Regenerative pump

Abstract: The present invention provides a regenerative pump ( 11 ) for supplying fuel into an injection device for an internal combustion engine. The regenerative pump ( 11 ) has a longer pressurizing passage ( 37 ) and a slanted discharge port ( 36 ) connected thereto and formed at an outer periphery thereof. The pressure loss in the pump is small because the fuel flows smoothly into the discharge port ( 36 ) from the pressurizing passage ( 37 ), and accordingly the efficiency of the pump is high and the pump can be made small in size at the same time.

Description: 1. Field of the Invention The present invention relates to a regenerative pump having an improved discharge port to improve the efficiency of the regenerative pump, particularly, a fuel supply pump used in a fuel injection system for an internal combustion engine. 2. Description of Related Art As shown in FIG. 11, Japanese Patent Laid-Open Publication No. Sho-60-79193 discloses a regenerative pump having a pump casing 1 and an impeller 2 disposed in the pump casing 1. In the casing 1, there is provided a C-shaped passage 3. The pump casing 1 is composed of a casing 1a shown in FIG. 12 and a casing cover 1b shown in FIG. 13, both being overlapped on each other. On the casing 1a, a depressed portion which serves as a impeller space 4 is formed. Around the impeller space 4, a circular ditch 3a constituting the passage 3 is formed. On the casing cover 1b, another circular ditch 3b constituting the passage 3 is formed. At an upstream end of the circular ditch 3b of the casing cover 1b, a suction port 5 is formed. At a downstream end of the circular ditch 3a of the casing 1a, a discharge port 6 is formed. On the periphery of the impeller 2, a plurality of blades 2a and blade ditches 2b sticking out in the passage is alternately formed. AS the impeller rotates, fluid in the blade ditches 2b is pushed out to the passage 3 by friction force from the blades 2a, and the fluid pushed out to the passage 3 is sucked into the blade ditches 2b and pushed out again to the passage 3. The fluid is circulated in this manner and thereby pressurized in the course it flows from the upstream end to the downstream end, and it is discharged from the discharge port 6 as a pressurized fluid. A portion indicated by a part number 7 in FIGS. 11 and 12 is a sealing wall. The regenerative pump of this kind is often used as a fuel supply pump in a fuel injection device for an internal combustion engine, because it can produce a relatively high fuel pressure for a low viscosity fluid. In the conventional regenerative pump, the discharge port 6 is provided at the downstream end of the passage 3, stretching perpendicularly to the passage 3, i.e., in parallel to the impeller axis. In the conventional regenerative pump described above, the discharge port 6 is located at the same position as the downstream end of the passage 3, and therefore the downstream end is occupied by the discharge port 6. Accordingly, the passage 3 is terminated at a position immediately before the discharge port 6, resulting in shortening an effective length of the passage 3 and in decreasing pressurizing effect achieved by a rotation of the impeller 2. To compensate this negative effect, it is conceivable to increase the rotational speed of the impeller 2. However, if the rotational speed were increased, a friction loss between an impeller axis and a bearing supporting the impeller and other losses would be increased, and accordingly the efficiency of the pump would be decreased. In addition, since the discharge port 6 is formed in a direction perpendicular to the passage 3, the pressurized liquid fuel flowing through the passage 3 hits the wall 6a at the downstream end of the passage 3 as shown an arrow "A" in FIG. 14. The liquid fuel has to change its flow direction by approximately 90-degree at the discharge port 6, and therefore a loss for changing the flow direction becomes large, resulting in decreasing the efficiency of the pump. To decrease the loss resulting from changing the flow direction, a pump having a slope 8 as shown in FIG. 14 has been heretofore proposed. However, when the slope 8 like this is formed at the downstream end of the passage, the effective length of the passage is further decreased. In Japanese Patent Laid-Open Publication No. Hei-1-177492, a multi-stage regenerative pump shown in FIG. 15 is disclosed. In this pump the discharge port 6 is formed at the downstream end which is made at a position stretched tangentially from a mid portion of the passage 3. The