FI113560B - Radial piston hydraulic motor - Google Patents

Abstract

The motor has one or several cylinder in radial groups (1) placed in a stationary position, which cylinder groups contain piston position mechanisms (16a1, 16a2; 17a1, 17a2... ) moving radially back and forth. The motor has a distributor (13), with a duct (31), which communicates with the power pressure and which is opened on the side face (13a) of the distributor, in which connection the force is applied, through the fluid at the power pressure, to the side face of the distributor. The piston mechanisms comprise a piston and a press wheel (17al,17a2 ... ), and in which equipment a hydraulic fluid is passed into the cylinder spaces (Pl,P2...) of the piston mechanisms so that the press wheels of the pistons that are at a power stage are pressed with force against the wave-shaped face (12a) of the cam ring (12) and bring the cam ring into a revolving movement.

Description

113560

The invention relates to a radial piston hydraulic motor.

From the prior art, GB 1 300 046 and GB 2 261 710 are mentioned.

10 Radial piston hydraulic motor solutions are known in the art which rotate the housing body to which the housing body has a distributor attached thereto. The divider is the so-called. a distributor valve comprising bores in the longitudinal axis of the distributor sleeve, which open from the face of the distributor. The splitter has inlet channels and outlets. The inlet channels open to the front face of the divider, as well as the outlet channels. The respective manifold valve channels are alternately connected to the piston compartments, the piston compartments comprising the pistons and associated press wheels adapted to move against the cam ring associated with the housing body. As a result, some of the pines are in the process of working and some are not. Pistons that are in the process of working, ·; *; a pressurized medium is introduced through the distributor channels and respectively the pistons, which have bypassed the working step, drain the oil through the distributor through the distributor outlet channels. Piston press wheels in piston press • · * * »... cam ring on housing. The cam ring has a wavy shape, whereby the press wheels * · rotate the cam ring and the associated housing body. In order for the splitter to function as well as possible, the splitter face must be tightly slidable. -. 25 against the face of the cylinder body, which comprises passageways for the piston spaces.

* <In practice, it has been shown that pressurized oil tends to deform / twist _ '' '. divider and hence contact with said forehead surfaces tends to degrade.

In order to avoid this problem, the present application proposes as a solution that the divider comprises passages extending to its side surface which open to the side surface.

11356C

2 gasurines. This avoids the torque torque of the distributor by applying force to the side surfaces of the distributor. The divider preferably comprises bores in the first annular groove in the side surface and in the second annular groove in the side surface. The first annular groove is connected to the working pressure channels and the second annular groove is connected to the return channels. However, when reversing the direction of rotation of the motor, the functions of the above channels can be changed so that the working pressure channels become the return channels and the return channels become the working pressure channels. Preferably, the divider has seals between the annular grooves on its cylindrical surface. Thus, leakage through the ring grooves is prevented. Preferably, the seals are fitted to the ends of the annular projections 10 of the divider side surface into separate seal cavities located within the rotatable housing body. The seals are formed of ring seals.

The radial piston hydraulic motor of the invention is characterized in what is stated in the claims.

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The invention will now be described with reference to some preferred embodiments of the invention shown in the figures of the accompanying drawings, but which are not intended to be limited thereto.

Fig. 1A is a cross-sectional view of a radial piston hydraulic motor according to the invention.

»·!:! Fig. 1B is a schematic representation of the coupling and cooperation between the cam ring and the pistons.

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Fig. 2 is an enlarged scale showing the target area X of the invention in connection with a divider in Fig. 1A.

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Figure 3A shows a divider at the end.

Figure 3B shows section I -1 of Figure 3A.

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Figure 3C is a sectional view II-II in Figure 3A. The splitter comprises separate channels for the side surface of the splitter.

Fig. 4A illustrates an embodiment of the invention in which pressure is applied to only one pressure medium space Vi in connection with a sidewall of a distributor valve.

Figure 4B shows the area A10 of Figure 4A on an enlarged scale.

10A is a cross-sectional view of a radial piston hydraulic motor 10. Figure 2 illustrates the target area X of the invention from Figure 1A on an enlarged scale. The radial piston hydraulic motor 10 comprises a rotatable casing body 11. The casing body 11 is associated with a cam ring 12. In the embodiment of the figure, the casing body 11 with a stationary distributor 13 is rotated with a distributor valve comprising a plurality of axial bores nonA; and to the output channel e2. The distributor 13 rotates with the housing body 11 and the pressurized channels eiA and the return oil channels e2B are alternately in contact with the flow paths 18ai, 18a2 of the cylinders • · · * ··· piston 16ai, 16a2 ... of pistons 16ai, 16a2 ...

