The present invention is an optimised radial cylinder hydraulic motor, that is a hydraulic device of the type which is well-known in the field with cylinders arranged in a star shape which all act on the same eccentricity or crankshaft of the motor axle. The hydraulic motor which is the described here presents optimized characteristics in comparison with others in this technological field and reaches a significantly improved technological and economic performance.
In this technological field, there are various types of radial cylinder hydraulic motors with cylinders arranged in a star shape. These are in particular hydraulic motors where a single cylinder oscillates around an axis or point, close to the outer diameter of the skirt of the hydraulic motor, in order to carry out the oscillation required by the crankshaft with which it is in contact in order to generate rotary motion. This oscillation is necessary insomuch as the cylinder piston complex carries out the functions of “piston rod”, or a crank for rotary thrust, which oscillates to follow the evolution of the pivot of the crank or eccentricity of the drive motor.
In this technological field, there are two main ways of making these hydraulic motors, as stated above.
The first way is to support the cylinder during oscillation using lateral trunnions, positioned on an axis of oscillation parallel to the axis of the crankshaft and close to the outer skirt of the motor; they allow the passage of hydraulic oil through one of them and therefore the part of the cylinder that creates most obstruction, the jacket and its outer skirt, can be positioned far from the crank. In this way, the motor has greater engine displacement without changing the size of the engine. The respective piston is positioned so that it moves on the external surface of the crank or eccentric shaft, or it can work indirectly with interposed concentric organs, which rotate with it.
The second way of oscillation of the cylinder-piston complex in the said hydraulic motor is to support the cylinder-piston complex on a spherical surface, for every cylinder. This surface is positioned in proximity to the outer diameter of the skirt of the hydraulic motor. In this second way, the sliding part on the crank or eccentricity of the crankshaft is positioned, optionally, on an annular spherical surface, in an axial direction in relation to the shaft. Therefore, it presents the sliding surface with a preferential plane of lying of the cylinder-piston complex, which obviously corresponds to the plane of lying of the spherical surface present at the most outer diameter in order to support the thrust generated by the cylinder or piston. In fact, there are some well-known versions of the motor in the field in which the piston is positioned close to the outer diameter and the jacket and its skirt are positioned in proximity to the inner diameter, that is close to the diameter of oscillation on the eccentricity or crankshaft. However, this version creates clear disadvantages in terms of their dimensions.
It is well-known that the first way of oscillation of the cylinder-piston complex presents the critical point on the surfaces of oscillation of the trunnions. This is because the thrusts generated by the hydraulic liquid in the cylinder are transmitted to the skirt by way of the said trunnions and at the same time at least one trunnion must be hollow to allow the passage of hydraulic liquid. However, the construction of the coupling of the trunnions with the skirt for oscillation is very complex and costly and the trunnions often turn out to be weak during performance and in supporting the thrusts generated. Furthermore, in hydraulic motors of this type, which have variable engine displacement at minimum values, which are not zero, the amplitude of oscillation in the trunnions in significantly reduced, while the thrusts on the trunnions do not reduce. This limits the value of the thrusts at lower engine displacements.
In the second way of oscillation of the cylinder-piston complex, the passage of the hydraulic liquid from and towards the cylinder, happens from the exterior of the spherical surface of oscillation. It is carried out by increasing as much as necessary the diameter of the skirt or its dimension. This does not allow the dimensions of the hydraulic motor to be contained and limited. Therefore, the dimensions of the hydraulic motor become more evident and detrimental, especially when the plan is to have large dimensions in order to be able to have greater engine displacements and greater quantities of hydraulic liquid that cross the motor. In this second way, the speed of rotation and therefore the oscillation of the cylinder-piston complex is also limited by the whiplash that is generated at the bottom dead centre, between the piston and the cylinder, when the motor turns at increased speeds of rotation; the greater mass of the jacket or skirt of the cylinder undergoes a sudden inversion of acceleration at the passage of the said bottom dead centre, which then stress the sliding coupling between the piston and the jacket, in a limited point, with forces of inertia lying on the plane of oscillation of the cylinder-piston complex. This creates the tendency of the piston to stick during sliding in the jacket.
