HIGH SPEED ROTARY UNION

Abstract

Rotary union used for transferring a fluid between a fixed part and a rotary shaft, the rotary union having a rotary manifold coupled with the shaft in an angularly fixed manner, a stationary manifold coaxially mounted on the rotary manifold with bearings, an intermediate manifold arranged between the stationary manifold and the rotary manifold and supported by the rotary manifold with bearings, and a gear train arranged between the stationary manifold and the rotary manifold in such a way to cause the rotation of the intermediate manifold at a speed lower than the speed of the rotary manifold during operation.

Claims

1. A rotary union (100) used for transferring a fluid in a machine between a fixed part and a rotary shaft, the rotary union comprising: a rotary manifold provided with at least a first fluid passage, said rotary manifold being defined by the shaft and suitable for being coaxially mounted on the shaft in an angularly fixed position relative to the shaft; a stationary manifold provided with at least a second fluid passage and coaxially mounted on the rotary manifold by means of bearings; fluid communication passages to establish a fluidic communication between the first fluid passage and the second fluid passage; and an intermediate manifold arranged between the stationary manifold and the rotary manifold, mounted coaxially on the rotary manifold by means of bearings, and provided with at least one third fluid passage fluidically communicating with the first fluid passage and the second fluid passage through said fluid communication passages; and a gear train arranged between the stationary manifold and the rotary manifold in such a way to cause the rotation of the intermediate manifold at a speed lower than the speed of the rotary manifold during operation.

2. The rotary union according to claim 1, wherein the gear train is an epicyclic gear train.

3. The rotary union according to claim 2, wherein the gear train comprises a first crown gear coaxial to and angularly fixed to the rotary manifold, a second crown gear coaxial to and angularly fixed to the stationary manifold, and a number of pinions mounted on the intermediate manifold and simultaneously engaging with both the first and the second crown gears.

4. The rotary union according to claim 2, wherein the rotary manifold has radial through recesses, uniformly distributed around a rotation axis of the rotary manifold; each pinion is arranged in a respective said radial recess and is mounted in a rotating manner, by means of a bearing, on a pin parallel to the rotation axis of the rotary manifold and angularly and axially fixed to the rotary manifold.

5. The rotary union according to claim 1, wherein said fluid communication passages comprise, for each third fluid passage, a first annular recess formed in, and coaxial to, the intermediate manifold in a position facing an open end of the third fluid passage and facing an open end of said first fluid passage; and a second annular recess formed in, and coaxial to, the intermediate manifold in a position facing the other open end of the third fluid passage and facing an open end of the second fluid passage.

6. The rotary union according to claim 1, comprising sealing members to prevent fluid leakage between the intermediate manifold and the stationary manifold and between the rotary manifold and the intermediate manifold.

7. The rotary union according to claim 2, wherein the rotary manifold is defined by the shaft and the first crown gear is formed in a circumferential portion of the shaft or in a collar mounted coaxially on the shaft, in an angularly fixed position with respect to the shaft.

Description

[0031] According to the present invention, a rotary union according to the appended claims is disclosed.

[0032] FIG. 1 is a longitudinal sectional view of a rotary union according to the prior art.

[0033] FIG. 2 is a cross-sectional view of the rotary union according to the prior art of FIG. 1 along the line II-II.

[0034] FIG. 3 is a side view of a preferred embodiment of the rotary union according to the present invention.

[0035] FIG. 4 is a front view of the rotary union of FIG. 3.

[0036] FIG. 5 is a sectional view of FIG. 4 along the line V-V.

[0037] FIG. 6 is a sectional view of FIG. 5 along the line VI-VI.

[0038] FIG. 7 is a sectional view of FIG. 4 along the line VII-VII.

[0039] FIG. 8 is a sectional view of FIG. 7 along the line VIII-VIII.

[0040] FIG. 9 is a sectional view of FIG. 4 along the line IX-IX.

[0041] FIG. 10 is a sectional view of FIG. 9 along the line X-X.

[0042] FIG. 11 is a diagrammatic view of the rotary union according to the present invention, which shows some of the physical quantities involved in its operation, and the main mathematical relations between said quantities.

[0043] The present invention is described in detail with reference to the appended Figures in order for an expert of the art to make and use it. Numerous modifications to the embodiments described herein will be immediately evident to the experts of the field and the general precepts described herein can be applied to other embodiments and applications without leaving the protection scope of the invention, as defined by the appended claims. Therefore, the present invention must not be considered to be limited to the embodiments described and shown herein; moreover, the widest protection scope must be attributed to the present invention according to the precepts and the characteristics that are described and claimed herein.

