US20050025642A1 - Pump device - Google Patents
Pump device Download PDFInfo
- Publication number
- US20050025642A1 US20050025642A1 US10/893,984 US89398404A US2005025642A1 US 20050025642 A1 US20050025642 A1 US 20050025642A1 US 89398404 A US89398404 A US 89398404A US 2005025642 A1 US2005025642 A1 US 2005025642A1
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- United States
- Prior art keywords
- fluid
- pump device
- shaft
- bearing
- fluid passage
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/047—Bearings hydrostatic; hydrodynamic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
- F04D29/061—Lubrication especially adapted for liquid pumps
Definitions
- This invention generally relates to a pump device. More particularly, the invention pertains to a pump device for pressurizing and supplying a fluid by a rotation of an impeller driven by a motor.
- Known pump device circulates a fluid for cooling and lubrication flowing from an intake port through a circulation path by a rotation of an impeller, thereby achieving cooling and lubrication of a predetermined portion.
- a pump device is disclosed in Japanese Patent Laid-Open Publication JP07(1995)-217593A2.
- the disclosed pump device includes an impeller being rotatably supported on a shaft within a casing. Rotating the impeller by a rotation of the shaft causes the fluid on an intake side (feed side) where the fluid is inhaled to be supplied to a discharge side for circulating the fluid through the circulation path.
- the shaft supporting the impeller is rotatably supported by a bearing portion formed within the casing.
- the bearing portion and the discharge side are connected by a piping outside of the casing so that a part of the fluid with a high pressure on the discharge side is supplied to the bearing portion that supports the impeller.
- the piping for leading the fluid to the bearing portion is required to be provided outside of the casing, thereby causing a large size of the pump device.
- a gap formed between the bearing portion and the shaft is defined with a high dimensional accuracy so that no looseness causes in case of the impeller rotating.
- a foreign matter entering into the gap between the bearing portion and the shaft may be pinched therebetween. Then, the foreign matter does not easily come out from the gap, thereby causing a malfunction of the bearing portion, which leads a deterioration of the pump device life.
- a pump device includes a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port, a motor housing including a stator, and a shaft whose one end projects into the pump housing and to which an impeller is assembled and whose the other end is rotatably supported by a first bearing portion within the motor housing.
- the pump device also includes a rotor assembled to the shaft and facing the stator, and a bearing plate disposed between the pump housing and the motor housing and including a second bearing portion rotatably supporting the shaft.
- the bearing plate is formed by a first fluid passage for leading the fluid to the bearing plate.
- a pump device includes a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port, a motor housing including a stator, a shaft whose one end projects into the pump housing and to which an impeller is assembled and whose other end is rotatably supported by a first bearing portion within the motor housing, and a rotor assembled to the shaft and facing the stator.
- the impeller is formed by a first fluid passage extending in a radial direction of the impeller for leading the fluid to the first bearing portion.
- FIG. 1 is a cross-sectional view of a pump device according to a first embodiment of the present invention.
- FIG. 2 is a cross-sectional view of the pump device according to a second embodiment of the present invention.
- FIG. 1 is a cross-sectional view showing a structure of a pump device 10 according to a first embodiment of the present invention.
- the pump device 10 may be employed in a vehicle, for example, to a water pump for circulating a fluid (coolant water in this case) between an engine and a radiator (not shown) in an engine room, an oil pump for supplying a fluid for lubrication (oil in this case) to the engine, and the like.
- the pump device 10 is electrically driven.
- the pump device 10 includes a pump housing 11 made of metal and a motor housing 12 made of resin, which constitute an outer form of the pump device 10 .
- the pump housing 11 includes a fluid chamber 15 to which the fluid is supplied, an intake port 11 a through which the fluid is inhaled to flow into the fluid chamber 15 , and a discharge port 15 c through which the fluid in the fluid chamber 15 is highly pressurized and discharged outside of the pump device 10 .
- the pump housing 11 includes an opening for leading a part of the fluid at a portion 32 where the fluid is highly pressurized (high pressure portion).
- a bearing plate 13 made of resin is disposed between the pump housing 11 and the motor housing 12 , covering the opening of the pump housing 11 from an axial direction, thereby assuring a sealing performance between the pump housing 11 and the bearing plate 13 .
- the bearing plate 13 includes a bearing bore 13 a and a second bearing portion 13 b at a center portion in a radial direction of the bearing plate. 13 .
- the second bearing portion 13 b has a diameter smaller than the bearing bore 13 a.
- a shaft 21 having a large diameter portion and a small diameter portion is inserted into the bearing bore 13 a from an axial direction. An end portion of the small diameter portion of the shaft 21 projects into a center of the fluid chamber 15 formed within the pump housing 11 under the condition that the small diameter portion of the shaft 21 is rotatably supported by the second bearing portion 13 b.
- the shaft 21 is a part of a member of a motor 20 (to be mentioned later) provided opposite side of the fluid chamber 15 relative to the bearing plate 13 .
- One end of the shaft 21 on the motor 20 side is rotatably supported on a concave portion formed at a center of the motor housing 12 .
- an impeller 16 is assembled in a press fit manner to the other end of the shaft 21 on the pump housing 11 side that extends to the fluid chamber 15 .
- the impeller 16 is of a substantially circular shape when viewed from the intake port 11 a side and integrally formed with a plurality of blades 16 a at an outer periphery in a peripheral direction.
- the fluid chamber 15 includes a first fluid chamber 15 a continuously connected to the intake port 11 a having a cylindrical shape and a second fluid chamber 15 b (high pressure portion) formed on outer diameter side of the fluid chamber 15 relative to the first fluid chamber 15 a and highly pressurized as compared to the first fluid chamber 15 a when the pump device 10 is operated.
- the discharge port 15 c through which the fluid is discharged is arranged on a plane perpendicular to the intake port 11 a through which the fluid is inhaled and also formed at a portion where the fluid is highly pressurized and discharged by the rotation of the impeller 16 .
- the motor housing 12 includes a concave portion in which a core 24 formed by plurality of annularly-shaped metallic laminated sheets are arranged.
- a coil 23 is wound on the core 24 .
- the core 24 with the coil 23 wound thereon arranged within the concave portion forms a stator of the motor 20 .
- a surface of the concave portion where the stator is arranged is molded by, resin.
- the shaft 21 made of cylindrical-shaped metal includes small diameter portions 21 a and 21 c at both ends of the shaft 21 , having the same diameter as each other.
- a large diameter portion 21 b is disposed between the small diameter portions 21 a and 21 c so as to be integrally formed therewith.
- the large diameter portion 21 b faces to an inner diameter portion of the annular core 24 with keeping a predetermined distance therebetween.
- a magnet 22 (rotor) having a cylindrical shape is attached to the large diameter portion 21 b.
- the magnet 22 is a four-pole magnet in which north poles and south poles are alternately arranged in a peripheral direction at an outer periphery of the large diameter portion 21 b of the shaft 21 .
- the magnet 22 is fixed to the large diameter portion 21 b by an adhesive means such as an adhesive agent and a strong adhesive tape so that the magnet 22 rotates as a unit with the shaft 21 .
- the small diameter portion 21 c of the shaft 21 is rotatably supported by a first bearing portion 12 b formed at a center in the radial direction of the concave portion of the motor housing 12 .