purpose of this design is to reduce the hitting speed of the liquid fuel, according to the disclosure. However, the passage portion made for leading the fuel to the discharge port 6 can not be utilized for pressurizing the fuel, and accordingly the effective length of the passage 3 is shortened. Moreover, since the discharge port 6 in this disclosure is also bent by about 90-degree from the passage 3, it is unavoidable to decrease the efficiency of the pump. In addition, in the pump disclosed in this publication, the pump becomes large in size because the leading passage is extended tangentially from the mid portion of the passage 3 and it goes outside beyond the outer periphery of the passage 3. The US-A-5 401 143 shows a regenerative pump for sucking, pressurizing and discharging fluid comprising: a pump casing having at least one C-shaped passage including an upstream end and a downstream end, a suction port communicating with the upstream end, a discharge port communicating with the downstream end formed at an outside of the passage, and a sealing wall formed between the suction port and the discharge port for intercepting the fuel flow therebetween; and an impeller disposed in the pump casing having a plurality of blades and blade ditches alternately formed on an outer periphery thereof; wherein: the fluid is sucked from the suction port, pressurized in the passage by circulating the fluid between the blade ditches and the passage, and discharged from the discharge port according to rotation of the impeller Furthermore, the document US-A- 4 508 492 discloses a regenerative pump for sucking, pressurizing and discharging fluid comprising: a pump casing having at least one C-shaped passage including an upstream end and a downstream end, a suction port communicating with the upstream end, a discharge port communicating with the downstream end formed at an outside of the passage, and a sealing wall formed between the suction port and the discharge port for intercepting the fuel flow therebetween; and an impeller disposed in the pump casing having a plurality of blades and blade ditches alternately formed on an outer periphery thereof; wherein: the fluid is sucked from the suction port, pressurized in the passage by circulating the fluid between the blade ditches and the passage, and discharged from the discharge port according to rotation of the impeller. SUMMARY OF THE INVENTION The present invention is as described in claim 1. It is an object of the present invention to provide a regenerative pump in which the effective length of the passage is made long enough to pressurize the fluid and the loss resulting from the flow direction change at the discharge port is minimized. Another object of the present invention is to provide a regenerative pump having a smaller size by utilizing the housing space effectively while keeping the enough length of the sealing wall. According to the present invention, the discharge port is provided outside the passage in contact therewith in order to make the passage in which the fluid is pressurized longer. The fluid can flow smoothly from the downstream end of the passage to the discharge port because it has a centrifugal flow speed element in its flow pressurized by the friction force of the impeller blades. Moreover, since the space in a radial direction of the sealing wall is utilized effectively, the size of the pump can be small. The loss occurring when the fluid enters into the discharge port from the passage is deceased while keeping the length of the sealing wall long enough to prevent fluid leakage from the downstream end to the upstream end. The discharge port is disposed with a slant angle so that an angle of flow direction change at the discharge port becomes small according to the present invention. Therefore, the fluid flow from the passage to the discharge port is smooth. A guiding portion for guiding the pressurized fluid is provided, according to the present invention, at the entrance to the discharge port ( not in the passage ). Therefore, the fluid can flow smoothly from the pressurizing passage to the discharge port. It is preferable that a separating wall is provided in each blade ditch of the impeller according to the present invention, and, therefore, the small space for the blade ditch can be utilized effectively for pressurizing the fluid. Other objects and features of the present invention will become readily apparent from a better understanding of the preferred embodiment described below with reference to the following drawings. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view showing an embodiment of the present invention; FIG. 2 is a cross-sectional view taken along a line II-II of FIG. 1; FIG. 3 is a cross-sectional view showing a pump according to the embodiment; FIG. 4 is a partial cross-sectional view showing an impeller and a passage of the embodiment; FIG. 5 is a plan view showing a casing of the embodiment; FIG. 6 is a plan view showing a casing cover of the embodiment; FIG. 7 is a perspective view showing a casing of the embodiment; FIG. 8 is a perspective view showing a casing cover of the embodiment; FIG. 9 is a cross-sectional view showing a pump of the embodiment; FIG. 10 is a cross-sectional view showing a fuel pump assembly according to the present invention; FIG. 11 is a cross-sectional view showing a conventional regenerative pump; FIG. 12 is a plan view showing a casing of a conventional regenerative pump; FIG. 13 is a plan view showing a casing cover of a conventional regenerative pump; FIG. 14 is a cross-sectional view taken along a line XIV-XIV of FIG. 12; FIG. 15 is a plan view showing another conventional regenerative pump, a part of casing cover being removed; FIG. 16 is a flow analysis chart showing a cross-section taken along a line XVI-XVI of FIG. 14. FIG. 17 is another flow analysis chart for the pump shown in FIG. 14; FIG. 18 is a flow analysis chart for the embodiment according to the present invention; FIG. 19 is another flow analysis chart for the embodiment according to the present invention; FIG. 20 is a graph showing a total efficiency of the regenerative pump according to the present invention in comparison with a conventional one. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment according to the present invention will be explained, referring to the FIGS. 1 through 10. A regenerative fuel pump 11 shown in FIG. 10 is dipped in a fuel tank of an automotive vehicle. As shown in FIG. 10, the fuel pump 11 is composed of a motor 12 and a pump 13 both of which are contained in a housing 14. The motor 12 is a direct current motor having brushes therewith, and is composed of a permanent magnet 15 contained in the housing 14 and an armature 16 disposed inside the permanent magnet 15. At one end of the housing a bearing holder 17 is fixed and a radial bearing 19 for supporting one end of the armature shaft 18 is disposed in the bearing holder 17. On top of the bearing holder 17 a cover end support 21 is crimped with the housing 14. The inside of the housing 14 also serves as a chamber 20 for sending fuel discharged from the pump 13 to an injection device for an internal combustion engine. An outlet pipe 23 communicating with the chamber 20 is provided on the cover end support 21 via a ditch 22. A tube ( not shown in-the drawing ) is inserted into the outlet tube 23, and the pressurized fuel discharged from the pump 13 into the chamber 20 is supplied to the injection device for the internal combustion engine. The pump 13 is a regenerative pump, and is composed of a casing 24 having radial wall 24a and a side wall 24b closing one end of the radial wall 24a, both being formed in a single body, a casing cover 25 closing the other end of the radial wall 24a, and an impeller 26. The casing 24 is inserted into the other end of the housing 14, and the casing cover 25 is mounted on the casing 24 and crimped with the other end of the housing 14. A pump casing 28 is constituted by the casing 24 and the casing cover 25, forming an impeller space 27 therein. The casing 24 and the casing cover 25 are made of aluminum by die-casting in this embodiment, but they can be also made of plastic resin by molding. The other end of the armature shaft 18 is inserted into the pump casing 28, and supported by a radial bearing 29 held by the side wall 24b of the casing 24 and a thrust bearing 30 fixed on the casing cover 25. The impeller 26 is made of a phenol resin reinforced by glass fiber, PPS or the like, and has a disk shape. On the outer periphery of the impeller 26, a plurality of blades 31 and blade ditches 32 shown in FIG. 4 is formed alternately along the periphery. The blade ditches are formed at both side of the separating wall 33 as shown in FIG. 4. The impeller 26 is installed in the impeller space 27, and a D-shaped cut 18a of the armature shaft 18 is slidably inserted into the D-shape hole 34 of the impeller 26. Therefore, the impeller 26 rotates according to the rotation of the armature shaft 18 and is slidable axially. As shown in FIGS. 5 through 8, an suction port 35 is formed on the casing cover 25, and a