NL1019736C1 - Hydraulic device such as a hydraulic transformer, pump or motor, has rotor ports that can rotate along housing or second face plate, that is positioned in housing and may be part of housing to form a seal - Google Patents

Hydraulic device such as a hydraulic transformer, pump or motor, has rotor ports that can rotate along housing or second face plate, that is positioned in housing and may be part of housing to form a seal Download PDF

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Publication number
NL1019736C1
NL1019736C1 NL1019736A NL1019736A NL1019736C1 NL 1019736 C1 NL1019736 C1 NL 1019736C1 NL 1019736 A NL1019736 A NL 1019736A NL 1019736 A NL1019736 A NL 1019736A NL 1019736 C1 NL1019736 C1 NL 1019736C1
Authority
NL
Netherlands
Prior art keywords
drum
hydraulic
rotor
plate
mirror
Prior art date
Application number
NL1019736A
Other languages
Dutch (nl)
Inventor
Peter Augustinus Johann Achten
Original Assignee
Innas Bv
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Innas Bv filed Critical Innas Bv
Priority to NL1019736 priority Critical
Priority to NL1019736A priority patent/NL1019736C1/en
Priority claimed from NL1020932A external-priority patent/NL1020932C2/en
Application granted granted Critical
Publication of NL1019736C1 publication Critical patent/NL1019736C1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2007Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F01B3/0038Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to main shaft axis
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0041Arrangements for pressing the cylinder barrel against the valve plate, e.g. fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0047Particularities in the contacting area between cylinder barrel and valve plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0055Valve means, e.g. valve plate

Abstract

The hydraulic device comprises a housing and a rotor (14) that can rotate about a first axis, pistons (12) and chambers (9) that can rotate about a second axis (m1,m2). The rotor is provided, on the side remote from a first face plate (26), with rotor ports and with a second passage (29) through each piston for connecting the rotor port to the chamber. The rotor ports can rotate along the housing or a second face plate (28), that is positioned in the housing and may be part of the housing, so as to form a seal.

