WO2013145576A1 - ポンプ装置 - Google Patents
ポンプ装置 Download PDFInfo
- Publication number
- WO2013145576A1 WO2013145576A1 PCT/JP2013/001436 JP2013001436W WO2013145576A1 WO 2013145576 A1 WO2013145576 A1 WO 2013145576A1 JP 2013001436 W JP2013001436 W JP 2013001436W WO 2013145576 A1 WO2013145576 A1 WO 2013145576A1
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- WIPO (PCT)
- Prior art keywords
- pump
- piston
- pressure
- drive shaft
- stage
- Prior art date
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Classifications
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
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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
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
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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
- F04B2201/00—Pump parameters
- F04B2201/02—Piston parameters
- F04B2201/0201—Position of the piston
- F04B2201/02011—Angular position of a piston rotating around its own axis
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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
- F04B2201/00—Pump parameters
- F04B2201/08—Cylinder or housing parameters
- F04B2201/0802—Vibration
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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
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0201—Current
Definitions
- the present invention relates to a pump device including a vacuum pump and a pressure pump.
- An oscillating piston pump which is a kind of vacuum pump, is known as a reciprocating pump that alternately performs intake and exhaust of air in a pump chamber by reciprocating a piston in a cylinder. Widely used as a pump.
- a composite pump device having two pistons for evacuation and pressurization driven simultaneously by a common motor is also known.
- a driving method of this type of pump device there are known a method of reciprocating the two pistons in mutually opposite phases and a method of reciprocating them in the same phase (for example, Patent Document 1 below). reference).
- the former method that is, a driving method in which the rotational phases of both pistons are reciprocated by 180 ° has the advantage that the dynamic balance of each pump can be maintained well and the vibration of the entire pump device can be reduced.
- the latter method that is, a driving method in which both pistons are moved to the top dead center or the bottom dead center at the same time, can reduce the load fluctuation of the driving source and realize a stable operation of the pump device.
- an object of the present invention is to provide a pump device that can realize further reduction in power consumption.
- a pump device includes a drive motor, a first pump unit for evacuation, and a second pump unit for pressurization.
- the drive motor has a first drive shaft and a second drive shaft.
- the drive motor is configured to be able to rotate the first drive shaft and the second drive shaft in synchronization with the first shaft.
- the first pump unit responds to the reciprocation of the first piston that reciprocates in the second axial direction perpendicular to the first axis by the rotation of the first drive shaft, and the reciprocation of the first piston.
- a first pump chamber whose internal pressure changes.
- the second pump section includes a second piston that reciprocates in the second axial direction by rotation of the second drive shaft, and a second piston whose internal pressure changes according to the reciprocating movement of the second piston. And a pump chamber.
- the second piston advances with a rotational phase difference of more than 0 ° and less than 80 ° with respect to the first piston.
- FIG. 1 It is the perspective view seen from the front side of the pump apparatus which concerns on one Embodiment of this invention. It is the perspective view seen from the back side of the said pump apparatus. It is a right view of the said pump apparatus. It is a left view of the said pump apparatus. It is a longitudinal cross-sectional view which shows the structure of a part of vacuum pump part and drive part of the said pump apparatus. It is a schematic diagram explaining the relationship between the eccentric shaft by the side of the vacuum pump part of the said pump apparatus, and the eccentric shaft by the side of a pressurization pump part, (A) is a front view, (B) is from the vacuum pump part side.
- (B) shows the time change of the pump chamber pressure and the piston position in the pressurizing stage
- (C) shows the pressure waveform of the pump chamber in the vacuum stage and the pressure waveform of the pump chamber in the pressurizing stage.
- the composite waveform is shown. It is an experimental result which shows the relationship between the rotation phase difference of the piston of a pressurization stage with respect to the piston of a vacuum stage, and the consumption current of a motor.
- the internal pressure of the pump chamber in the oscillating piston pump changes periodically as the piston reciprocates. For example, when the piston moves from bottom dead center to top dead center, the volume of the pump chamber decreases, so the internal pressure changes in an increasing direction. When the piston moves from top dead center to bottom dead center, the volume of the pump chamber increases. Therefore, the internal pressure changes in the decreasing direction. At this time, in the case of a vacuum pump, the internal pressure of the pump chamber changes in a pressure range below the atmospheric pressure (negative pressure), and in the case of a pressure pump, the internal pressure of the pump chamber in a pressure range above the atmospheric pressure (positive pressure). Changes.
