KR101030794B1 - Pulseless metering pump using dual constant velocity cam - Google Patents

Pulseless metering pump using dual constant velocity cam Download PDF

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Publication number
KR101030794B1
KR101030794B1 KR1020100072435A KR20100072435A KR101030794B1 KR 101030794 B1 KR101030794 B1 KR 101030794B1 KR 1020100072435 A KR1020100072435 A KR 1020100072435A KR 20100072435 A KR20100072435 A KR 20100072435A KR 101030794 B1 KR101030794 B1 KR 101030794B1
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KR
South Korea
Prior art keywords
cam
constant velocity
constant speed
dual
constant
Prior art date
Application number
KR1020100072435A
Other languages
Korean (ko)
Inventor
이진용
Original Assignee
천세산업 주식회사
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Priority to KR1020100072435A priority Critical patent/KR101030794B1/en
Application granted granted Critical
Publication of KR101030794B1 publication Critical patent/KR101030794B1/en

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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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping
    • 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
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/60—Fluid transfer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Abstract

The metering pump using the dual constant speed cam includes a drive motor mounted on the housing, a worm gear rotated by receiving the driving force of the drive motor, a worm wheel shaft mounted and rotated, and an outer circumferential surface of the worm wheel shaft. The worm wheel is rotated to form a phase difference between the first constant speed cam and the first constant speed cam which protrude into the elliptical cam shape, and the same cam shape as the first constant speed cam and face the first constant speed cam. A first dual constant velocity cam including a second constant velocity cam coupled to the shaft, a second dual constant velocity cam coupled to the worm wheel shaft so as to form a phase difference of 180 ° with the first dual constant velocity cam; And a slider mounted to be slidable inside the housing by the first / second dual constant velocity cam, and a plunger that is slid under the movement pressure of the slider.

Description

Pulsating metering pump using dual constant velocity cams {PULSELESS METERING PUMP USING DUAL CONSTANT VELOCITY CAM}

The present invention relates to a pulsation metering pump, and more particularly, to a pulsation metering pump using a dual constant velocity cam that can be used even where a large force such as high viscosity liquid transfer is required.

In general, the metering pump refers to a pump capable of producing a high pressure at a low speed and accurately discharging a flow rate per unit time by reciprocating a piston, a diaphragm, or the like through a cam shaft. These metering pumps must be supplied quantitatively and reliably, with the desired amount of the user being not significantly affected by pressure.

The reciprocating metering pump, on the other hand, transfers fluid while the piston repeats forward and backward. In the reciprocating metering pump, the piston is advanced by the constant velocity cam when the fluid is discharged, and when the suction is performed, the reverse operation is performed by the spring force.

However, the above-described conventional metering pump has a structural limit that is difficult to improve the size and elastic force of the spring above a certain value, there is a problem that is difficult to apply when a large force for the reverse operation such as the transfer of high viscosity liquid is required. .

The present invention is to solve the problems of the background art described above, and provides a pulsation-free pulsation metering pump that can be applied even when a large force such as the transfer of high viscosity liquid is required.

According to one embodiment of the invention, the drive motor is mounted to the housing, the worm gear is rotated by receiving the driving force of the drive motor, the worm wheel shaft is mounted and rotated is mounted on the worm wheel, and the outer peripheral surface of the worm wheel shaft The same cam shape as the first constant speed cam and the first constant speed cam projecting into the elliptical cam shape and in the state facing the first constant speed cam are rotated to form a phase difference between the first constant speed cam and the worm wheel shaft. A first dual constant velocity cam including a second constant velocity cam coupled to the first dual constant velocity cam, and a rotational coupling to the worm wheel shaft such that a phase difference of 180 ° is formed between the first dual constant velocity cam and the first constant velocity cam and the second constant velocity cam. A second dual constant velocity cam coupled to the worm wheel shaft with the cam rotated so as to form a phase difference therebetween, and the first / second dual constant velocity cam slidable in the housing. And a slider that is, comprising a plunger which is a sliding movement by receiving the pressure of the slider,
The slider is provided with a movable frame movably mounted to the housing, a first roller bearing mounted on one side of the inner wall surface of the movable frame to receive the pressing force from the first constant velocity cam in the plunger direction, and the other side of the inner wall surface of the movable frame. And a second roller bearing mounted on the second roller bearing to receive the pressing force in a direction opposite to the plunger from the second constant velocity cam, and a rod member protruding from the outside of the moving frame to be coupled to the plunger.