Description

Hydraulic device
The invention relates to a device according to the preamble of claim 1. Such a device is known from US 3434429. The drawback of the known device is that it is necessary to movably attach the pistons to the rotor, whereby wear occurs and the device cannot be made robust. In order to avoid these drawbacks, the device is designed in accordance with the feature of claim 1. A stable device is hereby obtained in a simple manner, the chambers of which change in volume when the rotor and drum rotate.
In accordance with an improvement, the device is designed in accordance with claim 2. As a result, the drum sleeve is always sealed to the drum plate.
In accordance with an improvement, the device is designed in accordance with claim 3. As a result, the drum sleeve is pressed against the drum plate by the pressure in the chamber, whereby leakage of liquid is prevented.
In accordance with an improvement, the device is designed in accordance with claim 4. Hereby, the seal between the cylindrical wall and the piston is maintained even in the presence of wearing particles such as those found in contaminated oil.
In accordance with a further improvement, the device is designed in accordance with claim 5. This reduces the force with which the piston ring presses against the cylindrical wall and the frictional forces are lower.
2
In accordance with a further improvement, the device is designed in accordance with claim 6. As a result, the piston ring is supported by the piston in the skew position of the piston and the seal between piston ring and cylindrical wall is retained.
In accordance with a further improvement, the device is designed in accordance with claim 7. Hereby the drum plate is centered in a simple manner.
In accordance with another improvement, the device is designed in accordance with claim 8. As a result, the rotor is centered in a simple manner and, optionally, the drum plate can also be simply centered.
In accordance with a further improvement, the device is designed in accordance with claim 9. As a result, the axial forces on the rotor are balanced and there are hardly any axial forces on the bearing of the rotor.
In accordance with a further improvement, the device is designed in accordance with claim 10. This makes it possible for the supply and discharge of the oil to and from the chambers to take place via two different mirror plates. In this case, it is possible for a mirror plate to have a mirror plate gate closed over a part of its circumference so that it closes an opening in the housing. This makes it possible to rotate the mirror plate over a larger arc length than the arc length of the mirror plate gate and the control range of the device is simply increased by rotating the mirror plate.
3
In accordance with a further improvement, the device is designed in accordance with claim 11. As a result, the pressure peaks which occur when the drum gates are closed by the mirror plate are limited because the oil flow can flow along two mirror plates per chamber. This improves efficiency and reduces the production of noise.
In accordance with a further improvement, the device is designed in accordance with claim 10. As a result, the stroke volume is doubled in a simple manner by doubling the number of pistons, while the surface of the mirror plate ports is also doubled so that the losses do not increase.
In accordance with a further improvement, the device is designed in accordance with claim 13. As a result, an accurate and stable rotor is obtained in a simple manner.
In accordance with a further improvement, the device is designed in accordance with claim 14. This causes the pistons to move from the two drums alternately to the lower or upper dead center, so that the total number of pistons can be taken into account when considering the pulsations in oil flow and torque with rotor rotation. This makes these pulsations smaller.
In accordance with a further improvement, the device is designed in accordance with claim 15. When three or more mirror plate ports are used, the hydraulic device is used as a hydraulic transformer, chambers being closed by the mirror plate ports when the chambers are not in the lower or upper dead center. By making the number of pistons a multiple of the number of mirror plate ports, the axial force on the drum remains more or less constant, so that it can rotate more calmly and stably.
In accordance with a further improvement, the device is designed in accordance with claim 5. As a result, the opening and closing of the chambers in both drums does not take place at the same rotational position, so that coupling fluctuations and pressure peaks in a chamber can be avoided. This improves stability and efficiency.
The invention is explained below with reference to a few exemplary embodiments with the aid of a drawing. Shows in the drawing
Figure 1 is a sectional view of the interior of a hydraulic device, Figure 2 is a perspective view of the hydraulic device of Figure 1,
Figure 3 shows a detail of Figure 1 with the forces on the drum plate sleeve,
Figure 4 shows diagrammatically the planes through the axes of the rotor and the drum,
Figure 5 shows a second embodiment of the hydraulic device, and
Figure 6 shows a hydraulic device according to a third embodiment.
The parts shown in figures 1 and 2 are the parts of a hydraulic transformer mounted in a housing. Such a hydraulic transformer is described, for example, in the published applications WO 9731185 and WO 9940318 of the same applicant, the contents of which are considered to be known. Bearings are mounted in the housing in a known manner in which a rotor shaft 2 with a center line 1 can rotate. A rotor 14 with rotor holes 15 is mounted on the rotor shaft 2. Pistons 12 are mounted in the rotor holes 1. The pistons 12 are provided with piston rings 10, the outer surface of the piston rings 10 being in the form of a sphere and the center of these spheres for all pistons on one side of the rotor 14 lying in one plane. The left side and the right side of the rotor 14 are symmetrical with respect to the center of the rotor 14. Each side of the rotor 14 cooperates with a drum that rotates about a center line mi and m2, the center lines 1 and mi 10 and 1 and m2 respectively intersect in the plane perpendicular to 1 through the centers of the outer surfaces of the piston rings 10 for the pistons 12 located on that side.