Finally, in this technological field there are also hydraulic motors with several cylinder-piston stars side by side on the same crankshaft. These types of motors are not easy if a single distributor is used, due to the arrangement of the connecting channels. The dimension of the said channels is limited if a reduced radial dimension is desired.
In fact, a notable quality of radial cylinder hydraulic motors is that of having a large engine displacement in its dimensions, i.e. it produces greater torque without the hydraulic liquid working at higher pressures and at the same time can function at higher speeds of rotation achieving a maximum flexibility which was not possible before. This allows for a better performance than other types of hydraulic motor as is well known. Further limits of the existing technology are the need to increase the openings and channels for supply and/or discharge of hydraulic liquid which is not possible without increasing the dimensions; the need to reduce the length of the said channels in order to reduce the clearance volume which generates sound due to the constant variation of pressure of the column of liquid contained in them; the need to reduce the outer dimensions of the motor equal to the engine displacement and mechanical performance, which would make it more desirable for users in that they could insert it into spaces and dimensions that are much smaller.
Therefore, the existing technology can be significantly improved with regards to realizing an optimized radial hydraulic motor, with oscillating cylinders, which overcomes the disadvantages above making the reduction of the dimensions and of the masses concerned more practical, easy and functional.
The technical problem that is the basis of the present invention is that of having an optimized radial hydraulic motor with oscillating cylinders, in which the cylinder-piston group is housed in the motor body in the simplest and most economical way possible i.e. the work needed to house the group must be very economical. In addition to this improved method of housing, the radial cylinder hydraulic motor with oscillating cylinders must also be able to offer the technological advantages for which it is known.
A further and not final aim of the present invention is that of achieving an optimized radial hydraulic motor with oscillating cylinders in which the reduction of the dimensions with the same engine displacement of the motor, or vice versa with the same dimensions with an increased engine displacement, also makes it possible to reduce the clearance volumes present in the passages for supplying and discharging from the cylinders.
Finally, a further part of the technical problem explained above regards achieving an optimized radial hydraulic motor with oscillating cylinders in which the section of the passages for supplying and discharging from the cylinders can be increased in order to make the passage of hydraulic liquid from the installation to the cylinders and vice versa easier and more effective. The objective is to have greater flow rates than those that have been achieved in the existing technology.
This problem is solved, according to the present invention, by a radial cylinder hydraulic motor, comprising: oscillating cylinders in proximity to the outer skirt to the crown or star of cylinder-piston groups; the pistons of the said groups slide on a crankshaft or eccentric shaft, or on interposed organs concentric to it, and create alternate motion in the oscillating cylinders; it is characterized in that it presents the respective surface of oscillation for each cylinder of the said groups, in proximity to the outer skirt, constituted by a portion of cylindrical surface with axial direction parallel to the axis of rotation of the crankshaft or eccentric shaft and positioned in the part of skirt including the diametral plane of lying of the said crown or star of radial cylinders; furthermore the contact between the cylindrical support surface of a bottom plate of each cylinder on the portion of cylindrical surface of oscillation happens because of the thrust created by the radial thrust devices which act on at least one side of the said cylinder.
In a further and advantageous form of construction: the portion of cylindrical surface of oscillation of the cylinder is made though mechanical production, in proximity to the inner diameter, directly in the same skirt.
Furthermore, in a specific version, the portion of cylindrical surface of oscillation of the cylinder is made on an inserted mechanical organ, in proximity to the inner diameter of the same skirt.
In a further form of construction: the portion of cylindrical surface of oscillation of the cylinder, made on an inserted mechanical organ, is connected to the skirt either in parts or lateral caps of the hydraulic motor in a detachable way.
Furthermore, in another form of construction, which is very beneficial, the axis of curvature of the portion of cylindrical surface of oscillation of each cylinder is in a position external to the outer diameter of the skirt.
In a further form of construction: the axis of curvature of the portion of cylindrical surface of oscillation of each cylinder is in an internal position, but next to the outer diameter of the skirt.