The first dual constant velocity cam and the second dual constant velocity cam may be rotated and installed on the worm wheel shaft to have a phase difference of 180 °.

In the first constant speed cam and the second constant speed cam, the second constant speed cam is 0 ° at the maximum displacement of the first constant speed cam, and the first constant speed cam is 0 ° at the maximum displacement of the second constant speed cam. It may be coupled to have a rotation.

The first constant velocity cam and the second constant velocity cam can be combined to have a phase difference in the range of 180 ° to 270 °.

The first constant velocity cam and the second constant velocity cam may be combined to have a phase difference of 237.3 °.

delete

According to one embodiment of the present invention, the constant velocity cam replaces the function of the spring of the conventional pulsation-free metering pump, so that a stable operation of the pulsation-free metering pump is possible even when a large force such as high viscosity liquid is transferred.

1 is a perspective view schematically showing a pulsation metering pump using a dual constant speed cam according to an embodiment of the present invention.
2 is an exploded perspective view of the pulsation metering pump using the dual constant velocity cam of FIG.
3 is a view showing a state in which the first and second dual constant velocity cams are respectively installed inside the slider.
FIG. 4 is a side view of the installed state of the first / second dual constant velocity cam of FIG. 1.
5 is a displacement graph according to a rotation angle of the first constant velocity cam.
6 is a displacement graph according to a rotation angle of a second constant velocity cam.
FIG. 7 is a displacement graph overlapping the displacement graph of FIG. 5 and the displacement graph of FIG. 6.

Hereinafter, a pulsation-free pulsation metering pump using a dual constant velocity cam according to embodiments of the present invention will be described in detail with reference to the accompanying drawings. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. It is provided to let you know.

1 is a perspective view schematically showing a pulsation metering pump using a dual constant velocity cam according to an embodiment of the present invention, Figure 2 is an exploded perspective view of the pulsation metering pump using a dual constant velocity cam of Figure 1;

1 and 2, the pulsation-free metering pump 100 using the dual constant speed cam according to an embodiment of the present invention, the drive motor 10 is mounted to the housing 11, the drive motor First / first to be installed on the worm wheel 20 and the worm wheel shaft 30 is rotated by mounting the worm gear 20 is rotated by receiving the driving force of the (10), the worm wheel meshed with the worm gear 20 2 dual constant velocity cams 40A and 40B, a slider 50 mounted to be slidable by the first and second dual constant velocity cams 40A and 40B, and a plunger moved in conjunction with the slider 50 ( 60).

The drive motor 10 is installed in the housing 11 to transmit the driving force. The drive motor 10 is equipped with a motor controller 13 to control the drive of the drive motor 10, it is installed in the housing by the attachment (15). Reference numeral 12 is a housing supporter, and 17 is a gasket. Operation control of the motor controller 13 is well known and detailed description thereof will be omitted below. The driving force of the drive motor 10 is transmitted to the worm gear 20.

The worm gear 20 is rotated by receiving the driving force of the drive motor 10 from the inside of the housing 11, the worm wheel shaft 30 is engaged. Reference numeral 21 is a leaf spring and 23 is a bearing.

The worm wheel shaft 30 is mounted with a worm wheel 31 meshed with the worm gear 20 so as to be rotationally driven inside the housing 11. The first dual constant velocity cam 40A and the second dual constant velocity cam 40B are respectively coupled to the worm wheel shaft 30.

The first dual constant velocity cam 40A and the second dual constant velocity cam 40B are coupled to the worm wheel shaft 30 in a rotated state to have a phase difference of 180 degrees. The first dual constant velocity cam 40A and the second dual constant velocity cam 40B are coupled in a state of being rotated to have a phase difference of 180 degrees to prevent pulsation from occurring during operation of the pulsationless metering pump. It is known to reduce the pulsation of the pulsation-free pulsation metering pump by forming two equal velocity cams with a 180 ° phase difference, and a detailed description thereof will be omitted.

