A screw compressor, including: a housing including at least one air inlet and at least one air outlet; a screw rotor disposed in the housing, the screw rotor including a male screw and a female screw that engage with each other; and a drive motor that drives the screw rotor to rotate. The male screw includes a plurality of first sheets that are sequentially stacked, the outer edge of which is provided with a plurality of convex blades, and the convex blades of adjacent first sheets are staggered and stacked in sequence. The female screw includes a plurality of second sheets that are sequentially stacked, the outer edge of which is provided with a plurality of inwardly recessed arcuate grooves, and the arcuate grooves of adjacent second sheets are staggered and stacked in sequence.

A screw compressor includes a first rotor and a second rotor, and each rotor is provided with a synchronisation gear. The screw compressor is further provided with an electric motor and one or two driving gears for driving the first rotor or second rotor. At least one of the synchronisation gears or driving gears is provided with spokes between a rim supporting a gear mesh and a corresponding gear hub.

The utility model relates to internal cycloidal gear mechanisms and can be used in various branches of mechanical engineering as working members of hydraulic machines (pumps and engines), compressors, internal combustion engines, as well as in planetary gearboxes, in particular in technical systems for drilling and repairing oil and gas wells. The problems to be solved by the utility model include the improvement of the quality of the process of designing working members having a cycloidal tooth profile, as well as the substantiation of the conditions for modifying cycloidal face profiles (by choosing the required combination of dimensionless gearing coefficients) in order to achieve the maximum or minimum open area of the gerotor mechanism having a different kinematic ratio.

The invention relates to a rotor pair for a compressor block of a screw machine, wherein the a rotor pair comprises a secondary rotor that rotates about a first axis and a main rotor that rotates about a second axis, wherein the number of teeth of the main rotor is 3 and the number of teeth of the secondary rotor is 4. The relative profile depth of the secondary rotor is at least 0.5, preferably at least 0.515, and at most 0.65, preferably at most 0.595. rk1 is an addendum circle radius drawn around the outer circumference of the secondary rotor and rf1 is a dedendum circle radius starting at the profile base of the secondary rotor, wherein the ratio of the axis distance of the first axis from the second axis and the addendum circle radius rk1 is at least 1.636, and at most 1.8, preferably at most 1.733.

A Rotary Claw Pump with at least one pair of intermeshing rotors has the same shape within a tolerance of 3% of the radii from edges to rotational centers. A convex portion of the claws has a nominal uniform rate of radius change with angle of rotation. There may be multiple stages wherein the thickness of each successive rotor pair maintains profile but has a thickness within 20% of the thickness of the first stage rotor pair multiplied by the inverse products of the compression ratios of the preceding stages. A discharge port is at least partially uncovered at any position of rotation from where intermeshing claw rotor tips are closest to where they are most distant. The discharge port is at least partially connected with a region connected with the rotor tips of both claws during rotation. The discharge port limits pressure increase in the region.

A screw compressor for a utility vehicle has at least one female screw, at least one male screw that meshes with the female screw, and at least one screw compressor drive which drives the female screw.

A rotor for a positive displacement compressor assembly having a housing defining an inlet, an outlet, and a rotor cavity in communication with the inlet and the outlet. The rotor may comprise a rotor body and a porous inner core enclosed within the rotor body. The rotor may comprise a tapered rotor body having an outer radius that decreases from a first end to a second end thereof. In one form, the positive displacement compressor assembly may comprise a supercharger assembly for an internal combustion engine.

A blower may include a blower housing that may include a plurality of rotor chambers and a plurality of rotors. The plurality of rotors may be substantially identical and each may include a twist angle and a helix angle. The rotors and the blower housing may be configured to create internal fluid compression when the rotors are rotating at a first rotational speed and not to create internal fluid compression when the rotors are rotating at a second rotational speed. The rotors and the blower housing may be configured to create the internal fluid compression without backflow slots in the blower housing. The twist angle may include the angular displacement of lobes of the plurality of rotors between axial ends of the plurality of rotors. The helix angle may be a function of the twist angle and a pitch diameter of the plurality of rotors.

This screw compressor is provided with a screw rotor, a casing accommodating the screw rotor, and a liquid feed mechanism for feeding a liquid into an operating chamber enclosed by the casing, wherein the pitch of the screw rotor changes in the axial direction from a suction end surface toward a discharge end surface.

A compressor (200), comprising: a first rotor (20) being rotatable around a first axis (11), the first rotor (20) comprising a first portion (22) and a second portion (24); and a first shaft (10) carrying the first portion (22) and the second portion (24), the first shaft (10) having a first end (12) and a second end (14) that are oppositely arranged, wherein the first rotor (20) is configured to be applied with a preset acting force in a direction from the first end (12) toward the second end (14) or from the second end (14) toward the first end (12) during rotation. The size of the compressor (200) can be reduced with the displacement of the compressor (200) remaining substantially unchanged.