- the pump device in order to realize further reduction of power consumption of the pump device, the pump device is configured as follows.
- a pump device includes a drive motor, a first pump unit for evacuation, and a second pump unit for pressurization.
- the drive motor has a first drive shaft and a second drive shaft.
- the drive motor is configured to be able to rotate the first drive shaft and the second drive shaft in synchronization with the first shaft.
- the first pump unit responds to the reciprocation of the first piston that reciprocates in the second axial direction perpendicular to the first axis by the rotation of the first drive shaft, and the reciprocation of the first piston. And a first pump chamber whose internal pressure changes.
- the second pump section includes a second piston that reciprocates in the second axial direction by rotation of the second drive shaft, and a second piston whose internal pressure changes according to the reciprocating movement of the second piston. And a pump chamber.
- the second piston advances with a rotational phase difference of more than 0 ° and less than 80 ° with respect to the first piston.
- the piston top dead center and the pressure peak position of the pump chamber almost coincide with each other in the first pump unit for evacuation, but the piston in the second pump unit for pressurization.
- the top dead center and the pressure peak position in the pump chamber did not match.
- the pump chamber reached a pressure peak before the piston reached top dead center.
- the rotational phase difference can be set as appropriate within a range of more than 0 ° and less than 80 °. For example, a stable power consumption reduction effect can be obtained at 40 ° ⁇ 30 °, and further consumption within a range of 40 ° ⁇ 15 °. A power reduction effect can be obtained. Thus, by optimizing the rotational phase difference, the pump device can be stably operated with low power consumption.
- FIG. 1 to 4 are external views showing a pump device according to an embodiment of the present invention.
- FIG. 1 is a perspective view seen from the front side
- FIG. 2 is a perspective view seen from the back side
- FIG. FIG. 4 is a left side view.
- the pump device 1 of the present embodiment includes a vacuum pump unit 11 (first pump unit) as a vacuum stage, a pressurizing pump unit 12 (second pump unit) as a pressurizing stage, a vacuum pump unit 11, And a drive unit 13 that drives the pressure pump unit 12 in common.
- the pump device 1 is used as, for example, a gas pressure booster used in a fuel cell system, a vacuum and a pressure pump used in a medical analyzer.
- the vacuum pump unit 11 and the pressurizing pump unit 12 typically have a common configuration, and are configured as a swing piston pump in this embodiment.
- the pump device 1 includes a first casing 101 that constitutes a part of the vacuum pump unit 11, a second casing 102 that constitutes a part of the pressure pump unit 12, and a second part that constitutes a part of the drive unit 13. And a pump case 100 including three casings 103.
- FIG. 5 is a longitudinal sectional view showing a part of the configuration of the vacuum pump unit 11 and the drive unit 13.
- an X axis, a Y axis, and a Z axis indicate three axial directions that are orthogonal to each other.
- the pressurization pump part 12 has the structure similar to the vacuum pump part 11, the vacuum pump part 11 is mainly demonstrated here.
- the vacuum pump unit 11 has a first casing 101, a piston 21, a connecting rod 22 (rod member), and an eccentric member 23.
- the first casing 101 includes a case main body 110, a cylinder 111, a pump head 112, and a pump head cover 113.
- the case body 110, the cylinder 111, the pump head 112, and the pump head cover 113 are integrated with each other so as to be stacked in the Z-axis direction.
- the case body 110 is connected to the third casing 103 that houses the motor M, and has a through hole 110h through which the connecting rod 22 passes.
- the case main body 110 includes a fixed portion 110 a that fixes the bearing 32 that rotatably supports the drive shaft 131 of the motor M, and a cylindrical portion 110 b that houses the coil 132 of the motor M.
- the drive shaft 131 is disposed parallel to the Y-axis direction (first axial direction), and rotates around the Y-axis by driving the motor M.
- the bearing 32 is disposed between the main body of the motor M and the eccentric member 23.
- the cylinder 111 is disposed between the case main body 110 and the pump head 112, and accommodates the piston 21 slidably in the Z-axis direction.
- the pump head 112 is disposed between the cylinder 111 and the pump head cover 113, and includes an intake valve 112a and an exhaust valve 112b.
