Source: http://www.google.com/patents/US6959638?dq=6377161
Timestamp: 2014-07-28 12:47:04
Document Index: 581287148

Matched Legal Cases: ['art 3', 'art 4', 'arts 52', 'arts 52', 'art 62', 'art 62', 'art 62', 'art 62', 'art 62', 'art 62', 'art 62', 'art 62', 'art 62']

Patent US6959638 - Rotary hydraulic machine - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign in<nobr>Advanced Patent Search</nobr>PatentsA rotary fluid machine includes a first operating part (49) and a second operating part (57), which are groups of axial piston cylinders, wherein a rotary valve (61) for controlling the intake and discharge of a working medium to and from the first and second operating parts (49, 57) is formed from a...http://www.google.com/patents/US6959638?utm_source=gb-gplus-sharePatent US6959638 - Rotary hydraulic machineAdvanced Patent SearchPublication numberUS6959638 B2Publication typeGrantApplication numberUS 10/469,734PCT numberPCT/JP2002/002036Publication dateNov 1, 2005Filing dateMar 5, 2002Priority dateMar 6, 2001Fee statusLapsedAlso published asDE60213376D1, DE60213376T2, EP1367219A1, EP1367219A4, EP1367219B1, US20040148928, WO2002070865A1Publication number10469734, 469734, PCT/2002/2036, PCT/JP/2/002036, PCT/JP/2/02036, PCT/JP/2002/002036, PCT/JP/2002/02036, PCT/JP2/002036, PCT/JP2/02036, PCT/JP2002/002036, PCT/JP2002/02036, PCT/JP2002002036, PCT/JP200202036, PCT/JP2002036, PCT/JP202036, US 6959638 B2, US 6959638B2, US-B2-6959638, US6959638 B2, US6959638B2InventorsHiroyuki Makino, Kenji Matsumoto, Naoki Itoh, Yoichi KojimaOriginal AssigneeHonda Giken Kogyo Kabushiki KaishaExport CitationBiBTeX, EndNote, RefManPatent Citations (16), Referenced by (3), Classifications (25), Legal Events (4) External Links: USPTO, USPTO Assignment, EspacenetRotary hydraulic machineUS 6959638 B2Abstract A rotary fluid machine includes a first operating part (49) and a second operating part (57), which are groups of axial piston cylinders, wherein a rotary valve (61) for controlling the intake and discharge of a working medium to and from the first and second operating parts (49, 57) is formed from a first valve part that has a flat sliding surface (68) perpendicular to a rotational axis (L) of the rotor (27) and controls the intake and discharge of the working medium to and from the first operating part (49), and a second valve part that has a cylindrical sliding surface (71) centered on the rotational axis (L) of the rotor (27) and controls the intake and discharge of the working medium to and from the second operating part (57). Since the intake and discharge of the working medium to and from the first and second operating parts (49, 57) are controlled by the common rotary valve (61), the size of the rotary fluid machine can be reduced.
a casing (11);
a rotor (27) rotatably supported in the casing (11);
a first operating part (49) and a second operating part (57) provided in the rotor (27); and
intake/discharge control means (61) for controlling the intake and discharge of a working medium to and from the first operating part (49) and the second operating part (57), the intake/discharge control means (61) being provided between the casing (11) and the rotor (27);
wherein the intake/discharge control means (61) is formed from a first rotary valve (63, 64) that has a flat sliding surface (68) perpendicular to a rotational axis (L) of the rotor (27) and controls the intake and discharge of the working medium to and from the first operating part (49), and a second rotary valve (70, 27) that has a cylindrical sliding surface (71) centered on the rotational axis (L) of the rotor (27) and controls the intake and discharge of the working medium to and from the second operating part (57).
2. The rotary fluid machine according to claim 1 wherein the first rotary valve (63, 64) controls the intake and discharge of a high pressure working medium, and the second rotary valve (70, 27) controls the intake and discharge of a low pressure working medium.
3. The rotary fluid machine according to claim 1 wherein the first rotary valve (63, 64) controls the intake and discharge of a high temperature working medium, and the second rotary valve (70, 27) controls the intake and discharge of a low temperature working medium.