• · 20 with duct ends. Thus, part of the pistons 16ai, 16a2 ... of the cylinders is in the operating * ·· 'stage, whereby the pressurized medium is led through the divider 13 to the cylinder spaces «IIf» pi, p2 ... and part of the pistons 16ai, 16a2 ... wherein oil is introduced from the cylindrical spaces pi, p2 ... of said pistons 16ai, 16a2 ... into a discharge channel e2 through a divider 13. A non-rotatable cylinder in the non-rotatable central shaft 14; V, 25 frame body 15 comprises a cylinder group 1, the cylinder body 15 having a plurality of cylinders, · * ·, blade spaces pi, p2 --- and in these pistons 16ai, 16a2 .... piston 16ai, 16a2 ... are adapted to move. in piston space pi, p2 ... due to the oil pressure introduced therein. As depicted in the figure, each piston 16 comprises a press wheel 17ai, 17a2 ... Presses - having a circular cross-section set freely on its upper surface; By pushing the piston 16ai, 16a2 ... against the corrugated surface 12a of the cam ring 12, '* *' causes the cam ring 12 and associated housing body 11 and the valve 13 associated with the housing body 11, 113560 4 to rotate. Through the passages 31 and 32, the pressurized medium is led to the grooves V1 and V2 on the surface 13a of the divider 13. Thereby, an annular radial force effect is provided in the grooves V1, V2, and the divider 13 is kept straight and sealed at its front surface f so that no lateral oil-5 leakage occurs through the front surface f.

The housing body 11 is rotated on a bearing G1 and G2 relative to a central shaft 14.

10 In the figure, a spring is shown with the letter J. By means of a spring, the divider valve 13 is pressed against its front face against the cylinder face of the cylinder body. The purpose of the spring J is to provide an initial force during start-up to keep the dividing surface between the parts 13 and 15 tight. The shape of the pressure channel spaces U1, U2 is so selected that when pressure has developed in the ducts, the pressure is applied to the distributor valve 13 and compressed by force 15 axially against the face of the cylinder body 15.

Figure 1B is a schematic view of the operation of the cam ring 12 and the pistons 16ai, 16a2. Some of the pistons 16ai, 16a2 are at working pressure and some of the pistons • · · · 'are connected via jet 13 to the lower return pressure side.

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As shown in Figure 2, the divider 13 comprises channels 31 and 32. The channels 31 are in communication with the annular space U1 between the central shaft 14 and the divider 13 and the lateral> I, '! a surface groove V1, said annular space Ui being further led to a support channel no.

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The annular groove Vi of the distributor side surface is sealed sideways by a seal N 1, C 1 and N 2 25 C 2. Similarly, the annular space Ui between the central shaft 14 and the divider 13 is sealed, **, with seals C4 and C5 in the shaft. A pressurized medium is introduced into the annular space Ui, i. From the annular space Ui there are channels for non-A divider front face and further to the piston. The ends of channels dA are denoted in Fig. 3A by reference numerals A. The ring seals C1, C2 and C3 are located in the annular '30 cavities 0i, 02 and O3 of the housing body 11. The actual '· *' sealing rings of the seal extending into the cavities 0i, 02 and O3 are Ni, N2 and N3. It is a two-piece gasket consisting of a rubber

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the O-ring C1, C2 and C3 and its support ring, i.e. the sealing ring Ni, N2 and N3, which is preferably a Teflon bronze alloy.

The outlet channel e2 opens into a second annular space 5 U2 between the central shaft and the distributor, from which the channel 32 is provided to the annular groove V2 on the side surface of the distributor. The annular groove V2 is sealed sideways with seals N2, C2 and N3, C3 passing around the divider. The channels e2B which open out of the ring space U2 are also directed to the front face f of the distributor 13 and through these channels e2B are discharged from the inoperative pistons 16ai, 16a2 first to the ring space U2 and further to the return channel e2. Changing the rotation direction of the 10 motors changes the channel assignments. Shaft 14 has grooves 04.05 and Οό with seals C4, Cs and Ce. Seals C4 and C5 are on both sides of annular space U1 and on both sides of annular space U2 are seals C5 and C0 so that oil leakage does not occur sideways at the interface 13.

Figure 3A is a front view of a divider. Figure 3B shows section I -1 of Figure 3A. Figure 3C is a sectional view Π - Π of Figure 3A.

In Fig. 3 A, reference marks A show the channel ends of the working pressure channels •: not A of the face f of the divider 13. The channels AA open at one end to the annular space Ui between the central axis 14 and 20 of the divider 13. The end openings of the return channels e2A are denoted by the reference coefficients '·' B. Said channels e2B open to the annular space U2 between the central axis 14 and the divider 13 and further to the return channel e2.