- the pump head cover 113 is disposed on the pump head 112 and has an intake chamber 113a that communicates with the intake port 114a and an exhaust chamber 113b that communicates with the exhaust port 114b. As shown in FIGS. 1 and 2, the intake port 114a and the exhaust port 114b are provided on the side surfaces of the pump portions 11 and 12 facing each other.
- the piston 21 has a disk shape, and is fixed to the first end 221 of the connecting rod 22 via a screw member 25.
- the piston 21 forms a pump chamber 26 between the piston 21 and the pump head 112.
- the piston 21 changes the internal pressure of the pump chamber 26 by reciprocating in the direction parallel to the Z-axis direction (second axial direction) inside the cylinder 111.
- the piston 21 performs a predetermined pump action by alternately sucking and exhausting the pump chamber 26 via the intake valve 112a and the exhaust valve 112b.
- the connecting rod 22 connects the piston 21 and the eccentric member 23 to each other.
- the connecting rod 22 has a first end 221 connected to the piston 21 and a second end 222 connected to the eccentric member 23.
- the first end 221 is formed in a circular shape having substantially the same diameter as the piston 21.
- a disc-shaped seal member 24 is attached between the piston 21 and the first end 221. The peripheral portion of the seal member 24 is bent toward the pump chamber 26 so as to be slidable on the inner peripheral surface of the cylinder 111.
- the peripheral edge of the seal member is bent toward the pump chamber, contrary to the above example.
- a fitting hole 222a for fitting with the eccentric shaft 232 of the eccentric member 23 is formed in the second end portion 222 of the connecting rod 22, a fitting hole 222a for fitting with the eccentric shaft 232 of the eccentric member 23 is formed.
- a bearing 31 that rotatably supports the eccentric shaft 232 is mounted in the fitting hole 222a.
- the eccentric member 23 connects the drive shaft 131 of the motor M accommodated in the third casing 103 and the connecting rod 22 to each other.
- the eccentric member 23 has a substantially cylindrical base block 230.
- a drive shaft 131 is connected to the surface of the base block 230 on the motor M side, and an eccentric shaft 232 is formed on the surface of the connecting rod 22 side.
- the shaft axis of the eccentric shaft 232 is eccentric with respect to the drive shaft 131 so as to be deflected as the drive shaft 131 rotates.
- the drive shaft 131 is connected to the base block 230 by screws 41 fastened to the side peripheral surface of the base block 230.
- a counterweight 51 is attached to the eccentric member 23.
- the counterweight 51 is fixed to the side peripheral portion of the eccentric member 23 by a fixing screw 42 fastened to the side peripheral surface of the base block 230.
- the counterweight 51 rotates together with the piston 21 and has a function of canceling vibration generated when the connecting rod 22 rotates around the eccentric shaft 232 as the drive shaft 131 rotates.
- the counterweight 51 is disposed at a position deviated in the direction opposite to the eccentric direction of the eccentric shaft 232 with respect to the drive shaft 131.
- the eccentric member 23 rotates around the drive shaft 131 by driving the motor M, so that the eccentric shaft 232 is offset from the drive shaft 131. Revolves around the drive shaft 131 along a circumference having a radius corresponding to.
- the connecting rod 22 connected to the eccentric shaft 232 converts the rotation of the drive shaft 131 into the reciprocating movement of the piston 21 inside the cylinder 111. That is, the piston 21 reciprocates in the Z-axis direction while swinging in the X-axis direction in FIG. As a result, intake and exhaust of the pump chamber 26 are alternately performed, and a predetermined vacuum exhaust action by the vacuum pump unit 11 is obtained.
- the pressurizing pump unit 12 is configured in the same manner as the vacuum pump unit 11, and the drive shaft 131 protrudes also to the pressurizing pump unit 12 side and is connected to an eccentric shaft (not shown) of the pressurizing pump unit 12. The Thus, the pressurizing pump unit 12 is driven by the common motor M simultaneously with the vacuum pump unit 11 and performs a predetermined pressurizing (pressurizing) action.
- the vacuum pump unit 11 and the pressurizing pump unit 12 are driven in mutually different phases. That is, in the present embodiment, the piston 21 (second piston) of the pressurizing pump unit 12 advances with a rotational phase difference of more than 0 ° and less than 80 ° with respect to the piston 21 (first piston) of the vacuum pump unit 11. Configured to do.