This application is the national phase under 35 U.S.C. � 371 of PCT International Application No. PCT/JP02/02036 which has an International filing date of Mar. 5, 2002, which designated the United States of America.
FIELD OF THE INVENTION The present invention relates to a rotary fluid machine that includes a casing, a rotor rotatably supported in the casing, a first operating part and a second operating part provided in the rotor, and intake/discharge control means for controlling the intake and discharge of a working medium to and from the first operating part and the second operating part, the intake/discharge control means being provided between the casing and the rotor.
BACKGROUND ART A hydrostatic transmission is known from U.S. Pat. No. 5,062,267, in which a radially outer axial piston pump fixed to a casing is arranged coaxially with a radially inner axial piston motor provided on a rotor rotatably supported in the casing, and by guiding the piston of the axial piston pump and the piston of the axial piston motor by separate swash plates, the axial piston motor, which is connected to an output shaft, is driven by a working oil discharged by the axial piston pump, which is connected to an input shaft, thus outputting the rotation of the input shaft via the output shaft at a different speed. This hydrostatic transmission has a rotary valve for switching over oil passages in response to the rotation of the rotor, the rotary valve being provided between the axial piston pump and the axial piston motor.
DISCLOSURE OF THE INVENTION The present invention has been achieved in view of the above-mentioned circumstances, and an object thereof is to provide a rotary fluid machine that includes first and second operating parts, in which the size of intake/discharge control means for controlling the intake and discharge of a working medium to and from the two operating parts can be reduced.
In order to achieve this object, in accordance with a first aspect of the present invention, there is proposed a rotary fluid machine that includes a casing, a rotor rotatably supported in the casing, a first operating part and a second operating part provided in the rotor, and intake/discharge control means for controlling the intake and discharge of a working medium to and from the first operating part and the second operating part, the intake/discharge control means being provided between the casing and the rotor, wherein the intake/discharge control means is formed from a first rotary valve that has a flat sliding surface perpendicular to a rotational axis of the rotor and controls the intake and discharge of the working medium to and from the first operating part, and a second rotary valve that has a cylindrical sliding surface centered on the rotational axis of the rotor and controls the intake and discharge of the working medium to and from the second operating part.
In accordance with this arrangement, since the intake/discharge control means for controlling the intake and discharge of the working medium to and from the first and second operating parts of the rotary fluid machine is formed from the first rotary valve that has a flat sliding surface perpendicular to the rotational axis of the rotor and is connected to the first operating part, and the second rotary valve that has a cylindrical sliding surface centered on the rotational axis of the rotor and is connected to the second operating part, it is possible to control the intake and discharge of the working medium to and from the first and second operating parts by the common intake/discharge means, and the size of the rotary fluid machine can be reduced compared with a case in which separate intake/discharge control means are provided in the first and second operating parts.
A first group of axial piston cylinders 49 and a second group of axial piston cylinders 57 of embodiments correspond to the first operating part and the second operating part of the present invention, a rotary valve 61 of the embodiments corresponds to the intake/discharge control means of the present invention, a stationary valve plate 63 and a movable valve plate 64 of the embodiments correspond to the first rotary valve of the present invention, and a rotor 27 and a sliding member 70 of the embodiments correspond to the second rotary valve of the present invention.
BRIEF DESCRIPTION OF DRAWINGS FIG. 1 to FIG. 18 illustrate a first embodiment of the present invention;
FIG. 1 is a vertical sectional view of an expander;
FIG. 3 is an enlarged view of part 3 in FIG. 1;
FIG. 4 is an enlarged sectional view of part 4 in FIG. 1 (sectional view along line 4�4 in FIG. 8);
FIG. 5 is a view from arrowed line 5�5 in FIG. 4;
FIG. 6 is a view from arrowed line 6�6 in FIG. 4;
FIG. 7 is a sectional view along line 7�7 in FIG. 4;
FIG. 8 is a sectional view along line 8�8 in FIG. 4;
FIG. 9 is a sectional view along line 9�9 in FIG. 4;
FIG. 10 is a view from arrowed line 10�10 in FIG. 1;
FIG. 11 is a view from arrowed line 11�11 in FIG. 1;
FIG. 12 is a sectional view along line 12�12 in FIG. 10;
FIG. 14 is a sectional view along line 14�14 in FIG. 10;
FIG. 15 is a graph showing torque variations of an output shaft;
FIG. 16 is an explanatory diagram showing the operation of an intake system of a high-pressure stage;
FIG. 17 is an explanatory diagram showing the operation of a discharge system of the high-pressure stage and an intake system of a low-pressure stage; and
FIG. 18 is an explanatory diagram showing the operation of a discharge system of the low-pressure stage.