discharge port 36 is formed on the side wall 24b of the casing 24 with a certain angle apart from the suction port 35. As shown in FIG. 9, a C-shaped passage 37 connecting the suction port 35 and the discharge port 36 is formed circularly around the impeller space 27 of the pump casing 28. The blades 31 of the impeller 26 is sticking out in the passage 37. An end of the passage 37 at the suction port 35 is referred to as an upstream end hereafter and the other end of the passage 37 at the discharge port as a downstream end. The downstream end of the passage 37 is composed of an end ditch 38a of the casing 24 and an end ditch 39a of the casing cover 25, as shown in FIGS. 5 and 6. As shown in FIGS. 5 through 9, a radial space surrounding the impeller 26 is made by making a diameter of the radial wall 24a of the casing 24 larger than an outer diameter of the impeller 26. A axial space at both sides of the blades 31 is made by forming a C-shaped groove 38 on the side wall 24b of the casing 24 and another C-shaped groove 39 on the casing cover 25, respectively. A sealing wall 40 is formed on the side wall 24a between both ends of the C-shaped groove 38, so that a radial gap between the outer diameter of the impeller 26 and the sealing wall 40 becomes as small as possible in order to prevent leakage of the pressurized fuel from the discharge port 36 to the suction port 35 through the radial gap. The longer the sealing wall 40 becomes, the more perfect sealing is attained. The suction port 35 is open at the upstream end of the passage 37 and communicates with the fuel tank through the casing cover 25. Fuel in the fuel tank is sucked into the passage 37 of the pump 13 according to rotation of the impeller 26. The cross-sectional area of the passage 37 is made so that it becomes gradually smaller from the upstream end toward the downstream end only for a certain angle "α" shown in FIG. 6. To change the cross-sectional area of the passage 37 as mentioned above, the width and height of both C-shaped grooves 38 and 39 are changed. This means that the cross-sectional area of the passage 37 is relatively large at the upstream end thereof. This prevents that the fuel passage is abruptly narrowed at a neighborhood of suction port 35, thereby preventing cavitation of the fuel. A small hole 41 for discharging fuel vapor to the fuel tank is formed at the upstream side of the C-shaped groove 39 of the casing cover 25. The passage 37 is composed of two portions, that is, one is the portion with an angle "α" indicated in FIGS. 5 and 6 where the cross-sectional area thereof is gradually decreasing as mentioned above, and the other is the portion with an angle "β" where the cross-sectional area thereof is constant and the fluid is actually pressurized. The discharge port 36, as shown in FIG. 1, is formed on the radial wall 24a of the casing 24 next to the sealing wall 40, and is located outside the passage 37 in contact therewith. One end of the discharge port 36 is open at the downstream end of the passage 37 and the other end is open at the chamber 20 in the housing 14, passing through the side wall 24b of the casing 24, as shown in FIG. 3. The discharge port 36 has a rectangular shape with its longer side made in a rotational direction of the impeller 26. The liquid fuel pressurized according to the rotation of the impeller 26 is discharged from the discharge port 36 to the chamber 20. The down stream end of the C-shaped groove 39 of the casing cover 25 is widened to form a widened portion 39a which corresponds to the discharge port 36, so that the pressurized fuel can flow smoothly to the discharge port 36 through the widened portion 39a. As shown in FIG. 2, the discharge port 36 is formed with a slant angle. That is, the discharge port is slanted from the passage 37 side toward the chamber 20 side, so that the fuel flowing in the direction "B" shown in FIG. 2 can smoothly enters into the discharge port 36. As shown in FIG. 1, the slanted portion of the discharge port 36 is formed under the sealing wall 40, leaving a narrow side wall 42 at one side of the sealing wall 40. Therefore, the discharge port 36 has two slanted surfaces 36a and 36b as shown in FIGS. 1 and 2. The slanted surface 36a stretches from the narrow side wall 42. Now, the operation of the regenerative fuel pump according to the present invention will be explained. The impeller 26 is driven by the armature shaft 18 of the motor 12. As the impeller 26 rotates, the pump 13 sucks the liquid fuel in the tank into the passage 37 through the suction port 35. The fuel