A centering surface 22 is formed on the rotor shaft 2 around which a drum plate 7 can pivot. The centering surface 22 is spherical with the center of the sphere lying in the plane where the center of the spherical piston rings 10 lies. The rotation of the drum plate 7 is coupled to the rotation of rotor shaft 2 by means of a key 16 which engages in a keyway. The key 16 has a rounding radius in the plane of the surface of the shaft that is smaller than the radius of the centering surface 22, so that the key 16 does not clamp in the keyway when the drum plate 7 rotates. There may be more than one key 16.
The drum plate 7 is provided on the side facing the pistons 12 with drum plate sleeves 11 which are clamped against the drum plate 7 with a bushing holder 18. The drum plate sleeve 11 has a cylindrical wall 23 on the inside. Each piston 12 is enclosed by a drum plate sleeve 11, whereby the piston ring 10 can move sealingly along the cylindrical wall 23. The piston 12 and the cylindrical bush 11 thus form a chamber 9 whose volume changes with rotation. Through the change in volume, oil flows in and out of the chamber 9 via a drum sleeve β opening 24, a drum plate gate 6 and a mirror plate gate 3 to an opening in the housing. The corresponding mirror plate ports 3 are connected to each other in the housing. Because the rotational axes of the rotor 14 and the drum plate 7 make an angle with each other, the pistons 12 in the plane of the drum plate 7 describe an elliptical path and the drum plate bushes 11 will slide over a contact surface 8 of the drum plate 7 . The holder 18 is provided with openings that make this sliding possible and also ensures that the gap between the drum plate 7 and the drum plate sleeve 11 remains limited so that pressure can be created in the chamber 9 when starting.
The mirror plate port 3 is arranged in a mirror plate 4 which rests against a surface of the housing. This plane is not perpendicular to the center line 1, but makes an angle therewith and thus determines the direction of the center line ma or m2 and thus also the rotation position at which the volume in the chamber 9 is minimal or maximum. The mirror plate 4 is rotatably mounted in the housing about the axis mi or m2 and is provided over a part of its circumference with a toothing 5 which cooperates with a pinion driven by a drive. For centering the rotation of the mirror plate 4 in the housing, use can be made in a known manner of a centering bush, which is not shown. By rotating the mirror plate 4, the setting of the hydraulic transformer changes as described in the aforementioned patent applications.
In order to keep the gaps between mirror plate 4 and drum plate 7 at start-up when there is not yet any pressure in the chambers 9, a pressure ring 19 is provided which rests against the centering surface 22. Between the pressure ring 19 and a fastener fixed in the drum plate 7 ring 21 are provided with plate springs 20, with which the
. ·. ·· '.J
7 drum plate 7 is always pressed against the mirror plate 4.
Figure 3 shows the drum plate sleeve 11 which rests on the contact surface 8 of the drum plate 7. In the chambers 9 and 5 the drum gate 6 is in operation under high pressure and outside the drum plate sleeve 11 there is a lower pressure. In the gap in the contact surface 8 between the drum sleeve 11 and the drum plate 7, an oil pressure will develop as indicated in the figure by arrows A. To prevent the gap from becoming larger under the influence of this oil pressure, the drum sleeve opening 24 has a smaller surface area than the sealing surface of the piston 12 in the cylindrical wall 23. Now there is an edge around the drum sleeve opening 24 on which oil pressure, indicated by arrows B, exerts a force directed towards the contact surface 8 on the drum sleeve 11. By properly dimensioning the drum sleeve 11, it can be ensured that under the influence of the oil pressure the drum sleeves 11 are always pressed against the contact surface 8.
Figure 3 also shows the forces on the piston ring 10. The piston ring 10 has a convex surface on the outside, so that the sealing between piston ring 10 and the cylindrical surface 23 takes place in the plane perpendicular to the cylindrical surface 23, that is to say perpendicular to the axis m. not a pure sphere but is barrel-shaped. The piston ring 10 is not uniformly loaded by the angles between the center lines 1 and m all around because the surface that is high on the outside due to oil under high pressure at E, as indicated by the arrows, and at D is small.
Because the pressurized area at D is small, the piston ring 10 would press heavily against the cylindrical wall 23 under the influence of the inner pressure indicated by the arrows C and cause a great frictional force.
This frictional force is greatly reduced because the inside of the piston ring 10 is provided with a breast 25. If this breast 25 is halfway the width of the piston ring 10, the outwardly directed force is halved. As shown, the inward directed force at E is greater than the outward directed force. Under the influence of this, the piston ring 10 rests on the piston 12, while the seal between the piston ring 10 and the cylindrical wall 23 remains intact all the way through the displacement of the drum plate sleeve 11. By supporting the piston ring 10 exerts a resulting force R on the piston 12, this force R drives the rotor 14. It is, of course, also possible to equip the device without piston rings 10, but provisions will have to be made for avoiding contaminants that can cause wear.