BEST MODE FOR CARRYING OUT THE INVENTION The first embodiment of the present invention is explained below by reference to FIG. 1 to FIG. 18.
Seven sleeves 41 formed from members that are separate from the rotor 27 are arranged within the rotor 27 so as to surround the axis L at equal intervals in the circumferential direction. High-pressure pistons 43 are slidably fitted in high-pressure cylinders 42 formed at inner peripheries of the sleeves 41, which are supported by sleeve support bores 27 a of the rotor 27. Hemispherical parts of the high-pressure pistons 43 projecting forward from forward end openings of the high-pressure cylinders 42 abut against and press against seven dimples 39 a recessed in a rear surface of the swash plate 39. Heat resistant metal seals 44 are fitted between the rear ends of the sleeves 41 and the sleeve support bores 27 a of the rotor 27, and a single set plate 45 retaining the front ends of the sleeves 41 in this state is fixed to a front surface of the rotor 27 by means of a plurality of bolts 46. The sleeve support bores 27 a have a slightly larger diameter in the vicinity of their bases, thus forming a gap α (see FIG. 3) between themselves and the outer peripheries of the sleeves 41.
The high-pressure pistons 43 include pressure rings 47 and oil rings 48 for sealing the sliding surfaces with the high-pressure cylinders 42, and the sliding range of the pressure rings 47 and the sliding range of the oil rings 48 are set so as not to overlap each other. When the high-pressure pistons 43 are inserted into the high-pressure cylinders 42, in order to make the pressure rings 47 and the oil rings 48 engage smoothly with the high-pressure cylinders 42, tapered openings 45 a widening toward the front are formed in the set plate 45.
Since the high-pressure cylinders 42 are formed by fitting the seven sleeves 41 in the sleeve support bores 27 a of the rotor 27, a material having excellent thermal conductivity, heat resistance, abrasion resistance, strength, etc. can be selected for the sleeves 41. This not only improves the performance and the reliability, but also machining becomes easy compared with a case in which the high-pressure cylinders 42 are directly machined in the rotor 27, and the machining precision also increases. When any one of the sleeves 41 is worn or damaged, it is possible to exchange only the sleeve 41 with an abnormality, without exchanging the entire rotor 27, and this is economical.
Furthermore, since the gap α is formed between the outer periphery of the sleeves 41 and the rotor 27 by slightly enlarging the diameter of the sleeve support bores 27 a in the vicinity of the base, even when the rotor 27 is thermally deformed by the high-temperature, high-pressure steam supplied to the high-pressure operating chambers 82, this is prevented from affecting the sleeves 41, thereby preventing the high-pressure cylinders 42 from distorting.
The seven low-pressure cylinders 50 have low-pressure pistons 51 slidably fitted thereinto, and these low-pressure pistons 51 are connected to the swash plate 39 via links 52. That is, spherical parts 52 a at the front end of the links 52 are swingably supported in spherical bearings 54 fixed to the swash plate 39 via nuts 53, and spherical parts 52 b at the rear end of the links 52 are swingably supported in spherical bearings 56 fixed to the low-pressure pistons 51 by clips 55. A pressure ring 78 and an oil ring 79 are fitted around the outer periphery of each of the low-pressure pistons 51 in the vicinity of the top surface thereof so as to adjoin each other. Since the sliding ranges of the pressure ring 78 and the oil ring 79 overlap each other, an oil film is formed on the sliding surface of the pressure ring 78, thus enhancing the sealing characteristics and the lubrication.