sucked into the passage 37 flows from the upstream end of the passage 37 toward the downstream end of the passage 37. In the course of the flow, the fuel flows in the blade ditches 32 as shown by arrows "C" and "D" in FIG. 4 by a friction force received from the blades 31, and is send out to the passage 37. The fuel in the passage 37 is again sucked into the blade ditches 32. Thus, the fuel circulates between the blade ditches 32 and the passage 37. In other words, the fuel flows along walls of the separating wall 33 in the blade ditches and then hits a side wall 37a of the fuel passage 37 and changes its flow direction there, and flows out into the passage 37 and again is sucked into the blade ditches 32. The fuel, thus circulating in the blade ditches 32 and the passage 37, proceeds helically from the upstream end to the downstream end of the passage 37. The flow speed of the fuel is decreased when the fuel sent from the blade ditches 32 to the passage 37 merges the fuel flowing in the passage 37, and kinetic energy given to the fuel by the blades 31 is converted to a pressure energy. Accordingly, the pressure of the fuel flowing in the passage 37 increases. The fuel is pressurized during the course of flowing in a direction "B" shown in FIG. 9 through a pressurizing passage with an angle "β" shown in FIGS. 5 and 6, and flows into the discharge port 36. Then, the pressurized fuel is discharged into the chamber 20 in the housing 14 and sent out to the fuel injection device through a tube connected to the outlet pipe 23. In the embodiment according to the present invention, the pressurizing passage of the passage 37 can be longer because the discharge port 36 is disposed outside the passage as opposed to a conventional pump in which the discharge port is disposed at the end of the passage. Therefore, the fuel can be pressurized higher. In other words, since the fluid is pressurized in the regenerative pump as it circulates between the blade ditches and the passage during the course of flowing through the pressuring passage, the higher the fuel pressure can be obtained, the longer the pressuring passage becomes. In the conventional pump, there is provided a guide passage 8, as shown in FIG. 12, for decreasing the change of the fuel flow direction when the fuel enters into a discharge port 6 from a passage 3a. The guide passage 8 can not be utilized for pressuring the fuel, and accordingly the pressurizing passage has to be shorter by the length of the guide passage 8. As opposed to this, according to the present invention, the discharge port 36 is formed outside the passage 37 and the guide passage like the passage 8 of the conventional pump is not necessary because the discharge port 36 is formed with a slant angle as explained later. Therefore, the pressuring passage can be made longer according to the present invention, and the kinetic energy given to the fluid per one rotation of the impeller can be made larger. Accordingly, the fluid can be pressurized higher without increasing the rotational speed of the impeller 26. As mentioned above, the pressurizing passage is not a whole length of the passage 37 but a length corresponding to the angle "β". Therefore, saving the length of the guide passage has a relatively large effect in increasing the fluid pressure in the pump. In addition, a guiding portion which has the substantially same cross-sectional area as the pressurizing passage is formed at the end of the pressurizing passage, facing the discharge port. Therefore, the pressurized fluid can flow smoothly into the discharge port. According to the present invention, since the discharge port 36 is formed outside the passage 37 ( not inside the passage ) and the fluid flowing through the passage 37 has a radial velocity element due to a centrifugal force, the pressure loss occurring when the fluid changes its flow direction in entering the discharge port 36 is very small, and accordingly the fluid is discharged into the chamber 20 without loosing its pressure. Moreover, since the discharge port 36 is formed with a slant angle as shown in FIGS. 1 and 2, the fluid flowing through the passage 37 having a velocity element along the passage hits the slanted wall 36a and changes its flow direction there. In other words, the fluid changes its flow direction on the slanted wall 36a as shown by an arrow "E" in FIG. 2. The flow direction change is an angle "γ" which is less than 90-degree, resulting in a less pressure loss in changing the flow direction. In this particular embodiment, the angle "γ" is made at 