Hereinafter, the configuration and operation of the first and second dual constant speed cams 40A and 40B coupled to the wheelwheel shaft 30 will be described in more detail with reference to the drawings.

3 is a view showing a state in which the first and second dual constant speed cams 40A and 40B are respectively installed inside the slider 50, and FIG. 4 is a view of the first and second dual constant speed cams of FIG. It is the figure which looked at the installation state of 40A, 40B) from the side.

As shown in FIGS. 3 and 4, the first / second dual constant velocity cams 40A, 40B have a first constant velocity cam 41 and a second constant velocity for providing sliding drive force to the slider 50. Each cam 43 is included. The first dual constant velocity cam 40A and the second dual constant velocity cam 40B have the same configuration, and the configuration thereof will be described below only for one.

In the present embodiment, the first constant velocity cam 41 transmits the pressing force so that the slider 50 moves in the plunger 60 direction, and the second constant velocity cam 43 has the slider 50 of the plunger 60. The pressing force is transmitted to move in the opposite direction.

The slider 50 is installed to be movable inside the housing 11 to selectively move the plunger 60. The slider 50 and the first and second roller bearings 53 and 55 are provided. And a rod member 57.

The moving frame 51 moves inside the housing 11, forms a space therein, and may have a rectangular shape. Of course, the moving frame 51 is not limited to the shape of a rectangle, but may also be transformed into a shape of a polygon including a square or a curve.

The first roller bearing 53 is mounted on one side of the inner wall surface of the moving frame 51, and the second roller bearing 55 is mounted on the other side of the inner wall surface of the moving frame 51. That is, the first roller bearing 53 and the second roller bearing 55 are mounted at positions opposed to each other inside the moving frame 51.

The first roller bearing 53 is in contact with the first constant speed cam 41 to receive the moving pressing force, and the second roller bearing 55 is in contact with the second constant speed cam 43 to receive the moving pressing force. .

When the moving pressing force is transmitted to the first roller bearing 53, the slider 50 is moved in the plunger 60 direction and the plunger 60 connected to the rod member 57 is moved. When the plunger 60 is moved, deformation of the diaphragm, which is not shown, is generated, and a discharge action of the fluid occurs.

When the moving pressing force is transmitted to the second roller bearing 55, the slider 50 is moved in the opposite direction of the plunger 60 to generate a suction action of the fluid. The plunger 60 may be mounted by the gearbox flange 61 and the plunger housing 63. Reference numeral 65 denotes a suction part of the transfer fluid and 67 denotes a discharge part of the transfer fluid.

Hereinafter, referring to FIG. 4, the movement operation of the slider 50 will be described in more detail with reference to the configuration of the first and second constant velocity cams 41 and 43.

As shown in FIG. 4, the first / second constant velocity cams 41 and 43 are constant velocity cams of the same shape, and either one of the constant velocity cams is turned upside down of the other constant velocity cam. It is coupled in a state facing the side. The first constant velocity cam 41 and the second constant velocity cam 43 may be coupled to each other in surface contact with each other, or between the first constant velocity cam 41 and the second constant velocity cam 43. It is also possible to combine the two at a certain distance apart.

As described above, the first constant velocity cam 41 and the second constant velocity cam 43 are rotationally coupled to face each other to have a phase difference therebetween. Here, the phase difference between the first constant speed cam 41 and the second constant speed cam 43 is defined by the first constant speed cam 41 at a predetermined angle when the dual constant speed cams 40A and 40B rotate. To allow the 50 to slide to the plunger 60 in the maximum direction, and the slider 50 to the maximum sliding in the direction opposite to the discharge portion by the second constant velocity cam 43 at an angle corresponding to the phase difference. For sake.

