A blower according to an embodiment of the present disclosure includes: a case; a fan; and a diffuser disposed downstream of the fan and guiding air, discharged from the fan, toward the discharge ports, wherein the diffuser includes: an outer wall; an inner wall spaced apart inwardly from the outer wall so that an air passage is formed therebetween; and a plurality of vanes extending radially between the outer wall and the inner wall and dividing the air passage into a plurality of unit passages, wherein the outer wall and the inner wall are formed to have areas with different radial separation distances D between the outer wall and the inner wall, such that in an area of the air passage of the diffuser in which air is discharged to a portion having a high flow resistance in the blower, the radial separation distance D increases to widen the air passage S, thereby compensating for the asymmetry of the passage inside the blower, allowing a uniform volume of air to reach the entire area of the discharge ports, and improving the performance of the blower.

A compressor is described which includes a non-axial first rotor, and a second rotor disposed immediately downstream from the first rotor and being co-axial therewith about a longitudinal axis of rotation. The second rotor rotates in a direction opposite the non-axial first rotor to discharge fluid flow into an uninterrupted passage between an outlet of the second rotor and one of a downstream combustor or a further compression stage. The uninterrupted passage is free of a diffusing passage. A gas turbine engine including such a compressor and a method of compressing fluid flow is also described.

A fan for generating an air current includes a body having an air inlet, and a nozzle connected to the body. The nozzle includes an interior passage for receiving an air flow from the body and an air outlet from which the air flow is emitted from the fan. The interior passage extends about an opening or bore through which air from outside the nozzle is drawn by air emitted from the air outlet. The body includes a duct having an air inlet and an air outlet, an impeller located within the duct for drawing the air flow through the duct, and a motor for driving the impeller. An annular guide member extends about the duct for guiding air from the air inlet of the body to the air inlet of the duct. The guide member defines with the duct an annular noise suppression cavity.

A fan for generating an air current includes a body having an air inlet, and a nozzle connected to the body. The nozzle includes an interior passage for receiving an air flow from the body and an air outlet from which the air flow is emitted from the fan. The interior passage extends about an opening or bore through which air from outside the nozzle is drawn by air emitted from the air outlet. The body includes a duct having an air inlet and an air outlet, an impeller located within the duct for drawing the air flow through the duct, and a motor for driving the impeller. An annular guide member extends about the duct for guiding air from the air inlet of the body to the air inlet of the duct. The guide member defines with the duct an annular noise suppression cavity.

The present invention relates to the field of heat pump water heaters. Disclosed are a fan and a heat pump type water heater using same. The fan of the present invention is mounted upside down in an upper space of a water tank for pumping air refrigerated by an evaporator in the heat pump type water heater; the fan comprises volutes, a partition plate, and an impeller, the impeller is arranged in the volutes, the volutes are designed as an involute structure, and volute tongues of the volutes are in a backscrolling shape; there are two volutes, the partition plate is arranged between the two volutes, spiral shafts of the two volutes are perpendicular to the partition plate, and the two volutes are symmetrically arranged; an air inlet is formed in the side wall of each volute distant from the partition plate, the air inlets are perpendicular to the spiral shafts of the volutes, and air outlet directions of the air outlets of the two volutes are the same. The integrated heat pump water heater of the present invention can achieve effects such as high energy efficiency, large heating capacity, and low noise in a limited space mainly by means of optimization of a wind field of the whole system and reasonable layout of components.

The present invention relates to the field of heat pump water heaters. Disclosed are a fan and a heat pump type water heater using same. The fan of the present invention is mounted upside down in an upper space of a water tank for pumping air refrigerated by an evaporator in the heat pump type water heater; the fan comprises volutes, a partition plate, and an impeller, the impeller is arranged in the volutes, the volutes are designed as an involute structure, and volute tongues of the volutes are in a backscrolling shape; there are two volutes, the partition plate is arranged between the two volutes, spiral shafts of the two volutes are perpendicular to the partition plate, and the two volutes are symmetrically arranged; an air inlet is formed in the side wall of each volute distant from the partition plate, the air inlets are perpendicular to the spiral shafts of the volutes, and air outlet directions of the air outlets of the two volutes are the same. The integrated heat pump water heater of the present invention can achieve effects such as high energy efficiency, large heating capacity, and low noise in a limited space mainly by means of optimization of a wind field of the whole system and reasonable layout of components.

An impeller with different blades with different lengths for suppressing noise is disclosed. The impeller includes a fan hub and a plurality of blades. The blades are positioned at intervals around the fan hub and arranged in a circular array. The blades extend radially from the fan hub, and two opposite ends of each of the blades are a root portion and a head portion respectively. All root portions of the blades are connected to a peripheral side of the fan hub, and all head portions of the blades are located on a same circle. Every two adjacent blades are different in length in a longitudinal direction from the root portion thereof to the head portion thereof.

Disclosed are a cross-flow air duct and an air outlet device. The cross-flow air duct includes a volute and a volute tongue. The volute includes a first body, a first side of the first body is an air inlet side, and a second side of the first body is an air outlet side. The volute tongue includes a second body, a first side of the second body is an air inlet side, and a second side of the second body is an air outlet side. An air inlet port is formed between the first sides, and an air outlet port is formed between the second sides. According to the cross-flow air duct, multiple groups of air outlet areas in different directions are formed, the air outlet width is enlarged as a whole, and the air supply range is increased.

Disclosed are a cross-flow air duct and an air outlet device. The cross-flow air duct includes a volute and a volute tongue. The volute includes a first body, a first side of the first body is an air inlet side, and a second side of the first body is an air outlet side. The volute tongue includes a second body, a first side of the second body is an air inlet side, and a second side of the second body is an air outlet side. An air inlet port is formed between the first sides, and an air outlet port is formed between the second sides. According to the cross-flow air duct, multiple groups of air outlet areas in different directions are formed, the air outlet width is enlarged as a whole, and the air supply range is increased.

The invention relates to a fluid pump that has an electric motor with a shaft and an impeller with an outer diameter, that is connected to the shaft for conjoint rotation. A maximum volumetric flow and a maximum pressure difference (dp) can be generated in the fluid pump by the rotating impeller. A characteristic index number (K) for the fluid pump is greater than 350 kW/m.sup.2. The index number (K) corresponds to the product of the maximum volumetric flow and the maximum pressure difference in the fluid pump divided by the square of the outer diameter of the impeller.