45-degree. Though the fluid entering into the discharge port 36 also hits the narrow side wall 42, the pressure loss is small because the surface of the narrow wall 42 is small. In order to confirm the effects of the present invention, computer analyses have been made, the results of which will be explained below referring to FIGS. 16 through 19. The analyses have been made in use of an equation of motion according to a rotating coordinate system, a centrifugal force and a Coriolis force being added to the equation as external forces. As boundary conditions, an amount of flow from the suction port is set at 140 litters per an hour, and a rotational speed of the impeller is set at 7500 rpm. FIG. 16 shows a cross-sectional flow analysis chart along a line XVI-XVI of FIG. 14. Referring to FIG. 16, the followings have become clear. Since the discharge port is disposed perpendicularly to the blade ditches, a strong flow "E" is formed along a separating wall 33a. A flow "F" having a velocity element in a rotational direction of the impeller and a velocity element in an axial direction of the impeller is formed from a neighborhood of a top surface 33b of the separating wall. The flow "F" is more intense at an outer wall side of the discharge port than at an inner wall side thereof. A flow stagnation occurs at the inner wall side. In other words, only a part of the cross-sectional area of the discharge port is effectively used. Moreover, some backward flows "Q" are also observed. Accordingly, a large amount of pressure loss occurs. Further, the flow along the separating wall 33a is not uniform because the flow "E" is too strong, which also causes a pressure loss. FIG. 17 shows another cross-sectional flow analysis chart for the pump shown in FIG. 14. Followings have become clear from this chart. The fluid flowing from the blade ditches flows in the rotational direction and hits an inner surface 6a of the sealing wall 7, and changes the flow direction by 90-degree there. Therefore, pressure loss at the flow direction change is large. FIG. 18 shows a flow analysis chart of an embodiment according to the present invention having a discharge port disposed outside the passage 37 and formed perpendicularly thereto. Also, a guiding portion facing the discharge port and having the same cross-sectional area is formed at the downstream end of the passage 37. A flow along the separating wall 33a is uniform because the strong flow "E" shown in FIG. 16 does not exist. The fluid proceeds helically and along the four walls of the discharge port 36 having a rectangular cross-section, and is discharged outside. Since the flow along the separating wall 33a is uniform, the discharge port is formed outside the passage in contact therewith with an enough cross-sectional area, and the flow density in the discharge port is substantially uniform; the fluid flow from the blade ditches of the impeller to the discharge port through the passage portion where the flow direction is changed is smooth and therefore no substantial pressure loss occurs. In addition, no backward flow which was observed in the conventional pump does not exist. Accordingly, the pump efficiency is increased in the embodiment according to the present invention. FIG. 19 shows another flow analysis chart for another embodiment according to the present invention having a discharge port disposed outside the passage 37 and formed with a slant angle as shown in FIGS. 1 and 2. The fluid flow coming from the blade ditches 32 in the rotation direction hits the slanted wall 36a and changes its direction by the angle "γ" ( shown in FIG. 2 ) on the slanted wall 36a. In this particular embodiment, the angle "γ" is set at 45-degree. It is confirmed that the fluid flows smoothly along the slanted wall 36a and the pressure loss at the flow direction change is small. Accordingly, the pump efficiency is improved. FIG. 20 shows a total efficiency of the fuel pump according to the present invention in comparison with the conventional fuel pump. The efficiency is measured by changing the discharge pressure from 100 kP to 600 kP at a constant supply voltage ( 12 Volts ) to the motor. The total efficiency is defined here as PQ/VI, where P is a discharge pressure, Q is a discharge quantity, V is a supply voltage and I is a current consumed. As seen from the graph, the maximum total efficiency of the fuel pump according to the present invention is 19.2 % and that of the conventional one is 17.6 %. The efficiency has been increased by about 10 %, resulting in decreasing the consumed current from 5.2 