Furthermore, in a specific version, the thrust devices are constituted by a ring equipped with flaps which are curved, in relation to the axis of curvature of the portion of cylindrical surface of oscillation of each cylinder, according to a respective radius of curvature on the said thrust devices.
In a further form of construction, the thrust devices on the cylinder, for contact on the portion of cylindrical surface of oscillation, are positioned in a curved indent according to a respective radius of curvature in relation to the axis of curvature of the said portion of cylindrical surface of oscillation of the cylinder-piston group.
Furthermore, in a more beneficial form of construction, the thrust devices on the cylinder, for contact on the portion of cylindrical surface of oscillation, are constituted by a ring which presses into a curved step according to a respective radius of curvature in relation to the axis of curvature of the said portion of cylindrical surface of oscillation of the cylinder-piston group.
Furthermore, in a preferred form of construction, the passage of hydraulic liquid to and from the oscillating radial cylinder in order to achieve the supply and discharge from the cylinder, happens though at least one lateral outer surface on the side of the oscillating cylinder from and towards a supply channel on the body or lateral cover of the hydraulic motor; a seal ring equipped with at least one contact surface, which is resistant to abrasion on the surface of the sliding wall, is interposed between the lateral surfaces in contact for the passage of the liquid under pressure.
Furthermore, in a specific variation of construction, in an external lateral surface parallel to and opposite the lateral surface external to the oscillating cylinder crossed by the liquid supply, there is a compensation opening for the thrust, supplied by the liquid under pressure in the oscillating cylinder. Around this is a seal ring equipped with at least one contact surface that is resistant to abrasion on the surface of the wall used for sliding, in addition it is placed between the lateral surfaces in contact for the passage of liquid under pressure through the compensation opening.
Furthermore, in a preferred form of construction, the surface of action of the pressure in the said compensation opening for the thrust or in one of its niches made in the lateral sliding surface is slightly greater than the surface for the passage of liquid under pressure in the supply hole present in the radial oscillating cylinder.
Finally, the seal ring in sliding contact between a lateral surface external to the oscillating radial cylinder and a lateral sliding surface of the cylinder is constituted by an arrangement of parts in which: a metal ring functions as the surface that is resistant to abrasion, present on the side of the retainer in contact with the sliding surface of the seal ring; a ring made from soft, flexible material is interposed between the metal ring and the seat or niche in which the seal ring is housed; an anti-extrusion ring is placed between the metallic ring and the soft, flexible ring in order to avoid its discharge due to the pressure of the liquid during operation.
The characteristics and the advantages of the present invention, an optimized radial hydraulic motor with oscillating cylinders, will be shown in the description which follows of an example provided as a guide which is not restrictive, with reference to the seven drawings attached.
In
Each cylinder 4 presents, as clearly visible in
In
As can be clearly seen in
In
As can be clearly seen in
In
Each cylinder 106 presents on two outer lateral surfaces 116 and 117, parallel to each other, a supply hole 118, on the side of the parallel surface 116, and a compensating hole for the thrusts 119, on the side of the parallel surface 117. They respectively face a supply channel 120 in correspondence with the supply hole 118 in the cylinder 106 and on a compensating niche 121 in correspondence with the compensating hole 119 for the thrusts in the cylinder. The contact between the lateral, outer, parallel surface 116 of the cylinder 106 and the surface of a distribution cover 85, in the area around the supply channel 120 occurs by means of a seal ring 122 with a metal contact surface; in the same way, the contact between the lateral, outer surface 117 and the cover 111 of the body 110 of the hydraulic motor 105, on the opposite side to that of the distribution, in the area around the compensating niche 121, happens by means of an identical seal ring 122 with a metal contact surface; the sliding contact happens on sliding surfaces 123 on the covers 85 and 111 parallel to each other and perpendicular to the axis of the drive shaft 101. A hole 124 in the bottom plate 115 of the cylinder 106 supplies the cylindrical surface 112 of oscillation with hydraulic liquid for lubrification when it is in contact with the concave cylindrical surface 114 of the bottom plate of the cylinder.