- the small diameter portion 21 a penetrates through the bearing bore 13 a of the bearing plate 13 , projecting into the fluid chamber 15 .
- the impeller 16 is assembled to a tip end portion of the projected small diameter portion 21 a.
- a bush is preferably insert-molded to the first bearing portion 12 b for smoothening the rotation of the shaft 21 by improving a coaxiality of the shaft 21 by the first bearing portion 12 b and the second bearing portion 13 b of the bearing plate 13 .
- a fluid passage through which the fluid flows is explained as follows.
- a gap 12 t is formed between an inner wall 12 a of the motor housing 12 and an end portion in the axial direction of the magnet 22 .
- a slit-shaped gap 12 s extending in the radial direction is formed on a surface of the concave portion between an end portion in the axial direction of the large diameter portion 21 b and the inner wall 12 a of the motor housing 12 being molded.
- respective small gaps are formed between an inner diameter of the bearing bore 13 a of the bearing plate 13 and an outer periphery of the small diameter portion 21 a, and between an axially end face of the bearing bore 13 a on the motor 20 side and an axially end face of the large diameter portion 21 b on the pump housing 11 side.
- the shaft 21 is supported rotatably by both the bearing plate 13 and the motor housing 12 via the bearing portions 13 b and 12 b, respectively.
- the sealing performance between contact faces of the motor housing 12 and the bearing plate 13 is assured by an O-ring 25 .
- the sealing performance between the pump housing 11 and the bearing plate 13 is assured by putting an annular plate therebetween. Then, the pump housing 11 , the bearing plate 13 and the motor housing 12 are fixed to each other at several positions via a plurality of tightening members 19 .
- a feed port 31 a (opening) for leading a part of the fluid with a high pressure into the inner diameter side of the bearing plate 13 is opened in the second fluid chamber 15 b in which the fluid pressure is higher than the first fluid chamber 15 a, and extending into the bearing plate 13 .
- a fluid passage 31 (first fluid passage) extends obliquely from the second fluid chamber 15 b to the second bearing portion 13 b and the bearing bore 13 a towards the small diameter portion 21 a of the shaft 21 within the bearing plate 13 in a state of communicating with the feed port 31 a.
- the fluid passage 31 is formed, avoiding a portion where the O-ring 25 is provided for sealing the motor housing 12 and the bearing plate 13 .
- the fluid passage 31 is formed as a bore extending obliquely towards the shaft 21 in the bearing plate 13 or a bore extending from a position of the feed port 31 a in the axial direction (thickness direction) of the bearing plate 13 and being connected to a bore formed from a stepped portion positioned at an opposite side relative to the shaft 21 of the bearing plate 13 (i.e. end portion of the motor housing 12 on the pump housing 11 side) in the oblique direction.
- the fluid passage 31 may be formed by penetrating through both side faces in the axial direction of the bearing plate 13 , thereby achieving a simple structure.
- the fluid flows through the fluid passage 31 from the feed port 31 a to the second bearing portion 13 b for lubrication and/or cooling of the second bearing portion 13 b.
- a part of the fluid from the feed port 31 a is supplied to the gap formed between the bearing bore 13 a and the small diameter portion 21 a, and then to the outer periphery of the shaft 21 from the bearing bore 13 a via the gap formed between the outer periphery of the magnet 22 and the inner wall 12 a.
- a part of the fluid being highly pressurized is supplied to the first bearing portion 12 b of the shaft 21 .
- An end portion of the fluid passage 31 communicating with the feed port 31 a and formed in the oblique direction within the bearing plate 13 is blocked by an end portion of the inner diameter portion of the motor housing 12 in which the stator is provided.
- the fluid hitting the end portion of the fluid passage 31 being blocked is prevented from flowing in the oblique direction.
- the fluid is diverted to flow into the gap formed between the bearing bore 13 a and the small diameter portion 21 a and then supplied to the outer periphery of the shaft 21 .
- the fluid is supplied to an axially end portion of the shaft 21 within the first bearing portion 12 b.
- a filter 38 is provided at the feed port 31 a in order to prevent the foreign matter from entering into the fluid passage 31 .
- the pump device 10 When the coil 23 is energized by a controller (not shown) that drives the pump device 10 , the pump device 10 starts driving. An excitation to the magnet 22 attached to the large diameter portion 21 b of the shaft 21 is alternated by energizing the coil 23 , thereby causing the shaft 21 , to which the magnet 22 is fixed, to rotate integrally with the bearing portions 13 b and 12 b.
- the impeller 16 assembled to the shaft 21 rotates accordingly. Due to the rotation of the impeller 16 , the fluid is supplied from the intake port 11 a of the pump housing 11 and then flows into the first fluid chamber 15 a. The fluid supplied to the first fluid chamber 15 a is pressurized and sent to the second fluid chamber 15 b provided on the outer diameter side relative to the first fluid chamber 15 a.
- the fluid is discharged from the discharge port 15 c provided in the second fluid chamber 15 b of the pump housing 11 to the outside of the pump device 10 (for example, engine and the like in case of the vehicle). According to the above-mentioned flow of the fluid, the pump function of the pump device 10 may be obtained.
- a part of the fluid in the second fluid chamber 15 b being pressurized and sent from the first fluid chamber 15 a by the rotation of the impeller 16 i.e. the fluid in the vicinity of the feed port 31 a with a higher pressure than the intake port 11 a, flows into the fluid passage 31 via the feed port 31 a.
- the fluid flowing into the fluid passage 31 is pressurized and sent to the bearing bore 13 a, and also supplied to the second bearing portion 13 b by the rotation of the impeller 16 .
- the fluid passage 31 extends further in the oblique direction via the inner diameter of the bearing bore 13 a.
- a slit is formed in the axial direction on the inner diameter portion of the second bearing portion 13 b.
- a plurality of slits 13 s are formed in the radial direction on an end portion of the bearing bore 13 a on the motor 20 side.
- the fluid in the fluid passage 31 smoothly flows through the outer periphery of the small diameter portion 21 a of the shaft 21 and the gap formed between the outer periphery of the magnet 22 and the inner wall 12 a.
- the fluid then flows along the outer periphery of the small diameter portion 21 c of the shaft 21 and led to the first bearing portion 12 b to which the shaft 21 is rotatably supported.
- a fluid passage 21 p (third fluid passage) for letting the fluid flow into the first fluid chamber 15 a on the intake side is formed within the shaft 21 , axially penetrating through a center portion of the shaft 21 .
- an escape bore 16 b for letting the fluid led from the fluid passage 21 p flow into the first fluid chamber 15 a is formed at a tip end portion of the impeller 16 assembled to the tip end-portion of the shaft 21 . Therefore, the fluid reaching the first bearing portion 12 b flows through the fluid passage 21 p formed within the shaft 21 and the escape bore 16 b of the impeller 16 , and then ultimately returns to the first fluid chamber 15 a.
- a process of a part of the fluid in the second fluid chamber 15 b flowing through the feed port 31 a, the fluid passage 31 , and the like and then returning to the first fluid chamber 15 a has been explained. Focusing on a pressure balance between the first fluid chamber 15 a and the second fluid chamber 15 b, the pressure in the second fluid chamber 15 b is higher than that of the first fluid chamber 15 a when the pump is driven since the fluid in the first fluid chamber 15 a is pressurized and then sent to the second fluid chamber 15 b by the rotation of the impeller 16 . Therefore, the fluid flows smoothly from the feed port 31 a provided in the second fluid chamber 15 b through the fluid passage 31 , the inside of the motor 20 , and then to the first fluid chamber 15 a.