As hereinbefore described, since the front ends of the high-pressure pistons 43 of the first group of axial piston cylinders 49 are made in the form of hemispheres and are made to abut against the dimples 39 a formed in the swash plate 39, it is unnecessary to connect the high-pressure pistons 43 to the swash plate 39 mechanically, thus reducing the number of parts and improving the ease of assembly. On the other hand, the low-pressure pistons 51 of the second group of axial piston cylinders 57 are connected to the swash plate 39 via the links 52 and their front and rear spherical bearings 54 and 56, and even when the temperature and the pressure of medium-temperature, medium-pressure steam supplied to the second group of axial piston cylinders 57 become insufficient and the pressure of low-pressure operating chambers 84 becomes negative, there is no possibility of the low-pressure pistons 51 becoming detached from the swash plate 39 and causing knocking or damage.
As shown in FIG. 4, a rotary valve 61 is housed in a circular cross-section recess 27 b opening on the rear end surface of the rotor 27 and a circular cross-section recess 18 a opening on a front surface of the rear cover 18. The rotary valve 61, which is disposed along the axis L, includes a rotary valve main body 62, a stationary valve plate 63, and a movable valve plate 64. The movable valve plate 64 is fixed to the rotor 27 via a knock pin 66 and a bolt 67 while being fitted to the base of the recess 27 b of the rotor 27 via a gasket 65. The stationary valve plate 63, which abuts against the movable valve plate 64 via a flat sliding surface 68, is joined via a knock pin 69 to the rotary valve main body 62 so that there is no relative rotation therebetween. When the rotor 27 rotates, the movable valve plate 64 and the stationary valve plate 63 therefore rotate relative to each other on the sliding surface 68 in a state in which they are in intimate contact with each other. The stationary valve plate 63 and the movable valve plate 64 are made of a material having excellent durability, such as a super hard alloy or a ceramic, and the sliding surface 68 can be provided with or coated with a member having heat resistance, lubrication, corrosion resistance, and abrasion resistance.
The rotary valve main body 62 is a stepped cylindrical member having a large diameter part 62 a, a medium diameter part 62 b, and a small diameter part 62 c; an annular sliding member 70 fitted around the outer periphery of the large diameter part 62 a is slidably fitted in the recess 27 b of the rotor 27 via a cylindrical sliding surface 71, and the medium diameter part 62 b and the small diameter part 62 c are fitted in the recess 18 a of the rear cover 18 via seals 72 and 73. The sliding member 70 is made of a material having excellent durability, such as a super hard alloy or a ceramic. A knock pin 74 implanted in the outer periphery of the rotary valve main body 62 engages with a long hole 18 b formed in the recess 18 a of the rear cover 18 in the axis L direction, and the rotary valve main body 62 is therefore supported so that it can move in the axis L direction but cannot rotate relative to the rear cover 18.
A plurality of (for example, seven) preload springs 75 are supported in the rear cover 18 so as to surround the axis L, and the rotary valve main body 62, which has a step 62 d between the medium diameter part 62 b and the small diameter part 62 c pressed by these preload springs 75, is biased forward so as to make the sliding surface 68 of the stationary valve plate 63 and the movable valve plate 64 come into intimate contact with each other. A pressure chamber 76 is defined between the bottom of the recess 18 a of the rear cover 18 and the rear end surface of the small diameter part 62 c of the rotary valve main body 62, and a steam supply pipe 77 connected so as to run though the rear cover 18 communicates with the pressure chamber 76. The rotary valve main body 62 is therefore biased forward by the steam pressure acting on the pressure chamber 76 in addition to the resilient force of the preload springs 75.
The seventeenth steam passage P17 further communicates with a steam discharge chamber 90 formed between the rotary valve main body 62 and the rear cover 18 via an eighteenth steam passage P18 to a twentieth steam passage P20 formed within the rotary valve main body 62 and a cutout 18 d of the rear cover 18, and this steam discharge chamber 90 communicates with a steam discharge hole 18 c formed in the rear cover 18.
