 and the second input stage 234.Here, distribution stage 231 and carry in the level 232 each for example to be configured to concentric gear or eccentricity gear or have large or undersized chain.
Illustrate in greater detail, distribution stage 231 is eccentricity gear, and this distribution stage 231 is arranged on the main driving axle 11, and by the driving force of introducing by means of main driving axle 11 being distributed and driving force being provided to the first axle 12 and the second axle 13.Input stage 233 is concentric gear, and this input stage 233 is arranged on the first axle 12, link with distribution stage 131 via conveying level 232, and reception is from the driving force of the distribution of main driving axle 11.The second input stage 234 is eccentricity gear, and this second input stage 234 is arranged on the second axle 13, links with the distribution stage 131 of main driving axle 11, and receives driving force from the distribution of main driving axle 11.Therefore, distribute by means of dynamic transfer system 230 by the driving force that main driving axle 11 receives, so that the first axle 12 and the second axle 13 are with inconsistent angular velocity reaction ground operation, so that according to the distance between the operating conditions retainer shaft of the first axle 12 and the second axle 13.
Here, distribution stage 231 comprises the first transfer element 231a and the second transfer element 231b, and this first transfer element is eccentricity gear.The second transfer element 231b is configured to input part 231b-1, transport portion 231b-2 and the output 231b-3 of arranged in succession, this input part 231b-1 is the small eccentricity gear, this transport portion 231b-2 is concentric gear, and this output 231b-3 is the large eccentricity gear.
In addition, carrying level 232 is conversion element, is used for by the conveying of switching energy and the direction of driving force effect the first axle 12 and the second axle 13 being driven in opposite direction.Carry level 232 by utilizing the pony axle 232a between main driving axle 11 and the first axle 12 to arrange.The distribution stage 231 of eccentric idler gear 232b and main driving axle 11 links, and receives driving force.Carry level the 232 and first input stage 233 to link, change the direction of introducing the driving force of the first input stage 233 by idler gear 232b.
In addition, the second input stage 234 comprises: the first input part 234a, the concentric gear that this input part links for the first transmission unit 231a with the distribution stage 231 of main driving axle 11; Transport portion 234b, the input part 231b-1 of the second transmission unit 231b of this transport portion 234b and distribution stage 231 links; With the second input part 234c, the output 231b-3 of the second transmission unit 231b of this second input part 234c and distribution stage 231 links.
Shown in arrow among Fig. 6 A, dynamic transfer system 230 is arranged so that it passes through to transmit required power via driving force between main driving axle 11 exchange the first axles 12 and the second axle 13 and by the driving force between exchange main driving axle 11 and the second axle 13.
Fig. 7, Fig. 8 and Fig. 9 show pump according to another embodiment of the invention.The embodiment of this embodiment before the structure of the dynamic transfer system of pump transmission unit is different from.
Embodiment before similar, this embodiment's pump comprises transmission unit 320 and operating unit 330, it is spaced that described transmission unit 320 and operating unit 330 are positioned at housing 310 inherent both sides.This pump also comprises motor 340.
In the supply unit 320 in pump, that as above disposes is such, and the first axle 322 and second axle 324 of a pair of crankshaft are arranged abreast, and utilized via dynamic transfer system from the driving force of motor 340 conveyings and with inconsistent angular velocity operation.
In addition, operating unit 330 in series arranges on a side of transmission unit 320.In operating unit 330, the first cylinder body 336 is arranged on the identical horizontal line with the second cylinder body 337, and is connected to each other by through hole 335, limits thus a space.In addition, suction port 332 and exhaust port 334 are arranged in top part and the bottom part.
In addition, the first cylinder body 336 and the second cylinder body 337 are provided with piston 338, and piston comprises a pair of pistons 338a and 338b.Piston head 338a and 338b utilize the first axle 322 and the second axle 324 to be arranged in the first cylinder body 336 and the second cylinder body 337, so that the center of they and the first cylinder body 336 and the second cylinder body 337 is eccentric.The rotation of piston head 338a and 338b reaction ground is because inconsistent angular velocity and keep simultaneously distance between the axle of eccentric part.Piston 338 also comprises connector 338c, thereby this connector extends connection piston head 338a and 338b by through hole 335.In piston 338, the inwall of piston head 338a and 338b and the first cylinder body 336 and the second cylinder body 337 keeps sliding contact, and is divided into the first cylinder body 336 and the second cylinder body 337 that limits respectively a space, or is divided into right side part and left part.The rotation of the spatial volume response piston 338 that is divided in separately cylinder body 336 and cylinder body 337 and repeating and compression and expansion alternately sucks and discharging operation so that two cylinder bodies 336 and 337 can both be carried out with reaction and continuous mode.Therefore, fluid is carried forcibly by double action mechanical system.Here, connector 338c has first piston head 338a and the interconnective effect of the second piston head 338b and divides the first cylinder body 336 and the each other separately effect of the demarcation strip in space of the second cylinder body 337.