In the present embodiment, the first constant velocity cam 41 and the second constant velocity cam 43 may be rotatably coupled to have a phase difference of 237.3 °. However, in this embodiment, the first constant velocity cam 41 and the second constant velocity cam 43 are not limited to the phase difference of 237.3 degrees. That is, at the maximum displacement of the first constant velocity cam 41, the second constant velocity cam 43 is 0 °, and at the maximum displacement of the second constant velocity cam 43, the first constant velocity cam 41 is 0 °. It can be combined to rotate. Accordingly, the first constant velocity cam 41 and the second constant velocity cam 43 are not limited to the phase difference of 237.3 ° according to the change of the design specification, and may be selected and combined in the range of 180 ° to 270 ° phase difference. Hereinafter, an exemplary embodiment in which the first constant speed cam 41 and the second constant speed cam 43 have 237.3 ° will be described.

As described above, when the first constant velocity cam 41 and the second constant velocity cam 43 are coupled to have a phase difference of 237.3 °, the outer shape of the first constant velocity cam 41 is as shown in FIG. 4. The shape overlapping the outer shape of the second constant velocity cam 43 will always have a constant value regardless of the rotation angle. Therefore, the dual constant velocity cams 40A and 40B always move in close contact between the first roller bearing 53 and the second roller bearing 55 even if they are rotated. However, when the phase difference between the first constant speed cam 41 and the second constant speed cam 43 is out of 237.3 °, the sum of the displacements of the first constant speed cam 41 and the second constant speed cam 43 does not coincide. Will not. Accordingly, when the dual constant velocity cams 40A and 40B are rotated, they cannot always be in close contact with the first roller bearing 53 and the second roller bearing 55, so that the forward or backward operation of the plunger 60 is smoothly performed. It becomes impossible. This will be described in more detail with reference to the displacement graph below.

5 is a displacement graph according to the rotation angle of the first constant velocity cam, FIG. 6 is a displacement graph according to the rotation angle of the second constant velocity cam, and FIG. 7 overlaps the displacement graph of FIG. 5 with the displacement graph of FIG. One displacement graph.

As shown in FIG. 5, the first constant velocity cam 41 has a maximum displacement value at a rotation angle of 237.3 °, and as shown in FIG. 6, the second constant velocity cam 43 in an inverted state is 122.7. Has a maximum displacement at °. At this time, when the displacement graph is superimposed at 237.3 ° of the rotational angle 237.3 ° of the first constant velocity cam 41 and 0 ° of the rotational angle of the second constant velocity cam 43, the rotational angle always has a constant displacement value at any rotational angle. . That is, when the first constant speed cam 41 and the second constant speed cam 43 are combined to have a phase difference of 237.3 °, the first constant speed cam 41 and the second constant speed cam ( The sum of the displacements of 43) will always have a constant displacement value. Therefore, the dual constant speed cams 40A and 40B can move the slider 50 constantly in accordance with the rotation thereof.

In this embodiment, the first constant velocity cam 41 presses the first roller bearing 53 to control the slider 50 to move in the plunger 60 direction, and the second constant velocity cam 43 is The slider 50 controls the movement in the direction opposite to the plunger 60 direction. Therefore, the second constant velocity cam 43 replaces the spring which functions as the conventional second constant velocity cam 43, thereby quantifying the present embodiment even when a large force is required, such as when reversing the transfer of high viscosity liquid. Application of the pump becomes possible.

The present invention has been described above with reference to the embodiments shown in the drawings. However, the present invention is not limited thereto, and various modifications or other embodiments falling within the scope equivalent to the present invention are possible by those skilled in the art. Accordingly, the true scope of protection of the present invention should be determined by the following claims.

