Abstract: A catalyst converter having a retaining mat with a thickness wherein the apparent density during assembling becomes 0.25 g/cm3 or more and less than 0.51 g/cm3 and the outside diameter D1 of a catalyst retainer is set according to interference of the retaining mat in passing through a press-in tool and interference of the retaining mat after being pressed into a retaining tube. The retaining mat is formed of a non-expandable inorganic fiber sheet. A pressing force moves the catalyst retainer in the axial direction with respect to the retaining tube while the catalyst converter device is used with the length L2 along the longitudinal direction of the catalyst retainer in the retaining mat wound around the catalyst retainer being set longer than the winding diameter D1 of the retaining mat around the catalyst retainer so that a retaining force R greater than the pressing force F can be secured.

Abstract: An exhaust muffler device has a ceramic catalyst body, and a holding tube having an end portion configured to hold the ceramic catalyst body therein with a holding mat therebetween. The end portion is reduced in diameter to form a reduced diameter portion. An exhaust pipe is connected to the holding tube, with a downstream end portion thereof being fitted to an inner circumference of the reduced diameter portion of the holding tube. An inner circumferential surface of the downstream end portion of the exhaust pipe is in proximity to a boundary portion of the holding mat and the ceramic catalyst body.

Abstract: A catalyst converter having a retaining mat with a thickness wherein the apparent density during assembling becomes 0.25 g/cm3 or more and less than 0.51 g/cm3 and the outside diameter D1 of a catalyst retainer is set according to interference of the retaining mat in passing through a press-in tool and interference of the retaining mat after being pressed into a retaining tube. The retaining mat is formed of a non-expandable inorganic fiber sheet. A pressing force moves the catalyst retainer in the axial direction with respect to the retaining tube while the catalyst converter device is used with the length L2 along the longitudinal direction of the catalyst retainer in the retaining mat wound around the catalyst retainer being set longer than the winding diameter D1 of the retaining mat around the catalyst retainer so that a retaining force R greater than the pressing force F can be secured.

Abstract: A rotary fluid machine is provided in which, among first bearings (23f, 23r) and a second bearing (24) supporting in a casing (11) opposite ends of a rotor (22) that includes an axial piston cylinder group (56) for converting the pressure energy of a working medium into mechanical energy, only the first bearings (23f, 23r) are formed from combined angular bearings that can support an axial load, and the second bearing (24) is formed from a radial bearing that can support a radial load and is axially movable relative to the rotor (22). Since the rotor (22) is axially positioned relative to the casing (11) by only the first bearings (the combined angular bearings) (23f, 23r), a difference in the amount of axial thermal expansion between the casing (11) and the rotor (22) can be absorbed by the second bearing (radial bearing) (24) without any problem. This can solve effectively problems caused by a difference in the amount of thermal expansion between the casing and the rotor of the rotary fluid machine.

Abstract: Pistons (41) are slidably received in a plurality of cylinders (39) disposed radially in a rotor (31), and a plurality of vanes (42) cooperating with the pistons (41) are disposed radially in the rotor (31), so that a vane chamber (54) is defined between a pair of the adjacent vanes (42). The radial movements of each of the pistons (41) and each of the vanes (42) are substantially stopped, so that the volumes of each of the cylinders (39) and each of the vane chambers (54) are not changed, for a period from the end of an exhaust stroke at which a gas-phase working medium is discharged from the cylinder (39) and the vane chamber (54) to the start of an intake stroke at which the supplying of the gas-phase working medium is started. Thus, it is possible to prevent the generation of a water hammer phenomenon due to a liquid-phase working medium confined in the cylinder (39) and the vane chamber (54).

Abstract: A Rankine cycle system is provided in which, with regard to a given relationship between the pressure (Pevp) and the temperature (Tevp) of a vapor that is taken into an expander (4) that includes a cylinder chamber in a first stage and a vane chamber in a second stage, the chambers being disposed in line, the expansion ratio of the vapor that the expander (4) takes in and discharges is set at a predetermined expansion ratio (?) according to the given relationship so that the pressure (Pexp2) and the temperature (Texp2) of the vapor that is discharged from the expander (4) coincide with target values, thereby making the expander (4) and the condenser (5) exhibit maximum performance. Since the vapor within the cylinder chamber in the first stage is in a superheated vapor region and contains no water, the phenomenon of water hammer will not be caused in the cylinder chamber.

Abstract: A rotary fluid machine is provided that includes a rotary valve (61) for controlling the intake and discharge of a working medium to and from an operating part (49, 57) formed from an axial piston cylinder group, a steam supply pipe (77) that is disposed on an axis (L) of a rotor (27) and supplies steam to the rotary valve (61), the steam supply pipe (77) being provided separately from a rotary valve main body (62), and gland packing sealing means (97) disposed between the steam supply pipe (77) and the rotary valve main body (62).

