SU1679070A1 - Power cylinder - Google Patents

Abstract

The invention relates to mechanical engineering, in particular to a volumetric hydraulic actuator, and can be used in power cylinders with fixation of the working body in any given position. The aim of the invention is to improve the working ability and increase durability while reducing material consumption. In the power cylinder, equipped with a device for fixing the rod, made in the form of a non-self-braking screw pair, the nut of which is placed on the rod, and the screw 12 together with the friction disk 16 and the pressure piston 17 - in the housing cover 4, the thrust bearing 25 is used, connecting screw 12 with cover 4, providing in all possible modes of robots loading bearing 25 only with the force Q required to drive screw 12 into rotation. This force is transmitted to the ring 30 or cover 4 through stops 26, 27, springs 28 and the bearing ring 29 25. When locking the screw 12, the latter moves axially to the distance A h, and the stops 26, 27 come in contact with the cover 4 or with the fixed element of the bearing 25. The gap Ah depending on the force Q, factor P (L with

Description

The invention relates to mechanical engineering, in particular to a volumetric hydraulic drive, and can be used in power cylinders with fixation of the working member in any given position.

The aim of the invention is to improve the performance and durability while reducing material consumption.

Fig. 1 shows a schematic diagram of a power cylinder with two-sided stem locking and a two-cavity control clutch; figure 2 - thrust bearing assembly; FIG. 3 shows the structure of the thrust bearing, the inner ring of which is spring-loaded relative to the housing; figure 4 is the same, with the inner ring rigidly fixed relative to the screw; Fig. 5 shows a power cylinder with a single-cavity control clutch; Fig. 6 is a general structural diagram of a cylinder with one-sided fixation of the rod (the variant with the placement of the thrust bearing in the pressure piston); Fig.7 - bearing assembly with fixation of the outer rings relative to the screw; on Fig the same, with the fixation of the inner ring relative to the screw; figure 9 is the same, with one-sided fixation / inner ring relative to the screw; in fig. 10 - the same, using the end wall of the push piston as a support for the rolling elements of the bearing; figure 11 is a variant of the cylinder with a two-cavity clutch and the placement of the thrust bearing B case and the pressure piston; Fig, 12 - the same, with a single-cavity clutch.

The power cylinder contains a piston 2 with a rod 3 housed in a housing 1. Along the ends of the housing 1, covers 4 and 5 are installed, studded by studs 6. The piston 2 forms cavities 7 and 8. The output elements of housing 1 are eyes 9 and 10 that prevent rotation of the housing 1 and the rod 3. In the cavity 11 of the rod 3, a screw 12 is placed, forming with a nut 13 placed on the rod 3, a non-braking threaded pair. In the nut 13, a channel 14 is provided for communicating the cavity 11 with the cavity 8.

The lower end of the screw 12 splined connection 15 (Fig.2) is associated with the disk 16

placed between the cover 4 and the pushing piston 17, loaded with cup springs -18. The pressure piston 17 forms the cavities 19 and 20. The disk 16, the pressure piston 17, the springs 18 and the cavities 19 and 20 form the guide clutch. In the housing 1 and the lids 4 and 5, channels 21-24 are made to communicate the cavities 7, 8, 19 and 20 s. pressure source of working fluid. and discharge

(not shown). The screw 12 is connected to the cover 4 of the housing 1 via the thrust bearing 25. When placing the thrust bearing

25 in the cover 4 (FIGS. 2-4), the stops 26 and 27 of the screw 12 can be connected via springs 28 through

the inner ring 29 of the bearing 25, which is fixed relative to the cover 4 by the retaining ring 30 (FIG. 3), or the stops

26 and 27 tightly fix the screw 12 relative to the outer rings 31 and 32 of the bearing

25, when springs 33 and 34 are installed between the inner ring 29 and the lid 4 (FIG. 3), or the lugs 26 and 27 rigidly couple the screw 12 to the inner ring 29, with this, the outer rings 31 and 32 are spring loaded against the lid 4 (FIG. 4). ).

The described construction can be implemented in the embodiment with a single-cage control coupling (Fig. 5), the cavity 19 of which in this case is associated with cavities 7 and 8

- through a pressure-controlled valve in these cavities 35.

When placing the thrust bearing 25 in the pressure piston 17 in the housing 1, an additional partition is installed

36 for fixing the disk 16 (FIGS. 6-9), or the pin surface facing the cavity 8 is used for this purpose (FIGS. 10-12).

If the bearing 25 is entirely accommodated in the pressure piston 17, the screw 12 is provided with an additional stop 37. In this case, the screw 12 can be firmly fixed relative to the outer rings 31 and 32 with a spring suspension of the inner ring 29 (Fig.7) or the screw 12 is fixed relative to the inner ring 29 with a spring suspension of the outer ring 31 and replacement of the friction control clutch with a cam one (Fig. 8), or one-sided fixation of the screw 12 relative to the inner

rings 29 using the spring 38 (Fig.9).

It is also possible spring suspension of the inner ring 29 relative to the pressure piston 17 with the placement of part 39 of the bearing 25 outside the pressure piston 17. In this case, a spacer 40 is installed between the pressure piston 17 and the disk 16 (FIG. 10).

Parts 41 and 42 of the bearing 25 can also be placed in the pressure piston 17 and in the lid 4. In this case, their inner rings 43 and 44 (FIG. 11) or the outer rings 45 and 46 (FIG. 12) can be spring-loaded. In all embodiments, the axial movement Ah of the screw 12 in the case of bilateral fixation of the rod 3 is defined as Ah Q / 2C and in the case of one-sided fixation of the rod 3 as A h Q / C-h, where Q is the axial force required to freely rotate the screw 12; h is the pre-compression deformation of the springs loading screw 12; C is the stiffness of these springs.

When the cylinder is in operation for any design variant (including the plunger cylinder, FIG. 10), corresponding communication of the cavities 7 and 8 with a pressure source or drain ensures the force action of the working fluid on the piston 3, which is held in a predetermined position by the threaded pair 12 and 13 if the screw 12 is kept from rotating by the disk 16. When pressure is applied in the cavity 19 or 20, the pressure piston 17 releases the disk 16 and, accordingly, the screw 12.

Due to the elastic connection of the screw 12 with the thrust bearing 25 when the screw 12 is released, the bearing 25 is loaded only with a force not exceeding that which is necessary to drive the screw 12 into rotation. With the screwed screw 12, the force transmitted through the threaded pair 12 and 13 is closed through the stops 26, 27 and 37 to the cover 4 of the housing 1.

Claims (1)

The invention includes a cylinder comprising a housing with channels for communication with a source of pressure of the working fluid and a drain, a piston rod and a stem locking device in the form of a non-braking screw pair, the nut of which is placed on the rod, and a screw locking coupling with a spring-controlled housing. a push piston, the screw being mounted coaxially to the rod and provided with a thrust bearing, characterized in that, in order to improve the working capacity and increase durability while reducing material consumption, the screw is dinner in the axial direction relative to the thrust bearing and provided with stops in the housing, limiting its axial movement within the gap A h, the value of which satisfies the inequality for ensuring the bilateral fixation of the stem and A & And - p - h for providing one-sided fixation of the stem, where Q is the axial force required for free turning of the screw moving the stem; h is the deformation of the preliminary compression of the elastic element, the spring-loaded screw; C - stiffness coefficient. f n  rgpf 91 92 / Y 02 (G91 91 (F OL06LQI 17 YU 36 ft 36 Fig.8 26- 77 -L L2 25 38 37 10 § &