FreshPatents.com Logo
stats FreshPatents Stats
n/a views for this patent on FreshPatents.com
Updated: September 07 2014
newTOP 200 Companies filing patents this week


    Free Services  

  • MONITOR KEYWORDS
  • Enter keywords & we'll notify you when a new patent matches your request (weekly update).

  • ORGANIZER
  • Save & organize patents so you can view them later.

  • RSS rss
  • Create custom RSS feeds. Track keywords without receiving email.

  • ARCHIVE
  • View the last few months of your Keyword emails.

  • COMPANY DIRECTORY
  • Patents sorted by company.

Follow us on Twitter
twitter icon@FreshPatents

Pump

last patentdownload pdfdownload imgimage previewnext patent


20130028779 patent thumbnailZoom

Pump


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.
Related Terms: Spaces

USPTO Applicaton #: #20130028779 - Class: 418204 (USPTO) - 01/31/13 - Class 418 
Rotary Expansible Chamber Devices > Interengaging Rotating Members >Eccentrically Mounted

Inventors: Phil Chan Rha

view organizer monitor keywords


The Patent Description & Claims data below is from USPTO Patent Application 20130028779, Pump.

last patentpdficondownload pdfimage previewnext patent

CROSS REFERENCE TO RELATED APPLICATION

The present application claims priority from Korean Patent Application Numbers 10-2011-75023 filed on Jul. 28, 2011 and 10-2012-26107 filed on Mar. 14, 2012, the entire contents of which application are incorporated herein for all purposes by this reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

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. In this pump, 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.

2. Description of Related Art

Several types of double action rotary pumps for forcibly delivering fluid have been developed and used to dates. 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. In addition, in the operating unit, a piston 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.

According to the operating condition for the rotation of the piston, 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. However, in the pump configured as above, 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.

However, in the operation of this type of pump, 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°. In this fashion, 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.

Therefore, 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.

In addition, in the pump as described above, 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.

Furthermore, since 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. In addition, 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.

The information disclosed in this Background of the Invention section is only for the enhancement of understanding of the background of the invention, and should not be taken as an acknowledgment or any form of suggestion that this information forms a prior art that would already be known to a person skilled in the art.

BRIEF

SUMMARY

OF THE INVENTION

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.

Also provided is 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.

Also provided is 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.

In an aspect of the present invention, provided is 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. In the operating unit, 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. In addition, it is possible to decrease the length of the route along which power is transmitted and reduce the number of the stages of the power transmission system by simplifying the structure, thereby reducing mechanical friction or load. Accordingly, it is possible to increase the operating efficiency of the pump and improve the quality of the pump.

According to embodiments of the invention, 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.

In addition, according to embodiments of the invention, it is possible to precisely measure a flow rate and forcibly deliver a fixed amount of fluid by maintaining the amount of fluid that is pumped by the pump to be uniform, thereby enabling high-precision control over forced delivery.

Furthermore, according to embodiments of the invention, 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.

In addition, according to embodiments of the invention, 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.

Furthermore, according to embodiments of the invention, since 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.

The methods and apparatuses of the present invention have other features and advantages which will be apparent from, or are set forth in greater detail in the accompanying drawings, which are incorporated herein, and in the following Detailed Description of the Invention, which together serve to explain certain principles of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

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; and

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.

DETAILED DESCRIPTION

OF THE INVENTION

Reference will now be made in detail to various embodiments of the present invention, examples of which are illustrated in the accompanying drawings and described below. 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.

First, 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.

The main drive shaft 11 and the first and second shafts and 13 are associated with each other by the power transmission system, which obtains a suitable transmission ratio by combining several types using large/small concentric or eccentric gears or the like. In an example, as shown in FIG. 3A and FIG. 3B, 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.

Describing in more detail, 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.

Here, 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.

In addition, the operating unit 20 is provided in series on one side of the transmission unit 10. In the operating unit 20, 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.

In addition, 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. In response to the intake and exhaust operations of a piston, which will be described later, 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. Here, 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.

In the piston 26, 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.

With reference to FIG. 4A to FIG. 4E, a description will be given of the process of operating the pump according to this embodiment of the invention. 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. Here, 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. Here, 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. At the same time, in contrast, the second cylinder 22 is opened, and fluid is being taken into the divided left space of the second cylinder 22.



Download full PDF for full patent description/claims.

Advertise on FreshPatents.com - Rates & Info


You can also Monitor Keywords and Search for tracking patents relating to this Pump patent application.
###
monitor keywords



Keyword Monitor How KEYWORD MONITOR works... a FREE service from FreshPatents
1. Sign up (takes 30 seconds). 2. Fill in the keywords to be monitored.
3. Each week you receive an email with patent applications related to your keywords.  
Start now! - Receive info on patent apps like Pump or other areas of interest.
###


Previous Patent Application:
Stator of a gerotor device and a method for manufacturing roller pockets in a stator of a gerotor device
Next Patent Application:
Iron-based sintered powder metal for wear resistant applications
Industry Class:
Rotary expansible chamber devices
Thank you for viewing the Pump patent info.
- - - Apple patents, Boeing patents, Google patents, IBM patents, Jabil patents, Coca Cola patents, Motorola patents

Results in 0.50396 seconds


Other interesting Freshpatents.com categories:
Software:  Finance AI Databases Development Document Navigation Error

###

Data source: patent applications published in the public domain by the United States Patent and Trademark Office (USPTO). Information published here is for research/educational purposes only. FreshPatents is not affiliated with the USPTO, assignee companies, inventors, law firms or other assignees. Patent applications, documents and images may contain trademarks of the respective companies/authors. FreshPatents is not responsible for the accuracy, validity or otherwise contents of these public document patent application filings. When possible a complete PDF is provided, however, in some cases the presented document/images is an abstract or sampling of the full patent application for display purposes. FreshPatents.com Terms/Support
-g2-0.1951
     SHARE
  
           

FreshNews promo


stats Patent Info
Application #
US 20130028779 A1
Publish Date
01/31/2013
Document #
13556717
File Date
07/24/2012
USPTO Class
418204
Other USPTO Classes
418209
International Class
/
Drawings
14


Spaces


Follow us on Twitter
twitter icon@FreshPatents