- an original function of the fluid passage that the fluid is pressurized and sent to a required portion within the motor 20 for lubrication and/or cooling may not be deteriorated by forming the fluid passage 31 within the bearing plate 13 in the oblique direction with avoiding a portion where the O-ring 25 is provided. Further, the foreign matter included in the fluid that circulates through the inside of the pump device 10 is surely eliminated by the filter 38 provided on the high-pressure side. As a result, a high lubricity may be obtained, thereby improving the reliability of the pump device 10 .
- a second embodiment of the present invention is explained referring to FIG. 2 .
- a structure of the second embodiment is basically same as that of the first embodiment but differs in a method how the highly pressurized fluid is led to the bearing portion of the shaft 21 and then returned to the intake side. Therefore, the same structure as the first embodiment is omitted and a different structure only is explained as follows.
- the fluid passage 31 is not formed within the bearing plate 13 . Instead, a fluid passage 33 (first fluid passage) is formed within the impeller 16 .
- the impeller 16 made of resin is insert-molded by a bush 17 made of metal being inserted into a center of the impeller 16 .
- the impeller 16 includes the plurality of blades 16 a and a base portion 16 c for supporting the blades 16 a.
- the fluid passage 33 is formed in the base portion 16 c of the impeller 16 , extending in the radial direction of the impeller 16 .
- the fluid passage 33 penetrates into the bush 17 .
- the fluid passage 33 communicates with the second fluid chamber 15 b with a higher pressure than the intake port 11 a.
- a filter 35 for preventing the foreign matter from entering into the fluid passage 33 is provided on an outer diameter side thereof.
- a fluid passage 36 (second fluid passage) is formed within the shaft 21 in the radial direction so as to communicate with the fluid passage 33 formed within the impeller 16 .
- a fluid passage 37 (second fluid passage) is formed in a center portion of the shaft 21 , extending in the axial direction thereof from an end portion of the first bearing portion 12 b so as to communicate with the fluid passage 36 .
- a part of the fluid that is highly pressurized by the rotation of the impeller 16 flows through the fluid passage 33 after passing through the filter 35 , thereby preventing the foreign matter from entering into the fluid passage 33 formed within the impeller 16 .
- the fluid is supplied from the axially center portion of the shaft 21 to the first bearing portion 12 b via the fluid passages 36 and 37 .
- the fluid is then supplied around the shaft 21 and the inner wall 12 a of the motor 20 , thereby achieving the lubrication and/or cooling within the motor 20 including the shaft 21 .
- the fluid is supplied to the outer periphery of the shaft 21 , the inner wall 12 a of the motor 20 , and the bearing portions 12 b and 13 b via the gaps shown in the first embodiment.
- the fluid led to the second bearing portion 13 b flows into a penetrating bore 16 d penetrating through both sides in the axial direction of the base portion 16 c, then into the first fluid chamber 15 a on the intake side of the fluid chamber 15 .
- an extra piping is not required to be employed.
- a labyrinth L is formed between the base portion 16 c and the bearing plate 13 on a radially outward side relative to the penetrating bore 16 d, thereby effectively leading the fluid from the second bearing portion 13 b to the first fluid chamber 15 a.
- the effective cooling and/or lubrication may be achieved.
- the filter 35 is provided at a feed port for the fluid and thus the foreign matter may be caught by the filter 35 .
- the filter 35 is provided on the outer peripheral portion of the impeller 16 , so that the foreign matter may be blown outside of the impeller 16 due to centrifugal force occurring when the impeller 16 rotates even if the foreign matter exists on the outer diameter portion of the impeller 16 .
- the foreign matter is prevented from accumulating on a surface of the filter 35 . Therefore, the bearing portions 13 b and 12 b to which the shaft 21 is rotatably supported for rotating the impeller 16 may be protected by a simple structure of providing the filter 35 at the feed port of the impeller 16 .
- the magnetic foreign matter included in the fluid and passing through the filter 35 may be caught by the magnetic force of the magnet 22 fixed to the shaft 21 when the fluid flows through the axially center portion of the shaft 21 .
- the fluid passages 36 and 37 each having a uniform diameter in the axial direction may be provided with a reduced diameter portion.
- the fluid passage 31 for leading the fluid into the bearing plate 13 is formed within the bearing plate 13 .
- an extra piping is not required to be employed outside of the pump device 10 for leading the fluid to the bearing portions 12 b and 13 b, thereby achieving a downsizing of the pump device 10 as a whole.
- the fluid passage 31 through which the fluid is pressurized and sent to a required portion within the motor 20 for lubrication or cooling is formed within the pump device 10 , thereby achieving high space efficiency.
- one end of the fluid passage 31 is formed with the opening facing the fluid chamber 15 .
- the other end of the fluid passage 31 is provided adjacent to the second bearing portion 13 b and communicates with the bearing bore 13 a having a larger diameter than the second bearing portion 13 b.
- the fluid may be led from the fluid chamber 15 to the bearing portions 12 b and 13 b via the bearing bore 13 a.
- the opening is provided in the second fluid chamber 15 b in which the fluid has a high pressure in the pump housing 11 .
- a part of the fluid may be led to the opening, being pressurized and sent to the lubricant portion.
- the filter 38 is provided at the feed port 31 a for leading the fluid to the fluid passage 31 .
- the filter 38 is provided at the feed port 31 a for leading the fluid to the fluid passage 31 .
- the fluid passage 31 may penetrate through the both side faces of the bearing plate 13 in the axial direction, thereby obtaining the fluid passage 31 with a simple structure.
- the first bearing portion 12 b and the second bearing portion 13 b communicate with each other via a gap formed between the stator of the motor 20 and the magnet 22 , thereby cooling the stator and the magnet 22 .
- the fluid passage 21 p is formed within the shaft 21 for connecting the first bearing portion 12 b and the first fluid chamber 15 a on the intake side.
- the fluid supplied to the first bearing portion 12 b may easily flow by using the intake pressure of the first fluid chamber 15 a.
- the end portion of the bearing bore 13 a on the motor 20 side is formed with a slit in the radial direction of the shaft 21 .
- the fluid may smoothly flow through the gap formed between the bearing bore 13 a and the shaft 21 .
- the fluid passage 31 formed within the bearing plate 13 and extending in the radial direction thereof keeps a predetermined angle with the shaft 21 .
- the fluid passage 31 may be formed with a simple structure.
- the fluid passage 33 is formed within the impeller 16 in the radial direction for leading the fluid to the first bearing portion 12 b.
- an extra piping is not required to be provided outside of the pump device 10 for leading the fluid to the first bearing portion 12 b.
- the fluid passages 36 and 37 communicating with the fluid passage 33 and leading the fluid to the first bearing portion 12 b is formed in the shaft 21 .
- an extra piping is not required to be provided outside of the pump device 10 for leading the fluid to the first bearing portion 12 b.
- the fluid passage 33 is formed in the base portion 16 c for supporting the blades 16 a of the impeller 16 .