- the positions of the eccentric shafts 232 of the pumps 11 and 12 are made different so that the pistons have the rotational phase differences as described above. According to the present embodiment, since the eccentric member 23 is fixed to the drive shaft 131 only by fastening the screw 41, the relative positions of the eccentric shafts 232 in the two pumps 11 and 12 can be easily adjusted.
- the counterweight 52 of the pressurizing pump unit 12 is rotated in the rotational direction of the drive shaft 131 (centered on the Y axis in FIG. It is fixed at a position advanced in the clockwise direction (counterclockwise around the Y axis in FIG. 4) by the predetermined rotational phase difference (over 0 ° and less than 80 °).
- FIG. 6A and 6B are schematic views for explaining the relationship between the eccentric shaft 232v on the vacuum pump unit 11 side and the eccentric shaft 232c on the pressure pump unit 12 side
- FIG. FIG. 4B is a side view seen from the vacuum pump unit 11 side.
- the eccentric shaft 232c on the pressure pump side is provided at a position advanced by a predetermined rotational phase difference ⁇ from the eccentric shaft 232v on the vacuum pump unit 11 side.
- the piston 21v on the vacuum pump unit 11 side and the piston 21c on the pressure pump unit 12 side are driven with a phase difference ⁇ shifted from each other, and the piston 21c is driven by a time corresponding to the phase difference ⁇ relative to the piston 21v. Reach top dead center early.
- FIG. 7 (A) is an experimental result showing the time change between the pump chamber pressure and the piston position in the vacuum pump
- FIG. 7 (B) shows the time change between the pump chamber pressure and the piston position in the pressurizing pump. It is one experimental result shown.
- the solid line represents the experimental results during 50 Hz operation
- the broken line represents the experimental results during 60 Hz operation.
- the head of the pump apparatus used for the experiment was 40 [kPa (absolute pressure)] in the vacuum stage (vacuum pump) and 220 [kPaG (gauge pressure)] in the pressurization stage (pressurization pump).
- the internal pressure of the pump chamber was measured through a tube inserted in the pump chamber in an airtight manner.
- the piston position used the output of the accelerometer attached to the lower part of the connecting rod.
- the cylinder diameter of each stage of the pump was 37 mm, the eccentric amount of the eccentric shaft was 3.3 mm, and the rotational speed of the motor was about 1400 rpm / 1700 rpm (50 Hz / 60 Hz).
- the conditions of the experimental results shown in FIGS. 8 and 9 are the same.
- the pump chamber pressure changes in the same phase in synchronization with the piston position (FIG. 7A), whereas in the pressurization stage, the pump chamber pressure does not synchronize with the piston position. A phase difference is generated between them (FIG. 7B). More specifically, a pressure peak appears in the pump chamber before the pressurizing stage piston reaches top dead center.
- the time variation of the internal pressure is in reverse phase typically means that the pressure waveforms in the two pump chambers have a phase of 180 °, but the present invention is not limited to this. It is only necessary to have a phase relationship that can be interpreted as a relationship of.
- the reverse phase in a substantial sense can be defined as a phase relationship in which power consumption is smaller than when both pistons are driven in the same phase.
- FIGS. 7C shows a combined waveform of the pressure waveform of the pump chamber in the vacuum stage and the pressure waveform of the pump chamber in the pressurization stage.
- a predetermined phase difference is provided between the pressure-stage piston and the vacuum-stage piston so that the pressure waveform of the vacuum-stage pump chamber pressure and the pressure waveform of the pressure-stage pump chamber pressure are in opposite phases.
- the pressure stage piston is set to a rotational phase difference advanced by more than 0 ° and less than 80 ° with respect to the vacuum stage piston.
- the experimental results when the rotational phase difference is 40 ° are shown in FIGS.
- FIG. 8A shows the time change between the pump chamber pressure and the piston position in the vacuum stage
- FIG. 8B shows the time change between the pump chamber pressure and the piston position in the pressurization stage.
- FIG. 8C shows a combined waveform of the pressure waveform of the pump chamber in the vacuum stage and the pressure waveform of the pump chamber in the pressurization stage.
- FIG. 9 is an experimental result showing the relationship between the rotational phase difference of the pressurizing stage piston with respect to the vacuum stage piston and the current consumption of the motor.
- the rotational phase difference on the horizontal axis represents the phase advance angle of the pressurizing stage piston with respect to the vacuum stage piston (the phase angle in which the pressurizing side piston advances from the vacuum side piston in the rotational direction of the drive shaft).