The hydraulic transformer is designed in such a way that the pistons 12 on either side of the rotor 14 come alternately into the upper dead center, so that fluctuations in the oil flow and the torque on the rotor 14 can be calculated with the total number pistons 12, in the example shown thus eighteen pistons 12. In the embodiment shown, in which the pistons 12 are aligned on either side of the rotor 14, this is achieved by placing the upper dead center of the pistons on one side rotate through an angle α with respect to the upper dead center on the other side. Here, α is equal to half the rotation angle between two pistons 12. The mirror plates 4 are also rotated this angle relative to each other. This is shown in Figure 4a, where Vi is the plane through the center lines 1 and mi and V2 is the plane through the center lines 1 and 9 m2. Another embodiment is shown in Figure 4b. The center lines 1, mi and m2 are thereby located in a plane V and the pistons 12 are staggered in the rotor 14. This embodiment is particularly interesting if the volumes 5 of the chambers 9 which consecutively have a maximum volume are coupled through channels with valves as discussed in applications PCT NL01 00839 and PCT NL01 00840 from the same applicant.
The rotation of the two mirror plates 4 is preferably coupled, so that only a drive is required. This is achieved, for example, by rotating the mirror plates 4 with a gear coupled to an axis and coupling the two axes with a homokinetic coupling so that the rotation of both mirror plates is accurately synchronous. The two mirror plates 4 are optionally provided with their own drive, so that a hydraulic bias can be obtained in certain operating conditions.
The angle β between the center lines 1 and m determines the stroke volume of the device. In the embodiment shown with 9 pistons 12 per side, the angle is 9 degrees. As the number of pistons 12 increases, this angle must be reduced because otherwise the constriction of piston 12 in order to remain free of the drum plate sleeve 11 always becomes too large. In the embodiment shown, a maximum speed of the rotor 14 of 8,000 revolutions per minute has been calculated. If this becomes larger, a smaller angle β is necessary to prevent inadmissible pressure spots occurring.
In the exemplary embodiment shown, it is shown that the drum plate 7 is centered with the centering surface 22. It is also possible to perform this in other ways, for example by providing the drum plate 7 on the outer circumference with a ball bearing which is mounted in the House. Another embodiment can be to center the drum plate 7 relative to the mirror plate 4, for example by giving it a conical shape. A centering bush can also be placed in the housing for centering both the mirror plate 4 and the drum plate 7.
Figure 5 shows another embodiment of the hydraulic transformer. The heart lines 1, mi and m2 of the rotor 14 and both drums can herein lie in one plane, but it is also possible that they are designed in accordance with what is shown in figure 4a. The chambers 9 on either side of the rotor 14 are connected to each other through a channel 27 through the pistons 12.
Mirror plates 26 and 28 are designed such that the mirror plate port 3 to the tank connection is directly connected to the interior of the housing via a channel 29, this interior being connected to the tank connection. The mirror plates 26 and 28 are embodied such that, of the remaining two mirror plate ports 3, each mirror plate 26 or 28 has one of the two ports and is closed at the other port. This makes it possible for the connection in the housing to have an opening to the mirror plate through a large angle and the mirror plates to be able to rotate through a large angle, whereby the control range of the hydraulic transformer can be enlarged in a simple manner by rotating the mirror plate. The rotation of the mirror plates 26 and 28 is coupled in the manner described above.
In the exemplary embodiments given above, the device is described as a hydraulic transformer. It is clear to the person skilled in the art that the device can only be made suitable for use as a pump or motor with minor modifications, such as to the mirror plates 4 and the rotor shaft 2, among others.
Figure 6 shows an exemplary embodiment in which pistons 12 are included on only one side.
The embodiment thereof corresponds to what is described in the embodiment of figures 1 and 2. For axially balancing the rotor 14, it is provided on the side remote from the piston with a mirror plate 34. The rotor 14 is on the side of the mirror plate 34 is provided with 10 chambers 31 which are connected via a channel 30 to the chambers 9. The surface of the chambers 31 is comparable to the sealing surface of the pistons 12, so that the rotor 14 is balanced in the axial direction.
The mirror plate 34 can be designed without mirror-plate plates. In one embodiment, there may also be mirror plate ports 33 which are connected to channels in the housing. As a result, pulsations in fluid flow and fluid pressure can be reduced because the fluid flow to and from the chamber 9 takes place via two mirror plates 20.
In the exemplary embodiment shown in Figure 6, the rotor shaft 2 is extended beyond the housing and ends with a shaft end 37. For this purpose, the shaft is provided with a seal 36 and a bearing 35. This embodiment is particularly suitable as a pump or motor.
In the exemplary embodiments discussed above, the angles between the center lines are constant and the stroke volume is varied by rotation of the mirror plates. Of course, the construction of the rotor with the fixedly mounted pistons and the drum with the bushes that are perpendicular to the center line of the drum can also be used in embodiments in which the center line of the drum can pivot relative to the center line of the rotor.
· * R i ·.
l