- the bearing portions 12 b and 13 b may be protected with high space efficiency by using the base portion 31 c not having a feature of moving the fluid.
- the penetrating bore 16 d is formed on the base portion 16 c for penetrating through the both sides of the base portion 16 c.
- an extra piping for leading the fluid to the first fluid chamber 15 a is not required.
- the fluid flowing through the fluid passage 33 is led to the first fluid chamber 15 a on the intake side of the fluid chamber 15 via the fluid passages 36 and 37 , the first bearing portion 12 b, the gap between the stator and the magnet 22 , the second bearing portion 13 b formed at the bearing plate 13 disposed between the pump housing 11 and the motor housing 12 and rotatably supporting the shaft 21 , the gap formed between the bearing plate 13 and the base portion 13 c, and the penetrating bore 16 d.
- the lubrication and cooling of each bearing portion 12 b and 13 b, the stator and the magnet 22 may be performed with a short piping.
- the labyrinth L is formed between the base portion 16 c and the bearing plate 13 .
- the fluid may be effectively supplied to the first fluid chamber 15 a.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
A pump device includes a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port, a motor housing including a stator, and a shaft whose one end projects into the pump housing and to which an impeller is assembled and whose the other end is rotatably supported by a first bearing portion within the motor housing. The pump device also includes a rotor assembled to the shaft and facing the stator, and a bearing plate disposed between the pump housing and the motor housing and including a second bearing portion rotatably supporting the shaft. The bearing plate is formed by a first fluid passage for leading the fluid to the bearing plate.
Description
- This application is based on and claims priority under 35 U.S.C. § 119 to Japanese Patent Application 2003-305542, filed on Aug. 28, 2003, the entire content of which is incorporated herein by reference.
- This invention generally relates to a pump device. More particularly, the invention pertains to a pump device for pressurizing and supplying a fluid by a rotation of an impeller driven by a motor.
- Known pump device circulates a fluid for cooling and lubrication flowing from an intake port through a circulation path by a rotation of an impeller, thereby achieving cooling and lubrication of a predetermined portion. Such a pump device is disclosed in Japanese Patent Laid-Open Publication JP07(1995)-217593A2. The disclosed pump device includes an impeller being rotatably supported on a shaft within a casing. Rotating the impeller by a rotation of the shaft causes the fluid on an intake side (feed side) where the fluid is inhaled to be supplied to a discharge side for circulating the fluid through the circulation path.
- According to the above-mentioned pump device, the shaft supporting the impeller is rotatably supported by a bearing portion formed within the casing. The bearing portion and the discharge side are connected by a piping outside of the casing so that a part of the fluid with a high pressure on the discharge side is supplied to the bearing portion that supports the impeller.
- According to the above-mentioned structure, however, the piping for leading the fluid to the bearing portion is required to be provided outside of the casing, thereby causing a large size of the pump device.
- Further, a gap formed between the bearing portion and the shaft is defined with a high dimensional accuracy so that no looseness causes in case of the impeller rotating. Thus, a foreign matter entering into the gap between the bearing portion and the shaft may be pinched therebetween. Then, the foreign matter does not easily come out from the gap, thereby causing a malfunction of the bearing portion, which leads a deterioration of the pump device life.
- Thus, a need exists for a pump device that can achieve a downsizing without a piping provided outside of the device. In addition, a need exists for the pump device which protects a bearing portion by preventing the foreign matter from entering.
- According to an aspect of the present invention, a pump device includes a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port, a motor housing including a stator, and a shaft whose one end projects into the pump housing and to which an impeller is assembled and whose the other end is rotatably supported by a first bearing portion within the motor housing. The pump device also includes a rotor assembled to the shaft and facing the stator, and a bearing plate disposed between the pump housing and the motor housing and including a second bearing portion rotatably supporting the shaft. The bearing plate is formed by a first fluid passage for leading the fluid to the bearing plate.
- According to another aspect of the present invention, a pump device includes a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port, a motor housing including a stator, a shaft whose one end projects into the pump housing and to which an impeller is assembled and whose other end is rotatably supported by a first bearing portion within the motor housing, and a rotor assembled to the shaft and facing the stator. The impeller is formed by a first fluid passage extending in a radial direction of the impeller for leading the fluid to the first bearing portion.
- The foregoing and additional features and characteristics of the present invention will become more apparent from the following detailed description considered with reference to the accompanying drawings, wherein:
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FIG. 1 is a cross-sectional view of a pump device according to a first embodiment of the present invention; and -
FIG. 2 is a cross-sectional view of the pump device according to a second embodiment of the present invention. - Embodiments of the present invention are explained referring to attached drawings.
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FIG. 1 is a cross-sectional view showing a structure of apump device 10 according to a first embodiment of the present invention. Thepump device 10 may be employed in a vehicle, for example, to a water pump for circulating a fluid (coolant water in this case) between an engine and a radiator (not shown) in an engine room, an oil pump for supplying a fluid for lubrication (oil in this case) to the engine, and the like. Thepump device 10 is electrically driven. - The
pump device 10 includes apump housing 11 made of metal and amotor housing 12 made of resin, which constitute an outer form of thepump device 10. Thepump housing 11 includes afluid chamber 15 to which the fluid is supplied, anintake port 11 a through which the fluid is inhaled to flow into thefluid chamber 15, and adischarge port 15 c through which the fluid in thefluid chamber 15 is highly pressurized and discharged outside of thepump device 10. In addition, thepump housing 11 includes an opening for leading a part of the fluid at aportion 32 where the fluid is highly pressurized (high pressure portion). Abearing plate 13 made of resin is disposed between thepump housing 11 and themotor housing 12, covering the opening of thepump housing 11 from an axial direction, thereby assuring a sealing performance between thepump housing 11 and thebearing plate 13. - The
bearing plate 13 includes abearing bore 13 a and a second bearingportion 13 b at a center portion in a radial direction of the bearing plate. 13. The second bearingportion 13 b has a diameter smaller than the bearing bore 13 a. Ashaft 21 having a large diameter portion and a small diameter portion is inserted into the bearing bore 13 a from an axial direction. An end portion of the small diameter portion of theshaft 21 projects into a center of thefluid chamber 15 formed within thepump housing 11 under the condition that the small diameter portion of theshaft 21 is rotatably supported by the second bearingportion 13 b. - The
shaft 21 is a part of a member of a motor 20 (to be mentioned later) provided opposite side of thefluid chamber 15 relative to thebearing plate 13. One end of theshaft 21 on themotor 20 side is rotatably supported on a concave portion formed at a center of themotor housing 12. Meanwhile, animpeller 16 is assembled in a press fit manner to the other end of theshaft 21 on thepump housing 11 side that extends to thefluid chamber 15. Theimpeller 16 is of a substantially circular shape when viewed from theintake port 11 a side and integrally formed with a plurality ofblades 16 a at an outer periphery in a peripheral direction. - The