- the rotational phase difference ⁇ with the lowest current value is 40 °
- the pressure waveforms in the pump chambers of the respective stages at this time are in an opposite phase relationship as shown in FIGS. is there.
- the combined waveform of the internal pressures of the pump chambers of each stage is as shown in FIG. 8C, and the pump chamber pressures of the respective stages cancel each other.
- the current consumption of the motor is minimized. Conceivable.
- the power consumption can be further effectively reduced, and the current value can be reduced by about 4.1% at 50 Hz and about 2.2% at 60 Hz. It was.
- phase difference ⁇ 40 ° ⁇ 15 °
- vibrations generated when the pump device 1 is driven can be reduced.
- ⁇ 40 °
- the vacuum pump unit 11 and the pressurizing pump unit 12 constituting the pump device are each constituted by an oscillating piston pump.
- the present invention is not limited to this, and other reciprocating type such as a diaphragm pump, for example.
- Each pump may be composed of a piston pump.
- the pump apparatus which has a single drive motor and two pump parts as an example, a plurality of pump units comprised by the said drive motor and two pump parts (
- the present invention can be applied to a pump device provided with two sets.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
上記駆動モータは、第1の駆動軸と、第2の駆動軸とを有する。上記駆動モータは、上記第1の駆動軸および上記第2の駆動軸を第1の軸まわりに同期して回転させることが可能に構成される。
上記第1のポンプ部は、上記第1の駆動軸の回転によって上記第1の軸と直交する第2の軸方向に往復移動する第1のピストンと、上記第1のピストンの往復移動に応じて内圧が変化する第1のポンプ室と、を有する。
上記第2のポンプ部は、上記第2の駆動軸の回転によって上記第2の軸方向に往復移動する第2のピストンと、上記第2のピストンの往復移動に応じて内圧が変化する第2のポンプ室と、を有する。上記第2のピストンは、上記第1のピストンに対して0°超80°未満の回転位相差をもって進相する。
上記駆動モータは、第1の駆動軸と、第2の駆動軸とを有する。上記駆動モータは、上記第1の駆動軸および上記第2の駆動軸を第1の軸まわりに同期して回転させることが可能に構成される。
上記第1のポンプ部は、上記第1の駆動軸の回転によって上記第1の軸と直交する第2の軸方向に往復移動する第1のピストンと、上記第1のピストンの往復移動に応じて内圧が変化する第1のポンプ室と、を有する。
上記第2のポンプ部は、上記第2の駆動軸の回転によって上記第2の軸方向に往復移動する第2のピストンと、上記第2のピストンの往復移動に応じて内圧が変化する第2のポンプ室と、を有する。上記第2のピストンは、上記第1のピストンに対して0°超80°未満の回転位相差をもって進相する。
11…真空ポンプ
12…加圧ポンプ
21,21v,21c…ピストン
26…ポンプ室
51,52…カウンタウェイト
131…駆動軸
232,232v,232c…偏芯軸
M…モータ
Claims (3)
- 第1の駆動軸と、第2の駆動軸と、を有し、前記第1の駆動軸および前記第2の駆動軸を第1の軸まわりに同期して回転させることが可能な駆動モータと、
前記第1の駆動軸の回転によって前記第1の軸と直交する第2の軸方向に往復移動する第1のピストンと、前記第1のピストンの往復移動に応じて内圧が変化する第1のポンプ室と、を有する真空排気用の第1のポンプ部と、
前記第2の駆動軸の回転によって前記第2の軸方向に往復移動する第2のピストンと、前記第2のピストンの往復移動に応じて内圧が変化する第2のポンプ室と、を有し、前記第2のピストンが前記第1のピストンに対して0°超80°未満の回転位相差をもって進相する加圧用の第2のポンプ部と、
を具備するポンプ装置。 - 請求項1に記載のポンプ装置であって、
前記回転位相差は、40°±15°である
ポンプ装置。 - 請求項1に記載のポンプ装置であって、
前記第1のポンプ部は、前記第1のピストンと共に前記第1の駆動軸のまわりを回転する第1のカウンタウェイトをさらに有し、
前記第2のポンプ部は、前記第1のカウンタウェイトに対して前記回転位相差をもって前記第2のピストンと共に前記第2の駆動軸のまわりを回転する第2のカウンタウェイトをさらに有する
ポンプ装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014507375A JP5878625B2 (ja) | 2012-03-30 | 2013-03-07 | ポンプ装置 |
EP13768264.7A EP2832998B1 (en) | 2012-03-30 | 2013-03-07 | Pump device |
CN201380017010.XA CN104204522B (zh) | 2012-03-30 | 2013-03-07 | 泵装置 |
KR1020147026361A KR101602089B1 (ko) | 2012-03-30 | 2013-03-07 | 펌프 장치 |