According to the core texture as this embodiment's characteristics, the number of mechanical elements of the dynamic transfer system of transmission unit 320 has reduced effectively, simplifies the structure thus, has reduced the path on Energy transfer institute edge, and has reduced mechanical friction or resistance.
Illustrate in greater detail, the dynamic transfer system 323 of this embodiment's transmission unit 320 comprises worm screw 323a and a pair of eccentric worm gear 323b and 323c.The end of worm screw 323a further extends, thereby forms the bar section with predetermined length.The end of the bar section of worm screw 323a is fixed (supporting element connects with the top part of housing 310) by supporting element 323a-1, so that be delivered to the there from the driving force of the output shaft 342 of motor 340.The other end of worm screw 323a forms free end.Worm screw 323a places between worm gear 323b and the 323c, and these will be described below, and worm screw is guided by the guide rail of the bottom part that is arranged on housing 310, so that worm screw moves as pendulum.
In addition, the engagement of the both sides of worm gear 323b and 323c and worm screw 323a, thereby worm screw 323a is positioned at the centre of worm gear 323b and 323c.Worm gear 323b and 323c are arranged on respectively on the first axle 322 and the second axle 324 prejudicially.
In the dynamic transfer system 323 of as above configuration, when supplying with worm gear 323b and 323c by distribution from the driving force of motor 340 and with driving force, worm screw 323a moves between eccentric worm gear 323b and 323c as pendulum.
In addition, in order to transmit the driving force of motor 340, flexible delivery element 350 is arranged between output shaft 342 and the worm screw 323a.Here, delivery element 350 can be embodied as elasticity or flexible material with resilience, for example disc spring, rubber material or analog.Delivery element receives the output shaft 342 of fixing motor 340 and variation or the change between the movable worm screw 323a, and described motor is installed on the housing 310, and movable worm screw 323a is the sample motion at housing 310 interior picture pendulums.
With reference to figure 10A, 10B, 10C and 10D, provided the explanation of operation of this embodiment's pump.
Figure 10 A shows pump operated reset condition, is positioned at 0 ° and arrival top dead at this state piston 338.Here, the second cylinder body 337 is closed and the first cylinder body 336 is opened, thereby fluid begins to enter via suction port 332 lower space that is divided of the first cylinder body 336.
The second piston head 338b that the first piston head 338a that Figure 10 B shows piston 338 is rotated in a clockwise direction 90 ° and piston 338 is the position at half-twist place in the counterclockwise direction.Here, the lower space that is divided of the first cylinder body 336 expands, thereby proceeds to suck the process of fluid.Simultaneously, the second cylinder body 337 that is in closed condition is opened, thereby begins fluid is sucked the division space of bottom.
Figure 10 C shows piston 338 and is positioned at 180 ° of positions that arrive thus bottom dead center.The first cylinder body 336 is closed when expanding into maximum, thereby has finished the process that sucks fluid.Contrast simultaneously ground, fluid is inhaled in the lower space that is divided of the second cylinder body 337.
The first piston head 338a that Figure 10 D shows piston 338 is further rotated about 270 ° along clockwise direction, the second piston head 338b of piston 338 is further rotated about 270 ° state in the counterclockwise direction simultaneously.The lower space that the is divided compression of the first cylinder body 336 begins the fluid that enters by floss hole 25 dischargings thus.Contrast simultaneously ground, the lower space that is divided of the second cylinder body 337 expands, and continues so that suck the process of fluid.
The second piston head 338b that the first piston head 338a of piston 338 is further rotated 360 ° of while pistons 338 along clockwise direction is further rotated 360 ° in the counterclockwise direction, thereby piston 338 turns back to the position of Figure 10 A.In this, the space of the first cylinder body 336 is in the centre that sucks operation and discharging operation, and discharge amount is maximum.Contrast ground, the space of the second cylinder body 337 expand into maximum, has finished thus the process that sucks fluid.Here, do not have fluid to suck the space of the second cylinder body 336 or discharge from the space of the second cylinder body.