Claims (16)

1. Hydraulic device comprising a housing with a rotor rotatable in the housing about a first axis coupled to pistons, a drum with chambers rotatable about a second axis, each chamber being formed by a cylindrical wall and a piston with spherical sealing means which can move sealingly along the cylindrical wall, and a first mirror plate with mirror plate ports which, when the drum is rotated, are alternately connected to the different chambers via drum-gate ports arranged in the drum, the first center line below the second center line intersects an angle in the plane through the centers of the spherical sealing means and coupling means are provided for coupling the rotation of the rotor and the drum, characterized in that the pistons are fixed to the rotor and the drum has a drum plate with the drum gates and at each drum gate a drum sleeve with on the inside the cylindrical wall and the drum mmelbus perpendicular to the second axis is sealingly slidable over the drum plate.
2. Hydraulic device as claimed in claim 1, wherein the drum sleeve is provided on the outside with means which cooperate with a holder attached to the drum plate for holding the drum sleeve against the drum plate.
3. Hydraulic device as claimed in claim 1 or 2, wherein the drum sleeve has an opening in the contact surface 30 with the drum plate with a surface that is smaller than the sealing surface of the piston in the plane perpendicular to the axis of the drum plate.
4. Hydraulic device according to claim 1, 2 or 3, wherein each piston is provided with a spherical or barrel-shaped piston ring, preferably designed as a ring with an opening.
5. Hydraulic device according to claim 4, wherein the piston is provided with a piston-spring groove with a first breast and the piston ring on the inside is provided with a second breast, the second breast 10 sealing under the influence of the pressure in the chamber presses against the first chest.
6. Hydraulic device according to claim 4 or 5, wherein the piston and piston ring are dimensioned such that the outer circumference of the piston ring protrudes outside the outer circumference of the piston 15 when the inner circumference of the piston ring rests against the pressure of the chamber. piston.
7. Hydraulic device according to any one of the preceding claims, wherein the first mirror plate and / or the housing and mirror plate are provided with means for centering the drum plate.
8. Hydraulic device according to any one of the preceding claims, wherein the rotor is connected to a shaft and the shaft is rotatable in bearings and is optionally provided with spherical centering means for centering the drum plate.
9. Hydraulic device according to any one of the preceding claims, wherein the rotor on the side remote from the drum is provided with rotor ports and each rotor port is in communication with the chamber through a bore in the piston and wherein the rotor by means of the hydraulic pressure in the rotor ports against a second mirror plate placed in the housing.
10. Hydraulic device according to claim 9, wherein the second mirror plate is designed with one or more mirror plate ports.
11. Hydraulic device according to claim 9 or 10, wherein the first mirror plate and the second mirror plate open or close the connections between chamber and mirror plate ports at identical rotational positions of the rotor.
12. A hydraulic device according to any one of the preceding claims, wherein the rotor is designed on both sides with pistons which co-act with drums and mirror plates placed on both sides of the rotor.
13. Hydraulic device according to claim 13, wherein the rotor is provided with holes in which a rod-shaped part is mounted and both ends of this part are designed as pistons.
14. Hydraulic device according to claim 13, wherein the surfaces through the axis of the rotor and the first drum and through the axis of the rotor and the second drum make an angle with each other where as the number of pistons cooperating with a drum is equal to n the angle is equal to 25 (1 + 2k) * 180 ° / n with k equal to 0 or an integer.
15. A hydraulic device according to any one of the preceding claims, wherein the or each mirror plate has three or more mirror plate ports and the number of chambers per drum is a multiple of the number of mirror plate ports.
16. A hydraulic device according to any one of claims 12-15, wherein the pistons are each provided with a bore which connects the chambers in both drums and the ports of both mirror plates are mirror-image identical and the mirror plates are a mirror-image relative to the upper dead center. have different position. H -r "» "
NL1019736A 2002-01-12 2002-01-12 Hydraulic device such as a hydraulic transformer, pump or motor, has rotor ports that can rotate along housing or second face plate, that is positioned in housing and may be part of housing to form a seal NL1019736C1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
NL1019736 2002-01-12
NL1019736A NL1019736C1 (en) 2002-01-12 2002-01-12 Hydraulic device such as a hydraulic transformer, pump or motor, has rotor ports that can rotate along housing or second face plate, that is positioned in housing and may be part of housing to form a seal