fluid chamber 15 includes afirst fluid chamber 15 a continuously connected to theintake port 11 a having a cylindrical shape and asecond fluid chamber 15 b (high pressure portion) formed on outer diameter side of thefluid chamber 15 relative to thefirst fluid chamber 15 a and highly pressurized as compared to thefirst fluid chamber 15 a when thepump device 10 is operated. At this time, thedischarge port 15 c through which the fluid is discharged is arranged on a plane perpendicular to theintake port 11 a through which the fluid is inhaled and also formed at a portion where the fluid is highly pressurized and discharged by the rotation of theimpeller 16. - A structure of the
motor 20 is explained as follows. Themotor housing 12 includes a concave portion in which acore 24 formed by plurality of annularly-shaped metallic laminated sheets are arranged. In addition, acoil 23 is wound on thecore 24. Thecore 24 with thecoil 23 wound thereon arranged within the concave portion forms a stator of themotor 20. A surface of the concave portion where the stator is arranged is molded by, resin. - The
shaft 21 made of cylindrical-shaped metal includessmall diameter portions shaft 21, having the same diameter as each other. Alarge diameter portion 21 b is disposed between thesmall diameter portions large diameter portion 21 b faces to an inner diameter portion of theannular core 24 with keeping a predetermined distance therebetween. A magnet 22 (rotor) having a cylindrical shape is attached to thelarge diameter portion 21 b. Themagnet 22 is a four-pole magnet in which north poles and south poles are alternately arranged in a peripheral direction at an outer periphery of thelarge diameter portion 21 b of theshaft 21. Themagnet 22 is fixed to thelarge diameter portion 21 b by an adhesive means such as an adhesive agent and a strong adhesive tape so that themagnet 22 rotates as a unit with theshaft 21. - The
small diameter portion 21 c of theshaft 21 is rotatably supported by a first bearingportion 12 b formed at a center in the radial direction of the concave portion of themotor housing 12. Thesmall diameter portion 21 a penetrates through the bearing bore 13 a of thebearing plate 13, projecting into thefluid chamber 15. Theimpeller 16 is assembled to a tip end portion of the projectedsmall diameter portion 21 a. In this case, a bush is preferably insert-molded to the first bearingportion 12 b for smoothening the rotation of theshaft 21 by improving a coaxiality of theshaft 21 by the first bearingportion 12 b and the second bearingportion 13 b of thebearing plate 13. - A fluid passage through which the fluid flows is explained as follows. A
gap 12 t is formed between aninner wall 12 a of themotor housing 12 and an end portion in the axial direction of themagnet 22. In addition, a slit-shapedgap 12 s extending in the radial direction is formed on a surface of the concave portion between an end portion in the axial direction of thelarge diameter portion 21 b and theinner wall 12 a of themotor housing 12 being molded. Further, respective small gaps are formed between an inner diameter of the bearing bore 13 a of the bearingplate 13 and an outer periphery of thesmall diameter portion 21 a, and between an axially end face of the bearing bore 13 a on themotor 20 side and an axially end face of thelarge diameter portion 21 b on thepump housing 11 side. Theshaft 21 is supported rotatably by both the bearingplate 13 and themotor housing 12 via the bearingportions - The sealing performance between contact faces of the
motor housing 12 and the bearingplate 13 is assured by an O-ring 25. In addition, the sealing performance between thepump housing 11 and the bearingplate 13 is assured by putting an annular plate therebetween. Then, thepump housing 11, the bearingplate 13 and themotor housing 12 are fixed to each other at several positions via a plurality of tighteningmembers 19. - A
feed port 31 a (opening) for leading a part of the fluid with a high pressure into the inner diameter side of the bearingplate 13 is opened in thesecond fluid chamber 15 b in which the fluid pressure is higher than thefirst fluid chamber 15 a, and extending into the bearingplate 13. In addition, a fluid passage 31 (first fluid passage) extends obliquely from thesecond fluid chamber 15 b to thesecond bearing portion 13 b and the bearing bore 13 a towards thesmall diameter portion 21 a of theshaft 21 within the bearingplate 13 in a state of communicating with thefeed port 31 a. In this case, thefluid passage 31 is formed, avoiding a portion where the O-ring 25 is provided for sealing themotor housing 12 and the bearingplate 13. Thefluid passage 31 is formed as a bore extending obliquely towards theshaft 21 in the bearingplate 13 or a bore extending from a position of thefeed port 31 a in the axial direction (thickness direction) of the bearingplate 13 and being connected to a bore formed from a stepped portion positioned at an opposite side relative to theshaft 21 of the bearing plate 13 (i.e. end portion of themotor housing 12 on thepump housing 11 side) in the oblique direction. Thefluid passage 31 may be formed by penetrating through both side faces in the axial direction of the bearingplate 13, thereby achieving a simple structure. The fluid flows through thefluid passage 31 from thefeed port 31 a to thesecond bearing portion 13 b for lubrication and/or cooling of thesecond bearing portion 13 b. In this case, a part of the fluid from thefeed port 31 a is supplied to the gap formed between the bearing bore 13 a and thesmall diameter portion 21 a, and then to the outer periphery of theshaft 21 from the bearing bore 13 a via the gap formed between the outer periphery of themagnet 22 and theinner wall 12 a. In addition, a part of the fluid being highly pressurized is supplied to thefirst bearing portion 12 b of theshaft 21. - An end portion of the
fluid passage 31 communicating with thefeed port 31 a and formed in the oblique direction within the bearingplate 13 is blocked by an end portion of the inner diameter portion of themotor housing 12 in which the stator is provided. The fluid hitting the end portion of thefluid passage 31 being blocked is prevented from flowing in the oblique direction. Thus, the fluid is diverted to flow into the gap formed between the bearing bore 13 a and thesmall diameter portion 21 a and then supplied to the outer periphery of theshaft 21. Finally, the fluid is supplied to an axially end portion of theshaft 21 within thefirst bearing portion 12 b. In this case, an existence of foreign matter in the fluid supplied to theshaft 21 may cause a rotation failure of theshaft 21. Thus, afilter 38 is provided at thefeed port 31 a in order to prevent the foreign matter from entering into thefluid passage 31. - An operation of the
pump device 10 is explained as follows. - When the
coil 23 is energized by a controller (not shown) that drives thepump device 10, thepump device 10 starts driving. An excitation to themagnet 22 attached to thelarge diameter portion 21 b of theshaft 21 is alternated by energizing thecoil 23, thereby causing theshaft 21, to which themagnet 22 is fixed, to rotate integrally with the bearingportions impeller 16 assembled to theshaft 21 rotates accordingly. Due to the rotation of theimpeller 16, the fluid is supplied from theintake port 11 a of thepump housing 11 and then flows into thefirst fluid chamber 15 a. The fluid supplied to thefirst fluid chamber 15 a is pressurized and sent to thesecond fluid chamber 15 b provided on the outer diameter side relative to thefirst fluid chamber 15 a. Afterwards, the fluid is discharged from thedischarge port 15 c provided in thesecond fluid chamber 15 b of thepump housing 11 to the outside of the pump device 10 (for example, engine and the like in case of the vehicle). According to the above-mentioned flow of the fluid, the pump function of thepump device 10 may be obtained. - According to the aforementioned embodiment, a part of the fluid in the