In correspondence with the outer lateral surfaces 116 and 117 at the lower edges of these, there are curved steps 146 on both surfaces, which have a curvature corresponding to the cylindrical surface of oscillation 112 of the cylinder 106. These act in corresponding curved grooves 147 made on a ring 148 for each side of the cylinder-piston group. Their purpose is to maintain the contact between the cylindrical surfaces of oscillation 112, on the skirt 155, and the concave cylindrical surface 114 in the bottom plate of the oscillating cylinder 106, during start-up and when there is a lack of pressure in the liquid in the cylinder.
During completion of this form of construction, there is a supply channel 125 in correspondence with the supply channel in the cover 85. It is connected with a rotating disc distributor 126 of the type that is well-known in the field, positioned in synchronous rotation with the drive shaft 101 by means of a frontal clutch 127 which is also well-known.
Finally in the Figures which show the oscillating cylinder 106, the radius RO of curvature of the cylindrical surface of oscillation 112 and of the cylindrical concave surface 114 on the bottom plate 115 of the cylinder can be seen as well as the parts already described; furthermore, the radius of curvature RS of the curved steps 146 is clearly concentric to the radius RO of curvature of the cylindrical surface of oscillation. Therefore, in the concave cylindrical surface 114 for coupling there is a decline in order to create hydrostatic balance in the surface around the hole 124 in oscillating contact on the cylindrical surface of oscillation 112.
The seal rings 122 are composed of a ring of soft, flexible material, known as an “O ring”, which is housed in a seat for each of the two lateral holes of the cylinder 106, an anti-extrusion ring and a metallic contact ring which can slide against the surfaces 116 and 117 on the side of the cylinder 106 of the hydraulic motor 105 represented.
In the first form of construction in
In the forms of construction in
As stated above, in
In the three forms of construction described above, the sliding of the cylinder on the outer cylindrical support surface 18, of the sleeve 6, or 27 inserted to the inner diameter of the skirt 25 or 57 and made in pieces at the inner diameter of the skirt 55, is permitted without the need for positioning on a predetermined radial plane. However, during functioning, each single group undergoes small axial displacements at the shaft without affecting the functioning of the motor and the crown of the cylinder-piston groups.
In the second from of construction, in
The dimensioning of the holes 7, 30 or 59 can be carried out at the desired value in order to exploit in the best way the dimensions of the channels for fluid connection and the dimensions of the space used for the cylinder. Furthermore, a greater the radius of oscillation, obtained with positioning more towards the exterior of the axis of oscillation, 28 or 58, in relation to the skirt, allows for a greater radius of the handle and therefore increased torque on equal terms with engine displacement and the hydraulic parameters used.
Furthermore, in the fourth form of construction, the combination of the cylindrical surface of oscillation of the cylinder piston group with the feed on the side of the cylinder, allows for a significant reduction of the radial dimensions. Therefore, on the basis of this radial dimensioning it is possible to have a radial oscillating cylinder hydraulic motor with an engine displacement that is significantly greater than what known technology offers.
The advantages obtained from an optimized radial hydraulic motor, according to the invention, can be summarized as follows. The optimized radial hydraulic motor generally better exploits the space allowed i.e. with a greater engine displacement. The user of an optimized radial hydraulic motor can even house it in narrow spaces in the application required. The performance of the motor equals that of other heavier and bulkier motors. Finally, the formation n of the optimized radial hydraulic motor, in which the surfaces of oscillation of the cylinder, in the cylinder-piston group according to the invention, occurs on a cylindrical rather than spherical surface. The axial position of the group is not necessary, but can present slight axial sliding on the cylindrical support surface close to the skirt and on the usual cylindrical surface on the button of the crank or eccentric shaft on the drive motor.
Furthermore, the arrangement of the supply channels for hydraulic liquid to the respective cylinder is more homogeneous and functional. There can therefore be increases in the section for the passage of the said channels or, if desired, the channels can pass side by side through different cylinders when there are two crowns or stars of cylinders side by side. This allows for the use of a single distributor in order to contain the over-all dimensions of the motor.