A lower breather chamber 101 defined between an upper wall 12 a of the casing main body 12 and the breather chamber dividing wall 23 communicates with a lubrication chamber 102 within the casing 11 via a through hole 12 b formed in the upper wall 12 a of the casing main body 12. Oil is stored in the oil pan 19 provided in a bottom part of the lubrication chamber 102, and the oil level is slightly higher than the lower end of the rotor 27 (see FIG. 1). Provided within the lower breather chamber 101 so as to project upward are three dividing walls 12 c to 12 e having their upper ends in contact with a lower surface of the breather chamber dividing wall 23. The through hole 12 b opens at one end of a labyrinth formed by these dividing walls 12 c to 12 e, and four oil return holes 12 f running through the upper wall 12 a are formed partway along the route to the other end of the labyrinth. The oil return holes 12 f are formed at the lowest position of the lower breather chamber 101 (see FIG. 14), and the oil condensed within the lower breather chamber 101 can therefore be reliably returned to the lubrication chamber 102.
An upper breather chamber 103 is defined between the breather chamber dividing wall 23 and the breather chamber cover 25, and this upper breather chamber 103 communicates with the lower breather chamber 101 via four through holes 23 a and 23 b running through the breather chamber dividing wall 23 and projecting in a chimney-shape within the upper breather chamber 103. A recess 12 g is formed in the upper wall 12 a of the casing main body 12 at a position below a condensed water return hole 23 c running through the breather chamber dividing wall 23, and the periphery of the recess 12 g is sealed by a seal 104.
One end of a first breather passage B1 formed in the breather chamber dividing wall 23 opens at mid height in the upper breather chamber 103. The other end of the first breather passage B1 communicates with the steam discharge chamber 90 via a second breather passage B2 formed in the casing main body 12 and a third breather passage B3 formed in the rear cover 18. Furthermore, the recess 12 g, which is formed in the upper wall 12 a, communicates with the steam discharge chamber 90 via a fourth breather passage B4 formed in the casing main body 12 and the third breather passage B3. The outer periphery of a part providing communication between the first breather passage B1 and the second breather passage B2 is sealed by a seal 105.
Even after the communication between the second steam passage P2 and the third steam passages P3 has been blocked due to rotation of the rotor 27, the high-temperature, high-pressure steam expands within the high-pressure operating chamber 82 and causes the high-pressure piston 43 fitted in the high-pressure cylinder 42 of the sleeve 41 to be pushed forward from top dead center toward bottom dead center, and the front end of the high-pressure piston 43 presses against the dimple 39 a of the swash plate 39. As a result, the reaction force that the high-pressure pistons 43 receive from the swash plate 39 gives a rotational torque to the rotor 27. For each one seventh of a revolution of the rotor 27, the high-temperature, high-pressure steam is supplied into a fresh high-pressure operating chamber 82, thus continuously rotating the rotor 27.
As shown in FIG. 17, while the high-pressure piston 43, having reached bottom dead center accompanying rotation of the rotor 27, retreats toward top dead center, the medium-temperature, medium-pressure steam pushed out of the high-pressure operating chamber 82 is supplied to the eleventh steam passage P11 communicating with the low-pressure operating chamber 84 that, among the second group of axial piston cylinders 57, has reached top dead center accompanying rotation of the rotor 27, via the fourth steam passage P4 of the rotor 27, the third steam passage P3 of the movable valve plate 64, the sliding surface 68, the fifth steam passage P5 and the sixth steam passage P6 of the stationary valve plate 63, the seventh steam passage P7 to the tenth steam passage P10 of the rotary valve main body 62, and the sliding surface 71. Since the medium-temperature, medium-pressure steam supplied to the low-pressure operating chamber 84 expands within the low-pressure operating chambers 84 even after the communication between the tenth steam passage P10 and the eleventh steam passage P11 is blocked, the low-pressure piston 51 fitted in the low-pressure cylinder 50 is pushed forward from top dead center toward bottom dead center, and the link 52 connected to the low-pressure piston 51 presses against the swash plate 39. As a result, the pressure force of the low-pressure piston 51 is converted into a rotational force of the swash plate 39 via the link 52, and this rotational force transmits a rotational torque from the high-pressure piston 43 to the rotor 27 via the dimple 39 a of the swash plate 39. That is, the rotational torque is transmitted to the rotor 27, which rotates synchronously with the swash plate 39. In order to prevent the low-pressure piston 51 from becoming detached from the swash plate 39 when a negative pressure is generated during the expansion stroke, the link 52 carries out a function of maintaining a connection between the low-pressure piston 51 and the swash plate 39, and it is arranged that the rotational torque due to the expansion is transmitted from the high-pressure piston 43 to the rotor 27 rotating synchronously with the swash plate 39 via the dimples 39 a of the swash plate 39 as described above. For each one seventh of a revolution of the rotor 27, the medium-temperature, medium-pressure steam is supplied into a fresh low-pressure operating chamber 84, thus continuously rotating the rotor 27.