As mentioned above, piston 338 is in cylinder body 336 and 337 interior rotations, and the second cylinder body 337 is discharged fluid so that the first cylinder body 336 sucks fluid.By this way, the first cylinder body 336 and the second cylinder body 337 alternately and are repeatedly carried out and are sucked operation and discharging operation, thereby desired pumping operation is carried out.
Certain exemplary embodiments of the present invention be for setting forth and the purpose of explanation in front description.They are not intended to for exhaustive or limit the invention to disclosed accurate form, and significantly, according to above-mentioned instruction many corrections and variation arranged may.Selecting and describing exemplary embodiment is in order to explain some principle of the present invention and their practical application, thereby so that others skilled in the art can make and utilize the various exemplary embodiments of the present invention and variously substitute and revise.Scope of the present invention is intended to limit by appended here claim and their equivalent.
Claims (10)
1. pump comprises:
Transmission unit, described transmission unit comprises the first axle and second axle of a pair of crankshaft, described the first axle operates with consistent or inconsistent angular velocity from the driving force of motor transmission by means of dynamic transfer system with the second axle utilization, and described dynamic transfer system comprises the combination of concentric gear and eccentricity gear;
Operating unit, described operating unit and transmission unit in series arrange, and wherein said operating unit comprises:
-be positioned at suction port and the exhaust port of the both sides of operating unit;
-be arranged in the first cylinder body and second cylinder body of top part and the bottom part of operating unit, wherein
Described the first cylinder body and the second cylinder alms bowl demarcate mutually, and interconnect by means of through hole;
-comprise the piston of pair of pistons head, each piston head utilizes the corresponding axis in the first axle and the second axle and is arranged in the corresponding cylinder body in the first cylinder body and the second cylinder body, so that the center of each piston head and corresponding cylinder body is eccentric, piston head rotates with inconsistent angular velocity by counteractive mode, distance between the while retainer shaft, described piston also comprises connector, and described connector passes the through hole extension and piston head is interconnected; And
-wherein, the rotation of the volume response piston in the space in the cylinder body of dividing by piston repeats and compression and expansion alternately, thus cylinder body reaction ground and carrying out continuously sucks and discharging operation, carries forcibly thus fluid;
Main driving axle, described main driving axle is arranged between the first axle and the second axle, wherein each axle in main driving axle and the first axle and the second axle all links, and comprise distribution stage, described distribution stage is by distributing the driving force of introducing from motor and this driving force being supplied to the first axle and the second axle;
Be arranged on the first input stage on the first axle, the distribution stage of described the first input stage and main driving axle links, and receives the driving force of distributing;
Be arranged on the second input stage on the second axle, the distribution stage of described the second input stage and main driving axle links, and receives the driving force of distributing; With
Carry level, describedly carry between distribution stage that level places main driving axle and the first order on the first axle or place between the distribution stage and the second level on the second axle of main driving axle, in order to the first axle and the second axle are operated in opposite direction,
Wherein, be incorporated into the driving force of main driving axle by the distribution stage distribution and by carrying level to supply with, so that the first axle and the second axle operate in order to have the opposite effect each other with inconsistent angular velocity.
2. pump according to claim 1, wherein, described distribution stage comprises eccentricity gear, the second input stage of described distribution stage and the second axle and link with carrying level, and distribute driving force.
3. pump according to claim 1, wherein, described distribution stage comprises the first transfer element and the second transfer element, and the second input stage of described the first transfer element and the second axle links, and the first input stage of described the second transfer element and the first axle links.
4. pump according to claim 1, wherein, described distribution stage comprises the first transfer element and the second transfer element, and the second input stage of described the first transfer element and the second axle links, and is input to the second transfer element and exports from the second transfer element from the driving force of the second input stage.
5. pump according to claim 4, wherein, the second transfer element comprises input part, transport portion and output.
6. pump according to claim 1, wherein, carry level to comprise: the input part, thus the distribution stage that described input part is arranged on the pony axle between main driving axle and the first axle with main driving axle links; With, output, the first input stage of described output and the first axle links.
7. pump according to claim 1 wherein, carries level to comprise chain, and described chain directly connects between the first input stage of the distribution stage of main driving axle and the first axle.