[0044] In FIGS. 3 to 11, the reference numeral 100 is used to indicate a rotary union according to the present invention. For clarity purposes, whenever possible, parts of the rotary union 100 that are identical or correspond to parts of the rotary union 1 of the prior art described with reference to FIGS. 1 and 2 will be indicated with the same reference numerals used for the rotary union 1.

[0045] With reference to FIGS. 3, 4, 5, 7 and 8, exactly like the aforementioned example, the rotary union 100 comprises a rotary manifold 4 defined by a tube coaxial to the axis 3 and coupled to the shaft 2 by means of a coupling device 5, specifically friction jaws.

[0046] The rotary manifold 4 is provided with a given number of fluid passages, each of them comprising a radial hole 6 with an opening on the external lateral surface of the rotary manifold 4, and an axial hole 7 in fluidic communication with the radial hole 6 and provided with an opening disposed on an axial end of the rotary manifold 4 and provided with a connection element 8 for connection to a delivery pipe (not shown) of a service point.

[0047] Preferably, as shown in FIGS. 7 and 8, the passages for the fluid of the rotary manifold 4 are angularly spaced in a uniform way around the axis 3.

[0048] Moreover, exactly like in the aforementioned example, the rotary union 100 comprises a stationary manifold 9 defined by a tube coaxial to the axis 3, angularly fixed with respect to the shaft 2 and supported by the rotary manifold 4 by means of bearings 10.

[0049] The stationary manifold 9 is provided with fluid passages, each of them comprising a radial hole 13 with an opening disposed on the external lateral surface of the stationary manifold 9 and provided with a connection element 14 for connection to a delivery pipe (not shown) of a fluid feeding circuit.

[0050] The number of radial holes 13 is equal to the number of radial holes 6 and each radial hole 13 is preferably longitudinally aligned to a corresponding radial hole 6, so that both the radial holes 6 and the radial holes 13 lie on the same plane perpendicular to the axis 3.

[0051] Preferably, the radial holes 13 are spaced out along the axis 3, as shown in FIG. 3.

[0052] Unlike the aforementioned rotary union 1 of the prior art, the rotary union 100 of the present invention also comprises an intermediate manifold 18 defined by a tube coaxial to the axis 3 and supported by the rotary manifold 4 by means of bearings 19.

[0053] With specific reference to FIGS. 7 and 8, the intermediate manifold 18 is provided with fluid passages defined by through holes 20, each of them extending from an external lateral surface to an internal lateral surface of the intermediate manifold 18 and provided with an end opening that is aligned, in parallel direction to the axis 3, to a radial hole 13 of the stationary manifold 9 and with the other end opening that is aligned, in parallel direction to the axis 3, to a radial hole 6 of the rotary manifold 4.

[0054] Preferably, as shown in the example of FIG. 7, the through holes 20 are radial holes relative to the axis 3 and each of them lies on the same plane perpendicular to the axis 3 whereon the radial holes 6 and the radial holes 13 lie.

[0055] Moreover, for each through hole 20, the intermediate manifold 18 is provided with two annular recesses for fluid distribution in coaxial position to the axis 3 and comprising a first annular recess 21 obtained on the external lateral surface of the intermediate manifold 18, in a position facing the end opening of the through hole 20 and the radial hole 13 of the stationary manifold 9, and a second annular recess 22 obtained on the internal lateral surface of the intermediate manifold 18, in a position facing the end opening of the through hole 20 and the radial hole 6 of the rotary manifold 4.

[0056] In view of the above, regardless of the mutual angular position of the stationary manifold 9, of the intermediate manifold 18 and of the rotary manifold 4, each radial hole 13 of the stationary manifold 9 will always be in fluidic communication with a radial hole 6 of the rotary manifold 4, through the annular recess 21, the through hole 20 and the annular recess 22.

[0057] Each annular recess 21 is flanked by two annular recesses obtained on the external lateral surface of the intermediate manifold 18 and housing respective sealing members 23. Likewise, each annular recess 22 is flanked by two annular recesses obtained on the internal lateral surface of the intermediate manifold 18 and housing respective sealing members 24. Preferably, the annular sealing members 23 and 24 are made of elastomeric material.

