High speed whirlpool pump

Abstract: A pump for Whirlpool and Spa applications has a series wound universal motor which is directly coupled to a centrifugal impeller for operation in the range of 4000 to 9000 RPM. Variable speed of the pump is easily accomplished with a universal motor by varying the voltage to the motor.

Description: BACKGROUND OF THE INVENTION This invention relates to an electric machine according to the preamble of claim 1 and more particularly to such a machine including a high speed pump for Whirlpool and Spa applications. An electric machine of this kind is known from FR-A-2565296. Other similar devices primarily fall into five categories: a. Close coupled end suction (non-self draining), low speed pump on single speed, A.C. induction motor. b. Close coupled end suction, self-draining, low speed pump on single speed, A.C. induction motor. c. Close coupled end suction (non-self draining), low speed pump on two speed, A.C. induction motor. d. Close coupled end suction, self-draining, low speed pump on variable speed, variable frequency induction motor. e. Belt driven, low speed submersible pump powered by high speed series wound universal motor (portable Whirlpool units only). All of the above categories of Whirlpool pumps, provide flow and pressure to the liquid to be circulated in the normal manner consistent with single stage centrifugal, Kinetic pumps, of radial vane, closed impeller construction. Substantially all of the whirlpool pumps are driven by various types of induction motors, as is the case with most electric motor driven centrifugal pumps. The biggest shortcoming with the above mentioned current devices is the inherent relative high cost of the motor. The size and, therefore, cost of the motor is inversely related to the motor speed. The higher the speed the smaller the size and the lower the cost. The maximum motor speed on normal household A. C. current is 3600 RPM, based on an A.C. induction motor, with the minimum number (two) of motor poles and 60 cycles per second current frequency in the USA. Devices have been developed for induction type A.C. motors which can vary the cycle frequency (and therefore motor speed) up or down, however, this does not reduce, but rather increase the complexity and cost of the motor plus controls package. Even when the motor speed (and therefore pump speed) is increased by means of a variable frequency device, there is a limit to the speed of a conventional centrifugal pump in whirlpool or Spa applications due to cavitation in the inlet of the impeller vanes. This is why belt-driven submersible pumps powered by high speed universal motors are stepped down to about 3600 RPM today. Further, conventional universal motors are inherently noisy and must normally operate at very high speeds (over 10,000 RPM) to provide sufficient cooling for the power levels required with a fixed installation Whirlpool pump. FR-A-2565296 discloses a high speed pump for sanitary equipment provided with a turbine type impeller, the speed of which however, is restricted by insufficient cooling means. Additionally, the following patents were developed in searching the various features of the invention: US Patent No 353 994 4 661 041 3 384 022 4 019 829 4 449 889 4 523 900 4 642 023 4 213 742 4 389 159 4 518 311 3 516 757 4 126 360 4 286 919 2 991 927 4 842 481 3 286 639 French Patent No 2 389 784 Accordingly, the high speed pump for Whirlpool and Spa application of the invention overcomes the limitations of the prior art devices. SUMMARY OF THE INVENTION An object of the invention is to provide an electric machine including a motor and an improved pump which operates at high speed. This object is achieved by a machine having the features of claim 1. According to the broader aspects of this invention, a series wound universal motor is used to power, thru a direct drive (close coupled), a high speed centrifugal impeller, to speeds in the range of 4000 RPM to 9000 RPM, for whirlpool and Spa applications. A universal motor is cheaper than a single speed, two speed or variable speed induction motor, due to the higher speed and subsequent smaller motor size. Also, variable speed is easily accomplished with a universal motor by just varying only the voltage to the motor, and variable speed is a desirable option in the Whirlpool and Spa market. A feature of the invention includes unique modifications to the pump motor fan to both reduce the motor noise level and increase motor cooling. The basic function of a motor cooling fan is to draw ambient air into the motor housing, thru the stator laminations, over the field coils, armature, commutator and brushes, while providing sufficient air currents to also cool the motor bearings. Fans of this are well known to the motor industry, and for best cooling and noise they normally maximize the number of vanes on the fan to the point that additional full vanes will block air flow through the inlet portion of the fan. The fan according to the invention is more effective (quieter and better cooling) due to the application of splitter (short) vanes equally spaced between the normal full length fan blades, coupled with a reduction of the rear fan shroud diameter below the maximum blade outer diameter. The use of splitter vanes allows more blades/vanes to be used on the fan without blocking the air inlet to the fan. The higher number of blades/vanes reduces the pressure loading on the fan individual blades/vanes, which reduces the noise level, and increases the frequency of the motor noise which makes the noise easier to block. The reduction of the rear shroud reduces the blockage of the axial component of the air flow at the discharge of the fan, as it exits the motor housing vents with as little restriction as possible. The better cooling from this fan also allows a smaller outer fan diameter which further reduces the noise level. The main feature of this invention includes a modification to the motor housing stationary "peeler" tongue which is close to the outer diameter of the fan blades and vanes. The peeler tongue has been skewed at an angle with respect to the fan blades to further reduce motor/fan noise. Without the skewing, the valving effect of the high and low pressure sides of each fan vane passing close to the peeler tongue causes strong pressure pulsations, or noise. By skewing the peeler tongue, this causes a more gradual fluctuation of the fan exit pressure as the fan blades pass close to the tongue, thus generating less noise. BRIEF DESCRIPTION OF THE DRAWINGS The object of the present invention will become more fully apparent from the following detailed description of the preferred embodiment, the appended claims and the accompanying drawings in which: Figure 1 is a cross-sectional view of a pump provided with the fan and motor housing according to the invention; Figure 2 is a frontal view of the fan according to the invention; Figure 2A is a cross-sectional view taken along arrows A-A of Figure 2; Figure 3 is a partial cross-sectional showing the fan and housing vents taken along lines 4-4 of Figure 1; Figure 3A is a cross-sectional view showing the motor housing vents, peeler tongue and fan taken along arrows A-A of Figure 3. Figure 3B is a partial view showing the fan and peeler tongue taken along line B-B of Figure 3. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT The pump apparatus of the invention will best be understood by reference to Figure 1. As illustrated, the apparatus includes a suction cover 11, suction inlet 12, insert 13, and self-draining channel 14. A O-ring 16 is positioned between cover 11 and casing 18 having an outlet 19. Cover 11 and casing 18 are mounted to universal motor housing 20 by self taping screws in a standard manner. The universal motor includes a stator 22 and an armature 24. The armature 24 includes a commutator 25, and a shaft 26 having a threaded end 27 and a splined end 28. The commutator brushes for the universal motor are located in the housing 20 in a plane perpendicular to the cross-sectional view. Threaded on shaft end 27 is an inducerpeller 30 having mounted thereon a rubber boot 31, ceramic ring 32, and metal retaining ring 33 which form part of a mechanical seal. The other part of the mechanical seal includes a carbon seal ring 35, rubber boot 36, spring 37, and retaining cup 38. An O-ring 39 is positioned between cup 38 and casing 18. Inducerpeller 30 has two step front surfaces 40, 41 which run with a clearance between the complementary inner surfaces 13a, 13b of insert 13 to provide an impeller seal wear ring surface to reduce recirculation leakage flow into the pump suction. The inducerpeller has a vane 42 with a vane portion 42a which extends forward along the axial portion of the front shroud 40a, and sweeps back an angle of approximately 5° to 15° to the impeller axis to improve suction performance. A slinger 44 is mounted on shaft 26 adjacent bearing hub 46 of housing 20. Bearings 48, rotatably mount shaft 26 in hub 46, and bearings 50 rotatably mount the splined end 28 to housing bearing surface 52, and bearing 50 is retained on housing bearing surface 52 by means of strap 53. A fan 55 is spline mounted on the spline end 28 of shaft 26. An elastomeric motor mounting foot 60, encloses a compartment 61, in which may be mounted a circuit board 62 for mounting electrical components 62a, b for motor speed control. Back plate 65 encloses another compartment 66 in which may be mounted another circuit board 67 for mounting other of the electrical components 67a, b to control motor speed. Terminals 70, 71, 72 are used to connect leads to and from circuit boards and power source. Power leads (not shown) are coupled through opening 21 in housing 20 in known manner. Eack plate 65 may be metal to facilitate heat transfer though fins 65a from circuit board 67 which may be the high power circuit board of the control requiring the most heat dissipation. In the preferred embodiment, cover 11, insert 13, casing 18, housing 20, inducerpeller 30, fan 55, and mounting foot 60 are made of plastic suitable for injection molding. Figures 2 and 2A illustrate the motor fan according to the invention. The fan 55 includes thirteen full length blades 55a, thirteen short (splitter) vanes 55b, a hub 55c for pressing onto splined shaft, and a rear fan shroud 55d. The rear fan shroud 55d has a diameter 55e which is less than the diameter 55f. As described in the Summary of the Invention, the splitter vanes equally spaced between the full length blades improves the effective cooling, and the reduced shroud diameter improves the air flow at the discharge of the fan as it exits the motor housing. The fan features will be better understood by reference to Figure 3, which is a partial cross-sectional view taken along lines 4-4 of figure 1 to show the effect of air flow through the fan and vents. Motor housing 20 has housing vents 20a, 20b for air exhaust from fan 55. Rear fan shroud 55d has a diameter 55e shorter than the outer diameter 55f to facilitate air flow represented by arrows 80, 81 to the exhaust vents throughout the fan compartment 20c. In figure 3A, a peeler tongue 20d is shown in vent 20a close to the outer diameter of the fan blades/vanes, and as shown in Figure 3B, the motor housing 20 peeler tongue 20d is skewed at an angle 84 of approximately fifteen degrees with respect to the fan blades 55a to further reduce motor/fan noise. Without skewing, the high and low pressure sides of the blades/vanes cause higher pressure pulsations or increased noise. While the present invention has been disclosed in connection with a preferred embodiment thereof, it should be understood that there may be other embodiments which fall within the scope of the invention as defined by the following claims.