The channels 7, 30, 59, 120 from the distributor to the individual cylinders have a reduced length. The same axial channels can also be extended to supply the radial cylinders, or individual axial channels in phase for each cylinder of a star and the adjacent cylinder of a star side by side with the first can be used; the latter solution where the stars of radial cylinders are not in phase creates greater uniformity of the torque on the way out of the hydraulic motor.
The thrust devices on the cylinder 40, 70 or 80 in the second or third form of construction described, maintain the contact of the cylinder 24 or 54 even when there is no or negative pressure in the motor; in the first form of construction the cylindrical contact surface 17 maintains contact with the bottom plate to create the effect of undercut. It is in opposition to the cylindrical support surface 16 of the bottom plate 10 of cylinder 4 on the sleeve 6, compared to the outer diameter 18 of the sleeve.
In the fourth form of construction, the thrust devices work in the same way as in the other forms. The presence of two rings 148, one on each side of the cylinder 106 insures a reduction of the dimensions as the rings are thinner and a possible cylinder application with a larger cylinder bore which increases the engine displacement without increasing the radial dimensions.
The thrust rings 44, 148, advantageously, are made of metal material for springs.
It is clear that a technician in the field, whose objective is to satisfy specific demands in certain situations, will be able to make numerous adjustments to an optimized radial hydraulic motor. All of these adjustments, however, will come into the area that protects the present invention which is defined in the following claims. Although it would be less beneficial the first form of construction of the radial hydraulic motor could be made with thrust devices 40, as illustrated for the other two forms of construction. The said thrust devices differ from the ring 44 or 84 with folded flaps 43 or 83 illustrated, but will operate in the same way, i.e. they remain positioned in respective curved indents 41 or 71 and push the cylinder against the cylindrical support and oscillation surface to react in relation to the other parts of the thrust device. Furthermore, the form of the thrust ring 44 or 84, and their corresponding arched flaps 43 or 83, can differ from what is represented, but will function in the same way: it pushes parts of the cylinder 24 or 54 against the portion of cylindrical surface of oscillation causing reaction on the other cylinders and relating parts on which similar flaps, as represented lean. Finally, the thrust devices composed of curved strikers 147 against curved steps 146 on each cylinder 106 can also be applied to the preceding forms of construction of a radial hydraulic motor as they result in decreased dimensions and more secure contact the cylindrical surface of oscillation and the corresponding cylindrical support surface on the bottom plate of the cylinder.
Number | Date | Country | Kind |
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MO2010A0080 | Mar 2010 | IT | national |
MO2010A0321 | Nov 2010 | IT | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
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PCT/IT2011/000087 | 3/23/2011 | WO | 00 | 11/26/2012 |
Publishing Document | Publishing Date | Country | Kind |
---|---|---|---|
WO2011/117904 | 9/29/2011 | WO | A |
Number | Name | Date | Kind |
---|---|---|---|
2621607 | Trapp | Dec 1952 | A |
2642748 | Widmer | Jun 1953 | A |
3656407 | Hause | Apr 1972 | A |
3695146 | Orshansky, Jr. | Oct 1972 | A |
3945766 | Gelon | Mar 1976 | A |
4018139 | Landreau | Apr 1977 | A |
4223595 | Ortelli | Sep 1980 | A |
4609128 | Amellal | Sep 1986 | A |
4683806 | Ryzner | Aug 1987 | A |
5967018 | Breveglieri | Oct 1999 | A |
7258057 | Nagler et al. | Aug 2007 | B2 |
8206130 | Pecorari et al. | Jun 2012 | B2 |
20090301291 | Pecorari et al. | Dec 2009 | A1 |
Number | Date | Country |
---|---|---|
359 543 | Sep 1922 | DE |
0 172 076 | Feb 1986 | EP |
2 822 199 | Sep 2002 | FR |
364 549 | Aug 2006 | FR |
1 520 912 | Aug 1978 | GB |
WO 03078797 | Sep 2003 | WO |
WO 2007122644 | Nov 2007 | WO |
Entry |
---|
PCT International Search Report dated Aug. 17, 2011. |
International Preliminary Report on Patentability dated Nov. 16, 2011. |
Number | Date | Country | |
---|---|---|---|
20130064691 A1 | Mar 2013 | US |