second fluid chamber 15 b being pressurized and sent from thefirst fluid chamber 15 a by the rotation of theimpeller 16, i.e. the fluid in the vicinity of thefeed port 31 a with a higher pressure than theintake port 11 a, flows into thefluid passage 31 via thefeed port 31 a. The fluid flowing into thefluid passage 31 is pressurized and sent to the bearing bore 13 a, and also supplied to thesecond bearing portion 13 b by the rotation of theimpeller 16. Thefluid passage 31 extends further in the oblique direction via the inner diameter of the bearing bore 13 a. However, the end portion of thefluid passage 31 formed in the oblique direction is blocked with the end portion of the inner diameter portion of themotor housing 12. Therefore, the fluid reaching the gap formed between the bearing bore 13 a and theshaft 21 flows along the axial direction of theshaft 21 into the gap formed between themagnet 22 and theinner wall 12 a molding the stator. In this case, a slit is formed in the axial direction on the inner diameter portion of thesecond bearing portion 13 b. In addition, a plurality ofslits 13 s are formed in the radial direction on an end portion of the bearing bore 13 a on themotor 20 side. Thus, the fluid in thefluid passage 31 smoothly flows through the outer periphery of thesmall diameter portion 21 a of theshaft 21 and the gap formed between the outer periphery of themagnet 22 and theinner wall 12 a. The fluid then flows along the outer periphery of thesmall diameter portion 21 c of theshaft 21 and led to thefirst bearing portion 12 b to which theshaft 21 is rotatably supported. - A
fluid passage 21 p (third fluid passage) for letting the fluid flow into thefirst fluid chamber 15 a on the intake side is formed within theshaft 21, axially penetrating through a center portion of theshaft 21. In this case, an escape bore 16 b for letting the fluid led from thefluid passage 21 p flow into thefirst fluid chamber 15 a is formed at a tip end portion of theimpeller 16 assembled to the tip end-portion of theshaft 21. Therefore, the fluid reaching thefirst bearing portion 12 b flows through thefluid passage 21 p formed within theshaft 21 and the escape bore 16 b of theimpeller 16, and then ultimately returns to thefirst fluid chamber 15 a. - A process of a part of the fluid in the
second fluid chamber 15 b flowing through thefeed port 31 a, thefluid passage 31, and the like and then returning to thefirst fluid chamber 15 a has been explained. Focusing on a pressure balance between thefirst fluid chamber 15 a and thesecond fluid chamber 15 b, the pressure in thesecond fluid chamber 15 b is higher than that of thefirst fluid chamber 15 a when the pump is driven since the fluid in thefirst fluid chamber 15 a is pressurized and then sent to thesecond fluid chamber 15 b by the rotation of theimpeller 16. Therefore, the fluid flows smoothly from thefeed port 31 a provided in thesecond fluid chamber 15 b through thefluid passage 31, the inside of themotor 20, and then to thefirst fluid chamber 15 a. - According to the above-mentioned structure, an original function of the fluid passage that the fluid is pressurized and sent to a required portion within the
motor 20 for lubrication and/or cooling may not be deteriorated by forming thefluid passage 31 within the bearingplate 13 in the oblique direction with avoiding a portion where the O-ring 25 is provided. Further, the foreign matter included in the fluid that circulates through the inside of thepump device 10 is surely eliminated by thefilter 38 provided on the high-pressure side. As a result, a high lubricity may be obtained, thereby improving the reliability of thepump device 10. - A second embodiment of the present invention is explained referring to
FIG. 2 . A structure of the second embodiment is basically same as that of the first embodiment but differs in a method how the highly pressurized fluid is led to the bearing portion of theshaft 21 and then returned to the intake side. Therefore, the same structure as the first embodiment is omitted and a different structure only is explained as follows. - According to the second embodiment, the
fluid passage 31 is not formed within the bearingplate 13. Instead, a fluid passage 33 (first fluid passage) is formed within theimpeller 16. - The
impeller 16 made of resin is insert-molded by abush 17 made of metal being inserted into a center of theimpeller 16. Theimpeller 16 includes the plurality ofblades 16 a and abase portion 16 c for supporting theblades 16 a. Thefluid passage 33 is formed in thebase portion 16 c of theimpeller 16, extending in the radial direction of theimpeller 16. Thefluid passage 33 penetrates into thebush 17. Thefluid passage 33 communicates with thesecond fluid chamber 15 b with a higher pressure than theintake port 11 a. Afilter 35 for preventing the foreign matter from entering into thefluid passage 33 is provided on an outer diameter side thereof. - A fluid passage 36 (second fluid passage) is formed within the
shaft 21 in the radial direction so as to communicate with thefluid passage 33 formed within theimpeller 16. At the same time, a fluid passage 37 (second fluid passage) is formed in a center portion of theshaft 21, extending in the axial direction thereof from an end portion of thefirst bearing portion 12 b so as to communicate with thefluid passage 36. - According to the aforementioned structure of the second embodiment, a part of the fluid that is highly pressurized by the rotation of the
impeller 16 flows through thefluid passage 33 after passing through thefilter 35, thereby preventing the foreign matter from entering into thefluid passage 33 formed within theimpeller 16. Then, the fluid is supplied from the axially center portion of theshaft 21 to thefirst bearing portion 12 b via thefluid passages shaft 21 and theinner wall 12 a of themotor 20, thereby achieving the lubrication and/or cooling within themotor 20 including theshaft 21. In this case, the fluid is supplied to the outer periphery of theshaft 21, theinner wall 12 a of themotor 20, and the bearingportions second bearing portion 13 b flows into a penetratingbore 16 d penetrating through both sides in the axial direction of thebase portion 16 c, then into thefirst fluid chamber 15 a on the intake side of thefluid chamber 15. Thus, an extra piping is not required to be employed. Further, a labyrinth L is formed between thebase portion 16 c and the bearingplate 13 on a radially outward side relative to the penetratingbore 16 d, thereby effectively leading the fluid from thesecond bearing portion 13 b to thefirst fluid chamber 15 a. - According to the above-mentioned structure, the effective cooling and/or lubrication may be achieved. The
filter 35 is provided at a feed port for the fluid and thus the foreign matter may be caught by thefilter 35. Thefilter 35 is provided on the outer peripheral portion of theimpeller 16, so that the foreign matter may be blown outside of theimpeller 16 due to centrifugal force occurring when theimpeller 16 rotates even if the foreign matter exists on the outer diameter portion of theimpeller 16. The foreign matter is prevented from accumulating on a surface of thefilter 35. Therefore, the bearingportions shaft 21 is rotatably supported for rotating theimpeller 16 may be protected by a simple structure of providing thefilter 35 at the feed port of theimpeller 16. - With the
shaft 21 made of metal being employed in the structure ofFIG. 2 , the magnetic foreign matter included in the fluid and passing through thefilter 35 may be caught by the magnetic force of themagnet 22 fixed to theshaft 21 when the fluid flows through the axially center portion of theshaft 21. In addition, thefluid passages - According to the aforementioned first embodiment, the
fluid passage 31 for leading the fluid into the bearingplate 13 is formed within the bearingplate 13. Thus, an extra piping is not required to be employed outside of thepump device 10 for leading the fluid to the bearingportions pump device 10 as a whole. Thefluid passage 31 through which the fluid is pressurized and sent to a required portion within themotor 20 for lubrication or cooling is formed within thepump device 10, thereby achieving high space efficiency. - In addition, according to the aforementioned first embodiment, one end of the