A to 4.7 A. Dimensions of the fuel pump of the embodiment according to the invention used in measuring the total efficiency are: the diameter of the impeller is 30 mm, the slant angle "γ" of the discharge port is 45-degree, and the rectangular shape of the discharge port in the side wall 24b is 3.8 mm × 2.0 mm ( a long side along the rotational direction is 3.8 mm, and a short side in the radial direction is 2.0 mm ). The embodiment described above is a single stage pump having one set of the impeller and the passage. However, the present invention can be also applied to a multi-stage pump having plural sets of the impeller and the passage in which the fluid pressurized in one stage is sent to the next stage consecutively. Also, the present invention can be applied to a double-passage pump in which two concentric passages, i.e., an inner passage and an outer passage are formed, the discharge port of the inner passage is connected to the suction port of the outer passage, and two sets of blades and blade ditches are formed on the impeller, each set being disposed in each passage. Further, the present invention is applied not only to the fuel pumps but also to other pumps for pressurizing fluid therein and discharge the pressurized fluid outside. While the present invention has been shown and described with reference to the foregoing preferred embodiments, it will be apparent to those skilled in the art that changes in form and detail may be made therein without departing from the scope of the invention as defined in the appended claims.

Claims: A regenerative pump (11) for sucking, pressurizing and discharging fluid comprising: a cylindrical pump casing (28) having at least one C-shaped passage (37) including an upstream end and a downstream end, a suction port (35) communicating with the upstream end, a discharge port (36) communicating with the downstream end, and a sealing wall (40) formed between the suction port (35) and the discharge port (36) for intercepting the fluid flow therebetween; and an impeller (26) disposed in the pump casing (28) having a plurality of blades (31) and blade ditches (32) alternately formed on an outer periphery thereof, wherein the fluid is sucked from the suction port (35), pressurized in the passage (37) by circulating the fluid between the blade ditches (32) and the passage (37), and discharged from the discharge port (36) according to rotation of the impeller (26), the regenerative pump (11) characterized in that : the discharge port (36) is formed within the cylindrical pump casing (28) at a radial outside of the C-shaped passage (37) in contact with an outer periphery of the C-shaped passage (37) at the downstream end of the C-shaped passage; the discharge port (36) includes an inlet opening formed inside of an outer periphery of the cylinder pump casing (28) and an outlet passage connected to the inlet opening, the outlet passage including a slanted surface (36a) formed adjacent to and radially outside the sealing wall (49) and slanted relative to an axial direction of the impeller (26) toward its rotational direction; and the fluid pressurized in the C-shaped passage (37) smoothly flows out through the inlet opening and the outlet passage of the discharge port (36), without making a sharp change in its flow direction. A regenerative pump (11) according to claim 1, wherein the impeller (26) has a separating wall (33) formed in the blade ditch (32) sticking out radially in the ditch. The regenerative pump (11) defined in claim 1, further characterized in that : the suction port (35) is open to a bottom surface of the cylindrical pump casing (28), and the discharge port (36) is open to an upper surface to the cylindrical pump casing (28) along the slanted surfaces (36a, 36b). The regenerative pump (11) defined in claim 3, further characterized in that : the slanted surface (36a, 36b) are formed at a radial outside of the sealing wall (40). The regenerative pump (11) defined in claim 4, further characterized in that : the pressurized fluid discharged from the discharge port (36) flows in an axial direction of the impeller (26). The regenerative pump (11) defined in claim 1, further characterized in that : the inlet opening of the discharge port (36) is formed in a rectangular shape elongated in the rotational direction of the impeller (26).

Inventors: ITO MOTOYA, KOBAYASHI ATSUSHIGE, MURAMATSU TOSHIHIKO, ITO, MOTOYA, KOBAYASHI, ATSUSHIGE, MURAMATSU, TOSHIHIKO
Applicants: DENSO CORP, DENSO CORPORATION
Application year: 1997
Main classification: F04D5
IPC codes: F04D5