Figure 3B is a sectional view I-I of Figure 3A. As shown in the figure, the divider: ·, · (25 of the annular spaces Ui is a channel not a for the divider front surface f. Similarly, the second annular · space U2 formed between the divider 13 and the central axis 14 is return;

Figure 3C is a sectional view Π - Π of Figure 3A. As shown in Figure 3C, the hinges 30 extend from opposite sides of the divider 13 to the side surface 13a of the divider 13 into the first annular groove V1 of the side surface and the annular space U2, respectively.

11356C

6 channels extending from the divider sides 32 to the sidewall 13a of the divider 13 into the second annular groove V2 of the sidewall 13a.

In the embodiment shown in the previous figures, the oil under working pressure is introduced into a groove V1, V2 on the side of the distributor, which groove is limited to both the structure of the distributor and the counter surface formed a split valve 13. Such coupling is made possible by the shock 50 shown in the previous Figs. The surface Ti of the housing body 11 itself and the division between the surface 13a of the valve 13 is a sliding fit. The aforementioned rigidity enables the counter force to be applied to the distributor by applying pressure to the grooves V1, V2. The pin 50 transmits the rotation torque to the distribution valve 13, whereby the distribution valve 13 rotates as the housing body 11 is rotated. However, the socket allows axial movement of the distributor valve 13, whereby by the spring force of the spring J and the hydraulic pressure, the distributor valve 13 is pressurized to the cylinder body to provide a sealed distributor surface.

4A and 4B are also possible within the scope of the invention. a form in which the groove V2 is formed as in the previous embodiments, dividing the vent • · · * · '·' 20 to the side surface 13a of the brick 13 but opposed by the inner surface 60 'of the separate ring 60.

The ring 60 is disposed freely on the surface 13a of the distributor valve 13, between the shoulder 130 of the valve 13 and the locking ring 70. The sealing structure is similar to previous • · !!! In the embodiments, the ring 60 comprises seals Ni, Ci and N2, C2 pressed against the diverting valve 13 in its grooves to seal sideways the space V2, the space V2 25 being in this embodiment now formed on the inner ring 60 *.

In the embodiment of Figures 4A and 4B, the casing body 11 is connected to the locking ring 70 of the shock 80, the locking ring 70 being pins 90 connected to the diverting valve 13. The blind 30 'is 80 slidably connected to the securing ring 70; axial movement of the locking ring 70.

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The pins 80 and 90 connect the parts 13, 70 and the housing body 11 so that the rotation torque is transferred to the divider valve 13 from the housing body 11. Thus, the diverting valve 13 rotates with and with the housing body 11. The ring 60 is disposed freely with a sliding fit over the side surface 13a of the divider 13. State V2 communicates via channel 5 32 to a pressurized oil channel.

In order for the distributor valve 13 to rotate reliably with respect to the central axis and to avoid any rotational resistance, the locking ring 70 must be attached to the housing body 11 so that it is also allowed a certain radial movement relative to the central axis 14. This radial movement is made possible by a groove ai in the locking ring 70 in which a pin 90 is inserted in the groove ai. The pin 90 is further connected to the split valve 13 by its pin hole a2. Thus, the locking ring 70 is axially held in a fixed position relative to the valve 13, but is allowed a certain radial movement. Thus, the locking ring 70 may be freely positioned on a suitable radial weapon 15. The locking ring 70 and the cotter pin 80 between the housing body 11 again enable axial movement of the valve 13, but the locking ring 70 and the housing body 11 are themselves held radially relative to one another. The locking ring 70, however, is provided by means of a pin 80 which passes through the holes bi to move the rotation drive and. · Torque j for valve 13 from housing housing 11.

In the embodiment of the invention shown in Figures 4A and 4B, a pressurized medium II * »* 1 · ,, is introduced into only one annular space V2 which is fitted to the right end of the divider !! *, as shown in practice. that this part of the distributor valve 13 is less rigid, whereby the greatest benefit of the arrangement according to the invention is obtained by placing the distributor * ·, · · ·, valve 13 at this point under pressure V2.

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One groove V2 which in the embodiment is made on the inner surface 60 'of the ring 60 and which groove communicates with the channel 32 and further with the other channel system as shown in the figures. The embodiment of the pattern may also be such that it corresponds fully; There are two prior art embodiments and thus grooves; grooves V1 and V2 '' 'on the inner surface 60' of the ring 60. The pressure medium for importing pressure media is similar to

e 11356C

O

in the previous embodiment. However, Figures 4A and 4B show a simplified embodiment in which the pressure application is arranged at a point in the structure where force compensation is specifically required.