fluid passage 31 is formed with the opening facing thefluid chamber 15. The other end of thefluid passage 31 is provided adjacent to thesecond bearing portion 13 b and communicates with the bearing bore 13 a having a larger diameter than thesecond bearing portion 13 b. Thus, the fluid may be led from thefluid chamber 15 to the bearingportions second fluid chamber 15 b in which the fluid has a high pressure in thepump housing 11. Thus, a part of the fluid may be led to the opening, being pressurized and sent to the lubricant portion. - Further, according to the aforementioned first embodiment, the
filter 38 is provided at thefeed port 31 a for leading the fluid to thefluid passage 31. Thus, the foreign matter from thefluid chamber 15 is prevented from being mixed into the fluid and reaching theshaft 21. The malfunction of thepump device 10 due to entering of the foreign matter may be avoided. - Furthermore, according to the aforementioned first embodiment, the
fluid passage 31 may penetrate through the both side faces of the bearingplate 13 in the axial direction, thereby obtaining thefluid passage 31 with a simple structure. - Furthermore, according to the aforementioned first embodiment, the
first bearing portion 12 b and thesecond bearing portion 13 b communicate with each other via a gap formed between the stator of themotor 20 and themagnet 22, thereby cooling the stator and themagnet 22. - Furthermore, according to the aforementioned first embodiment, the
fluid passage 21 p is formed within theshaft 21 for connecting thefirst bearing portion 12 b and thefirst fluid chamber 15 a on the intake side. Thus, the fluid supplied to thefirst bearing portion 12 b may easily flow by using the intake pressure of thefirst fluid chamber 15 a. - Furthermore, according to the aforementioned first embodiment, the end portion of the bearing bore 13 a on the
motor 20 side is formed with a slit in the radial direction of theshaft 21. Thus, the fluid may smoothly flow through the gap formed between the bearing bore 13 a and theshaft 21. - Furthermore, according to the aforementioned first embodiment, the
fluid passage 31 formed within the bearingplate 13 and extending in the radial direction thereof keeps a predetermined angle with theshaft 21. Thus, thefluid passage 31 may be formed with a simple structure. - Furthermore, according to the aforementioned second embodiment, the
fluid passage 33 is formed within theimpeller 16 in the radial direction for leading the fluid to thefirst bearing portion 12 b. Thus, an extra piping is not required to be provided outside of thepump device 10 for leading the fluid to thefirst bearing portion 12 b. - Furthermore, according to the aforementioned second embodiment, the
fluid passages fluid passage 33 and leading the fluid to thefirst bearing portion 12 b is formed in theshaft 21. Thus, an extra piping is not required to be provided outside of thepump device 10 for leading the fluid to thefirst bearing portion 12 b. - Furthermore, according to the aforementioned second embodiment, the
fluid passage 33 is formed in thebase portion 16 c for supporting theblades 16 a of theimpeller 16. Thus, the bearing portions12 b and 13 b may be protected with high space efficiency by using the base portion 31 c not having a feature of moving the fluid. - Furthermore, according to the aforementioned second embodiment, the penetrating
bore 16 d is formed on thebase portion 16 c for penetrating through the both sides of thebase portion 16 c. Thus, an extra piping for leading the fluid to thefirst fluid chamber 15 a is not required. - Furthermore, according to the aforementioned second embodiment, the fluid flowing through the
fluid passage 33 is led to thefirst fluid chamber 15 a on the intake side of thefluid chamber 15 via thefluid passages first bearing portion 12 b, the gap between the stator and themagnet 22, thesecond bearing portion 13 b formed at the bearingplate 13 disposed between thepump housing 11 and themotor housing 12 and rotatably supporting theshaft 21, the gap formed between the bearingplate 13 and the base portion 13 c, and the penetratingbore 16 d. Thus, the lubrication and cooling of each bearingportion magnet 22 may be performed with a short piping. - Furthermore, according to the aforementioned second embodiment, the labyrinth L is formed between the
base portion 16 c and the bearingplate 13. Thus, the fluid may be effectively supplied to thefirst fluid chamber 15 a. - The principles, preferred embodiment and mode of operation of the present invention have been described in the foregoing specification. However, the invention which is intended to be protected is not to be construed as limited to the particular embodiments disclosed. Further, the embodiments described herein are to be regarded as illustrative rather than restrictive. Variations and changes may be made by others, and equivalents employed, without departing from the sprit of the present invention. Accordingly, it is expressly intended that all such variations, changes and equivalents which fall within the spirit and scope of the present invention as defined in the claims, be embraced thereby.
Claims (16)
1. A pump device comprising:
a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port;
a motor housing including a stator:
a shaft whose one end projects into the pump housing and to which an impeller is assembled, and whose the other end is rotatably connected to a first bearing portion within the motor housing;
a rotor assembled to the shaft and facing the stator; and
a bearing plate disposed between the pump housing and the motor housing and including a second bearing portion rotatably supporting the shaft; wherein the bearing plate is formed with a first fluid passage for leading the fluid to inside of the bearing plate.
2. A pump device according to claim 1 , wherein the first fluid passage includes a first end including an opening facing the fluid chamber and a second end communicating with a bearing bore formed at the bearing plate and provided adjacent to the second bearing portion and having a larger diameter than the second bearing portion.
3. A pump device according to claim 2 , wherein the opening is provided in a second fluid chamber having a high fluid pressure in the pump housing.
4. A pump device according to claim 3 , wherein the opening includes a filter.
5. A pump device according to claim 1 , wherein the first fluid passage penetrates through both side faces of the bearing plate in an axial direction.
6. A pump device according to claim 2 , wherein the first bearing portion and the second bearing portion communicate with each other via a gap formed between the stator and the rotor.
7. A pump device according to claim 6 , wherein the shaft includes a fluid path for connecting the second bearing portion and a first fluid chamber provided on an intake side of the fluid chamber.
8. A pump device according to claim 7 , wherein a side end portion of the bearing bore on the motor side is formed by a slit in a radial direction of the shaft.
9. A pump device according to claim 5 , wherein the first fluid passage formed in the bearing plate and extending in a radial direction thereof keeps a predetermined angle with the shaft.
10. A pump device comprising:
a pump housing including a fluid chamber for inhaling a fluid flowing through the fluid chamber via an intake port and discharging the fluid to an outside via a discharge port;
a motor housing including a stator:
a shaft whose one end projects into the pump housing and to which an impeller is assembled, and whose other end is rotatably connected to a first bearing portion within the motor housing; and
a rotor assembled to the shaft and facing the stator; wherein the impeller is formed with a first fluid passage extending in a radial direction of the impeller for leading the fluid to the first bearing portion.
11. A pump device according to claim 10 , wherein the shaft includes a second fluid passage communicating with the first fluid passage and leading the fluid to the first bearing portion.
12. A pump device according to claim 11 , wherein the first fluid passage includes a feed port to which the fluid is led and at which a filter is provided.
13. A pump device according to claim 10 , wherein the first fluid passage is formed in a base portion of the impeller for supporting a blade of the impeller.
14. A pump device according to claim 13 , wherein the base portion includes a penetrating bore penetrating through both sides of the base portion in an axial direction thereof.
15. A pump device according to claim 14 , wherein the fluid supplied from the first fluid passage is led to a first fluid chamber on an intake side of the fluid chamber via the second fluid passage, the first bearing portion, a gap formed between the stator and the rotor, a second bearing portion formed at a bearing plate disposed between the pump housing and the motor housing and rotatably supporting the shaft, a gap formed between the bearing plate and the base portion, and the penetrating bore.
16. A pump device according to claim 15 , further comprising a labyrinth formed between the base portion and the bearing plate radially outside of the penetrating bore.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003282998 | 2003-07-30 | ||
JP2003-282998 | 2003-07-30 | ||
JP2003305542A JP2005061391A (en) | 2003-07-30 | 2003-08-28 | Pump device |
JP2003-305542 | 2003-08-28 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050025642A1 true US20050025642A1 (en) | 2005-02-03 |
Family
ID=33543586
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/893,984 Abandoned US20050025642A1 (en) | 2003-07-30 | 2004-07-20 | Pump device |
Country Status (4)
Country | Link |
---|---|
US (1) | US20050025642A1 (en) |
EP (1) | EP1503085A3 (en) |
JP (1) | JP2005061391A (en) |
CN (1) | CN1576607A (en) |
Cited By (10)
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US7828791B2 (en) | 2004-05-14 | 2010-11-09 | Ethicon Endo-Surgery, Inc. | Medical instrument having a guidewire and articulated catheter |
US20110116948A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Method for manufacturing stator for electric water pump |
US20110116953A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Electric Water Pump |
US20110116952A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Electric water pump |
US20110116947A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Electric water pump |
DE102010062137A1 (en) * | 2010-11-29 | 2012-05-31 | Mahle International Gmbh | Liquid conveying device |
US20140241915A1 (en) * | 2013-02-26 | 2014-08-28 | Shinano Kenshi Co., Ltd. | Electric fluid pump |
DE102014202283A1 (en) * | 2014-02-07 | 2015-08-13 | Bühler Motor GmbH | Oil pump drive |
CN110285067A (en) * | 2019-06-28 | 2019-09-27 | 安徽泾县天和泵阀有限公司 | A kind of long-life, low-maintenance cost magnetic drive pump |
US11988218B2 (en) | 2021-03-10 | 2024-05-21 | Multi Parts Supply Usa, Inc. | Electric coolant pump with expansion compensating seal |
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CN101213457A (en) * | 2005-03-30 | 2008-07-02 | 微流体科技有限公司 | Electroosmotic pump and liquid feeder |
JP4607833B2 (en) * | 2006-08-08 | 2011-01-05 | ジヤトコ株式会社 | Hydraulic control device for belt type continuously variable transmission |
TW201000766A (en) * | 2008-06-20 | 2010-01-01 | Shang-Neng Wu | Magnetic transmission structure for water ejecting device |
DE102008038787A1 (en) * | 2008-08-13 | 2010-02-18 | Siemens Aktiengesellschaft | Fluid energy machine |
JP2010190333A (en) * | 2009-02-19 | 2010-09-02 | Toyo Electric Mfg Co Ltd | Oil level adjusting device for main motor for vehicle |
JP5318730B2 (en) * | 2009-11-17 | 2013-10-16 | 株式会社荏原製作所 | Motor pump |
EP2458225A1 (en) * | 2010-11-24 | 2012-05-30 | Frideco AG | Covering board for a screw centrifuge wheel pump and screw centrifuge wheel pump comprising such a covering board |
DE102011117183B4 (en) * | 2011-10-28 | 2014-10-16 | Ruhrpumpen Gmbh | Partial flow guide, in particular a magnetic coupling pump |
DE102012204044A1 (en) * | 2012-03-15 | 2013-09-19 | Schaeffler Technologies AG & Co. KG | Adjustable coolant pump with a multi-part modular design |
US9360015B2 (en) * | 2012-07-16 | 2016-06-07 | Magna Powertrain Of America, Inc. | Submerged rotor electric water pump with structural wetsleeve |
JP2017096205A (en) * | 2015-11-26 | 2017-06-01 | 株式会社山田製作所 | Electric pump |
JP2018048606A (en) * | 2016-09-23 | 2018-03-29 | アイシン精機株式会社 | Pump system |
JP6990119B2 (en) * | 2018-02-20 | 2022-01-12 | 株式会社荏原製作所 | Motor pump |
DE102018104015A1 (en) * | 2018-02-22 | 2019-08-22 | Nidec Gpm Gmbh | Coolant pump with optimized bearing arrangement and improved heat balance |
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-
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- 2004-07-20 US US10/893,984 patent/US20050025642A1/en not_active Abandoned
- 2004-07-21 EP EP04017248A patent/EP1503085A3/en not_active Withdrawn
- 2004-07-27 CN CNA2004100549710A patent/CN1576607A/en active Pending
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US4465437A (en) * | 1981-02-14 | 1984-08-14 | Grundfos A/S | Pump comprising a canned motor |
US5997264A (en) * | 1995-01-26 | 1999-12-07 | Ansimag Incorporated | Shaft for a magnetic-drive centrifugal pump using a plurality of grooves |
US5949171A (en) * | 1998-06-19 | 1999-09-07 | Siemens Canada Limited | Divisible lamination brushless pump-motor having fluid cooling system |
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Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
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US7828791B2 (en) | 2004-05-14 | 2010-11-09 | Ethicon Endo-Surgery, Inc. | Medical instrument having a guidewire and articulated catheter |
US8747082B2 (en) * | 2009-11-19 | 2014-06-10 | Hyundai Motor Company | Electric water pump |
US20110116953A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Electric Water Pump |
US20110116952A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Electric water pump |
US20110116947A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Electric water pump |
US20110116948A1 (en) * | 2009-11-19 | 2011-05-19 | Hyundai Motor Company | Method for manufacturing stator for electric water pump |
US8839503B2 (en) | 2009-11-19 | 2014-09-23 | Hyundai Motor Company | Method for manufacturing stator for electric water pump |
US8961154B2 (en) | 2009-11-19 | 2015-02-24 | Hyundai Motor Company | Electric water pump |
DE102010062137A1 (en) * | 2010-11-29 | 2012-05-31 | Mahle International Gmbh | Liquid conveying device |
US20140241915A1 (en) * | 2013-02-26 | 2014-08-28 | Shinano Kenshi Co., Ltd. | Electric fluid pump |
US9470237B2 (en) * | 2013-02-26 | 2016-10-18 | Shinano Kenshi Co., Ltd. | Electric fluid pump |
DE102014202283A1 (en) * | 2014-02-07 | 2015-08-13 | Bühler Motor GmbH | Oil pump drive |
CN110285067A (en) * | 2019-06-28 | 2019-09-27 | 安徽泾县天和泵阀有限公司 | A kind of long-life, low-maintenance cost magnetic drive pump |
US11988218B2 (en) | 2021-03-10 | 2024-05-21 | Multi Parts Supply Usa, Inc. | Electric coolant pump with expansion compensating seal |
Also Published As
Publication number | Publication date |
---|---|
EP1503085A3 (en) | 2005-11-16 |
EP1503085A2 (en) | 2005-02-02 |
JP2005061391A (en) | 2005-03-10 |
CN1576607A (en) | 2005-02-09 |
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Owner name: AISIN SEIKI KABUSHIKI KAISHA, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:DEAI, JUNJI;REEL/FRAME:015594/0050 Effective date: 20040712 |
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