Abstract: An outer periphery of an output shaft integral with a rotor of an expander of a vane-type operated by a high-pressure vapor is supported at its opposite ends by a static-pressure bearing mounted at one end thereof in a floated state provided by a liquid film of a pressurized liquid-phase fluid supplied from a pressurized liquid-phase fluid feed bore through a pressurized liquid-phase fluid passage, and by a static-pressure bearing mounted at the other end thereof in a floated state provided by a liquid film of a pressurized liquid-phase fluid supplied from a pressurized liquid-phase fluid feed bore through pressurized liquid-phase fluid passages. Vanes supported radially in the rotor for reciprocal movement are supported in floated states by a liquid film of a pressurized liquid-phase fluid supplied through pressurized liquid-phase fluid passages extending radially outwards within the rotor.

Abstract: In a rotary fluid machine for converting the reciprocal movement of pistons and the rotational movement of a rotor from one into another by the engagement of rollers and annular grooves with each other, a value in a positive peak region of a pressure load of pistons received by the rollers engaged in the annular grooves and a value of a positive peak region of a centrifugal force load received by the rollers are set, so that they are substantially equal to each other, and phases of the two peak regions are deviated from each other. In addition, the phase negative peak region of a vane pushing-down load received by the rollers and the phase of the positive peak region of the pressure load of the pistons received by the rollers are established, so that they are overlapped at least partially on each other.

Abstract: In a rotary fluid machine including pistons (37) reciprocally received in cylinders (33) provided in a rotor (27), and vanes (44) fitted in vane grooves provided in the rotor (27) for reciprocal movement, the rotor (27) includes a rotor core (31) which is supported on a rotary shaft (21) and in which the cylinders (33) are accommodated, and twelve rotor segments (32) separated in a circumferential direction and fixed to surround an outer peripheral surface of the rotor core (31); and each of the vane grooves (43) is defined between the adjacent rotor segments (32). Thus, the dimensional accuracy of the vane grooves (43) can be enhanced without need for a special accurate working or processing.

Abstract: An expander includes a rotor rotatably supported by a casing, a group of axial pistons and cylinders installed so that its axis is surrounded by the rotor, and a swash plate having a rotating surface inclined with respect to the axis of the rotor and is rotatably supported by the casing. The relative rotation of the swash plate and the rotor around the axis is restricted and the relative shifting of the swash plate and rotor in the direction of the axis is allowed, by fitting a slider, fixed to the swash plate by a synchro-pin, into a long hole of an output shaft. Therefore, it is possible to prevent wrenching between the swash plate and the rotor due to thermal expansion while reducing the bending moment acting on the pistons of the group of axial pistons and cylinders of the expander.

Abstract: A Rankine cycle system is provided in which, with regard to a given relationship between the pressure (Pevp) and the temperature (Tevp) of a vapor that is taken into an expander (4) that includes a cylinder chamber in a first stage and a vane chamber in a second stage, the chambers being disposed in line, the expansion ratio of the vapor that the expander (4) takes in and discharges is set at a predetermined expansion ratio (v) according to the given relationship so that the pressure (Pexp2) and the temperature (Texp2) of the vapor that is discharged from the expander (4) coincide with target values, thereby making the expander (4) and the condenser (5) exhibit maximum performance. Since the vapor within the cylinder chamber in the first stage is in a superheated vapor region and contains no water, the phenomenon of water hammer will not be caused in the cylinder chamber.

Abstract: A waste heat recovery system for an internal combustion engine. The internal combustion engine includes first and second raised temperature portions. The raised temperature is higher at the first portion than at the second portion. A first evaporating portion generates a first vapor from the first raised temperature portion. A second evaporating portion generates a second vapor from the second raised temperature portion and with a lower pressure than the first vapor. First and second energy converting portions of a displacement type expander converts expansion energy of the first and second vapor into mechanical energy. A condenser and a supply pump are also provided.

Abstract: In a rotary fluid machine including pistons (37) reciprocally received in cylinders (33) provided in a rotor (27), and vanes (44) fitted in vane grooves provided in the rotor (27) for reciprocal movement, the rotor (27) includes a rotor core (31) which is supported on a rotary shaft (21) and in which the cylinders (33) are accommodated, and twelve rotor segments (32) separated in a circumferential direction and fixed to surround an outer peripheral surface of the rotor core (31); and each of the vane grooves (43) is defined between the adjacent rotor segments (32). Thus, the dimensional accuracy of the vane grooves (43) can be enhanced without need for a special accurate working or processing.

Abstract: In a rotary fluid machine for converting the reciprocal movement of pistons (41) and the rotational movement of a rotor (31) from one into another by the engagement of rollers (59) and annular grooves (60) with each other, a value in a positive peak region of a pressure load of pistons (41) received by the rollers (59) engaged in the annular grooves (60) and a value of a positive peak region of a centrifugal force load received by the rollers (59) are set, so that they are substantially equal to each other, and phases of the two peak regions are deviated from each other. In addition, the phase of a negative peak region of a vane (42) pushing-down load received by the rollers (59) and the phase of the positive peak region of the pressure load of the pistons (41) received by said rollers (59) are established, so that they are overlapped at least partially on each other.

Abstract: Pistons (41) are slidably received in a plurality of cylinders (39) disposed radially in a rotor (31), and a plurality of vanes (42) cooperating with the pistons (41) are disposed radially in the rotor (31), so that a vane chamber (54) is defined between a pair of the adjacent vanes (42). The radial movements of each of the pistons (41) and each of the vanes (42) are substantially stopped, so that the volumes of each of the cylinders (39) and each of the vane chambers (54) are not changed, for a period from the end of an exhaust stroke at which a gas-phase working medium is discharged from the cylinder (39) and the vane chamber (54) to the start of an intake stroke at which the supplying of the gas-phase working medium is started. Thus, it is possible to prevent the generation of a water hammer phenomenon due to a liquid-phase working medium confined in the cylinder (39) and the vane chamber (54).

Abstract: A vane type fluid machine includes: a casing; a rotor rotating in the casing; and a plurality of vanes supported by the rotor to slide on an inner surface of the casing. A seal portion of each vane is formed to be elastically deformable so as to slide on the inner surface of the casing while bending backward of a rotational direction of the rotor. Therefore, an improved structure of the seal portion of each vane secures good sealing performance even if machining accuracy of the inner surface of the casing is alleviated.

Abstract: Rotary type fluid machine includes a casing 7, a rotor 31 and a plurality of vane-piston units U1-U12 which are disposed in a radiate arrangement on the rotor 31. Each of the vane-piston units U1-U12 has a vane 42 sliding in a rotor chamber 14 and a piston 41 placed in abutment against an on-slide side of the vane 42. When it functions as an expanding machine 4, the expansion of a high pressure gas is used to operate the pistons 41 thereby to rotate the rotor 31 via vanes 42 and the expansion of a low pressure gas caused by a pressure reduction in the high pressure gas is used to rotate the rotor 31 via the vanes 41. On the other hand, when it functions as a compressing machine, the rotation of rotor 31 is used to supply a low pressure air to the side of pistons 41 via vanes 42 and further, the pistons 41 are operated by the vanes 42 to convert the low pressure air to the high pressure air.

Abstract: Rotary type fluid machine includes a casing 7, a rotor 31 and a plurality of vane-piston units U1-U12 which are disposed in a radiate arrangement on the rotor 31. Each of the vane-piston units U1-U12 has a vane 42 sliding in a rotor chamber 14 and a piston 41 placed in abutment against a non-slide side of the vane 42. When it functions as an expanding machine 4, the expansion of a high pressure gas is used to operate the pistons 41 thereby to rotate the rotor 31 via vanes 42 and the expansion of a low pressure gas caused by a pressure reduction in the high pressure gas is used to rotate the rotor 31 via the vanes 41. On the other hand, when it functions as a compressing machine, the rotation of rotor 31 is used to supply a low pressure air to the side of pistons 41 via vanes 42 and further, the pistons 41 are operated by the vanes 42 to convert the low pressure air to the high pressure air.

Abstract: Rotary type fluid machine includes a casing 7, a rotor 31 and a plurality of vane-piston units U1-U12 which are disposed in a radiate arrangement on the rotor 31. Each of the vane-piston units U1-U12 has a vane 42 sliding in a rotor chamber 14 and a piston 41 placed in abutment against a non-slide side of the vane 42. When it functions as an expanding machine 4, the expansion of a high pressure gas is used to operate the pistons 41 thereby to rotate the rotor 31 via vanes 42 and the expansion of a low pressure gas caused by a pressure reduction in the high pressure gas is used to rotate the rotor 31 via the vanes 41. On the other hand, when it functions as a compressing machine, the rotation of rotor 31 is used to supply a low pressure air to the side of pistons 41 via vanes 42 and further, the pistons 41 are operated by the vanes 42 to convert the low pressure air to the high pressure air.