[0058] Finally, the rotary union 100 comprises a gear train 25 configured in such a way to guide the rotation of the intermediate manifold 18 around the axis 3, relative to the stationary manifold 9 and the rotary manifold 4.

[0059] As shown in FIGS. 5 and 6, the gear train 25 comprises a plurality of pinions 26, each of them being housed in a respective through radial recess of the intermediate manifold 18 and revolvingly mounted by means of a bearing on a pin 27 that is rigidly fixed to the rotary manifold 4 and provided with a longitudinal axis 28 parallel to the axis 3. Therefore each pinion 26 is free to rotate, relative to the pin 27, around the axis 28, but is axially constrained on the pin 27.

[0060] In the example of FIG. 6 six pinions are provided and angularly distributed around the axis 3. Nevertheless, according to different embodiments that are not shown herein, the number of pinions 6 can be higher or lower, according to the diameter and the rotational speed of the shaft 2.

[0061] As shown in FIGS. 9 and 10, in order to simplify the assembly of the pinions 26, the intermediate manifold 18 is preferably formed of two semi-tubes that are axially constrained by means of tie rods 29 parallel to the axis 3.

[0062] Moreover, the gear train 25 comprises two crown gears in coaxial position to the axis 3, which engage with the pinions 26.

[0063] In particular, as shown in FIGS. 5 and 6, a first crown gear 30 is fixed to the stationary manifold 9 and develops completely inside the contact diameter of the sealing members 23, whereas a second crown gear 31 is fixed to the rotary manifold 4 and develops completely outside the contact diameter of the sealing members 24.

[0064] The crown gear 30 can be directly obtained on the internal surface of the stationary manifold 9 (not shown) or, as in the example, the crown gear 30 can be obtained in the internal surface of a collar 32 disposed between two semi-tubes that form the fixed manifold 9 and are axially constrained by means of threaded bars 33 (FIG. 9). The latter solution is preferred it simplifies the assembly operations of the rotary union 100.

[0065] As shown in the example, the crown gear 31 can be directly obtained on the external surface of the rotary manifold 4. Otherwise, according to another embodiment (not shown), the crown gear 31 can be obtained on the external surface of a collar that is coupled to the rotary manifold 4.

[0066] During operation, when the shaft 2 is driven into rotation around its axis 3, the coupling between the pinions 26 and the crown gears 30 and 31 determines the rotation of the pinions 26 around their axes 28 in the opposite direction relative to the shaft 2 and, simultaneously, the rotation of the pinions 26 and consequently of the intermediate manifold 18 around the axis 3 in the same direction as the shaft 2.

[0067] In view of the above, the structure of the gear train 25 is functionally similar to the one of a one-stage planetary arrangement, wherein the crown gear 31 fixed to the rotary manifold 4 is the sun gear, the crown gear 30 fixed to the stationary manifold 9 is the planet gear, the pinions 26 are the satellites that are simultaneously engaged with the sun and the planet, and finally the intermediate manifold 18 is the satellite-holder that constrains the axes 28 of the satellites to rotate around the main axis of the gear train, i.e. the axis 3.

[0068] Consequently, given the known formulas of planetary gears, the intermediate manifold 18 rotates at a lower speed than the speed of the rotary manifold 4, practically at half of its speed, as diagrammatically shown in FIG. 11.

[0069] Therefore, in the same operating conditions, the rubbing speed perceived by the sealing elements 23 and 24 is lower, practically half, than the rubbing speed perceived by the sealing elements 16 of the rotary union 1 of the prior art.

[0070] Considering that, when a rotary union is used for transferring fluids to a shaft, the maximum rotational speed of the shaft is limited by the permitted rubbing speed of the seals, the rotary union of the present invention permits to achieve a maximum speed of the shaft that is almost double than the maximum speed permitted by a rotary union of the prior art.

[0071] Finally, it must be noted that, according to an embodiment that is not shown, the rotary union 100 of the present invention can be formed of two manifolds only, i.e. the stationary manifold 9 and the intermediate manifold 18. Practically speaking, according to the latter embodiment, which is conceptualy and functionally identical to the aforementioned example shown in FIGS. 3 to 11, the rotary manifold 4 is integral to the shaft 2 and, consequently, the stationary manifold 9 and the intermediate manifold 18 are directly mounted on the shaft 2 by means of the bearings 10 and, respectively, the bearings 19. Moreover, the radial holes 6 and the axial holes 7 are directly obtained in the shaft 2 and the crown gear 31 is defined by a collar that is coupled to the shaft 2.