As shown in FIG. 18, while the low-pressure piston 51, having reached bottom dead center accompanying rotation of the rotor 27, retreats toward top dead center, the low-temperature, low-pressure steam pushed out of the low-pressure operating chamber 84 is discharged into the steam discharge chamber 90 via the eleventh steam passage P11 of the rotor 27, the sliding surface 71, the sixteenth steam passage P16 of the sliding member 70, and the seventeenth steam passage P17 to the twentieth steam passage P20 of the rotary valve main body 62, and supplied therefrom into a condenser via the steam discharge hole 18 c. When the expander M operates as described above, since the seven high-pressure pistons 43 of the first group of axial piston cylinders 49 and the seven low-pressure pistons 51 of the second group of axial piston cylinders 57 are connected to the common swash plate 39, the outputs of the first and second groups of axial piston cylinders 49 and 57 can be combined to drive the output shaft 28, thereby achieving a high output while reducing the size of the expander M. During this process, since the seven high-pressure pistons 43 of the first group of axial piston cylinders 49 and the seven high-pressure pistons 51 of the second group of axial piston cylinders 57 are displaced by half a pitch in the circumferential direction, as shown in FIG. 15, pulsations in the output torque of the first group of axial piston cylinders 49 and pulsations in the output torque of the second group of axial piston cylinders 57 are counterbalanced, thus making the output torque of the output shaft 28 flat.
Moreover, when viewed from an angle perpendicular to the axis L, since the rear end of the first group of axial piston cylinders 49 is positioned forward relative to the rear end of the second group of axial piston cylinders 57, the heat escaping rearward in the axis L direction from the first group of axial piston cylinders 49 can be recovered by the second group of axial piston cylinders 57, and the efficiency of the expander M can be yet further enhanced. Furthermore, since the sliding surface 68 on the high-pressure side is present deeper within the recess 27 b of the rotor 27 than the sliding surface 71 on the low-pressure side, the difference in pressure between the outside of the casing 11 and the sliding surface 71 on the low-pressure side can be minimized, the amount of leakage of steam from the sliding surface 71 on the low-pressure side can be reduced and, moreover, the pressure of steam leaking from the sliding surface 68 on the high-pressure side can be recovered by the sliding surface 71 on the low-pressure side and utilized effectively.
The interior of the lubrication chamber 102 is filled with oil mist generated by splashing due to stirring of the oil, and oil vapor generated by vaporization due to heating by a high-temperature section of the rotor 27, and this is mixed with steam leaking into the lubrication chamber 102 from the high-pressure operating chambers 82 and low-pressure operating chambers 84. When the pressure of the lubrication chamber 102 becomes higher than the pressure of the steam discharge chamber 90 due to leakage of the steam, the mixture of oil content and steam flows through the through hole 12 b formed in the upper wall 12 a of the casing main body 12 into the lower breather chamber 101. The interior of the lower breather chamber 101 has a labyrinth structure due to the dividing walls 12 c to 12 e; the oil that condenses while passing therethrough drops through the four oil return holes 12 f formed in the upper wall 12 a of the casing main body 12, and is returned to the lubrication chamber 102.
The steam from which the oil content has been removed passes through the four through holes 23 a and 23 b of the breather chamber dividing wall 23, flows into the upper breather chamber 103, and condenses by losing its heat to the outside air via the breather chamber cover 25, which defines an upper wall of the upper breather chamber 103. Water that has condensed within the upper breather chamber 103 passes through the condensed water return hole 23 c formed in the breather chamber dividing wall 23 and drops into the recess 12 g without flowing into the four through holes 23 a, 23 b projecting in a chimney-shape within the upper breather chamber 103, and is discharged therefrom into the steam discharge chamber 90 via the fourth breather passage B4 and the third breather passage B3. Here, the amount of condensed water returned into the steam discharge chamber 90 corresponds to the amount of steam that has leaked from the high-pressure operating chambers 82 and the low-pressure operating chambers 84 into the lubrication chamber 102. Furthermore, since the steam discharge chamber 90 and the upper breather chamber 103 always communicate with each other via the first steam passage B1 to the third steam passage B3, which function as pressure equilibration passages, pressure equilibrium between the steam discharge chamber 90 and the lubrication chamber 102 can be maintained.