Claims: An electric machine including a motor in a motor housing (20) and a motor shaft (26) having an end (27) extending axially from one end of said motor housing (20), a pump housing (18) being mounted to said one end of said motor housing (20) and forming a chamber and an inducer impeller (30) being mounted on said one shaft end (27) for rotation within said chamber, characterized in that said motor housing (20) includes a fan (55) mounted on said shaft (26) and vents (20a, 20b), one having a skewed peeler tounge (20d) adjacent the outer diameter of said fan blades (55a) and vanes (55b), said peeler tounge (20d) being formed at an angle of approximately fifteen degrees with respect to the axis of one of the fan blades (55a). An electric machine according to claim 1, characterized in that the fan (55) has alternating fan blades (55a) and splitter vanes (55b), with the splitter vanes equally spaced between full length fan blades and a rear shroud (55d) with a diameter less then the outer diameter of the blades and vanes.

Inventors: BUDRIS ALLAN ROGER, HESSLER WILLIAM DEWITT, PATEL RAMESH MAGAN, YEDIDIAH SHMARIAHU, BUDRIS, ALLAN ROGER, HESSLER, WILLIAM DEWITT, PATEL, RAMESH MAGAN, YEDIDIAH, SHMARIAHU
Applicants: ITT, ITT INDUSTRIES, INC. (A DELAWARE CORPORATION)
Application year: 1991
Main classification: F04D13
IPC codes: H02K23, H02K5, F04D29, F04D15, A61H33, F04D13