8. pump according to claim 1 or 5, wherein, the conveying level comprises the free pulley on the pony axle that is arranged between main driving axle and the first axle, and the transport portion of the second transfer element of the distribution stage of this free pulley and main driving axle and the first input stage of the first axle link.
9. pump according to claim 1, wherein, dynamic transfer system comprises:
Worm screw is fixed an end that transmits from the driving force of motor output shaft thereby described worm screw has by supporting element, and has as the free-ended the other end; With
With the worm gear that mesh the both sides of worm screw, so that worm screw is arranged in the middle of these worm gears, worm gear is arranged on respectively on the first axle and the second axle prejudicially;
Wherein, when supplying with worm gear by distribution from the driving force of motor and with driving force, worm screw carries out the pendulum model motion between eccentric worm gear.
10. pump according to claim 9 also comprises the output shaft that places motor and the flexible delivery element between the worm screw, and this flexible delivery element transmits the driving force of motor towards worm screw.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2011-0075023 | 2011-07-28 | ||
| KR1020110075023A KR101305394B1 (en) | 2011-07-28 | 2011-07-28 | Pump |
| KR10-2012-0026107 | 2012-03-14 | ||
| KR1020120026107A KR101305395B1 (en) | 2012-03-14 | 2012-03-14 | Pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102979719A true CN102979719A (en) | 2013-03-20 |
Family
ID=46603597
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012103414137A Pending CN102979719A (en) | 2011-07-28 | 2012-07-27 | Pump |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20130028779A1 (en) |
| EP (1) | EP2551521A3 (en) |
| CN (1) | CN102979719A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1041606A (en) * | 1912-02-27 | 1912-10-15 | Emil Dembowsky | Engine. |
| CN1130416A (en) * | 1994-05-11 | 1996-09-04 | 罗弼灿 | Pump with twin cylindrical impellers |
| CN1210577A (en) * | 1996-11-11 | 1999-03-10 | 罗弼灿 | Twin-cylinder impeller pump |
| KR20030010453A (en) * | 2001-07-24 | 2003-02-05 | 이기만 | Positive displacement pump having a pair of pumping chambers and method of assembling thereof |
| KR20070064444A (en) * | 2005-12-17 | 2007-06-21 | 나필찬 | Non pulsation twin pump |
| CN101549674A (en) * | 2008-04-01 | 2009-10-07 | 通用汽车环球科技运作公司 | On-demand hydraulic pump for a transmission and method of operation |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH282182A (en) * | 1946-10-07 | 1952-04-15 | Eureka Williams Corp | Pump. |
| JPS58152189A (en) * | 1982-03-08 | 1983-09-09 | Kazuichi Ito | Pulsation-free rotary pump |
| KR20070006444A (en) * | 2005-07-08 | 2007-01-11 | 삼성테크윈 주식회사 | Method of forming bumps and apparatus of arraying conductivity ball |
-
2012
- 2012-07-24 EP EP12177655.3A patent/EP2551521A3/en not_active Withdrawn
- 2012-07-24 US US13/556,717 patent/US20130028779A1/en not_active Abandoned
- 2012-07-27 CN CN2012103414137A patent/CN102979719A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1041606A (en) * | 1912-02-27 | 1912-10-15 | Emil Dembowsky | Engine. |
| CN1130416A (en) * | 1994-05-11 | 1996-09-04 | 罗弼灿 | Pump with twin cylindrical impellers |
| CN1210577A (en) * | 1996-11-11 | 1999-03-10 | 罗弼灿 | Twin-cylinder impeller pump |
| KR20030010453A (en) * | 2001-07-24 | 2003-02-05 | 이기만 | Positive displacement pump having a pair of pumping chambers and method of assembling thereof |
| KR20070064444A (en) * | 2005-12-17 | 2007-06-21 | 나필찬 | Non pulsation twin pump |
| CN101549674A (en) * | 2008-04-01 | 2009-10-07 | 通用汽车环球科技运作公司 | On-demand hydraulic pump for a transmission and method of operation |
Also Published As
| Publication number | Publication date |
|---|---|
| US20130028779A1 (en) | 2013-01-31 |
| EP2551521A3 (en) | 2013-12-25 |
| EP2551521A2 (en) | 2013-01-30 |
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Legal Events
| Date | Code | Title | Description |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20130320 |