The first to third embodiments describe the expander M employing steam, which is a compressible fluid, as the working medium, but in the fourth embodiment a pump employing an incompressible fluid (for example, oil) as the working medium is shown. Since the incompressible fluid is used as the working medium, a second oil passage P2′ (corresponding to the second steam passage P2) as an intake port and a fifth oil passage P5′ (corresponding to the fifth steam passage P5) as a discharge port are made in the form of an arc having a central angle of approximately 180�.
Although embodiments of the present invention are explained above, the present invention can be modified in a variety of ways without departing from the spirit and scope thereof.
Patent CitationsCited PatentFiling datePublication dateApplicantTitleUS1840864 *Nov 24, 1920Jan 12, 1932Rayburn Alden GPower transmission apparatusUS2445281 *Oct 4, 1945Jul 13, 1948Rystrom Charles HHydraulic pumpUS3364679Oct 21, 1965Jan 23, 1968Chrysler CorpHydrostatic transmissionUS3464206Jun 14, 1967Sep 2, 1969Cambi Idraulici Badalini SpaHydraulic change speed gearUS4223594 *Apr 3, 1978Sep 23, 1980Lidio GhernerHydraulic motorUS4478134 *Nov 2, 1981Oct 23, 1984Honda Giken Kogyo Kabushiki KaishaSwash plate type hydraulic deviceUS5062267Dec 6, 1989Nov 5, 1991Hydromatik GmbhHydrostatic transmission containing an axial piston motor located in a recess of a valve controlled axial piston pumpUS5354180Jul 9, 1993Oct 11, 1994Linde AktiengesellschaftHydrostatic assembly having multiple pumpsUS5593291Jul 25, 1995Jan 14, 1997Thomas Industries Inc.Fluid pumping apparatusDE1500457A1Aug 18, 1965Jul 10, 1969Joh NeukirchAxialkolbengetriebeGB240107A Title not availableGB980837A Title not availableJP2000154775A Title not availableJPH09184478A Title not availableJPH10184532A Title not availableJPS5870475U Title not available* Cited by examinerReferenced byCiting PatentFiling datePublication dateApplicantTitleUS7080975 *Jun 25, 2003Jul 25, 2006Sapphire Engineering, Inc.Integrated pump and ceramic valveUS8340489 *Dec 11, 2008Dec 25, 2012Perkinelmer Singapore Pte. Ltd.Device and method for adjusting a position of an optical componentUS20100266252 *Dec 11, 2008Oct 21, 2010Wallac OyDevice and method for adjusting a position of an optical component* Cited by examinerClassifications U.S. Classification91/503International ClassificationF01B3/02, F04B27/08, F04B23/06, F04B41/06, F01B3/10, F04B1/22, F03C1/34, F04B1/20Cooperative ClassificationF04B41/06, F04B27/0839, F04B1/22, F04B1/2042, F04B23/06, F04B1/20, F03C1/0655, F04B27/0808European ClassificationF04B41/06, F04B27/08B2, F04B1/22, F04B1/20, F03C1/06E3D, F04B23/06, F04B27/08B4D, F04B1/20C3Legal EventsDateCodeEventDescriptionDec 22, 2009FPExpired due to failure to pay maintenance feeEffective date: 20091101Nov 1, 2009LAPSLapse for failure to pay maintenance feesMay 11, 2009REMIMaintenance fee reminder mailedApr 7, 2004ASAssignmentOwner name: HONDA GIKEN KOGYO KABUSHIKI KAISHA, JAPANFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MAKINO, HIROYUKI;MATSUMOTO, KENJI;ITOH, NAOKI;AND OTHERS;REEL/FRAME:015186/0934;SIGNING DATES FROM 20040210 TO 20040218RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services©2012 Google