Applications Claiming Priority (16)

Application Number Priority Date Filing Date Title
NL1019736A NL1019736C1 (en) 2002-01-12 2002-01-12 Hydraulic device such as a hydraulic transformer, pump or motor, has rotor ports that can rotate along housing or second face plate, that is positioned in housing and may be part of housing to form a seal
NL1020932A NL1020932C2 (en) 2002-01-12 2002-06-24 Hydraulic device.
JP2003558317A JP4413620B2 (en) 2002-01-12 2003-01-10 Hydraulic device
EP20030701924 EP1470318A1 (en) 2002-01-12 2003-01-10 Hydraulic device
JP2003558316A JP2005514552A (en) 2002-01-12 2003-01-10 Hydraulic device
AT03701926T AT374306T (en) 2002-01-12 2003-01-10 Hydraulic device
EP03701926A EP1468169B1 (en) 2002-01-12 2003-01-10 Hydraulic device
PCT/NL2003/000015 WO2003058034A1 (en) 2002-01-12 2003-01-10 Hydraulic device
AU2003203301A AU2003203301A1 (en) 2002-01-12 2003-01-10 Hydraulic device
ES03701926T ES2294263T3 (en) 2002-01-12 2003-01-10 HYDRAULIC DEVICE
DE2003616535 DE60316535T2 (en) 2002-01-12 2003-01-10 HYDRAULIC DEVICE
AU2003203303A AU2003203303A1 (en) 2002-01-12 2003-01-10 Hydraulic device
PCT/NL2003/000017 WO2003058035A1 (en) 2002-01-12 2003-01-10 Hydraulic device
US10/889,288 US20050017573A1 (en) 2002-01-12 2004-07-12 Hydraulic device
US10/889,289 US7311034B2 (en) 2002-01-12 2004-07-12 Hydraulic device
US11/355,031 US7731485B2 (en) 2002-01-12 2006-02-15 Reciprocating cylinder swash plate pump

Publications (1)

Publication Number Publication Date
NL1019736C1 true NL1019736C1 (en) 2003-07-15

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NL1019736A NL1019736C1 (en) 2002-01-12 2002-01-12 Hydraulic device such as a hydraulic transformer, pump or motor, has rotor ports that can rotate along housing or second face plate, that is positioned in housing and may be part of housing to form a seal

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Country Link
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1024002C2 (en) * 2003-07-25 2005-01-26 Innas Bv Hydraulic device.
DE102007016519A1 (en) 2007-04-05 2008-10-09 Muller, Katherina Axial piston hydraulic motor, has high pressure and low pressure connections separated from each other from side of formation of rotatable part of valve plate to another side of formation of non-rotatable part of valve plate
US10830221B2 (en) 2016-05-19 2020-11-10 Innas Bv Hydraulic device, a method of manufacturing a hydraulic device and a group of hydraulic devices
US10914172B2 (en) 2016-05-19 2021-02-09 Innas Bv Hydraulic device
US11067067B2 (en) 2016-05-19 2021-07-20 Innas Bv Hydraulic device

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3434429A (en) 1967-03-14 1969-03-25 Us Army Free piston and cylinder assembly for hydraulic pumps and motors

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3434429A (en) 1967-03-14 1969-03-25 Us Army Free piston and cylinder assembly for hydraulic pumps and motors

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1024002C2 (en) * 2003-07-25 2005-01-26 Innas Bv Hydraulic device.
EP1508694A1 (en) * 2003-07-25 2005-02-23 Innas B.V. Hydraulic Device
DE102007016519A1 (en) 2007-04-05 2008-10-09 Muller, Katherina Axial piston hydraulic motor, has high pressure and low pressure connections separated from each other from side of formation of rotatable part of valve plate to another side of formation of non-rotatable part of valve plate
US10830221B2 (en) 2016-05-19 2020-11-10 Innas Bv Hydraulic device, a method of manufacturing a hydraulic device and a group of hydraulic devices
US10914172B2 (en) 2016-05-19 2021-02-09 Innas Bv Hydraulic device
US11067067B2 (en) 2016-05-19 2021-07-20 Innas Bv Hydraulic device

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