10 ... drive motor 11 ... housing
12.Housing supporter 13 ... Motor controller
15.Attachment 17.Gasket
20 ... worm gear 21 ... plate spring
23 Bearing 30 Wheel Wheel Shaft
31 ... 윔 wheel 40A..1 dual constant speed cam
40B..2 Dual constant speed cam 50 ... slider
51 ... moving frame 53 ... first roller bearing
55 ... 2nd roller bearing 57 ... rod member
60 ... plunger

Claims (6)

A drive motor mounted to the housing;
A worm gear that is rotated by receiving the driving force of the driving motor;
A worm wheel shaft on which a worm wheel engaged with the worm gear is mounted;
Phase difference between the first constant speed cam projecting in the shape of an elliptical cam on the outer circumferential surface of the worm wheel shaft, and the same cam shape as the first constant speed cam and facing the first constant speed cam. A first dual constant velocity cam including a second constant velocity cam coupled to the worm wheel shaft in a rotated state such that a second rotation speed is formed;
The worm wheel is rotatably coupled to the worm wheel shaft to form a phase difference of 180 ° with the first dual constant speed cam, and the first constant speed cam and the second constant speed cam are rotated to form a phase difference between the worm wheels. A second dual constant velocity cam coupled to the shaft;
A slider mounted to be slidable inside the housing by the first / second dual constant speed cam; And
A plunger sliding under the movement pressure of the slider;
Including;
The slider,
A moving frame movably installed in the housing, a first roller bearing installed on one side of an inner wall surface of the moving frame and receiving a pressing force from the first constant velocity cam in the plunger direction, and an inner wall surface of the moving frame A second roller bearing installed on the other side of the second roller bearing to receive a pressing force from the second constant velocity cam in the opposite direction of the plunger, and a rod member protruding outside the moving frame to be coupled to the plunger; Pulseless metering pump with cam. The method of claim 1,
The first dual constant speed cam and the second dual constant speed cam is a non-pulsation metering pump using a dual constant speed cam is installed to rotate to have a phase difference of 180 ° to the worm wheel shaft. The method of claim 1,
The first constant speed cam and the second constant speed cam,
The dual constant velocity cam is rotatably coupled such that the second constant velocity cam is 0 ° at the maximum displacement of the first constant velocity cam, and the first constant velocity cam is 0 ° at the maximum displacement of the second constant velocity cam. Pulsation-free pulse metering pump. The method of claim 1,
And the first constant speed cam and the second constant speed cam are coupled to have a phase difference in a range of 180 ° to 270 °. The method of claim 1,
The first constant velocity cam and the second constant velocity cam is a pulsation metering pump using a dual constant velocity cam coupled to have a phase difference of 237.3 °. delete
KR1020100072435A 2010-07-27 2010-07-27 Pulseless metering pump using dual constant velocity cam KR101030794B1 (en)

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KR1020100072435A KR101030794B1 (en) 2010-07-27 2010-07-27 Pulseless metering pump using dual constant velocity cam

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Application Number Priority Date Filing Date Title
KR1020100072435A KR101030794B1 (en) 2010-07-27 2010-07-27 Pulseless metering pump using dual constant velocity cam

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101255595B1 (en) 2011-11-07 2013-04-16 이상헌 Constant volume pump
KR20180101876A (en) 2017-03-06 2018-09-14 윤병일 No pulsation pump
CN109296515A (en) * 2018-09-03 2019-02-01 陕西科技大学 A kind of double feed type delivery pumps

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1435456A2 (en) * 2002-12-06 2004-07-07 Delphi Technologies, Inc. Hydraulic Pump
KR20060005583A (en) * 2004-07-13 2006-01-18 천세산업 주식회사 Correction method for uniform velocity cam and pulseless diaphragm pump using it
KR20070110446A (en) * 2005-06-08 2007-11-16 봇슈 가부시키가이샤 Fuel feed pump and tappet structure

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1435456A2 (en) * 2002-12-06 2004-07-07 Delphi Technologies, Inc. Hydraulic Pump
KR20060005583A (en) * 2004-07-13 2006-01-18 천세산업 주식회사 Correction method for uniform velocity cam and pulseless diaphragm pump using it
KR20070110446A (en) * 2005-06-08 2007-11-16 봇슈 가부시키가이샤 Fuel feed pump and tappet structure

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101255595B1 (en) 2011-11-07 2013-04-16 이상헌 Constant volume pump
KR20180101876A (en) 2017-03-06 2018-09-14 윤병일 No pulsation pump
CN109296515A (en) * 2018-09-03 2019-02-01 陕西科技大学 A kind of double feed type delivery pumps

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