US14/386,641 US20150086402A1 (en) | 2012-03-30 | 2013-03-07 | Pump device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2012082015 | 2012-03-30 | ||
JP2012-082015 | 2012-03-30 |
Publications (1)
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WO2013145576A1 true WO2013145576A1 (ja) | 2013-10-03 |
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ID=49258896
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2013/001436 WO2013145576A1 (ja) | 2012-03-30 | 2013-03-07 | ポンプ装置 |
Country Status (7)
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US (1) | US20150086402A1 (ja) |
EP (1) | EP2832998B1 (ja) |
JP (1) | JP5878625B2 (ja) |
KR (1) | KR101602089B1 (ja) |
CN (1) | CN104204522B (ja) |
TW (1) | TWI619883B (ja) |
WO (1) | WO2013145576A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150147202A1 (en) * | 2013-11-27 | 2015-05-28 | Gardner Denver Thomas, Inc. | Pump having interchangeable heads |
WO2016037655A1 (de) * | 2014-09-11 | 2016-03-17 | Gaydoul Jürgen | Verdrängereinrichtung |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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CN104612937B (zh) * | 2015-03-06 | 2017-08-04 | 宁波捷美进出口有限公司 | 车用充气泵 |
CN111255666B (zh) * | 2018-12-03 | 2023-11-28 | 广东美的白色家电技术创新中心有限公司 | 增压泵和净水设备 |
CN112032022B (zh) * | 2020-09-10 | 2024-04-26 | 北京通嘉宏瑞科技有限公司 | 一种无死角吹扫气体的干式真空泵及其使用方法 |
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- 2013-03-07 KR KR1020147026361A patent/KR101602089B1/ko active IP Right Grant
- 2013-03-07 US US14/386,641 patent/US20150086402A1/en not_active Abandoned
- 2013-03-07 JP JP2014507375A patent/JP5878625B2/ja active Active
- 2013-03-07 CN CN201380017010.XA patent/CN104204522B/zh active Active
- 2013-03-07 WO PCT/JP2013/001436 patent/WO2013145576A1/ja active Application Filing
- 2013-03-07 EP EP13768264.7A patent/EP2832998B1/en active Active
- 2013-03-15 TW TW102109327A patent/TWI619883B/zh active
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JPH07310651A (ja) | 1994-05-17 | 1995-11-28 | Toshiba Seiki Kk | 往復動ポンプユニット |
JP2008190517A (ja) * | 2007-02-05 | 2008-08-21 | Kazumori Otogao | 可搬型空気圧縮装置 |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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US20150147202A1 (en) * | 2013-11-27 | 2015-05-28 | Gardner Denver Thomas, Inc. | Pump having interchangeable heads |
WO2016037655A1 (de) * | 2014-09-11 | 2016-03-17 | Gaydoul Jürgen | Verdrängereinrichtung |
EP3181902A1 (de) | 2014-09-11 | 2017-06-21 | Hermetik Hydraulik Ab | Verdrängereinrichtung |
CN107076125A (zh) * | 2014-09-11 | 2017-08-18 | 赫梅蒂克水力公司 | 位移装置 |
Also Published As
Publication number | Publication date |
---|---|
EP2832998B1 (en) | 2017-01-18 |
JPWO2013145576A1 (ja) | 2015-12-10 |
CN104204522B (zh) | 2016-08-24 |
JP5878625B2 (ja) | 2016-03-08 |
TW201400702A (zh) | 2014-01-01 |
EP2832998A4 (en) | 2016-01-20 |
TWI619883B (zh) | 2018-04-01 |
CN104204522A (zh) | 2014-12-10 |
KR101602089B1 (ko) | 2016-03-09 |
KR20140126757A (ko) | 2014-10-31 |
US20150086402A1 (en) | 2015-03-26 |
EP2832998A1 (en) | 2015-02-04 |
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