Abstract: A turbocharger impeller is provided with a hub portion with a plurality of vane portions extending outwardly thereof. The hub portion is substantially shaped as a truncated cone with a diameter that gradually increases along a rotation axis. The vane portions are formed on a surface of the hub portion and guide a fluid flowing along the rotation axis radially outward relative to the hub portion. Grooves are formed in and/or on surfaces of the vane portions along a direction of the fluid flowing radially outward during rotation of the impeller. Protruding crest portions are formed between adjacent grooves. Crest portions in a central region near the rotation axis are lower in height than crest portions in an outer region further away from the rotation axis.

Abstract: A turbocharger impeller is provided with a hub portion with a plurality of vane portions extending outwardly thereof. The hub portion is substantially shaped as a truncated cone with a diameter that gradually increases along a rotation axis. The vane portions are formed on a surface of the hub portion and guide a fluid flowing along the rotation axis radially outward relative to the hub portion. Grooves are formed in and/or on surfaces of the vane portions along a direction of the fluid flowing radially outward during rotation of the impeller. Protruding crest portions are formed between adjacent grooves. Crest portions in a central region near the rotation axis are lower in height than crest portions in an outer region further away from the rotation axis.

Abstract: Each suction port 43 of a cylinder block 11 has a narrow passage 50 located at a top dead center side and a wide passage 51 located at a bottom dead center side. A suction communication passage 45 of a rotary valve 41 passes by a first succeeding end 50b of the narrow passage 50 before passing by a second succeeding end 51b of the wide passage 51. A high-pressure groove 47 of a residual gas bypass groove 46 faces only a narrow passage 50 of a suction port 43A that corresponds to a high-pressure side compression chamber 26 when in communication with the suction port 43A. A width Tc between the first succeeding end 50b and a second preceding end 51a of the wide passage 51 in the rotation direction of the rotary valve 41 is smaller than a seal width W of a seal region S between the high-pressure groove 47 and the outlet 45b of the suction communication passage 45.

Abstract: A variable displacement compressor includes a swash plate guiding member that rotates integrally with and inclines relative to a drive shaft, a swash plate supported by the guiding member, and a piston engaged with the swash plate via a shoe. A clutch is located between the guiding member and the swash plate. The clutch is switched between an engaged state, where the clutch permits the guiding member and the swash plate to rotate integrally, and a disengaged state, where the clutch permits the guiding member and the swash plate to rotate relative to each other. Therefore, the compressor is capable of switching between a state where improving the displacement controllability is prioritized and a state where reduction of mechanical loss between the swash plate and the shoes is prioritized.

Abstract: The deformation of cylinder bores in a cylinder block is prevented. The cylinder block 19 is inserted into a front housing 11. The cylinder block 19 is fixed to the front housing 11 by tightening plural screws 38 which penetrate through the cylinder block 19, from an end surface 191 side thereof, to be screwed into an end wall 32 of the front housing 11. Plural deformation absorbing grooves 39 are provided on the end surface 191. Each one of the deformation absorbing grooves 39 is provided in each intermediate space between the adjacent paired cylinder bores 41.

Abstract: A gasket 36 is interposed between an end face 341 of a front housing 11 and an end face 351 of a rear housing 12. A coned disc spring 37 is interposed between an end face 192 of a cylinder 19 and the end face 341 of the front housing 11. When the end faces 341, 351 are caused to approach each other so as to be joined together, the coned disc spring 37 is first held by the end face 341 of the front housing 11 and the end face 192 of the cylinder 19. When the end faces 341, 351 are caused to approach each other further so as to be joined together, the gasket 36 is held between the end faces 341, 351. Thus, it is ensured that the cylinder and the seal material interposed between the first housing and the second housing are held therebetween.

Abstract: A gasket 36 is interposed between an end face 341 of a front housing 11 and an end face 351 of a rear housing 12. A coned disc spring 37 is interposed between an end face 192 of a cylinder 19 and the end face 341 of the front housing 11. When the end faces 341, 351 are caused to approach each other so as to be joined together, the coned disc spring 37 is first held by the end face 341 of the front housing 11 and the end face 192 of the cylinder 19. When the end faces 341, 351 are caused to approach each other further so as to be joined together, the gasket 36 is held between the end faces 341, 351.

Abstract: The deformation of cylinder bores in a cylinder block is prevented. The cylinder block 19 is inserted into a front housing 11. The cylinder block 19 is fixed to the front housing 11 by tightening plural screws 38 which penetrate through the cylinder block 19, from an end surface 191 side thereof, to be screwed into an end wall 32 of the front housing 11. Plural deformation absorbing grooves 39 are provided on the end surface 191. Each one of the deformation absorbing grooves 39 is provided in each intermediate space between the adjacent paired cylinder bores 41.