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Claims (9)

11356C 9 A radial piston hydraulic motor (10) comprising one or more cylindrical assemblies (1) in a fixed position comprising radially reciprocating piston mechanisms (16ai, 16a2; 17ai, 17a2 ...) which piston mechanisms (16ai, 16a2; 17ai, 17a2) . ..) the press wheels (17ai, 17a2 ...) force the cam ring (12) against the corrugated surface (12a) of the cam to cause the cam ring (12) to rotate and that the cam ring (12) engages the housing body (11) and the housing body (11) a manifold valve (13) for directing the pressurized oil flow to the cylinder spaces (pi, P2 ··) of the pistons (16ai, 16a2 ...) in the process, and at the same time the manifold valve (13) for returning the outgoing pistons (16ai, 16a2 ... .) cylinder spaces (pi, p2) 15, and in which apparatus the direction of rotation of the engine can be changed by changing the direction of the oil flow through the distributor valve (13) and that the oil is distributed to the distributor valve (13) with one or more cylindrical bodies (15) 14) through ducts (no, e2) '·', characterized in that the distributor (13) has a conduit (31) connected to the working pressure, which opens to the side surface (13a) of the distributor (13), whereby (13) to the side surface (13a), that the pressurized medium t * 'is introduced into the space (V2) between the side surface (13a) of the divider (13) and the ring (60) disposed around the separate divider (13), that the groove * ··· * (V2) is formed on the inner surface (60 ') of the ring (60) and that the groove (V2) is sealed on both sides by seals (N2, C2, N3, C3). I * » Radial piston hydraulic motor according to Claim 1, characterized in that the means for supplying the pressurized medium to the side surface of the distributor (13) are formed by a channel (31) formed in the distributor (13) which is connected to: · · 30 in a groove (Vi) on the side surface (13a) of the divider (13), which preferably passes around the ·. **: divider (13). 10 113560 Radial piston hydraulic motor according to the preceding claim, characterized in that the channel (31) opens at one end into a groove (Vi) between the side surface (13a) of the divider (13) and the housing body (11) and at the other end the central shaft (14) and divider. (13) in the annular space (Ui) formed therebetween, having channels (eu) on the divider's front face (f), whereby the divider (13) rotates to distribute the pressurized medium to the pistons (16ai, 16a2 ...) in operation Radial piston hydraulic motor according to any one of the preceding claims, characterized in that the groove (Vj) is formed on the side surface of the divider and that the groove is laterally sealed by O-seals (C1, C2) and sealing rings (Ni and N2) to the sealing cavities (O, C> 2) of the housing body (11). Radial piston hydraulic motor according to one of the preceding claims, characterized in that there is a second channel (32) which is connected to the return oil flow from the piston (16ai, 16a2 ...) · Radial piston hydraulic motor according to the preceding claim, characterized in that the channel (32) associated with the return oil flow is opened by the distributor *. *. · 20 (13) in the annular groove (V2) on the sidewall (13a), and at one end in the annular space (U2) between the central shaft (14) and the divider (13), the annular space (U2) having channels (e2B) outlet channel (e2) and that the annular groove · '*; * '(V2) is sealed sideways with O-seals (C2 and C3) and sealing rings (N2 and N3), * * · placed in sealing housings (02.03) of the housing body (11). . 25 Radial piston hydraulic motor according to one of the preceding claims, characterized in that, when changing the direction of rotation of the hydraulic motor, a pressurized medium is introduced into the channel (e2) and further into the annular space (U2) and above; * 'to the second annular groove (V2) on the side surface (13a) of the divider (13):' ·· 30 and the divider face (f) and the return flow from the piston (16ai, 16a2 ...) respectively through the channels (nonA) axial annular space (Ui) and thereafter 11356C therethrough to a return channel (no), whereby the functions of the channel systems have changed with respect to the working pressure and the return pressure when compared to the opposite rotational-directional drive. Radial piston hydraulic motor according to one of the preceding claims, characterized in that the radial piston hydraulic motor comprises seals (C4, Cs and C0) in the annular spaces (Uija U2) between the distributor (13) and the shaft (14), the seals (C4 and C5) and both sides of the annular space (U2) are seals (C5 and Ce), thereby preventing leakage through the central boundary between the central shaft (14) and the divider (13). Radial piston hydraulic motor according to the preceding claim, characterized in that the ring (60) is disposed between the shoulder (130) of the sidewall of the valve (13) and the locking ring (70) connected to the valve (13) and that the locking ring 15 (70) the cotter pins (80) to the housing body (11) of the radial piston hydraulic motor (10) but in the rotational direction without clearance, whereby the rotary movement of the housing body (11) to the locking ring (70) is transmitted via the cotter pins (80) to the distributor valve 13) is rotated through the housing body (11) therethrough, and in which configuration the axial movement of the valve (13) is also provided when the spring (J) '··' is pressed against the end face of the cylinder body (15). • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • • *